JP5141391B2 - Hydraulic brake device - Google Patents

Description

  The present invention includes a hydraulic brake device for a vehicle, in particular, an auxiliary hydraulic pressure source including a power-driven pump, and a pressure regulating valve that regulates and outputs the hydraulic pressure of the auxiliary hydraulic pressure source, and the output fluid of the pressure regulating valve The present invention relates to a hydraulic brake device of a type that generates a braking force by supplying a pressure and an output hydraulic pressure of a master cylinder to a wheel cylinder.

  A hydraulic brake device for a vehicle provided with the above-mentioned auxiliary hydraulic pressure source and a pressure regulating valve in addition to the master cylinder is disclosed, for example, in Patent Document 1 below. In the hydraulic brake device of Patent Document 1, the hydraulic pressure generated in the pressure chamber of the master cylinder is supplied to the wheel cylinder of the first system of the vehicle, and the hydraulic pressure of the auxiliary hydraulic pressure source is controlled by the pressure regulating valve. Is adjusted to a value corresponding to the output hydraulic pressure and supplied to the wheel cylinder of the second system.

In the hydraulic brake device disclosed in Patent Document 1, the master cylinder piston that pressurizes the brake fluid in the pressure chamber includes a first piston coupled to the brake operation member, and an axial slide on the outer periphery of the first piston. The second piston is configured to be fitted, and when the hydraulic pressure is normally supplied from the pressure regulating valve, the second piston receives the output hydraulic pressure of the pressure regulating valve at the rear end to generate a thrust, The force acts as a driving assist force for the master cylinder piston. Moreover, the output hydraulic pressure of the pressure regulating valve is supplied to the wheel cylinder via an electromagnetic valve that controls the hydraulic pressure.
JP-A-9-315288

  In the case of the hydraulic brake device having the structure described above, the output hydraulic pressure of the master cylinder is determined by the operation stroke of the brake operation member without being affected by the operation speed of the brake operation member. However, in the pressure regulating valve, the control piston that has received the output hydraulic pressure of the master cylinder moves the spool to a position corresponding to the output hydraulic pressure, and adjusts and outputs the hydraulic pressure supplied from the auxiliary hydraulic pressure source by the spool movement. In the system where the pressure regulating valve is installed when the operation speed of the brake operation member is high, the response delay occurs due to the influence of the internal throttling effect such as the solenoid valve for hydraulic pressure control on its operation. There is a tendency that the operation stroke of the brake operation member with respect to the wheel cylinder pressure becomes longer due to the delay in increasing the cylinder pressure.

  This means that the hydraulic pressure balance between the system that introduces the output hydraulic pressure of the master cylinder and the system that introduces the output hydraulic pressure of the pressure regulating valve varies depending on the operating speed of the brake operating member (the brake pedal depression speed). For example, the brake operation feeling and effectiveness change depending on how the brake pedal is depressed. As for the operation feeling, the driver feels a feeling of stepping and aftereffect in the initial stage of operation, and the braking effect is also deteriorated due to the delay in increasing the pressure of the wheel cylinder in one system.

  As a countermeasure, it is conceivable to increase the output hydraulic pressure of the pressure regulating valve with respect to the output hydraulic pressure of the master cylinder. However, if this method is used, the wall thickness of the casing (cylinder body) increases to ensure pressure resistance. The housing tends to be large.

  The present invention simplifies the operation stroke from the start of operation of the brake operation member to the rise of the wheel cylinder pressure in the hydraulic brake device described above in order to improve the response and effectiveness of the brake and improve the operation feeling. The problem is to reduce the cost by a method that is inexpensive and can avoid an increase in size.

  In order to solve the above problems, in the present invention, the brake fluid in the pressure chamber is pressurized by the master cylinder piston to generate a fluid pressure corresponding to the operation stroke of the brake operation member, and the fluid pressure is generated in the first system of the vehicle. A master cylinder that outputs to the wheel cylinder of the vehicle, and a pressure regulating valve that regulates the hydraulic pressure of the auxiliary hydraulic pressure source to a value corresponding to the hydraulic pressure of the pressure chamber and outputs the pressure to the wheel cylinder of the second system of the vehicle The equipped hydraulic brake system was improved as follows. Specifically, a passage through which the master cylinder piston communicates between the pressure chamber and a reservoir storing brake fluid, and an opening / closing valve that closes when the piston advances and opens when the piston returns. In addition, a throttle and a check valve (check valve) that allows only a liquid flow from the reservoir side to the pressure chamber side are provided in parallel in the passage on the reservoir side of the open / close valve. Here, the term “parallel” means that the circuits are parallel, and structurally includes a structure in which a throttle is formed in the valve portion of the check valve.

