Title of Invention	HYDRAULIC DISC BRAKE DEVICE
Abstract	ABSTRACT OF THE DISCLOSURE A hydraulic disc brake device comprises: a base assembly (G) moimted on a vehicle, a sliding assembly (H) slideably moimted on the base assembly (G), a return spring (95) disposed between the base assembly (G) and the sliding assembly (H), a brake lining assembly (70), a control valve assembly (50) disposed on the oil pressure system, hydraulic disc brake system that has an antilock effect. The hydraulic disc brake is low cost and has an antilock function.

Title of Invention

HYDRAULIC DISC BRAKE DEVICE

Abstract

ABSTRACT OF THE DISCLOSURE A hydraulic disc brake device comprises: a base assembly (G) moimted on a vehicle, a sliding assembly (H) slideably moimted on the base assembly (G), a return spring (95) disposed between the base assembly (G) and the sliding assembly (H), a brake lining assembly (70), a control valve assembly (50) disposed on the oil pressure system, hydraulic disc brake system that has an antilock effect. The hydraulic disc brake is low cost and has an antilock function.

Full Text	BACKGROUND OF THE INVENTION Field of the Invention The present invention relates to a hydraulic disc brake device, and more particularly to a hydraulic disc brake device used in a brake system of a vehicle. Description of the Prior Art Most of the conventional hydraulic disc brake devices utilize the oil cylinder to press the two brake lining shoes against the brake disc from both sides, and the friction force generated between the brake lining shoe and the brake disc stops the vehicle. However, these conventional hydraulic disc brake devices still have the following disadvantages: The clamping force caused by the oil pressure in the case of an emergency brake is always very great, and the resultant braking force will be excessively large, and thus probably causing a sudden dead lock. As a result, not only will the tire be locked, but also the vehicle will suffer an instant run-out, leading to a skidding or overtximing of the vehicle. The present invention has arisen to mitigate and/or obviate the afore-described disadvantages. SUMMARY OF THE INVENTION The primary objective of the present invention is to provide a hydraulic disc brake system that has an antilock effect. The secondary objective of the present invention is to provide an economical and low cost hydraulic disc brake system for a vehicle, without needing any precision electronic instruments or electric mechanism. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is an exploded view of a hydraulic disc brake device in accordance with a first embodiment of the present invention; Fig. 2 is an assembly cross sectional view of the hydraulic disc brake device in accordance with the first embodiment of the present invention; Fig. 3 is another assembly cross sectional view of the hydraulic disc brake device in accordance with the first embodiment of the present invention; Fig. 4 is a first cross section operational view of showing the hydravilic disc brake device in accordance with the first embodiment of the present invention; Fig. 5 is a second cross section operational view of showing the hydraulic disc brake device in accordance with the first embodiment of the present invention; Fig. 6 is a third cross section operational view of showing the hydraulic disc brake device in accordance with the first embodiment of the present invention; Fig. 7 is a fourth cross section operational view of showing the hydraulic disc bnke device in accordance with the first embodiment of the present invention; Fig. 8 is an exploded view of a hydraulic disc brake device in accordance with a second embodiment of the present invention; Fig. 9 is a cross section operational view of showing the hydraulic disc brake device in accordance with the second embodiment of the present invention; Fig. 10 is an exploded view of a hydrauUc disc brake device in accordance with a third embodiment of the present invention; Fig. 11 is a first cross section view in accordance with the third embodiment of the present invention of showing the status of the hydraulic disc brake device before a brake action; Fig. 12 is a second cross section view in accordance with the third embodiment of the present invention of showing the status of the hydraulic disc brake device before a brake action; Fig. 13 is a third cross section view in accordance with the third embodiment of the present invention of showing the status of the hydraulic disc brake device before a brake action; Fig. 14 is a fourth cross section view in accordance with the third embodiment of the present invention of showing the status of the hydraulic disc brake device before a brake action; Fig. 15 is a first cross section view in accordance with the third embodiment of the present invention of showing the status of the hydraulic disc brake device during a brake action; Fig. 16 is a second cross section view in accordance with the third embodiment of the present invention of showing the status of the hydraulic disc brake device during a brake action; Fig. 17 is a third cross section view in accordance with the third embodiment of the present invention of showing the status of the hydraulic disc brake device during a brake action; Fig. 18 is a fourth cross section view in accordance with the third embodiment of the present invention of showing the status of the hydrauHc disc brake device during a brake action; Fig. 19 is a first cross sectional view in accordance with the third embodiment of the present invention of showing the antilock action of the hydraulic disc brake device; Fig. 20 is a second cross sectional view in accordance with the third embodiment of the present invention of showing the antilock action of the hydraulic disc brake device; and Fig. 21 is a third cross sectional view in accordance with the third embodiment of the present invention of showing the antilock action of the hydraulic disc brake device. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to Figs. 1-5, a hydraulic disc brake device in accordance with the present invention is installed on a wheel carrier 10 and comprises: a base assembly G, a sliding assembly H, a spring assembly S and a positioning board F. Oil W circulates within the base assembly G. The positioning board F is fixed on the wheel carrier 10 by screws, and is provided with two positioning bolts Fl. The base assembly G is positioned on the wheel carrier 10 by the positioning board F and comprises: a pressing device 20, a first arc-shaped track 30, a second arc-shaped track 40, and a control valve assembly 50. The pressing device 20 includes an oil chamber 21, a piston 22, two oil seals 23,24, a steel-ball positioning disc 25 and a plurality of steel balls 26. A positioning arm 28 protrudes firom a side of the pressing device 20 and is to be positioned on one of the positioning bolts Fl by a positioning sleeve 281. The piston 22 is moveably sealed in the oil chamber 21 by the oil seals 23 and 24. The piston 22 is defined in its outer edge with an engaging groove 221, and the steel-ball positioning disc 25 is formed around its outer periphery with a protrusive engaging edge 251 to be engaged in the engaging groove 221. The plurality of steel balls 26 is positioned between the steel- ball positioning disc 25 and the piston 22. A plurality of through holes 252 is defined in the steel-ball positioning disc 25, and the respective steel balls 26 partially protrude firom the through holes 252. An exhaust valve 27 is disposed adjacent to the oil chamber 21. The first arc-shaped track 30 is located correspondingly to the center of the brake disc 11 and is disposed at a side of the pressing device 20, and an end of the first arc- shaped track 30 is positioned on another one of the positioning bolts Fl by a positioning sleeve 31. The first arc-shaped track 30 is covered with a wear-resistance cover 32. The second arc-shaped track 40 is located correspondingly to the center of the brake disc 11 and is square in cross section. A hole 41 is defined in the second arc-shaped track 40 and is located along the length thereof, and the second arc-shaped track 40 is located at another side of the pressing device 20 and also covered with a wear- resistance cover 42. A safety oil passage 43 is formed in the bottom of the hole 41 and connected to the oil chamber 21. The control valve assembly 50 includes a control groove 51, a control rod 52, a relief valve 53, a main passage 54, an auxiliary passage 55 and a pressure relief space 56. The control groove 51 is located adjacent to the oil chamber 21. A guide cover 511 with a central hole 513 and a dust-proof ring 512 is screwed to either side of the control groove 51. Both ends of the control rod 52 are protruded out of the center hole 513 of the two guide covers 511. The control groove 51 is coimected to the oil chamber 21 via the main passage 54 and the pressure relief space 56, and the avixiliary passage 55 is connected to the safety oil passage 43 of the second arc-shaped track 40. A sealing screw 542 cooperating with a sealing ring 541 is disposed opposite the main passage 54. Located opposite the auxiliary passage 55 is an oil feeding hole 551. The relief valve 53 includes a pressure relief steel ball 531, a pin 532 and a spring 533 disposed in the pressure relief space 56, respectively. A sealing screw 57 with a sealing ring 571 is disposed beside the pressure relief space 56. The pin 532 is to be pressed against the spring 533 and the oil pressure of the oil chamber 21. The pressure relief steel ball 531 is located in the control groove 51, and the pin 532 is sealed between the oil chamber 21 and the control groove 51 together with a first sliding bush 534, an oil seal 535, a second sliding bush 536 and an dust-proof cover 537. A plurality of oil seals 521, a first oil ring 522, a second oil ring 523 and a slidmg bush 59 are positioned in the mid section of the control groove 51 by a C ring 58. The first and second oil rings 522 and 523 each is formed with an open guiding structure for guiding oil out. The first oil ring 522 is located correspondingly to the main passage 54, and the second oil ring 523 is located correspondingly to the auxiliary passage 55. The control rod 52 is formed with a control passage 524, and an oil seal 526 and a sealing screw 525 are screwed in the end of the control passage 524. A first oil hole 527 and a second oil hole 528 are formed in the control passage 524 and are located correspondingly to the first oil ring 522 and the second oil ring 523, respectively. An annular neck portion 529 is formed on the control rod 52 and is located correspondingly to the pressure relief space 56. When the pressure relief steel ball 531 moves into the annular neck portion 529, a pressure relief oil space B will appear at another end of the pin 532 opposite the pressure relief steel ball 531. The shding assembly H is slideably disposed on the first and second arc-shaped track 30 and 40 of the base assembly G and includes a seat 60, a brake lining assembly 70 and a sliding device 80. The seat 60 includes a first positioning portion 61 and a second positioning portion 62 located correspondingly to the first and the second arc-shaped tracks 30 and 40 of the base assembly G. A stop portion 63 is formed at the end of the second positioning portion 62. An anti-collision piece 631 is fixed on the stop portion 63 by screws 632. A screw 633 is disposed at the center of the stop portion 63 and the anti-collision piece 631. Formed between the first and second positions 61 and 62 is an elliptical sliding hole 64 for passage of the piston 22 of the pressing device 20 and the flange Gl of the base assembly G. A stepped recess 641 is formed at a side of the elliptical sliding hole 64, and an anti-collision block 642 and a fixing piece 644 are fixed in the stepped recess 641 by screws 643. A brake-mounting portion 65 protrudes from the seat 60 and is located around the elliptical sliding hole 64, so that a brake space 66 is defined between the brake-mounting portion 65 and the elliptical sliding hole 64 for accommodation of the brake disc 11 and the brake lining assembly 70. Screwed on the brake-mounting portion 65 are two brake-lining positioning shafts 651 that are to be inserted in the seat 60 and located at both sides of the elliptical sliding hole 64. The brake-mounting portion 65 is provided with an engaging rib 652 located in the brake space 66. Two opposite abutting blocks 67 are arranged at a side of the elliptical sliding hole 64, and each of which is provided with an abutting screw 671 and an auditing nut 672. The two abutting blocks 67 are pressed against both ends of the control rod 52. The brake lining assembly 70 includes a fi-ont brake lining shoe 71 and a rear brake lining shoe 72 that are inserted on the two brake-lining positioning shafts 651 in a parallel manner, and the brake-lining positioning shafts 651 enables the firent brake lining shoe 71 and the rear brake lining shoe 72 to move within the brake space 66. A pressing spring leaf 73 is disposed against a side of the firont brake lining shoe 71 and the rear brake lining shoe 72 and is positioned on the engaging rib 652 of the brake- moimting portion 65 of the seat 60, thus preventing the front brake lining shoe 71 and the rear brake lining shoe 72 from becoming loose. In addition, the front brake lining shoe 71 is pressed against the steel balls 26 on the steel ball positioning disc 25, and can move smoothly under the aid of the steel balls 26. The sliding device 80 includes inverted U-shaped seats 81, dust-proof frames 82 and wear-resistance pieces 83. The inverted U-shaped seats 81 are fixed on the first and second positioning portions 61 and 62 of the seat 60 by rivets 85. The inverted U- shaped seats 81 are slideably moimted on the first and second arc-shaped fracks 30 and 40. A plurality of cavities 