JPH09309428A - Pump device and brake fluid pressure control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the durability and to reduce the number of part items, while realizing a small-sized pump device with structure capable of supplying circuits of two systems with fluid pressure, improving the layout freedom and the on-vehicle property thereby, and furthermore, reducing the load to the driving means such as a motor. SOLUTION: Larger diameter parts 12e and 13e, and smaller diameter parts 12f and 13f are formed at first and the second plungers 12a and 13a which are reciprocated by a cam 11, respectively, seal members 15 and 16 are provided to the above parts, and while main pumps 4 are formed between the seal members 15 and 16, supercharger pumps 8 are formed at the outer sides of the seal members 16, and a second discharge circuit 9a of one side supercharger pump 8, and the second discharge circuit 8a of the other side supercharger pump 8 are connected to a first suction and discharge port 14b of the other side main pump 4 and the first suction and discharge port 14b of one side main pump 4.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pump device and a brake fluid pressure control device to which the pump device is applied, and in particular, it is provided with a fluid pressure control circuit capable of performing antilock brake control and traction control control. The present invention relates to a brake fluid pressure control device and a pump device suitable for application to such a brake fluid pressure control device.

[0002]

2. Description of the Related Art Conventionally, as a brake control device for performing antilock brake control (hereinafter referred to as ABS control) and traction control control (hereinafter referred to as TCS control), for example, one disclosed in Japanese Patent Laid-Open No. 4-231256 is known. Are known. In this conventional technique, two hydraulic control circuits are provided between a master cylinder and a wheel cylinder of each wheel, and two main pumps that supply discharge pressure to each hydraulic control circuit are arranged in parallel. Further, a supercharging pump that supplies the discharge pressure to the suction side of one of the main pumps is provided in series with the main pump. Further, each hydraulic control circuit is provided with an inflow valve and an outflow valve, and is configured to switch between reducing, holding, and increasing the brake fluid pressure in the wheel cylinder based on the operation of both valves. The main pump has a plunger pump structure that reciprocates in contact with a cam rotated by a drive shaft driven by a motor.
A supercharging pump having a structure having a gear rotated by the drive shaft is used.

According to the prior art as described above, during the ABS control and the TCS control, the inflow valves and the outflow valves are driven to control the brake hydraulic pressure of the wheel cylinders so that the slip ratio of the wheels is predetermined. Within the range of
Prevent wheel lock or slip. Further, in the conventional technique, a load valve is provided on the discharge side of the supercharging pump, and the load valve is closed during ABS control. Therefore, during ABS control, only the discharge pressure of the main pump is supplied to the hydraulic control circuit. On the other hand,
During the TCS control, the load valve is opened and the discharge pressure of the supercharging pump is supplied to the main pump, so the discharge hydraulic pressure from the main pump rises in a shorter time than during the ABS control, and a high pressurization response is obtained. It exhibits performance and is particularly effective at low temperatures.

[0004]

However, in the above-mentioned conventional technique, the main pump and the supercharging pump are both driven by the same motor, but the main pump is the plunger pump structure. On the other hand, since the supercharging pump has a gear pump structure, the main pump is provided on the outer periphery of the drive shaft on one end side of the motor, while the supercharging pump is mounted on the drive shaft on the opposite side with the motor sandwiched. The gear was attached. As described above, since the structure is such that the pump is provided on both sides of the motor, there is a problem that the pump device becomes large.
This is a serious problem when applied to the ABS / TCS control device as in the above-mentioned prior art and mounted in a limited space of a vehicle. In addition, in the related art, when the supercharging by the supercharging pump is not necessary, the load valve is closed so that the supercharging pressure is not supplied. Since the load valve is installed in the turbocharger, the supercharging pump constantly discharges hydraulic pressure even when supercharging is not performed without performing TCS control, which causes a load on the motor and reduces the durability of the motor. The above-mentioned vehicle-mounted type has a problem that fuel consumption is adversely affected. Further, there is a problem that a relief valve for releasing pressure when the load valve is closed is required, and the number of parts is increased accordingly. The present invention has been made by paying attention to the above-mentioned conventional problems, and it is possible to reduce the size of a pump device having a structure capable of supplying hydraulic pressure to circuits of two systems, thereby improving layout flexibility and vehicle mountability. In addition, the load on the driving means such as the motor is reduced, and the durability is improved and the number of parts is reduced.