Preferred embodiments of the hydraulic brake device are listed below.
(1) The throttle and the check valve seal the outer periphery on the rear end side of the master cylinder piston and the rear end side of the master cylinder piston from the first seal portion that seals the outer periphery on the front end side of the master cylinder piston. 2 Disposed at the front end side of the master cylinder piston from the seal part.
(2) A first piston connecting the master cylinder piston to the brake operation member, and a liquid-tight and axially slidable fit on the outer periphery of the first piston, and a rear end of the master cylinder piston is output from the pressure regulating valve. It is composed of a second piston that faces a power chamber into which hydraulic pressure is introduced and that engages with the first piston when moving forward.
(3) The passage is composed of a main hole that is opened at the front end of the first piston and is provided at the center of the piston, and a branch hole that extends from the main hole to the outer periphery of the first piston. The first and second pistons communicated with the reservoir via annular liquid chambers provided on the outer circumferences.
(4) A sleeve whose front end is desired for the pressure chamber is liquid-tightly inserted into the main hole, a valve seat formed at the front end of the sleeve, a valve body that is brought into contact with and separated from the valve seat, and a valve body that is closed The on-off valve is configured by combining with an urging means for applying a valve force.
(5) The check valve is arranged behind the sleeve, and the amount of movement of the check valve in the valve opening direction is regulated at the rear end of the sleeve.
(6) The above-described check valve is incorporated in the sleeve.
(7) In addition to the configuration of (6) above, further, a clearance is provided between the outer periphery of the rear portion of the sleeve and the inner peripheral surface of the main hole, and the throttle is configured by the clearance. Also, the sleeve is provided with a radial communication hole that leads from the inside of the sleeve to the gap on the pressure chamber side. (8) The non-return is constituted by a valve seat provided on the inner periphery of the rear portion of the sleeve, a valve body that opens and closes a passage between the valve seat, and a stopper that regulates a movement amount of the valve body in the valve opening direction. Consists of a valve.
(9) The sleeve is composed of a main body part and a cylindrical cap connected to the rear part of the main body part, and the valve seat, valve body, and stopper constituting the check valve are provided inside the cap. thing. (10) The valve body is subjected to movement restriction by the stopper at a position where the valve body has moved to the connection hole setting portion, and the passage of the passage is formed through a gap formed between the communication hole and the valve body at the position. The parts with the valve body in between communicate with each other.
(11) A first branch hole and a second branch hole are provided as the branch holes, respectively, and the restriction is installed in the first branch hole and the check valve is installed in the second branch hole.
(12) The throttle is formed on a valve body or a valve seat of the check valve.
(13) The valve body of the check valve has a bottomed cylindrical shape, a through hole is provided in the bottom of the valve body, and the throttling is configured by the through hole.
(14) A groove is provided on the seat surface of the valve body of the check valve, and the throttle is constituted by the groove.
(15) An outer diameter of the valve body of the check valve is made smaller than an inner diameter of the valve body incorporating portion, and a sliding guide guided on the inner peripheral surface of the valve body incorporating portion is circumferentially provided on the outer periphery of the valve body A plurality of gaps are provided at intervals, and a passage for passing a liquid flow from the reservoir side to the pressure chamber side is generated between the outer peripheral surface of the valve body, the sliding guide, and the inner peripheral surface of the valve body incorporating portion. thing.

  In the hydraulic brake device to be improved by the present invention, when the brake operating member is operated at a high speed, the pressure of the master cylinder passes through the passage provided in the master cylinder piston until the on-off valve is closed. Brake fluid flows out rapidly from the chamber toward the reservoir. However, in the hydraulic brake device of the present invention, the throttle and the check valve are provided in parallel in the passage provided in the master cylinder piston, and the check valve is closed due to the pressure difference generated in the passage. Therefore, the brake fluid flowing out toward the reservoir inevitably passes through the throttle, and resistance is added to the flow of the brake fluid in the pressure chamber due to the throttle effect at that location, and the hydraulic pressure in the pressure chamber per unit operation stroke increases. . Therefore, the responsiveness of the pressure regulating valve is improved, the invalid stroke of the master cylinder is shortened, and the change in brake feeling due to the fluctuation of the operation speed is suppressed. This eliminates the feeling of empty treading and aftereffect at the initial stage of operation when the operation speed is high.