811 with steel balls 812 are formed in the respective inverted U-shaped seats 81, and the steel balls 812 are located between the inverted U-shaped seat 81 and the wear-resistance cover 32 and 42. The respective dust-proof frame 82 is fixed to the inverted U-shaped seat 81 by screws 84, so as to prevait dust from entering the arc-shaped tracks. The spring assembly S is confined in the hole 41 of the second arc-shaped track 40 by the anti-collision piece 631 and the screw 633 of the sliding assembly H, and includes a safety rod 90, two seal rings 91, a safety spring 92, a support bracket 93, a washer 94 and a return spring 95. One end of the return spring 95 cooperating with the washer 94 and the support bracket 93 is pressed against the bottom of the hole 41 of the second arc-shaped track 40, and another end of the return spring 95 is positioned on the screw 633 of the seat 60. The return spring 95 serves to push against the stop portion 63 of the sliding assembly H. The safety spring 92 is restricted in the support bracket 93 and the return spring 95, and the safety rod 90 is riveted to the support bracket 93. The safety rod 93 and the return spring 95 push the safety rod 90 to move, so as to close the safety oil passage 43 of the second arc-shaped track 40. As shown in Fig. 4, before braking action is initiated, the brake disc 11 rotates counterclockwise along with the wheel, the front brake lining shoe 71 and the rear brake lining shoe 72 are located at both sides of the brake disc 11 in a pressure fiwe manner. At this moment, since the return spring 95 is biased between the hole 41 of the second arc-shaped track 40 of the base assembly G and the anti-collision piece 631 of the sliding assembly H, the motionless base assembly G enables the sliding assembly H to be pushed by the return spring 95 to the lowest portion of the arc- shaped track. Accordingly, the two opposite abutting blocks 67 of the sliding assembly H are also located at the lowest portion of the arc-shaped track, and push the lower end of the control rod 52 of the control valve assembly 50 upward. Since the control rod 52 moves with respect to the control groove 51 of the control valve assembly 50, the control passage 524 of the control rod 52 will be aligned to the first oil hole 527, and the second oil hole 528 and the second oil ring 523 will exactly be aligned to the oil feeding hole 551. As a result, the oil W from the oil feeding hole 551 will flow to the oil chamber 21 via the second oil ring 523, the second oil hole 528, the control passage 524, the first oil hole 527, the first oil ring 522 and the main passage 54. However, before the oil W pressure increases, the piston 22 will not be driven by any oil pressure from the oil chamber 21. On the other hand, the sliding assembly H doesn't move relative to the base assembly G, therefore, the front surface of the front brake lining shoe 71 is not pressed against the steel balls 26. At this moment, the brake lining assembly 70 doesn't clamp the brake disc 11, and the annular neck portion 529 of the control rod 52 is located below the pressure relief steel ball 531 of the pressure relief valve 53. Therefore, the wheel can rotate freely without any resistance. When the hydraulic disc brake device is activated at a relatively high speed, as both shown in Figs. 4 and 5, the brake disc 11 still rotates coimterclockwise, at this moment, the oil W increases in pressure and flows from the oil feeding hole 551 to the oil chamber 21 via the second oil ring 523, the second oil hole 528, the control passage 524, the first oil hole 527, the first oil ring 522 and the main passage 54 (as indicated by the arrow). Meanwhile, the piston 22 of the pressing assembly 20 is moved by the oil pressure firom the oil chamber 21, pushing the front brake lining shoe 71 toward the rear brake lining shoe 72, as a result, the brake disc 11 is clamped firmly by the front and second brake lining shoes 71 and 72, causing an emergency braking action. After that, as shown in Fig. 5, at the instant the braking action is initiated, the front and second brake lining shoes 71 and 72 absorb a lot of counterclockwise stress from the brake disc 11, generating a very large counterclockwise sfress toward the center of the brake disc 11. Since the sliding assembly H is slideably disposed in the first and second arc-shaped tracks 30 and 40 of the base assembly G, the first and second arc- shaped tracks 30 and 40 are located opposite the center of the brake disc 11, plus the inertial force produced by an emergency of a high speed vehicle is larger than the critical value of the elastic force of the return spring 95 of the spring assembly S. The emergency-brake ca\ised sfress will push the sliding assembly H to slide counterclockwise while compressing the return spring 95 (as shown in Fig, 5). At the same time, the coimterclockwise motion of the slide assembly H causes a displacement of the slide assembly H relative to the base assembly G, and the abutting blocks 67 of the sliding assembly H push the confrol rod 52 of the confrol valve assembly 50 to move, so that the confrol groove 51 of tiie confrol valve assembly 50 changes with the upward movement of the confrol rod 52, and the first and second oil rings 522 and 523 are not aligned with the main passage 54 and the auxiliary passage 55 anymore. Therefore, the oil W stops flowing into the oil chamber 21. At this moment, the confrol rod 52 of the confrol valve assembly 50 moves upward, therefore, the annular neck portion 529 of the confrol rod 52 moves upward to a position aligned with the pressure relief steel ball 531. Under the effect of the pushing force of the spring 533 and the oil pressure of the oil chamber 21, the pin 532 pushes the pressure relief steel ball 531 into the annular neck portion 529 of the confrol rod 52, and as a result, a pressure relief oil space B appears at another end of the pin 532 facing the oil chamber 21. At this moment, the oil W will be decompressed instantly after flowing into the pressure relief oil space B, so that the piston 22 of the pressing device 20 reduces its pushing force on the front brake lining shoe 71, and accordingly, the brake lining assembly 70 relieves its clamping force against the brake disc 11. At this moment, the brake-caused counterclockwise stress disappears from the sliding assembly H, and the return spring 95 pushes the sliding assembly H back to its original position. Meanwhile, the sliding assembly H rotates about the base assembly G. The aimular neck portion 529 of the control rod 52 moves downward (to disengage from the pressure relief steel ball 531 again), the pressure relief steel ball 531 pushes the pin 532 and the spring 533 backward, so that the pressure relief oil space B disappears. Meanwhile, the control groove 51 of the control valve assembly 50 changes with the downward movement of the confrol rod 52, and the first and second oil rings 522 and 523 are aligned with the main passage 54 and the auxiliary passage 55 again. Therefore, the oil W flows into the oil chamber 21 again (the pressure thereof increases again), and the brake lining assembly 70 instantly clamps the brake disc 11 again. Such instant clamping and instant relief actions will occur repeatedly, preventing the brake disc from being clamped too tight (antilock effect). It is to be noted that a plurality of anti-collision structures are provided on the sliding assembly H and opposite the base assembly G, wear-resistance structures are arranged at the positions where the friction frequently occurs, and the present invention is also provided with a plurality of position adjustment structures. Referring then to Figs. 6 and 7, aiming at the safety operation, the present invention is particularly provided with the safety rod 90, the safety spring 92 and the support bracket 93. If the return spring 95 is broken (as shown in Fig. 6), the support bracket 93 will not be pushed by the return spring 95 anymore but will be subjected to the pushing force of the safety spring 92. At this moment, the support bracket 93 will be deformed or will move downward, and the safety rod 90 will lose its supporting force since it is riveted to the support bracket 93. As a result, the end of the safety rod 90 doesn't seal the safety oil passage 43 of the second arc-shaped frack 40 anymore. Meanwhile, the oil W from the oil feeding hole 551 flows into the safety oil passage 43 via the second oil ring 523 of the control valve assembly 50, and constantly increases the pressure of the oil chamber 21. Although the control rod 52 cooperates with the pressure relief steel ball 531 to produce a pressure relief oil space B, the oil from the safety oil passage 43 can still enable the brake lining assembly 70 to keep firmly pressing against the brake disc 11. Therefore, the emergency brake effect (only the antilock effect is lost) can still be ensured even if the return spring 95 is broken. Furthermore, if the return spring 95 fatigues, the safety rod 90, the safety spring 92 and the support bracket 93 can still produce the effect of emergency brake. Referring to Figs. 8 and 9, which show a second embodiment. In this embodiment, there are two sets of oil chambers 21, pistons 22 and steel-ball positioning discs 25, and each set includes the oil seals 23, 23a, 24, 24a, steel-ball positioning discs 25, 25a, a plurality of steel balls 26, 26a, and pistons 22, 22a slideably sealed in two oil chambers 21, 21a. The two oil chambers 21 are in commimication with each other via a main passage 54. An exhaust valve 27 is arranged beside the oil chamber 21, and a safety oil passage 43 is formed beside the oil chamber 21a. By using the double pressing devices 20, the resultant braking force will be more strong, and the antilock effect will be better. Fig. 10 shows a third embodiment of the present invention, this embodiment is additionally provided with a main cylinder C3 and an elastic oil-storage cylinder C31. The seat CI is installed on the wheel carrier 10 and serves to cooperate with the moveable base assembly C2. The status of the hydraulic disc brake device before braking action is shown in Figs. 11-14, the status of the hydraulic disc brake device during braking action is shown in Figs. 15-18, and the status of tiie hydraulic disc brake device during antilock action is shown in Figs. 19-21. The seat CI is fixed onto the wheel carrier 10, a L-shaped stop board CI 1 is riveted to either side of the seat CI, and a space is defined between the two L-shaped stop boards CI 1. The two L-shaped stop boards CI 1 are located in the arc-shaped route of the wheel axis. Two sliding members CI2 with opening facing each other are disposed in the arc-shaped route of the wheel axis, and each of the sliding members C12 is a structure with one end closed and with an interior receiving space. The base assembly C2 includes a pressing device C21, a first arc-shaped track C22, a second arc-shaped track C23, a control valve assembly C24, a spring assembly C25, the main cylinder C3 and the elastic oil-storage cylinder C31. The spring assembly C25 is confined in the first arc-shaped track C22 by the sliding assembly CI2, and includes a safety rod, two seal rings, a safety spring, a support bracket, a washer and a return spring. One end of the return spring cooperating with the washer and the support bracket is pressed against the bottom edge of the first arc- shaped track, and another end of the return spring is pressed against the sliding members CI 2 of the seat CI. The safety spring is restricted in the support bracket and the return spring, and the safety rod is riveted to the support bracket. The pressing device C21 includes a piston C211, and a plurality of oil seals C212. Since the pressing device C21 moves along with the base assembly C2 and the braking lining assembly C26, it doesn't need the steel balls and the steel-ball positioning disc, and it can use the conventional pressing device to cooperate with the brake lining assembly C26, and the brake lining assembly C26 is pressed to clamp the brake disc 11. The first and second arc-shaped tracks C22 and C23 are also provided with the wear- resistance covers C221, C231, the sling members C12 are slideably installed on the first and second arc-shaped tracks C22 and C23. An antic-collision cushion C232 is disposed at the end of the second arc-shaped track C23, and the first arc-shaped track C22 is interiorly formed with safety oil passage. The end of the safety rod of the spring assembly C25 is pushed by the return spring to close the safety oil passage. The assembly, function and effect of the control valve assembly C24 are similar to the previous embodiment, and the only difference is that the position and the structure of the oil route are changed appropriately. It is to be noted that the main cylinder C3 and the elastic oil-storage cylinder C31 are installed on the base assembly C2 directly. The main cylinder C3 utilizes a steel cord C32 to drive the main piston C33, so as to push the oil into the oil chamber. A pushing spring C34, an O-shaped ring C36, and a piston C35 are sealed in the elastic oil-storage cylinder C31 by a cover C37. The pushing spring C34 pvishes the piston C35 to move, so as to push the oil into the main cylinder C3, and the oil pressure of the main cylinder C3 is directly connected to the control valve assembly C24. In this embodiment, the seat CI is mounted on the wheel carrier 10. The main cylinder can also be mounted on the handlebar. I CLAIM: 1. A hydrauhc disc brake device, which is mounted on a wheel carrier (10) of a vehicle for brake by a change of a hydraulic pressure, comprising: a base assembly(G), which is mounted on the vehicle, including a pressing device(20) having an oil chamber(21); a sliding assembly(H) provided on the base assembly(G) for movement along a predetermined arched path; a return spring(95) disposed