[0005]

In order to achieve the above-mentioned object, in the pump device according to claim 1, a cam rotated by the drive means and a reciprocating motion in contact with the outer periphery of the cam, A pair of plungers slidably provided in the storage hole formed in the casing, a large diameter portion and a small diameter portion provided in each plunger, and the storage hole provided on the outer periphery of the large diameter portion and the small diameter portion. A seal member provided in contact with the inner circumference of the first pump chamber, a first pump chamber formed between the plunger and the receiving hole at a position sandwiched by these seal members, and the seal member from the cam. A second pump chamber formed between the plunger and the storage hole at a position outside the far side seal member and the first pump chamber communicate with each other to operate only in the suction direction of the first pump chamber. Circulation of liquid A first discharge circuit that allows the first discharge circuit and a first suction circuit that allows the working fluid to flow only in the discharge direction from the first pump; and a first suction circuit that communicates with the second pump chamber and only in the suction direction of the second pump chamber. A second discharge circuit that allows the working fluid to flow, and a second suction circuit that allows the working fluid to flow only in the discharge direction from the second pump chamber, and the cam includes one plunger and the other plunger. And the first and second pump chambers formed by the one plunger are used as supercharging pump chambers, while the other pump chamber is used as a main pump chamber, and , One of the first and second pump chambers formed by the other plunger serves as a supercharging pump chamber, while the other pump chamber serves as a main pump chamber and is connected to the supercharging pump chamber of one plunger. One discharge circuit to the other Is connected to the suction circuit that is communicated with the main pump chamber that is formed with, and the discharge circuit of the supercharging pump chamber that is formed with the other plunger is communicated with the main pump chamber that is formed with one plunger. A gate valve that opens and closes the circuit is provided in the suction circuit or the discharge circuit that is connected to the suction circuit that is connected to each of the supercharging pump chambers. Further, in the pump device according to the second aspect, in the pump device according to the first aspect, the gate valve is provided in an intake circuit that communicates with each supercharging pump chamber. According to a third aspect of the pump device, a plurality of pairs of the plungers are provided in the pump device according to the first or second aspect. Further, in the brake fluid pressure control device according to claim 4, the discharge circuit and the suction circuit, which are communicated with the main pump chamber of the pump device according to claims 1 to 3, are provided as a master cylinder and a wheel cylinder of a vehicle-mounted brake device. It is connected to a hydraulic pressure control circuit that is provided in the middle of the main circuit connecting the two, and is configured to control the brake hydraulic pressure by reducing, holding, and increasing the hydraulic pressure of the wheel cylinder. In the brake fluid pressure control device according to claim 5, in the brake fluid pressure control device according to claim 4, the fluid pressure control circuit includes:
A discharge side gate valve which is provided in the middle of the main circuit and is normally opened to close the brake circuit when the brake fluid pressure is increased, and a position closer to the wheel cylinder than the discharge side gate valve in the main circuit. Normally, the main circuit is opened and closed when the brake fluid pressure is maintained, and the exhaust circuit that connects the main circuit on the wheel cylinder side of this inflow valve and the reservoir is normally closed and closed when the brake fluid pressure is reduced. An outflow valve that is opened, a first bypass circuit that bypasses the discharge side gate valve and allows only flow in the direction from the master cylinder to the wheel cylinder, and a bypass circuit that bypasses the inflow valve and only flows in the direction from the master cylinder to the wheel cylinder. First to forgive
A bypass circuit, the suction circuit of the main pump is connected to the discharge circuit, and the discharge circuit of the main pump is connected between the discharge side gate valve and the inflow valve of the main circuit.

[0006]

In the pump device according to the first aspect, when the cam rotates, the pair of plungers reciprocate. And
With the reciprocating movement of the plunger, the main pump chamber and the supercharging pump chamber repeat compression and expansion in synchronization. At this time, each plunger reciprocates in antiphase based on the shape of the cam.

Therefore, when the main and supercharging pump chambers formed on one plunger side are performing a compression stroke, the main and supercharging pump chambers formed on the other plunger side are performing an expansion stroke. In the state where the gate valve is open, the working fluid discharged from the supercharging pump chamber on one plunger side to the discharge circuit is sucked into the main pump chamber on the other plunger side and then compressed and discharged. On the contrary, the working fluid discharged from the supercharging pump chamber on the other plunger side to the discharge circuit is sucked into the main pump chamber on the one plunger side and then compressed and discharged. Therefore, the discharge pressure of each main pump chamber increases by the amount of supercharging action by the supercharging pump chamber. On the other hand, in the state where the gate valve is closed, the working fluid is not discharged from the supercharging pump chamber, or even if the working fluid is discharged from the supercharging pump chamber, the working fluid is not supplied to the main pump chamber. Therefore, the discharge capacity is only in the main pump chamber. Further, in the invention according to claim 2, in the state where the gate valve is closed and the suction circuit of the supercharging pump chamber is shut off, the hydraulic fluid is not sucked into the supercharging pump chamber even when the cam rotates, so The supercharging action by the feed pump is not performed, and the load by the supercharging pump chamber is not applied to the drive means.
In the invention according to claim 3, the above operation is performed in parallel for each pair of plungers.

