Hydraulic control unit and saddled vehicle

Abstract

Provided is a hydraulic control unit that can be miniaturized relative to conventional products and can suppress the radial movement of a return spring during operation of the hydraulic control unit. The hydraulic control unit is provided with a pump that moves a brake fluid in an internal flow path that connects a wheel cylinder and a master cylinder. The pump is provided with: a piston part that has an input-side end pressed by a motor and has a partition-side end inserted into a compression chamber to partition the compression chamber; and a return spring that is provided outside the piston part and presses the piston part toward the motor. The piston part is provided with: a step portion that is provided on the outer circumference of the piston part, is in contact with the piston part-side end of the return spring, and is pressed by the return spring toward the motor; and an enlarged-diameter portion that is provided in a manner facing the inner circumference of the piston part-side end, and that increases in diameter as the distance to the step part decreases.

Description

[0001] [Document name] Statement

[0002] [Title of invention] Hydraulic pressure control unit and saddle-type vehicle

[0003] [Technical Field]

[0004]

[001] The present invention relates to a hydraulic control unit for a saddle-ride type vehicle, and to a saddle-ride type vehicle equipped with the hydraulic control unit.

[0005] [Background technology]

[0006] [. 0 0 2] Some conventional vehicles are equipped with a hydraulic control unit that controls the hydraulic pressure of brake fluid in a hydraulic circuit filled with brake fluid. For example, when the driver of the vehicle operates an input device such as a brake lever, the hydraulic control unit increases or decreases the hydraulic pressure of the brake fluid in the hydraulic circuit to adjust the braking force generated at the wheels and perform anti-lock brake control. Such a hydraulic control unit is equipped with a pump that sends brake fluid released from the wheel cylinders to the master cylinder. The pump also has a cylinder in which a compression chamber is formed that compresses the brake fluid, a piston portion whose one end is pressed by a motor to compress the brake fluid in the compression chamber, and a return spring that presses the piston portion toward the motor. Conventionally, this return spring has been located inside the compression chamber.

[0007] [Prior art documents]

[0008] [Patent documents]

[0009]

. 0 0 3

[0010] [Patent Document 1] Special Publication No. 2020 — 109919

[0011] Summary of the Invention

[0012] [Problem to be solved by the invention]

[0013]

[004] Compared to vehicles such as four-wheeled automobiles, straddle-type vehicles have less freedom in terms of component layout and therefore less freedom in the installation of hydraulic control units. For this reason, there has been a demand for miniaturization of hydraulic control units installed in straddle-type vehicles. Furthermore, when miniaturizing hydraulic control units, it is necessary to suppress radial movement of the return spring while the hydraulic control unit is in operation, in order to ensure that the return spring functions properly.

[0014]

[005] The present invention has been made in light of the above-mentioned problems, and has as its first object to provide a hydraulic control unit for a saddle-ride type vehicle that is equipped with a return spring and that can be made smaller than conventional hydraulic control units and that can suppress radial movement of the return spring while the hydraulic control unit is in operation. A second object of the present invention is to provide a saddle-ride type vehicle equipped with such a hydraulic control unit.

[0015] [Means for solving the problem]

[0016]

[006] A hydraulic control unit according to the present invention is a hydraulic control unit for a brake system mounted on a saddle-ride type vehicle, and comprises: a base body in which an internal flow path is formed that connects a wheel cylinder and a master cylinder; and a pump that moves brake fluid in the internal flow path, wherein the pump comprises: a cylinder in which a compression chamber that compresses brake fluid is formed; a piston portion having an input side end that is one end pressed by a motor that is a drive source of the pump and a partition side end that is the other end inserted into the compression chamber to define the compression chamber, the partition side end reciprocating within the compression chamber; and a return spring that presses the piston portion toward the motor, wherein the return spring is provided outside the piston portion, and the piston portion is provided on the outer periphery of the piston portion, and one end of the return spring, the piston portion side end, abuts against a stepped portion pressed by the return spring in a direction toward the motor, and an expanded diameter portion provided opposite an inner circumferential portion of the piston portion side end of the return spring, the expanded diameter portion expanding in diameter as it approaches the stepped portion.

[0007] The saddle-type vehicle according to the present invention is also equipped with the hydraulic pressure control unit according to the present invention.

[0017] [Effects of the invention]

[0018]

[0008] The present invention provides a hydraulic control unit that can be made smaller than conventional units and that can suppress radial movement of a return spring while the hydraulic control unit is in operation, and a saddle-type vehicle equipped with the hydraulic control unit.