between the base assembly(G) and the sliding assembly(H) that a relative movement of the base assembly(G) and the sliding assembly(H) causes a compression of the return spring(95); a brake lining assembly(70) including a front brake lining shoe(71) and a rear brake lining shoe(72) for clamping a brake disc(l 1) of a wheel of the vehicle by a change of a hydraulic pressure; and a control valve assembly(50), which controls the hydraulic pressure, including a control groove(51), a control rod(52), a relief valve(53), a main passage(54), and a pressure relief space(56), wherein the control rod(52) passes through the control groove(51), and the main passage(54) communicates the control groove(51) and the oil chamber(21), and the relief valve(53) is received in the pressure relief space(56) for free movement, and the pressure relief space(56) communicates the control groove(51) and the oil chamber(21) also, and when the front brake lining shoe(71) and the rear brake lining shoe(72) of the brake lining assembly(70) clamp the brake disc(ll), an inertia of the wheel is exerted on the control valve assembly(50) to move the sliding assembly(H) along the predetermined arched path relative to the base assembly(G) and to compress the return spring(95), and the sliding assembly(H) shifts the control rod(52) in the same time to cut off the main passage(54) that the control valve assembly(50) stops the hydrauhc pressure and forms a pressure rehef oil space(B) between the relief valve(53) and the oil chamber(2l) to drive the brake lining assembly(70) unclamping the brake disc(ll), and the return spring(95) returns the shding assembly(H) to close the pressure relief oil space(B), and then the control rod(52) is shifted reversely to open the main passage(54), and the control valve assembly(50) increases the hydraulic pressure to drive the brake lining assembly(70) clampmg the brake disc( 11); whereby the change of the hydraulic pressxire controls a reciprocation of the relief valve(53) of the control valve assenibly(50) to open or close the pressure rehef oil space(B) that the brake lining assembly(70) may clamp and unclamp the brake disc(l 1). 2. The hydraulic disc brake device as claimed in claim 1, wherein the base assembly(G) includes a first arc-shaped track(30) and a second arc-shaped track(40), both of which have a center of curvature at a center of the brake disc(ll), and the control assembly(50) is disposed in the base assembly(G), and the sliding assembly(H) is slid along the first arc-shaped track(30) and second arc-shaped track(40) of the base assembly(G). 3. The hydraulic disc brake device as claimed in claim 2, wherein the sliding assembly(H) includes a seat(60) having a brake space(66) to receive the brake disc(ll) and the brake lining assembly(70) therein and a sliding device(80) disposed on the seat(60) to provide the first arc-shaped track(30) and the second arc-shaped track(40) thereon. 4. The hydraulic disc brake device as claimed in claim 3, wherein the base assembly(G) is provided with a flange(Gl), and the pressing device(20) includes a piston(22) sealed in the oil chamber(21) for fi-ee movement, in which oil(W) is received to press the piston; the second arc-shaped track(40) has a hole(41) along an elongated direction thereof and a safety oil passage(43) formed on a bottom of the hole(41) to be communicated with the oil chamber(21), and the seat(60) of the sliding assembly(H) has an elliptical sUding hole(64) at a center thereof for passage of the piston(22) of the pressing device(20) and the flange(Gl) of the base assembly(G); and a brake-mounting portion(65) is protruded out of the elliptical sliding hole(64) of the seat(60), and the brake space(66) is formed between the brake-mounting portion(65) and the elliptical sliding hole(64). 5. The hydraulic disc brake device as claimed in claim 3, wherein the seat(60) of the sliding assembly(H) further includes a stop portion(63) associated with the second arc- shaped track(40) of the base assembly(G), and the return spring(95) biases the bottom of the hole(41) of the second arc-shaped track(40) of the base assembly(G) and the stop portion(63) of the sHding assembly(H). 6. The hydraulic disc brake device as claimed in claim 4, wherein the pressing device(20) includes a plurality of oil seals(23,24), a steel-ball positioning disc(25), and a plurality of steel balls(26), and the piston(22) is moveably restricted in the oil chamber(21) by the oil seals(23,24) to position the steel-ball positioning disc(25), and the steel balls(26) are positioned between the steel-ball positioning disc(25) and the piston(22), and the steel- ball positioning disc(25) has a plurality of through holes(252) that each of the steel balls has a portion protruded out of the steel-ball positioning disc(25) via the through holes(252) respectively, and the front brake lining shoe(71) and the rear brake lining shoe(72) of the brake lining assembly(70) are parallel and provided on the seat(60) that a front surface of the front brake lining shoe(71) touches the steel balls(26) of the steel-ball positioning disc(25) of the pressing device(20) for a smooth slide. 7. The hydraulic disc brake device as claimed in claim 5, wherein: the control valve(51) of the control valve assembly(50) is located beside the oil chamber(21) of the pressing device(20) and is provided with two guide covers(511), each of which has a central hole(513), and the control rod(52) has opposite ends passing through the center hole(513) of the guide cover(511); the reUef valve(53) includes a pressure relief steel ball(531), a pin(532) and a spring(533) disposed in the pressure relief space(56), and an auxiliary passage(55), wherein the pin(532) is biased by the spring(533), and the pressure relief steel ball(531) is received in the control groove(51), and the pin(532) is sealed between the oil chamber(21) and the confrol groove(51) for free sUde, and the auxiUary passage(55) is communicated with the safety oil passage(43) of the second arc-shaped frack(40); and a first oil ring(522) and a second oil ring(523) are positioned in a mid section of the confrol groove(51), wherein the first oil ring(522) is associated with the main passage(54) and the second oil ring(523) is associated with the auxiliary passage(55), and the confrol rod(52) is inserted into the confrol groove(51)to form a confrol passage(524)having a first oil hole(527) associated with the first oil ring(522) and a second oil hole(528) associated with the second oil ring(523), and the control rod(52) has an annular neck portion(529) associated with the pressure relief space(56) that when the pressure reUef steel ball(531) of the reUef valve(53) enters the annular neck portion(529), the pressure reUef oil space(B) is exposed at an end of the pin(532) opposite the pressure reUef steel ball(531). 8. The hydraulic disc brake device as claimed in claim 5, further comprising a spring assembly(S), which is confined in the hole(41) of the second arc-shaped track(40) by the stop portion(63) of the sliding assembly(H), including a safety rod(90), a safety spring(92), a support bracket(93), and the return spring(95), wherein the return spring(95) has an end cooperated with the support bracket(93) to press the bottom of the hole(41) of the second arc-shaped track(40) and an opposite end pressing the stop portion(63) of the sUding assembly(H), and the safety spring(92) is restricted in the support bracket(93), in which the safety rod(90) is received, whereby the return spring(95) biases the safety rod(90) to seal the oil passage(43) of the second arc-shaped track(40). 9. A hydraulic disc brake device providing a brake by a change of a hydraulic pressure, comprising: a seat(Cl) mounted on a wheel carriage(10) of a vehicle; a base assembly(C2) moved along a predetermined arched path relative to the seat(Cl); a return spring(95) disposed between the seat(Cl) and the base assembly(C2) that a relative movement of the seat(Cl) and the base assembly(C2) causes a compression of the return spring(95); a brake lining assembly(C26) including a fi-ont brake lining shoe(71) and a rear brake lining shoe(72) for clamping a brake disc(ll) of a wheel of the vehicle by a change of a hydrauHc pressure; and a control valve assembly(C24), which controls the hydraulic pressure, including a control groove(C241), a control rod(C242), a relief valve(C243), a main passage(C244), and a pressure reUef space(C246), wherein the control rod(C242) passes through the control groove(C241), and the main passage(C244) communicates the control groove(C241) and an oil chamber(21), and the relief valve(C243) is received in the pressure relief space(C246) for free movement, and the pressure relief space(C246) communicates the control groove(C241) and the oil chamber(21) also, and when the front brake lining shoe(71) and the rear brake lining shoe(72) of the brake lining assembly(C26) unclamp the brake disc(ll), an inertia of the wheel is exerted on the control valve assembly(C24) to move the base assembly(C2) along the predetermined arched path relative to the seat(Cl) and to compress the return spring(95), and the base assembly(C2) shifts the control rod(C242) in the same time to cut off the main passage(C244) that the control valve assembly(C24) stops the hydraulic pressure and forms a pressure relief oil space(B) between the relief valve(C243) and the oil chamber(21) to drive the brake lining assembly(C26) unclamping the brake disc(ll), and the return spring(95) returns the base assembly(C2) to close the pressure relief oil space(B), and then the control rod(C242) is shifted reversely to open the main passage(C244), and the control valve(C24) assembly increases the hydraulic pressure to drive the brake lining assembly(C26) clamping the brake disc( 11); whereby the change of the hydraulic pressure controls a reciprocation of the relief valve(C243) of the control valve assembly(C24) to open or close the pressxire relief oil space(B) that the brake lining assembly(C26) may clamp and unclamp the brake disc(l 1). 10. The hydraulic disc brake device as claimed in claim 9, wherein the base assembly(C2) includes a pressing device(C21) pressed by a pressure of a main cylinder(C3), a first arc-shaped track(C22), which is disposed in the seat(Cl) for free slide, provided with a spring assembly(C25) and a safety oil passage(C222), and a second arc-shaped track(C23) disposed in the seat(Cl) for free slide. 11. The hydraulic disc brake device as claimed in claim 9, wherein the confrol groove(C241) of the control valve assembly(C24) is located beside the oil chamber(21) of the pressing device(C21) and is provided with two guide covers(511), each of which has a central hole(513), and the control rod(C242) has opposite ends passing through the cenfral holes(513) of the guide covers(511), and the confrol groove(C241) is communicated with the oil chamber(21) of the pressing device(C21) through the main passage(C244) and the pressure reUef space(C246), and an auxiliary passage(C245) is communicated with the safety oil passage(C222) of the first arc-shaped track(C22), and an oil feeding hole(551) is located at an opposite end of the auxiliary passage(C245); and a first oil ring(522) and a second oil ring(523) are positioned in a mid section of the control gj:oove(C241), wherein the first oil ring(522) is associated with the main passage(C244) and the second oil ring(523) is associated with the auxiliary passage(C245), and the control rod(C242) has an annular neck portion(529) associated with the pressure relief space(C246), and the pressure relief valve(C243) includes at least one pressure rehef steel ball(531) and a pin(532), when the pressure rehef steel ball(531) of the relief valve(C243) enters the annular neck portion(529), the pressure relief oil space(B) is exposed at an end of the pin(532) opposite the pressure relief steel ball(531). 12. The hydraulic disc brake device as claimed in claim 10, wherein the pressing device(C21) includes a piston(C211) moveably sealed in the oil chamber(21) to be moved by an oil pressure in the oil chamber(21), and the first arc-shaped track(C22) is provided with a hole(41) having the safety oil passage(C222) on the bottom of the hole(41) in communication with the oil chamber(21) of the pressing device(C21); the sUding assembly(Cl) is installed on the wheel carriage(10); and the fi-ont brake lining shoe(71) and the rear brake lining shoe(72) of the brake lining assembly(C26) are provided on the seat(C2) in a parallel manner, wherein a fi-ont surface of the fi-ont brake lining shoe(71) is pressed by the piston(C211) of the pressing device(C21). 13. The hydraulic disc brake device as claimed in claim 10, fiirther comprising a spring assembly(C25), which is confined in the hole(41) of the first arc-shaped track(C22) by the shding member(C12) of the seat(Cl), including the return spring(95). 14. The hydraulic disc brake device as claimed in claim 11, wherein the relief valve(C243) includes a spring(533) disposed in the pressure relief space(C246) to bias the pin(532), and the pressure relief steel ball(531) is received in the control groove(C241), and the pin(532) is slideably sealed between the oil chamber(21) and the control groove(C241). 15. The hydraulic disc brake device as claimed in claim 13, wherein the spring assembly(C25) includes a safety rod(90), a safety spring(92), a support bracket(93), and the return spring(95), wherein the return spring(95) has an end cooperated with the support bracket(93) to press the bottom of the hole(41) of the first arc-shaped track(C22), and an opposite end thereof pressing the sliding member(C12) of the seat(Cl), and the safety spring(92) is restricted in the support bracket(93), in which the safety rod(90) is provided, and the safety rod(90) is moved by the retum spring(95) so as to close the safety oil passage(C222) of the second arc-shaped track(C23).