According to the fourth aspect of the present invention, when the gate valve is closed, the hydraulic pressure control circuit of the brake hydraulic pressure control device is supplied with hydraulic fluid corresponding to the capacity of the main pump chamber, thereby preventing wheel lock during braking. It is suitable for performing (ABS control). On the other hand, when the gate valve is open, the hydraulic pressure control circuit of the brake hydraulic pressure control device is supplied with hydraulic fluid that has been supercharged by the supercharging pump chamber, and high pressurization response is obtained. , Drive wheel slip prevention control during acceleration (TCS
Control). According to the fifth aspect of the present invention, during wheel lock prevention control (ABS control), the gate valve of the pump device is closed to set the discharge capacity only in the main pump chamber. When the pressure is reduced, the discharge side gate valve is closed to disconnect the master cylinder from the wheel cylinder by the main circuit, and the outflow valve is opened to release the hydraulic pressure in the wheel cylinder to the reservoir. After this decrease, in order to maintain the reduced brake fluid pressure, the outflow valve is returned to the closed state, and the inflow valve is closed so that the brake fluid pressure of the wheel cylinder is between the outflow valve and the inflow valve. Lock in. After that, when the brake fluid pressure is to be increased, the discharge pressure from the main pump chamber is supplied to the wheel cylinder and increased by opening the inflow valve while keeping the outflow valve closed. Further, during drive wheel slip prevention control (TCS control), the gate valve of the pump device is opened to discharge the hydraulic fluid from the pump device at a discharge pressure to which the supercharging amount of the supercharging pump chamber is added to increase the above-mentioned pressure increase / Hold and depressurize.

[0009]

Embodiments of the present invention will be described below with reference to the drawings. This Embodiment is Claim 1
The pump device according to the embodiment of the invention described in No.
The present invention is applied to a brake fluid pressure control device that performs BS control and TCS control, that is, an embodiment of the invention described in claims 4 and 5. The present embodiment is applied to a four-wheel drive vehicle. First, the overall configuration will be described with reference to FIG. In the figure, FL is the wheel cylinder for the left front wheel, RR is the wheel cylinder for the right rear wheel, FR is the wheel cylinder for the right front wheel, RL is the wheel cylinder for the left rear wheel, and MC is the hydraulic pressure supplied to each wheel cylinder FL to RL. A master cylinder as a source. This master cylinder MC
Is the first brake main circuit 1 connected to the wheel cylinders FL, RR on the left front wheel and right rear wheel side, and the wheel cylinders FR, FR on the right front wheel and left rear wheel in conjunction with stepping on the brake pedal BP. It is configured to generate two systems of brake fluid pressure, which is X-piped with the second brake main circuit 2 connected to the RL. The MC is connected to a reservoir tank RT for storing the working fluid in the master cylinder.

In the middle of each of the brake main circuits 1 and 2, the first
A brake fluid pressure control circuit 10 and a second brake fluid pressure control circuit 20 are provided. The configurations of both brake fluid pressure control circuits 10 and 20 are the same, so
Only the configuration of the brake fluid pressure control circuit 10 will be described, and the same configuration in both fluid pressure control circuits 10 and 20 will be denoted by the same reference numeral, and the second brake fluid pressure control circuit 2 will be described.
The description of the configuration of 0 is omitted. In the first brake hydraulic pressure control circuit 10, the first brake main circuit 1 includes a rear wheel branch circuit 1r from a branch point 1a to a wheel cylinder RR for the right rear wheel and a front wheel branch to reach a wheel cylinder FL for the left front wheel. It is branched to the circuit 1f.

Branch point 1a from the first brake main circuit 1
A discharge side gate valve 3 is provided on the way to the above, and a gate valve bypass circuit 1b that bypasses the discharge side gate valve 3 is provided. The discharge-side gate valve 3 is a normally closed 2-port 2-position electromagnetic valve that keeps the first brake main circuit 1 in a communicating state by a spring force when it is not operating, and shuts off the first brake main circuit 1 when operating. It is composed of a switching valve. Further, the gate valve bypass circuit 1b is provided with a one-way valve 1c provided on the way, from the upstream side (master cylinder MC side) to the downstream side (branch point 1).
Only the distribution to the a side) is possible.