[0019] [Brief description of the drawing]

[0020] [ 0 0 0 9 ]

[0021] FIG. 1 is a diagram showing the configuration of a saddle-ride type vehicle equipped with a brake system equipped with a hydraulic control unit according to an embodiment of the present invention.

[0022] FIG. 2 is a diagram showing the configuration of a brake system equipped with a hydraulic control unit according to an embodiment of the present invention.

[0023] FIG. 3 is a cross-sectional view showing the periphery of a pump and a motor of a hydraulic control unit according to an embodiment of the present invention.

[0024] FIG. 4 is a cross-sectional view showing a pump of a hydraulic control unit according to an embodiment of the present invention.

[0025] FIG. 5 is a cross-sectional view showing a portion of a pump of a hydraulic control unit according to an embodiment of the present invention.

[0026] FIG. 6 is a cross-sectional view showing a portion of a pump for explaining a modified example of a hydraulic control unit according to an embodiment of the present invention.

[0027] [Figure 7] A diagram for explaining a modified example of a hydraulic control unit according to an embodiment of the present invention, and a cross-sectional view showing a portion of a pump.

[0028] DETAILED DESCRIPTION OF THE INVENTION

[0029]

[0010] The following describes a hydraulic control unit and a straddle-type vehicle according to the present invention with reference to the drawings. While the following describes an example in which the hydraulic control unit according to the present invention is mounted on a motorcycle, which is an example of a straddle-type vehicle, the hydraulic control unit according to the present invention may also be mounted on other straddle-type vehicles besides motorcycles. Examples of other straddle-type vehicles besides motorcycles include bicycles (e.g., two-wheeled vehicles, three-wheeled vehicles, etc.), three-wheeled vehicles using at least one of an engine and an electric motor as a drive source, and buggies. Furthermore, a bicycle generally refers to any vehicle that can be propelled on a road by applying force to pedals. In other words, bicycles include ordinary bicycles, electrically assisted bicycles, and electric bicycles. In addition, two-wheeled or three-wheeled motor vehicles refer to so-called motorcycles, which include motorcycles, scooters, electric scooters, etc.

[0030]

[0011] In the following, an example in which the hydraulic control unit according to the present invention is used in a brake system having two hydraulic circuits is described, but the number of hydraulic circuits in a brake system in which the hydraulic control unit according to the present invention is used is not limited to two. A brake system in which the hydraulic control unit according to the present invention is used may have only one hydraulic circuit, or may have three or more hydraulic circuits.

[0031]

[0012] Furthermore, the configurations, operations, etc. described below are merely examples, and the present invention is not limited to such configurations, operations, etc. Furthermore, in each drawing, the same or similar members or parts may be designated by the same reference numerals or may not be designated by the reference numerals. Furthermore, detailed structures may be simplified or omitted as appropriate.

[0032] [ 0 0 1 3 ] Embodiments.

[0033] <Configuration and Operation of Brake System> The configuration and operation of a brake system equipped with a hydraulic pressure control unit according to this embodiment will be described. Fig. 1 is a diagram showing the configuration of a saddle-ride type vehicle 200 equipped with a brake system 10 equipped with a hydraulic pressure control unit 100 according to an embodiment of the present invention. Fig. 2 is a diagram showing the configuration of a brake system 10 equipped with a hydraulic pressure control unit 100 according to an embodiment of the present invention.

[0034]

[0014] As shown in Fig. 1 and Fig. 2, the brake system 10 is mounted on a saddle-riding vehicle 200. The saddle-riding vehicle 200 is, for example, a motorcycle powered by an engine. The saddle-riding vehicle 200 includes a body 1, a handlebar 2 rotatably held on the body 1, a front wheel 3 rotatably held together with the handlebar 2 on the body 1, and a rear wheel 4 rotatably held on the body 1.

[0035]

[0015] The brake system 10 includes a brake lever 11, a first hydraulic circuit 12 filled with brake fluid, a brake pedal 13, and a second hydraulic circuit 14 filled with brake fluid. The brake lever 11 is provided on a handlebar 2 and is operated by the driver's hand. The first hydraulic circuit 12 generates a braking force in a rotor 3 a that rotates together with the front wheels 3 according to the amount of operation of the brake lever 11. The brake pedal 13 is provided below the body 1 and is operated by the driver's foot. The second hydraulic circuit 14 generates a braking force in a rotor 4 a that rotates together with the rear wheels 4 according to the amount of operation of the brake pedal 13.