Full Text

BACKGROUND OF THE INVENTION
Field of the Invention
The present invention relates to a hydraulic disc brake device, and more particularly
to a hydraulic disc brake device used in a brake system of a vehicle.
Description of the Prior Art
Most of the conventional hydraulic disc brake devices utilize the oil cylinder to press
the two brake lining shoes against the brake disc from both sides, and the friction
force generated between the brake lining shoe and the brake disc stops the vehicle.
However, these conventional hydraulic disc brake devices still have the following
disadvantages:
The clamping force caused by the oil pressure in the case of an emergency brake is
always very great, and the resultant braking force will be excessively large, and thus
probably causing a sudden dead lock. As a result, not only will the tire be locked, but
also the vehicle will suffer an instant run-out, leading to a skidding or overtximing of
the vehicle.
The present invention has arisen to mitigate and/or obviate the afore-described
disadvantages.
SUMMARY OF THE INVENTION
The primary objective of the present invention is to provide a hydraulic disc brake
system that has an antilock effect.
The secondary objective of the present invention is to provide an economical and low
cost hydraulic disc brake system for a vehicle, without needing any precision
electronic instruments or electric mechanism.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is an exploded view of a hydraulic disc brake device in accordance with a first
embodiment of the present invention;
Fig. 2 is an assembly cross sectional view of the hydraulic disc brake device in
accordance with the first embodiment of the present invention;