The discharge side gate valve 3 and the branch point 1a
A first discharge circuit 4 for supplying discharge hydraulic fluid from a main pump (main pump chamber) 4 to a connection point 1d provided between
a is connected. A discharge valve 4b having a one-valve structure for preventing backflow and a damper 4c that absorbs discharge pulsation are provided in the middle of the first discharge circuit 4a, and in the middle of the first discharge circuit 4a and the first discharge circuit 4a. 1 Relief circuit 4d by connecting the main brake circuit 1 upstream of the discharge side gate valve 3
Is provided. In the middle of the relief circuit 4d, a relief valve 4e that releases hydraulic pressure when the pressure exceeds a predetermined pressure.
Is provided.

Each of the branch circuits 1r and 1f is provided with an inflow valve 5 and an outflow valve 6 for reducing, holding, and increasing the brake fluid pressure of the wheel cylinders FL and RR.
That is, the inflow valve 5 is connected to each of the branch circuits 1r and 1f.
And a normally open 2-port 2-position solenoid-operated switching valve that connects the branch circuits 1r and 1f to each other by a spring force when not in operation and shuts off each branch circuit 1r and 1f when in operation. . Further, the outflow valve 6 is branched from branch points 1e, 1e provided downstream (on the side of the wheel cylinders FL, RR) from the inflow valve 5 of each of the branch circuits 1r, 1f to a discharge circuit 1 which reaches the reservoir 7.
0a, which is provided in the middle of a normally closed state which shuts off the discharge circuit 10a when not in operation and connects the discharge circuit 10a when in operation.
It is composed of an electromagnetic switching valve with two ports. In addition, each branch circuit 1r, 1f is provided with an inflow valve bypass 1h having a valve 1g while bypassing the inflow valve 5 and allowing only the flow from downstream to upstream. A first suction circuit 4f connected to the suction side of the main pump 4 is connected to the discharge circuit 10a, and the main pump 4 sucks hydraulic fluid from the reservoir 7 in the middle of the first suction circuit 4f. A suction valve 4h having a one-valve structure for allowing the above is provided, and a discharge valve 4g having a one-valve structure for allowing a supercharging pump 8 described later to discharge hydraulic fluid to the main pump 4 side.

Further, the discharge valve 4 of the first suction circuit 4f
g to the branch point 4j provided between the suction valve 4h and
A second discharge circuit 8a connected to the discharge side of the supercharging pump (supercharging pump chamber) 8 is connected. That is, the supercharging pump 8 is the main pump 4 during the TCS control.
The second suction circuit 8b connected to the suction side of the supercharging pump 8 is connected to the reservoir tank RT in order to expedite the rise of the discharge pressure of the main pump 4 by discharging hydraulic fluid in series. . The main pump 4 and the supercharging pump 8 are each driven by one motor M. A suction side gate valve 9 and a backflow preventing suction valve 8c are provided in the middle of the second suction circuit 8b. The suction-side gate valve 9 is a normally closed 2-port 2 that shuts off the second suction circuit 8b by the force of a spring when it is not operating and connects the second suction circuit 8b when it is operating.
It is constituted by a position electromagnetic switching valve. In addition,
The operation of each valve 3, 5, 5, 6, 6, 9 of the solenoid valve structure is controlled by a control unit (not shown). That is, the control unit is connected to a wheel speed sensor that detects the rotational speed of the wheel not shown, and the control unit determines the slip ratio based on the signals input from these wheel speed sensors, ABS control or TCS control for reducing the slip ratio is performed when it becomes a predetermined value or more. However, this control is not the main configuration of the present application, and therefore the description thereof is omitted. The control unit drives the motor M to drive both pumps 4 and 8 during the ABS control and the TCS control.

Next, before explaining the structure of the main part of the pump device of the present embodiment, the overall operation of the brake fluid pressure control device shown in FIG. 2 will be described. Since the first and second brake hydraulic pressure control circuits 10 and 20 are similar in this operation, only the first brake hydraulic pressure control circuit 10 will be described. a) Normal brake operation Normally, each of the valves 3, 5, 5, 6, 6, and 9 is in a non-operating state shown in the figure, and when the brake pedal BP is depressed in this state, the brake is generated in the master cylinder MC. Brake fluid pressure
Connect the first brake main circuit 1 to the discharge side gate valve 3 and the branch point 1a.
Is further transmitted to the wheel cylinders FL and RR through the branch circuits 1r and 1f while passing through the inflow valve 5 on the way from the branch point 1a to the brake pedal BP.
The braking of the wheels is performed according to the pedaling force of.