  Further, in the case of the brake device of the above aspect (2), that is, the hydraulic brake device that can obtain the driving assist force of the master cylinder piston, the master cylinder piston has an advantage of the device by shortening the invalid stroke of the master cylinder. The step-up response is exhibited from the beginning of the brake operation, the braking effect is improved, and the braking stop distance of the vehicle can be shortened.

  Furthermore, the operation stroke until the wheel cylinder pressure rises without increasing the output hydraulic pressure of the pressure regulating valve relative to the output hydraulic pressure of the master cylinder can be shortened, so the casing (cylinder body) can be made thicker. Can be avoided. In addition to this, the master cylinder that employs an on-off valve called a center valve already has a passage and on-off valve that communicates between the pressure chamber and the reservoir, so a throttle and a check valve are added. All that is required is to avoid the complicated structure, large size, and cost increase.

  The actions and effects of the above aspects (1) to (15) will be described in the next section.

Embodiments of the hydraulic brake device according to the present invention will be described below with reference to FIGS. FIG. 1 shows the overall configuration of the first embodiment. In the figure, 1 is a brake operating member (it is a brake pedal), 2 is an input rod, 3 is a cylinder body, 4 is a reservoir, 5 is a hydraulic control unit, and 6 _{-1 to} 6 _-4 are wheels of the vehicle. It is a wheel cylinder attached to.

A master cylinder 7 and a pressure regulating valve 11 are incorporated in a cylinder hole 3a provided in the cylinder body 3 (refer to FIG. 2 simultaneously). The master cylinder 7 has a master cylinder piston 8 and a spring 9 for returning the piston, and the brake fluid in the pressure chamber 10 is pressurized by the master cylinder piston 8 to generate hydraulic pressure. In the illustrated brake system, in normal braking, the hydraulic pressure generated in the pressure chamber 10 is supplied to the wheel cylinders 6 _-1 and 6 _-2 of the first system (for example, front wheels).

Master cylinder piston 8, the first piston 8 _-1 divided axially, axially slidably fitted on the outer periphery of the first piston 8 _-1, and engages the first piston during forward a second piston _8-2 which is adapted to is constituted by, when the fluid pressure normally from the pressure regulating valve 11 to the power chamber 12 is supplied, the second piston 8 _-2 in the power chamber 12 A pressure is applied to the output pressure of the introduced pressure regulating valve at the rear end to generate a thrust, which is used as a driving assist force for the master cylinder piston.

The pressure adjusting valve 11 controls the hydraulic pressure supplied from the auxiliary hydraulic pressure source 15 by the control piston 13 that has received the output hydraulic pressure of the master cylinder 7 (the hydraulic pressure in the pressure chamber 10) to move the spool 14, and outputs the pressure. To do. The spool 14 moves to a position corresponding to the output hydraulic pressure of the master cylinder 7 to open the valve portion, and adjusts the opening degree of the valve portion. As a result, the hydraulic pressure supplied from the auxiliary hydraulic pressure source 15 is adjusted to a value corresponding to the output hydraulic pressure of the master cylinder 7 and output. The output hydraulic pressure of the pressure regulating valve is supplied to the second system wheel cylinders 6 ₋₃ and 6 ₋₄ .

  The illustrated auxiliary hydraulic pressure source 15 is included in the hydraulic pressure control unit 5, and a motor-driven pump including an accumulator is used as the auxiliary hydraulic pressure source 15.

  The master cylinder piston 8 and the pressure regulating valve 11 have the same basic configuration as that disclosed in the above-mentioned Patent Document 1, and therefore detailed description thereof is omitted here.

  In addition to the auxiliary hydraulic pressure source 15, the hydraulic pressure control unit 5 includes a pressurizing solenoid valve (which includes a check valve) 16 and a decompression solenoid valve 17 attached to each wheel cylinder, circuit switching and communication. Although the electromagnetic valves 18 to 20 for switching the state and the like as necessary, the pressure sensor 21 for detecting the hydraulic pressure of each system, the check valve 22 and the like are provided, the illustrated hydraulic pressure control unit 5 is merely an example. Absent. A control unit having a different circuit configuration may be used.