Fig. 3 is another assembly cross sectional view of the hydraulic disc brake device in
accordance with the first embodiment of the present invention;
Fig. 4 is a first cross section operational view of showing the hydravilic disc brake
device in accordance with the first embodiment of the present invention;
Fig. 5 is a second cross section operational view of showing the hydraulic disc brake
device in accordance with the first embodiment of the present invention;
Fig. 6 is a third cross section operational view of showing the hydraulic disc brake
device in accordance with the first embodiment of the present invention;
Fig. 7 is a fourth cross section operational view of showing the hydraulic disc bnke
device in accordance with the first embodiment of the present invention;
Fig. 8 is an exploded view of a hydraulic disc brake device in accordance with a
second embodiment of the present invention;
Fig. 9 is a cross section operational view of showing the hydraulic disc brake
device in accordance with the second embodiment of the present invention;
Fig. 10 is an exploded view of a hydrauUc disc brake device in accordance with a
third embodiment of the present invention;
Fig. 11 is a first cross section view in accordance with the third embodiment of the
present invention of showing the status of the hydraulic disc brake device before a
brake action;
Fig. 12 is a second cross section view in accordance with the third embodiment of
the present invention of showing the status of the hydraulic disc brake device before
a brake action;
Fig. 13 is a third cross section view in accordance with the third embodiment of the
present invention of showing the status of the hydraulic disc brake device before a
brake action;
Fig. 14 is a fourth cross section view in accordance with the third embodiment of the
present invention of showing the status of the hydraulic disc brake device before a
brake action;
Fig. 15 is a first cross section view in accordance with the third embodiment of the
present invention of showing the status of the hydraulic disc brake device during a
brake action;
Fig. 16 is a second cross section view in accordance with the third embodiment of the
present invention of showing the status of the hydraulic disc brake device during a
brake action;

Fig. 17 is a third cross section view in accordance with the third embodiment of the
present invention of showing the status of the hydraulic disc brake device during a
brake action;
Fig. 18 is a fourth cross section view in accordance with the third embodiment of the
present invention of showing the status of the hydrauHc disc brake device during a
brake action;
Fig. 19 is a first cross sectional view in accordance with the third embodiment of the
present invention of showing the antilock action of the hydraulic disc brake device;
Fig. 20 is a second cross sectional view in accordance with the third embodiment of
the present invention of showing the antilock action of the hydraulic disc brake
device; and
Fig. 21 is a third cross sectional view in accordance with the third embodiment of the
present invention of showing the antilock action of the hydraulic disc brake device.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Referring to Figs. 1-5, a hydraulic disc brake device in accordance with the present
invention is installed on a wheel carrier 10 and comprises: a base assembly G, a
sliding assembly H, a spring assembly S and a positioning board F. Oil W circulates
within the base assembly G.
The positioning board F is fixed on the wheel carrier 10 by screws, and is provided
with two positioning bolts Fl.
The base assembly G is positioned on the wheel carrier 10 by the positioning board F
and comprises: a pressing device 20, a first arc-shaped track 30, a second arc-shaped
track 40, and a control valve assembly 50.
The pressing device 20 includes an oil chamber 21, a piston 22, two oil seals 23,24, a
steel-ball positioning disc 25 and a plurality of steel balls 26. A positioning arm 28
protrudes firom a side of the pressing device 20 and is to be positioned on one of the
positioning bolts Fl by a positioning sleeve 281. The piston 22 is moveably sealed in
the oil chamber 21 by the oil seals 23 and 24. The piston 22 is defined in its outer
edge with an engaging groove 221, and the steel-ball positioning disc 25 is formed

around its outer periphery with a protrusive engaging edge 251 to be engaged in the
engaging groove 221. The plurality of steel balls 26 is positioned between the steel-
ball positioning disc 25 and the piston 22. A plurality of through holes 252 is defined
in the steel-ball positioning disc 25, and the respective steel balls 26 partially protrude
firom the through holes 252. An exhaust valve 27 is disposed adjacent to the oil
chamber 21.
The first arc-shaped track 30 is located correspondingly to the center of the brake disc
11 and is disposed at a side of the pressing device 20, and an end of the first arc-
shaped track 30 is positioned on another one of the positioning bolts Fl by a
positioning sleeve 31. The first arc-shaped track 30 is covered with a wear-resistance
cover 32.
The second arc-shaped track 40 is located correspondingly to the center of the brake
disc 11 and is square in cross section. A hole 41 is defined in the second arc-shaped
track 40 and is located along the length thereof, and the second arc-shaped track 40 is
located at another side of the pressing device 20 and also covered with a wear-
resistance cover 42. A safety oil passage 43 is formed in the bottom of the hole 41 and
connected to the oil chamber 21.
The control valve assembly 50 includes a control groove 51, a control rod 52, a relief
valve 53, a main passage 54, an auxiliary passage 55 and a pressure relief space 56.
The control groove 51 is located adjacent to the oil chamber 21. A guide cover 511
with a central hole 513 and a dust-proof ring 512 is screwed to either side of the
control groove 51. Both ends of the control rod 52 are protruded out of the center hole
513 of the two guide covers 511. The control groove 51 is coimected to the oil
chamber 21 via the main passage 54 and the pressure relief space 56, and the avixiliary
passage 55 is connected to the safety oil passage 43 of the second arc-shaped track 40.
A sealing screw 542 cooperating with a sealing ring 541 is disposed opposite the main
passage 54. Located opposite the auxiliary passage 55 is an oil feeding hole 551. The
relief valve 53 includes a pressure relief steel ball 531, a pin 532 and a spring 533
disposed in the pressure relief space 56, respectively. A sealing screw 57 with a
sealing ring 571 is disposed beside the pressure relief space 56. The pin 532 is to be
pressed against the spring 533 and the oil pressure of the oil chamber 21. The pressure
relief steel ball 531 is located in the control groove 51, and the pin 532 is sealed

between the oil chamber 21 and the control groove 51 together with a first sliding
bush 534, an oil seal 535, a second sliding bush 536 and an dust-proof cover 537. A
plurality of oil seals 521, a first oil ring 522, a second oil ring 523 and a slidmg bush
59 are positioned in the mid section of the control groove 51 by a C ring 58. The first
and second oil rings 522 and 523 each is formed with an open guiding structure for
guiding oil out. The first oil ring 522 is located correspondingly to the main passage
54, and the second oil ring 523 is located correspondingly to the auxiliary passage 55.
The control rod 52 is formed with a control passage 524, and an oil seal 526 and a
sealing screw 525 are screwed in the end of the control passage 524. A first oil hole
527 and a second oil hole 528 are formed in the control passage 524 and are located
correspondingly to the first oil ring 522 and the second oil ring 523, respectively. An
annular neck portion 529 is formed on the control rod 52 and is located
correspondingly to the pressure relief space 56. When the pressure relief steel ball 531
moves into the annular neck portion 529, a pressure relief oil space B will appear at
another end of the pin 532 opposite the pressure relief steel ball 531.
The shding assembly H is slideably disposed on the first and second arc-shaped track
30 and 40 of the base assembly G and includes a seat 60, a brake lining assembly 70
and a sliding device 80.
The seat 60 includes a first positioning portion 61 and a second positioning portion 62
located correspondingly to the first and the second arc-shaped tracks 30 and 40 of the
base assembly G. A stop portion 63 is formed at the end of the second positioning
portion 62. An anti-collision piece 631 is fixed on the stop portion 63 by screws 632.
A screw 633 is disposed at the center of the stop portion 63 and the anti-collision
piece 631. Formed between the first and second positions 61 and 62 is an elliptical
sliding hole 64 for passage of the piston 22 of the pressing device 20 and the flange
Gl of the base assembly G. A stepped recess 641 is formed at a side of the elliptical
sliding hole 64, and an anti-collision block 642 and a fixing piece 644 are fixed in the
stepped recess 641 by screws 643. A brake-mounting portion 65 protrudes from the
seat 60 and is located around the elliptical sliding hole 64, so that a brake space 66 is
defined between the brake-mounting portion 65 and the elliptical sliding hole 64 for
accommodation of the brake disc 11 and the brake lining assembly 70. Screwed on
the brake-mounting portion 65 are two brake-lining positioning shafts 651 that are to
be inserted in the seat 60 and located at both sides of the elliptical sliding hole 64. The