B) During ABS control When the wheels are locked or are likely to be locked during the above-described brake operation, the control unit detects the state based on the slip ratio,
ABS control is performed to keep the wheel slippage within a predetermined range and prevent the wheels from locking. In other words, this ABS control reduces the brake fluid pressure so that the wheels do not lock.
First, when the slip ratio of either the left front wheel, the right rear wheel, or both becomes a predetermined value or more due to the brake fluid pressure generated by the above-described brake operation, the control unit causes the motor M to drive. Is started, and the inflow valve 5 and the outflow valve 6 of the branch circuits 1r and 1f connected to the wheel cylinders FL and RR for braking the wheels that are likely to lock are energized to close the inflow valve 5 and the outflow. The valve 6 is opened. As a result of closing the inflow valve 5,
The pressure to the wheel cylinders FL and RR is not increased from the master cylinder MC side, and the working fluid of the wheel cylinders FL and RR is discharged through the outflow valve 6 through the outflow valve 1.
After passing 0a, the pressure is discharged to the reservoir 7 and the pressure is reduced, and the braking force is weakened. The hydraulic fluid stored in the reservoir 7 is sucked from the first suction circuit 4f by the driving of the main pump 4, and then returned to the first brake main circuit 1 via the first discharge circuit 4a. Then, as a result of the reduction in the braking force, when the slip ratio of the wheels falls below a predetermined value, the control unit stops the energization of the outflow valve 6 and closes the outflow valve 6 to close the wheel cylinders FL, RR. Hold hydraulic pressure.
Further, as a result of the holding operation, when the slip ratio falls below another predetermined value, the control unit cuts off the energization of the inflow valve 5 to open the valve, and as a result, the first brake main unit has a high pressure. The hydraulic fluid of the circuit 1 is supplied to the wheel cylinders FL and RR via the inflow valve 5 which is opened, and the braking force is increased again. By repeating the above-described operation, ABS control is performed in which the slip ratio of each wheel is kept within a predetermined range while the brake pedal BP is stepped on, and the maximum braking force is obtained while preventing wheel slip. It Further, during the above ABS control, the intake side gate valve 9
Since the valve is not energized and the valve closed state is maintained, the supercharging pump 8 cannot suck the hydraulic fluid even if it is driven by the motor M, and therefore does not serve as a load on the motor M.

C) TCS control At the time of sudden start / acceleration or cornering,
When it is detected that the slip ratio of the driving wheels has increased during non-braking, the control unit performs TCS control to keep the slip ratio within a predetermined range. In this case, the control unit starts driving the motor M and energizes both gate valves 3 and 9. Therefore, the discharge side gate valve 3 is closed and the first brake main circuit 1 is connected to the connection point 1d.
Is shut off upstream, and the intake gate valve 9 is opened to communicate the second intake circuit 8b. Therefore, the supercharging pump 8 sucks the hydraulic fluid in the reservoir tank RT and discharges the hydraulic fluid to the second discharge circuit 8a, and the main pump 4 sucks the pressurized hydraulic fluid in the second discharge circuit 8a. The hydraulic fluid is discharged to the first discharge circuit 4a. In this case, the hydraulic pressure increase speed of the discharge pressure of the main pump 4 becomes faster. Then, the hydraulic fluid discharged to the first discharge circuit 4a is supplied to the wheel cylinders FL and RR via the first brake main circuit 1 to perform the braking operation, and the slip ratio is reduced. After that, as in the above ABS control, the inflow valve 5
Also, based on the operation of the outflow valve 6, pressure increase / reduction is repeated until the slip ratio falls within a predetermined range even when both valves 5 and 6 are not energized. At this time, the discharge pressure of the main pump 4 becomes higher than in the ABS control by the amount of the supercharging action of the supercharging pump 8, and as a result, the responsiveness at the time of pressure increase becomes high.

Next, the structure of the pump device of the embodiment, that is, the main pump 4 and the supercharging pump 8 will be described. In FIG. 2, both pumps 4 and 8 are described as being separately provided for convenience of explanation of the entire system, but in the present embodiment, they are integrally provided.
FIG. 1 shows the pump device of this embodiment. In this embodiment, as shown in the drawing, the pump device is in contact with a cam 11 driven by a motor M and reciprocates in the axial direction by the cam 11. It is provided with a first pump section 12 having a first plunger 12a for performing and a second pump section 13 having a similar second plunger 13a. By the way, the cam 11 is formed in a cylindrical shape, and in the cam 11, C0 is the center of rotation, and C1 is the axis of the cam 11.