[0036]

[0016] The brake lever 11 and the brake pedal 13 are examples of a brake input unit. For example, a brake pedal other than the brake pedal 13 provided on the body 1 may be used as a brake input unit instead of the brake lever 11. Also, for example, a brake lever other than the brake lever 11 provided on the handlebars 2 may be used as a brake input unit instead of the brake pedal 13. Also, the first hydraulic circuit 12 may generate a braking force in the rotor 4 a that rotates together with the rear wheel 4 according to the amount of operation of the brake lever 11 or the amount of operation of a brake pedal other than the brake pedal 13 provided on the body 1. In addition, the second hydraulic circuit 14 may generate a braking force in the rotor 3 a that rotates together with the front wheel 3 according to the amount of operation of the brake pedal 13 or the amount of operation of a brake lever other than the brake lever 11 provided on the handlebars 2.

[0037]

[0017] The first hydraulic pressure circuit 12 and the second hydraulic pressure circuit 14 have the same configuration. Therefore, the following description will explain the configuration of the first hydraulic pressure circuit 12 as a representative. The first hydraulic pressure circuit 12 includes a master cylinder 21 incorporating a piston (not shown), a reservoir 22 attached to the master cylinder 21, a brake caliper 23 having brake pads (not shown), and a wheel cylinder 24 that operates the brake pads (not shown) of the brake caliper 23.

[0038]

[0018] An internal flow path 40 that connects the wheel cylinder 24 and the master cylinder 21 is formed in the base body 101 of the hydraulic control unit 100. Specifically, the internal flow path 40 communicates with the master cylinder 21 via a liquid pipe 15 described below, and communicates with the wheel cylinder 24 via a liquid pipe 16 described below. In this embodiment, the base body 101 is formed with a main flow path 41, a sub-flow path 42, and a pressure-boosting flow path 43 as the internal flow path 40. In the first hydraulic circuit 12, the master cylinder 21 and the wheel cylinder 24 are connected via a fluid pipe 15 connected between the master cylinder 21 and a master cylinder port MP formed in the base 101, a main flow path 41 formed in the base 101, and a fluid pipe 16 connected between the wheel cylinder 24 and a wheel cylinder port WP formed in the base 101. Brake fluid in the wheel cylinder 24 is released via a sub-flow path 42 to a main flow path intermediate portion 41a, which is a midpoint of the main flow path 41. Brake fluid in the master cylinder 21 is supplied via a pressure-boosting flow path 43 to a sub-flow path intermediate portion 42a, which is a midpoint of the sub-flow path 42. An inlet valve 25 is provided in a region of the main flow path 41 closer to the wheel cylinder 24 than the main flow path intermediate portion 41a. Opening and closing of the inlet valve 25 opens and closes the flow path portion of the main flow path 41 where the inlet valve 25 is installed, thereby controlling the flow rate of the brake fluid flowing through this region. In a region of the secondary flow path 42 upstream of the secondary flow path intermediate portion 42a, a release valve 26 and an accumulator 27 that stores brake fluid are provided, in this order from upstream to downstream. Opening and closing of the release valve 26 opens and closes the flow path portion of the secondary flow path 42 where the release valve 26 is installed, thereby controlling the flow rate of the brake fluid flowing through this region.In addition, a pump 50 is provided in the area of ​​the secondary flow path 42 downstream of the secondary flow path intermediate portion 42a, which applies pressure to the brake fluid in the secondary flow path 42 and moves the brake fluid. In other words, the pump 50 moves the brake fluid in the internal flow path 40. Note that, hereinafter, the portion of the secondary flow path 42 upstream of the pump 50 may be referred to as the first secondary flow path 42b. Furthermore, the portion of the secondary flow path 42 downstream of the pump 50 may be referred to as the second secondary flow path 42c.

[0039]

[0020] A switching valve 28 is provided in a region of the main flow path 41 closer to the master cylinder 21 than the main flow path intermediate portion 41a. The opening and closing operation of the switching valve 28 opens and closes the flow path portion of the main flow path 41 where the switching valve 28 is installed, thereby controlling the flow rate of the brake fluid flowing through this region. A pressure increase valve 29 is provided in the pressure increase flow path 43. The opening and closing operation of the pressure increase valve 29 opens and closes the flow path portion of the pressure increase flow path 43 where the pressure increase valve 29 is installed, thereby controlling the flow rate of the brake fluid flowing through the pressure increase flow path 43.