The first piston 8 _-1, a passage 23 communicating between the pressure chamber 10 and the reservoir 4, closed when the passage 23 is the first piston 8 _-1 advances, open when the return opening A valve 24, a throttle 25, and a check valve 26 are provided (see FIGS. 2 and 3 simultaneously).

Passage 23 has a main bore 23a provided in the center portion of the piston is opened to the front end of the first piston 8 _-1 (left end in the drawing. Consider the right end of the rear end. Other components similar), the main is composed of a Edaana 23b from apertures 23a escapes to the outer periphery of the first piston _{8 -1.} Between the outer periphery of the first piston 8 _-1 and the inner periphery of the second piston _8-2, and between the inner periphery of the second piston 8 _-2 periphery and the cylinder bore 3a, the axial ends There first seal portion S1 and the second seal portion S2 and the third seal portion S3 and the fourth seal portion S4 annular fluid chamber ₂₇ -1 sealed by, and _{27 -2} provided, the annular fluid chamber 27 _{- 1} , the branch hole 23b is opened, and the passage 23 communicates with the reservoir 4 via the two annular liquid chambers 27 _-1 and 27 _-2 .

The main bore 23a provided in the first piston 8 _-1, 2, as shown in FIG. 3, the sleeve 28 which has desired a front end to the pressure chamber 10 is inserted in a liquid-tight manner, the sleeve 28 The on-off valve 24 is constituted by a valve seat 24a formed at the front end, a valve body 24b that contacts and separates from the valve seat 24a, and an urging means (spring) 24c that presses the valve body 24b against the valve seat 24a. Yes. One end of the biasing means 24c is supported by a retainer 29 attached to the first piston _{8 -1} (Figure 2). The valve body 24b is provided with an integral rod 24d, and the retainer 30 (see FIG. 5) is attached to the control piston 13 via the rod 24d at a position where the master cylinder piston 8 and the control piston 13 are at the return end point. 2), the valve is held in the open position. Δ in FIG. 3 (a) is an idle stroke of the master cylinder 7, and when the master cylinder piston 8 moves forward to a position where the idle stroke becomes zero (pressed to the left in the figure), the open / close valve 24 is closed and the pressure is increased. The communication between the chamber 10 and the reservoir 4 is blocked.

  A gap is provided between the outer periphery of the rear portion of the sleeve 28 and the inner peripheral surface of the main hole 23a, and the diaphragm 25 is constituted by the gap having a small cross-sectional area. A check valve 26 is provided inside the sleeve 28. The check valve 26 includes a valve seat 26a provided on the inner periphery of the sleeve 28 and a valve body 26b that opens and closes a passage formed between the valve seat (the floating valve body shown in the drawing). And a stopper 26c that restricts the amount of movement of the valve body in the valve opening direction, and allows only liquid flow from the reservoir 4 side to the pressure chamber 10 side. On the pressure chamber 10 side of the check valve 26, a radial communication hole 31 is provided in the sleeve 28 that communicates from the inside of the sleeve 28 to the gap (throttle 25). FIG. 8 shows a circuit configuration equivalent to FIG. 3, and as can be seen from FIG. 8, the throttle 25 and the check valve 26 are arranged in parallel.

  When the brake operating member 1 (FIG. 1) is rapidly operated, the hydraulic brake device of the first embodiment configured as described above receives the hydraulic pressure generated in the pressure chamber 10 when the brake operating member 1 (FIG. 1) is rapidly operated. As shown in b), the check valve 26 is closed, so that the brake fluid flowing from the pressure chamber 10 toward the reservoir 4 passes through the restrictor 25 and receives outflow resistance there, and a certain amount of operation of the brake operation member is performed. The hydraulic pressure in the pressure chamber 10 with respect to the stroke is higher than that without a throttle. This speeds up the operation of the pressure regulator, shortens the invalid stroke of the master cylinder, suppresses changes in brake feeling due to fluctuations in the operating speed, and feels when the operating speed is high and when the operating speed is high. The feeling disappears.

  In addition, in the hydraulic brake device that can obtain the driving assist force of the master cylinder piston by shortening the invalid stroke of the master cylinder, excellent boosting response is exhibited from the beginning of the brake operation, and the braking effect is improved. The braking stop distance of the vehicle is shortened.