Each of the plungers 12a and 13a includes a first body 12b and 13b and a second body 12 respectively.
pump bodies 12d and 13d composed of c and 13c
Slidably stored in the pump body 12
The d and 13 d are fitted into the storage holes 14 a and 14 a formed in the pump casing 14, respectively.

The storage holes 14a are respectively connected to a first suction / discharge port 14b communicating with the first discharge circuit 4a and the first suction circuit 4f and a second suction circuit 8b connected to the second suction circuit 8b. 2 suction ports 14c and 2nd
The second discharge port 14d connected to the discharge circuit 8a is opened. The plungers 12a and 13a are
The large diameter portions 12e and 13e and the small diameter portion 12 are provided at both ends.
f, 13f are formed, and each part 12e, 13e, 12 is formed.
Sealing members 15 and 16 are provided on the outer circumferences of f and 13f, respectively. Also, in the first bodies 12b and 13b,
Large diameter holes 12g and 13g and small diameter holes 12h and 13h, respectively
The space formed between the large-diameter holes 12g, 13g and the large-diameter portions 12e, 13e sandwiched between the seals 15, 16 is the main pump 4, while the small-diameter portion 12 is formed.
The space formed by the end faces of f and 13f and the small diameter holes 12h and 13h is the supercharging pump 8. And the main pump 4
A spring 17 for urging the plungers 12a, 13a toward the cam 11 is provided inside the small diameter portion 12f,
A spring 18 for seating the ball forming the suction valve 8c in the valve hole is seated on the end face of 13f.
Then, the main pump 4 includes the first bodies 12b, 1
The first intake / discharge port 1 through the hole formed in 3b.
4b, the supercharging pump 8 is communicated with the second discharge port 14d through a hole formed in the first body 12b, 13b, and both bodies 12 are communicated with each other.
The second suction port 14c communicates with a space formed between b and 12c, a space formed between 13b and 13c, and a hole formed in the second body 12c and 13c. The supercharging pump 8 of the first pump unit 12 is in communication with the first suction / discharge port 14b of the main pump 4 of the second pump unit 13 via the second discharge circuit 8a, while the second pump unit 13 is in communication. The supercharging pump 8 is communicated with the first suction / discharge port 14b of the main pump 8 of the first pump unit 12 via the second discharge circuit 8a.

Next, the operation of the pump device of this embodiment will be described.

When the motor M is driven to rotate the cam 11, the first and second plungers 12a and 13a start reciprocating motion. With this reciprocating motion, the main pump 4 and the supercharging pump 8 alternately repeat compression and expansion. Therefore, in the main pump 4, the hydraulic fluid is sucked from the first suction / discharge port 14b communicating with the first suction circuit 4f and the second discharge circuit 8a, and also from the first suction / discharge port 14b via the discharge valve 4b. First
In the supercharging pump 8, the operation of discharging the hydraulic fluid to the discharge circuit 4a is performed, and in the supercharging pump 8, the second suction circuit 8b is provided via the suction valve 8c.
The operation liquid which is sucked from the second discharge circuit 8a is discharged. In the state where the intake side gate valve 9 is closed as shown in the figure, the supercharging pump 8 cannot suck the working fluid, and therefore does not discharge to the second discharge circuit 8a. , The load of the motor M does not occur.

Here, in the first pump section 12 and the second pump section 13, each plunger 12a, 13a is in contact with the same cam 11, and since this cam 11 has a structure in which a cylinder is eccentric, The phases of the reciprocating motions of the plungers 12a and 13a are different by 180 degrees, that is, when the first plunger 12a is performing the compression stroke, the second plunger 13a performs the expansion stroke, and in the former expansion stroke, the latter Both act symmetrically, such as performing a compression stroke. For this reason, in the state where the suction side gate valve 9 is opened, the supercharging pumps 8 and 8 of the first pump unit 12 and the second pump 13 discharge to the second discharge circuits 8a and 8a, respectively. Pump unit 13 and first pump unit 12
Main pumps 4, 4 of the second discharge circuits 8a, 8 respectively
The pressurized hydraulic fluid a is sucked, and the main pumps 4 and 4 are supercharged by the supercharging pumps 8 and 8, respectively. Therefore, in this case, the discharge pressure of the main pump 4 is increased in a short time.