brake-mounting portion 65 is provided with an engaging rib 652 located in the brake
space 66. Two opposite abutting blocks 67 are arranged at a side of the elliptical
sliding hole 64, and each of which is provided with an abutting screw 671 and an
auditing nut 672. The two abutting blocks 67 are pressed against both ends of the
control rod 52.
The brake lining assembly 70 includes a fi-ont brake lining shoe 71 and a rear brake
lining shoe 72 that are inserted on the two brake-lining positioning shafts 651 in a
parallel manner, and the brake-lining positioning shafts 651 enables the firent brake
lining shoe 71 and the rear brake lining shoe 72 to move within the brake space 66. A
pressing spring leaf 73 is disposed against a side of the firont brake lining shoe 71 and
the rear brake lining shoe 72 and is positioned on the engaging rib 652 of the brake-
moimting portion 65 of the seat 60, thus preventing the front brake lining shoe 71 and
the rear brake lining shoe 72 from becoming loose. In addition, the front brake lining
shoe 71 is pressed against the steel balls 26 on the steel ball positioning disc 25, and
can move smoothly under the aid of the steel balls 26.
The sliding device 80 includes inverted U-shaped seats 81, dust-proof frames 82 and
wear-resistance pieces 83. The inverted U-shaped seats 81 are fixed on the first and
second positioning portions 61 and 62 of the seat 60 by rivets 85. The inverted U-
shaped seats 81 are slideably moimted on the first and second arc-shaped fracks 30
and 40. A plurality of cavities 811 with steel balls 812 are formed in the respective
inverted U-shaped seats 81, and the steel balls 812 are located between the inverted
U-shaped seat 81 and the wear-resistance cover 32 and 42. The respective dust-proof
frame 82 is fixed to the inverted U-shaped seat 81 by screws 84, so as to prevait dust
from entering the arc-shaped tracks.
The spring assembly S is confined in the hole 41 of the second arc-shaped track 40 by
the anti-collision piece 631 and the screw 633 of the sliding assembly H, and includes
a safety rod 90, two seal rings 91, a safety spring 92, a support bracket 93, a washer
94 and a return spring 95. One end of the return spring 95 cooperating with the
washer 94 and the support bracket 93 is pressed against the bottom of the hole 41 of
the second arc-shaped track 40, and another end of the return spring 95 is positioned
on the screw 633 of the seat 60. The return spring 95 serves to push against the stop

portion 63 of the sliding assembly H. The safety spring 92 is restricted in the support
bracket 93 and the return spring 95, and the safety rod 90 is riveted to the support
bracket 93. The safety rod 93 and the return spring 95 push the safety rod 90 to move,
so as to close the safety oil passage 43 of the second arc-shaped track 40.
As shown in Fig. 4, before braking action is initiated, the brake disc 11 rotates
counterclockwise along with the wheel, the front brake lining shoe 71 and the rear
brake lining shoe 72 are located at both sides of the brake disc 11 in a pressure fiwe
manner. At this moment, since the return spring 95 is biased between the hole 41 of
the second arc-shaped track 40 of the base assembly G and the anti-collision piece
631 of the sliding assembly H, the motionless base assembly G enables the sliding
assembly H to be pushed by the return spring 95 to the lowest portion of the arc-
shaped track. Accordingly, the two opposite abutting blocks 67 of the sliding
assembly H are also located at the lowest portion of the arc-shaped track, and push the
lower end of the control rod 52 of the control valve assembly 50 upward. Since the
control rod 52 moves with respect to the control groove 51 of the control valve
assembly 50, the control passage 524 of the control rod 52 will be aligned to the first
oil hole 527, and the second oil hole 528 and the second oil ring 523 will exactly be
aligned to the oil feeding hole 551. As a result, the oil W from the oil feeding hole
551 will flow to the oil chamber 21 via the second oil ring 523, the second oil hole
528, the control passage 524, the first oil hole 527, the first oil ring 522 and the main
passage 54. However, before the oil W pressure increases, the piston 22 will not be
driven by any oil pressure from the oil chamber 21.
On the other hand, the sliding assembly H doesn't move relative to the base assembly
G, therefore, the front surface of the front brake lining shoe 71 is not pressed against
the steel balls 26. At this moment, the brake lining assembly 70 doesn't clamp the
brake disc 11, and the annular neck portion 529 of the control rod 52 is located below
the pressure relief steel ball 531 of the pressure relief valve 53. Therefore, the wheel
can rotate freely without any resistance.
When the hydraulic disc brake device is activated at a relatively high speed, as both
shown in Figs. 4 and 5, the brake disc 11 still rotates coimterclockwise, at this
moment, the oil W increases in pressure and flows from the oil feeding hole 551 to

the oil chamber 21 via the second oil ring 523, the second oil hole 528, the control
passage 524, the first oil hole 527, the first oil ring 522 and the main passage 54 (as
indicated by the arrow). Meanwhile, the piston 22 of the pressing assembly 20 is
moved by the oil pressure firom the oil chamber 21, pushing the front brake lining
shoe 71 toward the rear brake lining shoe 72, as a result, the brake disc 11 is clamped
firmly by the front and second brake lining shoes 71 and 72, causing an emergency
braking action.
After that, as shown in Fig. 5, at the instant the braking action is initiated, the front
and second brake lining shoes 71 and 72 absorb a lot of counterclockwise stress from
the brake disc 11, generating a very large counterclockwise sfress toward the center of
the brake disc 11. Since the sliding assembly H is slideably disposed in the first and
second arc-shaped tracks 30 and 40 of the base assembly G, the first and second arc-
shaped tracks 30 and 40 are located opposite the center of the brake disc 11, plus the
inertial force produced by an emergency of a high speed vehicle is larger than the
critical value of the elastic force of the return spring 95 of the spring assembly S. The
emergency-brake ca\ised sfress will push the sliding assembly H to slide
counterclockwise while compressing the return spring 95 (as shown in Fig, 5).
At the same time, the coimterclockwise motion of the slide assembly H causes a
displacement of the slide assembly H relative to the base assembly G, and the abutting
blocks 67 of the sliding assembly H push the confrol rod 52 of the confrol valve
assembly 50 to move, so that the confrol groove 51 of tiie confrol valve assembly 50
changes with the upward movement of the confrol rod 52, and the first and second oil
rings 522 and 523 are not aligned with the main passage 54 and the auxiliary passage
55 anymore. Therefore, the oil W stops flowing into the oil chamber 21. At this
moment, the confrol rod 52 of the confrol valve assembly 50 moves upward,
therefore, the annular neck portion 529 of the confrol rod 52 moves upward to a
position aligned with the pressure relief steel ball 531. Under the effect of the pushing
force of the spring 533 and the oil pressure of the oil chamber 21, the pin 532 pushes
the pressure relief steel ball 531 into the annular neck portion 529 of the confrol rod
52, and as a result, a pressure relief oil space B appears at another end of the pin 532
facing the oil chamber 21. At this moment, the oil W will be decompressed instantly
after flowing into the pressure relief oil space B, so that the piston 22 of the pressing

device 20 reduces its pushing force on the front brake lining shoe 71, and accordingly,
the brake lining assembly 70 relieves its clamping force against the brake disc 11. At
this moment, the brake-caused counterclockwise stress disappears from the sliding
assembly H, and the return spring 95 pushes the sliding assembly H back to its
original position. Meanwhile, the sliding assembly H rotates about the base assembly
G. The aimular neck portion 529 of the control rod 52 moves downward (to disengage
from the pressure relief steel ball 531 again), the pressure relief steel ball 531 pushes
the pin 532 and the spring 533 backward, so that the pressure relief oil space B
disappears. Meanwhile, the control groove 51 of the control valve assembly 50
changes with the downward movement of the confrol rod 52, and the first and second
oil rings 522 and 523 are aligned with the main passage 54 and the auxiliary passage
55 again. Therefore, the oil W flows into the oil chamber 21 again (the pressure
thereof increases again), and the brake lining assembly 70 instantly clamps the brake
disc 11 again. Such instant clamping and instant relief actions will occur repeatedly,
preventing the brake disc from being clamped too tight (antilock effect).
It is to be noted that a plurality of anti-collision structures are provided on the sliding
assembly H and opposite the base assembly G, wear-resistance structures are arranged
at the positions where the friction frequently occurs, and the present invention is also
provided with a plurality of position adjustment structures.
Referring then to Figs. 6 and 7, aiming at the safety operation, the present invention is
particularly provided with the safety rod 90, the safety spring 92 and the support
bracket 93. If the return spring 95 is broken (as shown in Fig. 6), the support bracket
93 will not be pushed by the return spring 95 anymore but will be subjected to the
pushing force of the safety spring 92. At this moment, the support bracket 93 will be
deformed or will move downward, and the safety rod 90 will lose its supporting force
since it is riveted to the support bracket 93. As a result, the end of the safety rod 90
doesn't seal the safety oil passage 43 of the second arc-shaped frack 40 anymore.
Meanwhile, the oil W from the oil feeding hole 551 flows into the safety oil passage
43 via the second oil ring 523 of the control valve assembly 50, and constantly
increases the pressure of the oil chamber 21. Although the control rod 52 cooperates
with the pressure relief steel ball 531 to produce a pressure relief oil space B, the oil
from the safety oil passage 43 can still enable the brake lining assembly 70 to keep
firmly pressing against the brake disc 11. Therefore, the emergency brake effect (only