  Further, when the hydraulic pressure control based on the command from the electronic control device is executed in a state where the driver does not perform the brake operation and the auxiliary hydraulic pressure source 15 sucks the brake fluid from the reservoir 4, FIG. Thus, the check valve 26 is opened, and the brake fluid smoothly flows from the reservoir 4 to the auxiliary hydraulic pressure source 15 via the pressure chamber 10 in a form in which the throttle 25 is bypassed, thereby ensuring a good pressure increase response.

Other effects and advantages are listed below.
(A) The passage 23 is constituted by a main hole 23a and a branch hole 23b provided in the first piston, and via annular liquid chambers 27 _-1 and 27 _-2 provided on the outer circumferences of the first piston and the second piston. The throttle 25 and the check valve 26 are connected to the reservoir 4 so that the inlet side of the cylinder hole 3a from the first seal portion S1 (that is, the rear end side of the master cylinder piston 8) and the cylinder from the second seal portion S2. Since it arrange | positions at the back end side (namely, front end side of master cylinder piston 8) of the hole 3a, the length increase of an apparatus is suppressed.
(B) Since the valve seat 24a is provided on the sleeve 28, the valve seat 24a can be easily processed, and the throttle 25 can be formed by a gap on the outer periphery of the sleeve.
(C) Since the check valve 26 is provided inside the master cylinder piston 8, the annular fluid chambers 27 _-1 and 27 _-2 are provided at the initial stage of the brake operation as compared with the case where the check valve is provided inside the cylinder body 3. The introduced hydraulic pressure is reduced, and the load of the sealing material of the first to fourth seal portions S1 to S4 is reduced. As a result, the durability of the sealing material is improved, and liquid leakage from the first to fourth seal portions S1 to S4 hardly occurs.
(D) Since the check valve 26 and is incorporated into the front end of the sleeve 28, it is possible to assemble the sleeve 28 to the first piston 8 _-1 keep incorporating a check valve 26 in advance in the sleeve 28 As a result, it is possible to simplify the assembly and reduce the labor of the assembly.
Since the (e) stop 25 constituted by the gap of the outer periphery of the sleeve 28, the large diameter of the large diameter and the device of the first piston 8 _-1 is suppressed.
(F) Since the check valve 26 is constituted by the valve seat 26a, the valve body 26b, and the stopper 26c, the check valve 26 can be simplified and downsized, and pre-assembly to the sleeve 28 is also easy. Yes.
(G) Since the movement of the valve body 26b is moved by the stopper 26c at the position where the valve body 26b is moved to the installation portion of the communication hole 31 (see FIG. 3A), the communication hole 31 and the valve body 26b are moved at the movement restriction position. The both side portions sandwiching the valve body of the passage 23 communicate with each other through a gap formed between the two. Therefore, it is not necessary to provide a large gap for the passage of brake fluid between the outer diameter of the valve body 26b and the inner diameter of the sleeve 28, and the effect of avoiding the increase in the diameter of the sleeve 28 is further enhanced.

FIG. 4 shows another example of the throttle 25 and the check valve 26 that characterize the present invention. The sleeve 28 in FIG. 4 includes a main body 28a and a cylindrical cap 28b attached to the rear of the main body, and a valve seat 26a, a valve body 26b, and a stopper 26c are provided inside the cap 28b. With such a structure, the check valve 26 can be unitized in advance and assembled to the main body portion 28a, and the assemblability is further improved. Other configurations are the same as those in FIG. Insert the sleeve 28 in a liquid tight manner to the main bore 23a provided in the first piston 8 _-1, that was built check valve 26 to the rear end of the sleeve 28, the main and rear outer circumference of the diaphragm 25 the sleeve 28 3 is the same as FIG. 3 in that it is configured with a gap provided between the inner peripheral surface of the hole 23a and the above-described effects (simplification of assembly, reduction of labor, avoiding enlargement of the apparatus, etc.). ) Can also be expected.

  5 and 6 show still another example of the throttle 25 and the check valve 26. FIG. The throttle 25 can be formed in the valve body 26 b of the check valve 26. The valve body 26b of the check valve 26 shown in FIG. 6A has a bottomed cylindrical shape, and a through hole is provided at the bottom of the valve body 26b. Moreover, the outer diameter is made smaller than the inner diameter of the valve body incorporating portion of the passage 23. A plurality of sliding guides 32 projecting radially in the outer periphery of the valve body 26b are provided at intervals in the circumferential direction.

The sliding guide 32 is a guide for guiding the valve body 26 b, and slides while being guided by the inner peripheral surface of the valve body incorporating portion of the passage 23.