As described above, in the pump device according to the embodiment, the large diameter portions 12e, 13e and the small diameter portion 12f, respectively, of the pair of first plungers 12a, 13a.
13f is provided for each plunger 12a, 13a
And the storage holes 14a, 14a between the plunger 12a,
Two pump chambers that are compressed / expanded by the reciprocating motion of 13a are formed, and are formed into the main pump 4 and the supercharging pump 8.
The second discharge circuit 8a for discharging the hydraulic fluid from the one supercharging pump chamber 8 is connected to the first suction / discharge circuit 14b of the other main pump 4, and the second supercharging pump 8 is connected to the other supercharging pump 8. The second discharge circuit 8a is connected to the first suction / discharge circuit 14b of the one main pump 4, and the plunger 12a,
The cam 11 that reciprocates 13a is attached to each plunger 12
Since a and 13a are formed to move in opposite phases, two main pump functions and two supercharging pump functions can be provided outside one cam 11, and the structure can be made compact. In particular, since one plunger 12a, 13a is provided with two pump functions, it is possible to obtain an effect that a large capacity can be obtained in a compact size as compared with providing a plurality of plungers having one pump function. Further, it is possible to obtain an effect that it is advantageous for vehicle mounting and layout. Further, since the suction side gate valve 9 is provided in the second suction circuit 8b on the suction side of the supercharging pump 8, the cam 11 rotates to rotate the supercharging pump 8 with the suction side gate valve 9 closed. Even if the compression / expansion is performed, the supercharging pump 8 does not suck the working fluid.
Therefore, the supercharging pump 8 does not become a load on the motor M that rotates the cam 11. Therefore, the durability of the motor M can be improved, and the energy consumption of the motor M can be reduced. Further, since the brake fluid pressure control device of the embodiment is configured to use the pump device having the effects described above, the brake capable of performing the lock prevention control of the braking wheel and the slip prevention control of the driving wheel. The effect that the hydraulic control device can be made compact is obtained.

Although the embodiment has been described with reference to the drawings, the present invention is not limited to this. For example,
In the embodiment, the example applied to the four-wheel drive vehicle is shown.
It can be applied to a front-wheel drive vehicle, a rear-wheel drive vehicle, or a multi-wheel drive vehicle having more than four wheels. In the embodiment, the first brake main circuit 1 is piped toward the wheel cylinders FL and RR for the left front wheel and the right rear wheel, and the second brake main circuit 2 is connected to the wheel cylinders FR and RL for the right front wheel and the left rear wheel. Although the X piping structure in which the piping is directed toward the front side is shown, for example, the former main circuit 1 may be connected to the front wheel side and the latter main circuit may be connected to the rear wheel side. Further, in the embodiment, the pump chamber on the side closer to the cam 11 of the plungers 12a and 13a is the main pump 4, and the far side is the supercharging pump 8. However, the main pump chamber and the supercharging pump chamber may be exchanged. Alternatively, or in the embodiment, the large-diameter portions 12e and 13e are provided on the side closer to the cam 11 and the small-diameter portions 12f and 13f are provided on the far side, but they may be arranged in reverse.

[0026]

As described above, in the pump device according to the first aspect, the large diameter portion and the small diameter portion are provided in each of the pair of plungers, and the pump is provided between each plunger and the storage chamber. Two chambers are formed to form a main pump chamber and a supercharging pump chamber, and the discharge circuit of one supercharging pump chamber is connected to the suction circuit of the other main pump chamber, while the other supercharging pump chamber Since the discharge circuit is connected to the suction circuit of one of the main pump chambers, and the cam that reciprocates the plunger is formed so that each plunger moves in the opposite phase, the main pump function and the supercharging pump function are combined into one. It can be installed on the outside of the cam, and the structure can be made compact. Especially, since one plunger has two pump functions, a plunger having one pump function cannot be duplicated. Compared to providing a plurality of devices, an effect that a large capacity can be obtained while being compact is obtained, and further, an effect that it is advantageous for vehicle mounting and layout is obtained. In the pump device according to claim 2, since the gate valve is provided in the suction circuit of the supercharging pump chamber, the cam rotates and the compression / expansion of the supercharging pump chamber occurs when the gate valve is closed. However, the hydraulic fluid is not sucked in the supercharging pump chamber. Therefore, the operation of the supercharging pump chamber does not become a load on the driving means for rotating the cam. Therefore, it is possible to improve the durability of the driving unit and reduce the energy consumption of the driving unit. In addition, the structure for releasing the discharge pressure is unnecessary, and the structure can be simplified. In the pump device according to the third aspect, since the plurality of pairs of plungers are provided around the cam, a large capacity can be obtained with a compact structure.

In the brake fluid pressure control device according to the fourth and fifth aspects, since the above-mentioned pump device is used, the brake capable of performing the lock prevention control of the braking wheel and the slip prevention control of the driving wheel. The effect that the hydraulic control device can be made compact is obtained.