the antilock effect is lost) can still be ensured even if the return spring 95 is broken.
Furthermore, if the return spring 95 fatigues, the safety rod 90, the safety spring 92
and the support bracket 93 can still produce the effect of emergency brake.
Referring to Figs. 8 and 9, which show a second embodiment. In this embodiment,
there are two sets of oil chambers 21, pistons 22 and steel-ball positioning discs 25,
and each set includes the oil seals 23, 23a, 24, 24a, steel-ball positioning discs 25,
25a, a plurality of steel balls 26, 26a, and pistons 22, 22a slideably sealed in two oil
chambers 21, 21a. The two oil chambers 21 are in commimication with each other via
a main passage 54. An exhaust valve 27 is arranged beside the oil chamber 21, and a
safety oil passage 43 is formed beside the oil chamber 21a. By using the double
pressing devices 20, the resultant braking force will be more strong, and the antilock
effect will be better.
Fig. 10 shows a third embodiment of the present invention, this embodiment is
additionally provided with a main cylinder C3 and an elastic oil-storage cylinder C31.
The seat CI is installed on the wheel carrier 10 and serves to cooperate with the
moveable base assembly C2. The status of the hydraulic disc brake device before
braking action is shown in Figs. 11-14, the status of the hydraulic disc brake device
during braking action is shown in Figs. 15-18, and the status of tiie hydraulic disc
brake device during antilock action is shown in Figs. 19-21.
The seat CI is fixed onto the wheel carrier 10, a L-shaped stop board CI 1 is riveted to
either side of the seat CI, and a space is defined between the two L-shaped stop
boards CI 1. The two L-shaped stop boards CI 1 are located in the arc-shaped route of
the wheel axis. Two sliding members CI2 with opening facing each other are
disposed in the arc-shaped route of the wheel axis, and each of the sliding members
C12 is a structure with one end closed and with an interior receiving space.
The base assembly C2 includes a pressing device C21, a first arc-shaped track C22, a
second arc-shaped track C23, a control valve assembly C24, a spring assembly C25,
the main cylinder C3 and the elastic oil-storage cylinder C31.
The spring assembly C25 is confined in the first arc-shaped track C22 by the sliding
assembly CI2, and includes a safety rod, two seal rings, a safety spring, a support
bracket, a washer and a return spring. One end of the return spring cooperating with

the washer and the support bracket is pressed against the bottom edge of the first arc-
shaped track, and another end of the return spring is pressed against the sliding
members CI 2 of the seat CI. The safety spring is restricted in the support bracket and
the return spring, and the safety rod is riveted to the support bracket.
The pressing device C21 includes a piston C211, and a plurality of oil seals C212.
Since the pressing device C21 moves along with the base assembly C2 and the
braking lining assembly C26, it doesn't need the steel balls and the steel-ball
positioning disc, and it can use the conventional pressing device to cooperate with the
brake lining assembly C26, and the brake lining assembly C26 is pressed to clamp the
brake disc 11.
The first and second arc-shaped tracks C22 and C23 are also provided with the wear-
resistance covers C221, C231, the sling members C12 are slideably installed on the
first and second arc-shaped tracks C22 and C23. An antic-collision cushion C232 is
disposed at the end of the second arc-shaped track C23, and the first arc-shaped track
C22 is interiorly formed with safety oil passage. The end of the safety rod of the
spring assembly C25 is pushed by the return spring to close the safety oil passage.
The assembly, function and effect of the control valve assembly C24 are similar to the
previous embodiment, and the only difference is that the position and the structure of
the oil route are changed appropriately.
It is to be noted that the main cylinder C3 and the elastic oil-storage cylinder C31 are
installed on the base assembly C2 directly. The main cylinder C3 utilizes a steel cord
C32 to drive the main piston C33, so as to push the oil into the oil chamber. A
pushing spring C34, an O-shaped ring C36, and a piston C35 are sealed in the elastic
oil-storage cylinder C31 by a cover C37. The pushing spring C34 pvishes the piston
C35 to move, so as to push the oil into the main cylinder C3, and the oil pressure of
the main cylinder C3 is directly connected to the control valve assembly C24.
In this embodiment, the seat CI is mounted on the wheel carrier 10.
The main cylinder can also be mounted on the handlebar.

I CLAIM:
1. A hydrauhc disc brake device, which is mounted on a wheel carrier (10) of a vehicle
for brake by a change of a hydraulic pressure, comprising:
a base assembly(G), which is mounted on the vehicle, including a pressing device(20)
having an oil chamber(21);
a sliding assembly(H) provided on the base assembly(G) for movement along a
predetermined arched path;
a return spring(95) disposed between the base assembly(G) and the sliding assembly(H)
that a relative movement of the base assembly(G) and the sliding assembly(H) causes a
compression of the return spring(95);
a brake lining assembly(70) including a front brake lining shoe(71) and a rear brake
lining shoe(72) for clamping a brake disc(l 1) of a wheel of the vehicle by a change of a
hydraulic pressure; and
a control valve assembly(50), which controls the hydraulic pressure, including a control
groove(51), a control rod(52), a relief valve(53), a main passage(54), and a pressure relief
space(56), wherein the control rod(52) passes through the control groove(51), and the
main passage(54) communicates the control groove(51) and the oil chamber(21), and the
relief valve(53) is received in the pressure relief space(56) for free movement, and the
pressure relief space(56) communicates the control groove(51) and the oil chamber(21)
also, and when the front brake lining shoe(71) and the rear brake lining shoe(72) of the
brake lining assembly(70) clamp the brake disc(ll), an inertia of the wheel is exerted on
the control valve assembly(50) to move the sliding assembly(H) along the predetermined
arched path relative to the base assembly(G) and to compress the return spring(95), and
the sliding assembly(H) shifts the control rod(52) in the same time to cut off the main
passage(54) that the control valve assembly(50) stops the hydrauhc pressure and forms a
pressure rehef oil space(B) between the relief valve(53) and the oil chamber(2l) to drive
the brake lining assembly(70) unclamping the brake disc(ll), and the return spring(95)
returns the shding assembly(H) to close the pressure relief oil space(B), and then the
control rod(52) is shifted reversely to open the main passage(54), and the control valve
assembly(50) increases the hydraulic pressure to drive the brake lining assembly(70)

clampmg the brake disc( 11);
whereby the change of the hydraulic pressxire controls a reciprocation of the relief
valve(53) of the control valve assenibly(50) to open or close the pressure rehef oil
space(B) that the brake lining assembly(70) may clamp and unclamp the brake disc(l 1).
2. The hydraulic disc brake device as claimed in claim 1, wherein the base assembly(G)
includes a first arc-shaped track(30) and a second arc-shaped track(40), both of which
have a center of curvature at a center of the brake disc(ll), and the control assembly(50)
is disposed in the base assembly(G), and the sliding assembly(H) is slid along the first
arc-shaped track(30) and second arc-shaped track(40) of the base assembly(G).
3. The hydraulic disc brake device as claimed in claim 2, wherein the sliding
assembly(H) includes a seat(60) having a brake space(66) to receive the brake disc(ll)
and the brake lining assembly(70) therein and a sliding device(80) disposed on the
seat(60) to provide the first arc-shaped track(30) and the second arc-shaped track(40)
thereon.
4. The hydraulic disc brake device as claimed in claim 3, wherein the base assembly(G) is
provided with a flange(Gl), and the pressing device(20) includes a piston(22) sealed in
the oil chamber(21) for fi-ee movement, in which oil(W) is received to press the piston;
the second arc-shaped track(40) has a hole(41) along an elongated direction thereof and a
safety oil passage(43) formed on a bottom of the hole(41) to be communicated with the
oil chamber(21), and the seat(60) of the sliding assembly(H) has an elliptical sUding
hole(64) at a center thereof for passage of the piston(22) of the pressing device(20) and
the flange(Gl) of the base assembly(G); and
a brake-mounting portion(65) is protruded out of the elliptical sliding hole(64) of the
seat(60), and the brake space(66) is formed between the brake-mounting portion(65) and
the elliptical sliding hole(64).
5. The hydraulic disc brake device as claimed in claim 3, wherein the seat(60) of the
sliding assembly(H) further includes a stop portion(63) associated with the second arc-

shaped track(40) of the base assembly(G), and the return spring(95) biases the bottom of
the hole(41) of the second arc-shaped track(40) of the base assembly(G) and the stop
portion(63) of the sHding assembly(H).
6. The hydraulic disc brake device as claimed in claim 4, wherein the pressing device(20)
includes a plurality of oil seals(23,24), a steel-ball positioning disc(25), and a plurality of
steel balls(26), and the piston(22) is moveably restricted in the oil chamber(21) by the oil
seals(23,24) to position the steel-ball positioning disc(25), and the steel balls(26) are
positioned between the steel-ball positioning disc(25) and the piston(22), and the steel-
ball positioning disc(25) has a plurality of through holes(252) that each of the steel balls
has a portion protruded out of the steel-ball positioning disc(25) via the through
holes(252) respectively, and the front brake lining shoe(71) and the rear brake lining
shoe(72) of the brake lining assembly(70) are parallel and provided on the seat(60) that a
front surface of the front brake lining shoe(71) touches the steel balls(26) of the steel-ball
positioning disc(25) of the pressing device(20) for a smooth slide.
7. The hydraulic disc brake device as claimed in claim 5, wherein:
the control valve(51) of the control valve assembly(50) is located beside the oil
chamber(21) of the pressing device(20) and is provided with two guide covers(511), each
of which has a central hole(513), and the control rod(52) has opposite ends passing
through the center hole(513) of the guide cover(511);
the reUef valve(53) includes a pressure relief steel ball(531), a pin(532) and a spring(533)
disposed in the pressure relief space(56), and an auxiliary passage(55), wherein the
pin(532) is biased by the spring(533), and the pressure relief steel ball(531) is received in
the control groove(51), and the pin(532) is sealed between the oil chamber(21) and the
confrol groove(51) for free sUde, and the auxiUary passage(55) is communicated with the
safety oil passage(43) of the second arc-shaped frack(40); and
a first oil ring(522) and a second oil ring(523) are positioned in a mid section of the
confrol groove(51), wherein the first oil ring(522) is associated with the main passage(54)
and the second oil ring(523) is associated with the auxiliary passage(55), and the confrol
rod(52) is inserted into the confrol groove(51)to form a confrol passage(524)having a first