As shown in FIG. 5, the valve body 26b is disposed behind the sleeve 28, and a seat surface on the outer periphery of the bottom portion (a spherical surface is preferable because it is easy to ensure sealing performance) is provided inside the first piston _8-1. The direction of the liquid flow through the passage 23 is controlled by making contact with the valve seat 26a. As shown in FIG. 5B, a passage 33 is created between the outer peripheral surface of the valve body 26b, the sliding guide 32, and the inner peripheral surface of the passage 23, and the forward direction indicated by the arrow in FIG. The liquid flows through the passage 33 from the reservoir side to the pressure chamber side. Further, as shown in FIG. 5 (a), when the valve body 26b is in contact with the valve seat 26a and the check valve 26 is closed, the through hole provided at the bottom of the valve body 26b functions as the throttle 25. Due to the throttling effect of the pressure, the hydraulic pressure in the pressure chamber per unit operation stroke increases and the responsiveness of the pressure regulating valve improves.

  In the structure of FIG. 5, the rear end (right end in the figure) of the sleeve 28 regulates the amount of movement of the valve body 26b in the valve opening direction. Therefore, there is no need to provide a dedicated stopper, and the structure and processing can be simplified. Further, since the throttling is configured by the through hole provided at the bottom of the valve body 26b, the advantage that the accuracy control of the passage area of the throttling is easier than the structure of FIG. 3 and FIG. The advantage of reducing the weight of the valve body by adopting the valve body 26b. Furthermore, since the cylindrical portion of the valve body 26b receives a liquid flow when the master cylinder is operated, the valve closing operation of the valve body is sensitive. There are also advantages.

FIG. 7 shows an example in which a throttle provided in the valve body of the check valve is formed by a groove. In this example, a groove is provided in the seat surface of the valve body 26b of the check valve 26 (a surface to be brought into contact with the valve seat 26a), and the throttle 25 is configured by the groove. Similar effects can be obtained.
The valve body 26b may be made of either metal or resin. However, in the embodiment in which the groove is formed in the valve body 26b as described above, the throttle can be configured without forming a hole in the valve body. In particular, when the valve body 26b is manufactured by metal pressing, drilling for drilling can be omitted, and productivity is remarkably improved.

  In the case where the throttle 25 is constituted by a groove, the groove may be provided in the valve seat 26a. However, the hole or groove that forms the throttle is more excellent in workability when installed in the valve body 26b.

  Thus, the throttle 25 can be provided on the valve body or the valve seat of the check valve 26, and this structure brings about the effect of downsizing and simplification of the apparatus. In the case where the check valve 26 is provided in the sleeve 28, if the valve body of the check valve is devised so that the posture of the valve body is kept substantially constant in the sleeve 28, the valve body and the valve seat 25 are throttled. Can be formed.

  FIG. 8 is a diagram showing the basic circuit configuration as described above. As shown in FIG. 8, the branch hole 23b of the passage 23 is divided into a first branch hole and a second branch hole. A structure in which 25 is installed in the first branch hole and check valve 26 is installed in the second branch hole is also conceivable. Although the structure as described in FIGS. 3 to 7 is easy to manufacture and downsizing is advantageous in practical use, it is advantageous in practical use. If the throttle 25 and the check valve 26 are provided in parallel, the purpose of shortening the operation stroke until the wheel cylinder pressure rises is achieved.

  Although the groove constituting the throttle can be provided in the valve seat of the check valve, it is advantageous to provide it in the valve body from the viewpoint of workability.

A hydraulic brake device (invention) provided by the first piston 8 25 stop in the passage 23 provided in the _-1 and the check valve 26 in parallel arrangement, check valve is provided with throttle the passage 23 FIG. 9 shows the results of a test for confirming the effect of shortening the stroke performed by mounting a conventional hydraulic brake device (comparative example) that is not installed on an actual vehicle.

  In this test, the relationship between the brake pedal operation stroke and the magnitude of vehicle deceleration until the vehicle was stopped after sudden braking from a predetermined traveling speed was examined. In the figure, I is the measurement data of the invention product and II is the comparison product. As can be seen from the test results, there is a clear difference in the brake pedal operation stroke from the start of operation until the vehicle deceleration reaches a predetermined value X, and the invention product I has a stroke reduction of about 30% compared to the comparison product II. The effect was seen.