[Brief description of drawings]

FIG. 1 is a diagram showing a brake fluid pressure control device according to an embodiment.

FIG. 2 is a diagram showing a pump device according to an embodiment.

[Explanation of symbols]

 FL Wheel cylinder RR Wheel cylinder FR Wheel cylinder RL Wheel cylinder MC Master cylinder 1 1st brake main circuit 2 2nd brake main circuit 3 Discharge side gate valve 4 Main pump (main pump chamber) 4a 1st discharge circuit 4b Discharge valve 4c Damper 4d Relief circuit 4f Relief valve 4f First suction circuit 4g Discharge valve 4h Suction valve 5 Inflow valve 6 Outflow valve 7 Reservoir 8 Supercharging pump chamber 8a Second discharge circuit 8b Second suction circuit 8c Suction valve 9 Suction gate valve 10th 1 Brake Fluid Pressure Control Circuit 10a Discharge Circuit 11 Cam 12a First Plunger 13a Second Plunger 12e Large Diameter Section 13e Large Diameter Section 12f Small Diameter Section 13f Small Diameter Section 15 Seal Member 16 Seal Member 20 Second Brake Fluid Pressure Control Circuit

Claims (5)

[Claims] 1. A cam which is rotated by a drive means and which is reciprocally movable in contact with the outer periphery of the cam,
A pair of plungers slidably provided in the housing hole formed in the casing, a large diameter portion and a small diameter portion provided in each plunger, and the accommodation hole provided on the outer periphery of the large diameter portion and the small diameter portion. A seal member provided in contact with the inner periphery of the seal member, a first pump chamber formed between the plunger and the storage hole at a position sandwiched by the seal members, and a seal member from the cam. A second pump chamber formed between the plunger and the storage hole at a position outside the far side seal member, and communicated with the first pump chamber to operate only in the suction direction of the first pump chamber. A first discharge circuit that allows the flow of liquid, a first suction circuit that allows the flow of hydraulic fluid only in the discharge direction from the first pump, and a second pump chamber that is in communication with the second pump chamber. Flow of hydraulic fluid only in the suction direction And a second suction circuit that allows the working fluid to flow only in the discharge direction from the second pump chamber, and the cam has the opposite phase between one plunger and the other plunger. One of the first and second pump chambers formed by the one plunger is used as a supercharging pump chamber, while the other pump chamber is used as a main pump chamber and the other plunger is used. One of the first and second pump chambers formed in 1 is used as the supercharging pump chamber, while the other pump chamber is used as the main pump chamber, and the discharge circuit connected to the supercharging pump chamber of one plunger is , The suction circuit communicating with the main pump chamber formed by the other plunger is connected, and the discharge circuit of the supercharging pump chamber formed by the other plunger is formed by one plunger. Is connected to the suction circuit is communicated with the main pumping chamber, each in the suction circuit or discharge circuit in communication with the supercharging pump chamber, the pump apparatus characterized in that a gate valve for opening and closing the circuit. 2. The gate valve is provided in an intake circuit communicating with each supercharging pump chamber.
A pump device as described. 3. The pump device according to claim 1, wherein a plurality of pairs of the plungers are provided. 4. A discharge circuit and an intake circuit communicating with the main pump chamber of the pump device according to claim 1 are provided in the middle of a main circuit connecting a master cylinder and a wheel cylinder of a vehicle-mounted brake device. The brake fluid pressure control device is characterized in that it is connected to a fluid pressure control circuit configured to control the brake fluid pressure by reducing, holding, and increasing the fluid pressure of the wheel cylinder. 5. A discharge side gate valve, which is provided in the middle of the main circuit and is normally opened when the main circuit is opened and closed during brake hydraulic pressure increase control, and the discharge side in the main circuit. An inflow valve that is located closer to the wheel cylinder than the gate valve and that normally opens the main circuit and is closed during brake fluid pressure maintenance control, and an exhaust circuit that connects the main circuit on the wheel cylinder side of this inflow valve to the reservoir. An outflow valve that is provided and normally closed and that is opened during brake fluid pressure reduction control, a first bypass circuit that bypasses the discharge side gate valve and allows only flow in the direction from the master cylinder to the wheel cylinder, and the inflow valve A first bypass circuit that bypasses and allows only the flow from the master cylinder to the wheel cylinder direction, wherein the suction circuit of the main pump is connected to the discharge circuit, Brake fluid pressure control apparatus according to claim 4, characterized in that it is connected between the discharge circuit in the pump and the discharge-side gate valve of the main circuit and the inlet valve.