oil hole(527) associated with the first oil ring(522) and a second oil hole(528) associated
with the second oil ring(523), and the control rod(52) has an annular neck portion(529)
associated with the pressure relief space(56) that when the pressure reUef steel ball(531)
of the reUef valve(53) enters the annular neck portion(529), the pressure reUef oil
space(B) is exposed at an end of the pin(532) opposite the pressure reUef steel ball(531).
8. The hydraulic disc brake device as claimed in claim 5, further comprising a spring
assembly(S), which is confined in the hole(41) of the second arc-shaped track(40) by the
stop portion(63) of the sliding assembly(H), including a safety rod(90), a safety
spring(92), a support bracket(93), and the return spring(95), wherein the return spring(95)
has an end cooperated with the support bracket(93) to press the bottom of the hole(41) of
the second arc-shaped track(40) and an opposite end pressing the stop portion(63) of the
sUding assembly(H), and the safety spring(92) is restricted in the support bracket(93), in
which the safety rod(90) is received, whereby the return spring(95) biases the safety
rod(90) to seal the oil passage(43) of the second arc-shaped track(40).
9. A hydraulic disc brake device providing a brake by a change of a hydraulic pressure,
comprising:
a seat(Cl) mounted on a wheel carriage(10) of a vehicle;
a base assembly(C2) moved along a predetermined arched path relative to the seat(Cl);
a return spring(95) disposed between the seat(Cl) and the base assembly(C2) that a
relative movement of the seat(Cl) and the base assembly(C2) causes a compression of
the return spring(95);
a brake lining assembly(C26) including a fi-ont brake lining shoe(71) and a rear brake
lining shoe(72) for clamping a brake disc(ll) of a wheel of the vehicle by a change of a
hydrauHc pressure; and
a control valve assembly(C24), which controls the hydraulic pressure, including a control
groove(C241), a control rod(C242), a relief valve(C243), a main passage(C244), and a
pressure reUef space(C246), wherein the control rod(C242) passes through the control
groove(C241), and the main passage(C244) communicates the control groove(C241) and
an oil chamber(21), and the relief valve(C243) is received in the pressure relief

space(C246) for free movement, and the pressure relief space(C246) communicates the
control groove(C241) and the oil chamber(21) also, and when the front brake lining
shoe(71) and the rear brake lining shoe(72) of the brake lining assembly(C26) unclamp
the brake disc(ll), an inertia of the wheel is exerted on the control valve assembly(C24)
to move the base assembly(C2) along the predetermined arched path relative to the
seat(Cl) and to compress the return spring(95), and the base assembly(C2) shifts the
control rod(C242) in the same time to cut off the main passage(C244) that the control
valve assembly(C24) stops the hydraulic pressure and forms a pressure relief oil space(B)
between the relief valve(C243) and the oil chamber(21) to drive the brake lining
assembly(C26) unclamping the brake disc(ll), and the return spring(95) returns the base
assembly(C2) to close the pressure relief oil space(B), and then the control rod(C242) is
shifted reversely to open the main passage(C244), and the control valve(C24) assembly
increases the hydraulic pressure to drive the brake lining assembly(C26) clamping the
brake disc( 11);
whereby the change of the hydraulic pressure controls a reciprocation of the relief
valve(C243) of the control valve assembly(C24) to open or close the pressxire relief oil
space(B) that the brake lining assembly(C26) may clamp and unclamp the brake disc(l 1).
10. The hydraulic disc brake device as claimed in claim 9, wherein the base
assembly(C2) includes a pressing device(C21) pressed by a pressure of a main
cylinder(C3), a first arc-shaped track(C22), which is disposed in the seat(Cl) for free
slide, provided with a spring assembly(C25) and a safety oil passage(C222), and a second
arc-shaped track(C23) disposed in the seat(Cl) for free slide.
11. The hydraulic disc brake device as claimed in claim 9, wherein the confrol
groove(C241) of the control valve assembly(C24) is located beside the oil chamber(21)
of the pressing device(C21) and is provided with two guide covers(511), each of which
has a central hole(513), and the control rod(C242) has opposite ends passing through the
cenfral holes(513) of the guide covers(511), and the confrol groove(C241) is
communicated with the oil chamber(21) of the pressing device(C21) through the main
passage(C244) and the pressure reUef space(C246), and an auxiliary passage(C245) is

communicated with the safety oil passage(C222) of the first arc-shaped track(C22), and
an oil feeding hole(551) is located at an opposite end of the auxiliary passage(C245); and
a first oil ring(522) and a second oil ring(523) are positioned in a mid section of the
control gj:oove(C241), wherein the first oil ring(522) is associated with the main
passage(C244) and the second oil ring(523) is associated with the auxiliary
passage(C245), and the control rod(C242) has an annular neck portion(529) associated
with the pressure relief space(C246), and the pressure relief valve(C243) includes at least
one pressure rehef steel ball(531) and a pin(532), when the pressure rehef steel ball(531)
of the relief valve(C243) enters the annular neck portion(529), the pressure relief oil
space(B) is exposed at an end of the pin(532) opposite the pressure relief steel ball(531).
12. The hydraulic disc brake device as claimed in claim 10, wherein the pressing
device(C21) includes a piston(C211) moveably sealed in the oil chamber(21) to be
moved by an oil pressure in the oil chamber(21), and the first arc-shaped track(C22) is
provided with a hole(41) having the safety oil passage(C222) on the bottom of the
hole(41) in communication with the oil chamber(21) of the pressing device(C21);
the sUding assembly(Cl) is installed on the wheel carriage(10); and the fi-ont brake lining
shoe(71) and the rear brake lining shoe(72) of the brake lining assembly(C26) are
provided on the seat(C2) in a parallel manner, wherein a fi-ont surface of the fi-ont brake
lining shoe(71) is pressed by the piston(C211) of the pressing device(C21).
13. The hydraulic disc brake device as claimed in claim 10, fiirther comprising a spring
assembly(C25), which is confined in the hole(41) of the first arc-shaped track(C22) by
the shding member(C12) of the seat(Cl), including the return spring(95).
14. The hydraulic disc brake device as claimed in claim 11, wherein the relief
valve(C243) includes a spring(533) disposed in the pressure relief space(C246) to bias
the pin(532), and the pressure relief steel ball(531) is received in the control
groove(C241), and the pin(532) is slideably sealed between the oil chamber(21) and the
control groove(C241).

15. The hydraulic disc brake device as claimed in claim 13, wherein the spring
assembly(C25) includes a safety rod(90), a safety spring(92), a support bracket(93), and
the return spring(95), wherein the return spring(95) has an end cooperated with the
support bracket(93) to press the bottom of the hole(41) of the first arc-shaped track(C22),
and an opposite end thereof pressing the sliding member(C12) of the seat(Cl), and the
safety spring(92) is restricted in the support bracket(93), in which the safety rod(90) is
provided, and the safety rod(90) is moved by the retum spring(95) so as to close the
safety oil passage(C222) of the second arc-shaped track(C23).

Documents:

2288-chenp-2006 abstract duplicate.pdf

2288-chenp-2006 claims duplicate.pdf

2288-chenp-2006 correspondence-others.pdf

2288-chenp-2006 correspondence-po.pdf

2288-chenp-2006 description (compelet) duplicate.pdf

2288-chenp-2006 drawings duplicate.pdf

2288-chenp-2006 form-1.pdf

2288-chenp-2006 form-18.pdf

2288-chenp-2006 form-26.pdf

2288-chenp-2006 form-3.pdf

2288-chenp-2006 form-5.pdf

2288-chenp-2006 petition.pdf

2288-CHENP-2006 CORRESPONDENCE OTHERS.pdf

2288-CHENP-2006 FORM 3.pdf

2288-CHENP-2006 POWER OF ATTORNEY.pdf

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Patent Number

230263

Indian Patent Application Number

2288/CHENP/2006

PG Journal Number

13/2009

Publication Date

27-Mar-2009

Grant Date

25-Feb-2009

Date of Filing

23-Jun-2006

Name of Patentee

TAN-CHENG HUANG

Applicant Address

6FL., No.2-1, Swei St., Taichung, Taiwan, R.O.C.,

Inventors:

#	Inventor's Name	Inventor's Address
1	TAN-CHENG HUANG	6FL., No.2-1, Swei St., Taichung, Taiwan, R.O.C.,

PCT International Classification Number

B60T8/52

PCT International Application Number

PCT/CN2003/001131

PCT International Filing date

2003-12-26

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1			NA