  In the above description, the master cylinder piston has been described by taking as an example an apparatus in which the first piston and the second piston are used. However, the scope of application of the present invention is that a single master cylinder piston is used. It extends to a hydraulic brake device composed of a piston.

  In each embodiment, the non-moving valve body that is not urged by the spring is used as the valve body 26b constituting the check valve 26. However, the present invention is not limited to this, and the valve body is made of a spring in order to stably operate the valve body. It may be energized and pressed against the valve seat.

The figure which shows an example of the whole structure of the hydraulic-brake apparatus of this invention Sectional drawing which expands and shows the principal part of the apparatus of FIG. (A): Cross-sectional view showing the inner throttle and check valve in the master cylinder piston of FIG. 2 further enlarged, (b): Cross-sectional view showing a state where the check valve is closed (A): Cross-sectional view showing another example of restriction and check valve inside master cylinder piston, (b): Cross-sectional view showing a state where the check valve is closed It is further another example of a throttle and a check valve, (a) is a sectional view in the state where the check valve was closed, (b) is a sectional view in the state where the valve was opened (A): Side view showing the valve body of the check valve in FIG. 5, (b): Cross-sectional view along line XX in FIG. 5 (a) Sectional drawing which shows the example which formed the aperture_diaphragm | restriction in the seat surface of the valve body of a non-return valve Sectional drawing which shows the further another example of the throttle and check valve inside the master cylinder piston The figure which shows the confirmation test result of the stroke shortening effect of the brake operation member

Explanation of symbols

First brake operating member 2 input rod 3 cylinder body 3a cylinder bore 4 reservoir 5 liquid pressure control unit ₆ -1 _{to 6 -4} wheel cylinders 7 master cylinder 8 master cylinder piston _{8 -1} first piston _8-2 the second piston 9 Spring 10 Pressure chamber 11 Pressure regulating valve 12 Power chamber 13 Control piston 14 Spool 15 Auxiliary hydraulic pressure source 16 Pressurizing solenoid valve 17 Depressurizing solenoid valve 18-20 Solenoid valve 21 Pressure sensor 22 Check valve 23 Passage 23a Main hole 23b Branch hole 24 on-off valve 24a valve seat 24b the valve element 24c urging means 24d rod 25 stop 26 check valve 26a valve seat 26b the valve element 26c stopper ₂₇ -1, _{27 -2} annular fluid chamber 28 the sleeve 28a main body portion 28b cap 29 Retainer 31 Communication hole 32 Sliding guide 33 Passages S1 to S4 First to fourth seal portions

Claims (17)

The brake fluid in the pressure chamber (10) is pressurized by the master cylinder piston (8) to generate a hydraulic pressure corresponding to the operating stroke of the brake operating member (1), and the hydraulic pressure is used for the first system wheel cylinder of the vehicle. To the second cylinder of the vehicle by adjusting the hydraulic pressure of the master cylinder (7) and the auxiliary hydraulic pressure source (15) to a value corresponding to the hydraulic pressure of the pressure chamber (10). In the hydraulic brake device provided with the pressure regulating valve (11) for outputting
The master cylinder piston (8)
A passage (23) communicating between the pressure chamber (10) and a reservoir (4) storing brake fluid, and the passage (23) are closed and returned when the master cylinder piston (8) advances. And an opening / closing valve (24) that is opened when the throttle valve (24) is located closer to the reservoir (4) than the opening / closing valve (24), and the liquid flow from the reservoir side to the pressure chamber side A hydraulic brake device characterized in that a check valve (26) that allows only the pressure is provided in parallel.   The throttle (25) and the check valve (26) are connected to the master cylinder piston (8) at the rear end side of the master cylinder piston (8) with respect to the front end side outer periphery of the master cylinder piston (8). 8) The hydraulic brake device according to claim 1, wherein the hydraulic brake device is arranged on a front end side of the master cylinder piston (8) with respect to a seal portion that seals an outer periphery on the rear end side. A first piston (8 _-1 ) that connects the master cylinder piston (8) to the brake operation member (1), and a liquid-tight and axial direction on the outer periphery of the first piston (8 _-1 ) A slidably fitted rear end faces the power chamber (12) into which the output hydraulic pressure of the pressure regulating valve (11) is introduced, and is engaged with the first piston (8 _-1 ) during advance. The hydraulic brake device according to claim 1 or 2, characterized by comprising two pistons (8 _-2 ). The passage (23) is opened at the front end of the first piston (8 _-1 ), and a main hole (23a) is provided at the center of the piston. The main hole (23a) extends from the first piston ( 8 _-1 ) annular liquid chambers (27 ₋₁ , 27 b) provided on the outer circumferences of the first and second pistons (8 ₋₁ , 8 ₋₂ ), respectively, with branch holes (23 b) extending to the outer periphery. 27. The hydraulic brake device according to claim 3, wherein the hydraulic brake device is communicated with the reservoir ( _27-2 ) via _27-2 ).   A sleeve (28) whose front end is desired for the pressure chamber (10) is liquid-tightly inserted into the main hole (23a), and a valve seat (24a) formed at the front end of the sleeve (28), and a valve seat ( 24. The on-off valve (24) is configured by combining a valve body (24b) to be brought into contact with and separated from 24a) and an urging means (24c) for applying a closing force to the valve body (24b). Item 5. The hydraulic brake device according to Item 4.   The check valve (26) is disposed behind the sleeve (28), and the amount of movement of the check valve (26) in the valve opening direction of the valve body (26b) is measured at the rear end of the sleeve (28). The hydraulic brake device according to claim 5, wherein the hydraulic brake device is regulated.   The hydraulic brake device according to claim 5, wherein the check valve (26) is built in the sleeve (28).   A clearance is provided between a rear outer periphery of the sleeve (28) and an inner peripheral surface of the main hole (23a), and the throttle (25) is configured by the clearance, and the pressure is higher than that of the check valve (26). The hydraulic brake device according to claim 7, wherein a radial communication hole (31) communicating with the gap from the inside of the sleeve (28) is provided in the sleeve (28) on the chamber (10) side.   A valve seat (26a) provided on the inner periphery of the rear portion of the sleeve (28), a valve body (26b) for opening and closing a passage between the valve seat (26a), and a valve opening direction of the valve body (26b) The hydraulic brake device according to claim 5 or 7, wherein the check valve (26) is configured with a stopper (26c) for regulating the amount of movement of the hydraulic brake.   A valve seat (26a) provided on the inner periphery of the rear portion of the sleeve (28), a valve body (26b) for opening and closing a passage between the valve seat (26a), and a valve opening direction of the valve body (26b) The hydraulic brake device according to claim 8, wherein the check valve (26) is constituted by a stopper (26c) for regulating the amount of movement of the hydraulic brake.   The sleeve (28) is composed of a main body portion (28a) and a cylindrical cap (28b) connected to the rear portion of the main body portion (28a), and the valve seat (26a) is disposed inside the cap (28b). ), A valve body (26b), and a stopper (26c), the hydraulic brake device according to claim 10, wherein:   The valve body (26b) is subjected to movement restriction by the stopper (26c) at the position where the valve body (26b) has moved to the installation portion of the communication hole (31), and at that position, the connection hole (31) and the valve body (26b) The hydraulic brake according to claim 10 or 11, wherein both side portions of the passage (23) sandwiching the valve element (26b) communicate with each other through a gap formed therebetween. apparatus.   As the branch hole (23b), a first branch hole and a second branch hole are provided, respectively, the throttle (25) as the first branch hole, and the check valve (26) as the second branch hole. The hydraulic brake device according to claim 4, wherein each is installed.   The hydraulic brake device according to any one of claims 1 to 6, wherein the throttle (25) is formed in a valve body (26b) or a valve seat (26a) of the check valve (26). The valve body (26b) of the check valve (26) has a bottomed cylindrical shape, a through hole is provided in the bottom of the valve body (26b), and the throttle (25) is configured by the through hole. The hydraulic brake device according to claim 14.   The hydraulic brake device according to claim 14, wherein a groove is provided in a seat surface of the valve body (26b) of the check valve (26), and the throttle (25) is configured by the groove.   The outer diameter of the valve body (26b) of the check valve (26) is made smaller than the inner diameter of the valve body incorporating portion, and the slide guided to the inner peripheral surface of the valve body incorporating portion on the outer periphery of the valve body (26b). A plurality of moving guides (32) are provided at intervals in the circumferential direction, and from the reservoir side between the outer peripheral surface of the valve body (26b), the sliding guide (32), and the inner peripheral surface of the valve body incorporating portion. The hydraulic brake device according to any one of claims 14 to 16, wherein a passage (33) through which a liquid flow to the pressure chamber is passed is formed.

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