[0040]

[0021] A master cylinder hydraulic pressure sensor 30 is provided in the main flow path 41 in an area closer to the master cylinder 21 than the switching valve 28, for detecting the hydraulic pressure of the brake fluid in the master cylinder 21. A wheel cylinder hydraulic pressure sensor 31 is provided in the main flow path 41 in an area closer to the wheel cylinder 24 than the inlet valve 25, for detecting the hydraulic pressure of the brake fluid in the wheel cylinder 24.

[0041]

[0022] In other words, the main flow path 41 communicates between the master cylinder port MP and the wheel cylinder port WP via the inlet valve 25. The secondary flow path 42 is defined as a part or all of the flow path that releases the brake fluid in the wheel cylinder 24 to the master cylinder 21 via the release valve 26. The pressure-boosting flow path 43 is defined as a part or all of the flow path that supplies the brake fluid in the master cylinder 21 to the upstream side of the pump 50 of the secondary flow path 42 via the pressure-boosting valve 29. In other words, the secondary flow path 42 and the pressure-boosting flow path 43 also communicate between the master cylinder port MP and the wheel cylinder port WP.

[0042]

[0023] The inlet valve 25 is a solenoid valve that switches the flow of brake fluid at its installation location from open to closed when it is switched from a de-energized state to an energized state, for example. The release valve 26 is a solenoid valve that switches the flow of brake fluid through its installation location toward the secondary flow path intermediate portion 42 a from closed to open when it is switched from a de-energized state to an energized state, for example. The switching valve 28 is a solenoid valve that switches the flow of brake fluid at its installation location from open to closed when it is switched from a de-energized state to an energized state, for example. The pressure booster valve 29 is a solenoid valve that switches the flow of brake fluid through its installation location toward the secondary flow path intermediate portion 42 a from closed to open when it is switched from a de-energized state to an energized state, for example.

[0043]

[0024] The pump 50 of the first hydraulic circuit 12 and the pump 50 of the second hydraulic circuit 14 are driven by a common motor 90. In other words, the motor 90 is the drive source of the pump 50.

[0044]

[0025] A hydraulic control unit 100 is configured by a base 101, the various components provided on the base 101 (inlet valve 25, release valve 26, accumulator 27, switching valve 28, pressure booster valve 29, master cylinder hydraulic pressure sensor 30, wheel cylinder hydraulic pressure sensor 31, pump 50, motor 90, etc.), and a control device (ECU) 105.

[0045]

[0026] The control device 105 controls the operation of the inlet valve 25, the release valve 26, the switching valve 28, the pressure increase valve 29, and the motor 90. The control device 105 may be a single device or may be divided into multiple devices. The control device 105 may be attached to the base 101, or may be attached to a member other than the base 101. Some or all of the control device 105 may be configured, for example, by a microcomputer, a microprocessor unit, or the like, or may be configured with updatable firmware, or may be a program module executed by commands from a CPU, etc.

[0046] For example, under normal conditions, the control device 105 controls the inlet valve 25, the release valve 26, the switching valve 28, and the pressure-increasing valve 29 to be in a non-energized state. When the brake lever 11 is operated in this state, the piston (not shown) of the master cylinder 21 in the first hydraulic circuit 12 is pressed, increasing the hydraulic pressure of the brake fluid in the wheel cylinder 24, and the brake pad (not shown) of the brake caliper 23 is pressed against the rotor 3a of the front wheel 3, thereby braking the front wheel 3. Furthermore, when the brake pedal 13 is operated, the piston (not shown) of the master cylinder 21 in the second hydraulic circuit 14 is pressed, increasing the hydraulic pressure of the brake fluid in the wheel cylinder 24, and the brake pad (not shown) of the brake caliper 23 is pressed against the rotor 4a of the rear wheel 4, thereby braking the rear wheel 4.

[0047]

[0028] The outputs of the various sensors (master cylinder hydraulic pressure sensor 30, wheel cylinder hydraulic pressure sensor 31, wheel speed sensor, acceleration sensor, etc.) are input to the control device 105. Depending on the outputs, the control device 105 outputs commands that control the operation of the inlet valve 25, the release valve 26, the switching valve 28, the pressure increase valve 29, and the motor 90, thereby performing pressure reduction control, pressure increase control, etc.

[0048]

[0029] For example, when the brake fluid pressure in the wheel cylinder 24 of the first hydraulic pressure circuit 12 is excessive or there is a possibility that the brake fluid pressure is excessive, the control device 105 executes pressure reduction control to reduce the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the first hydraulic pressure circuit 12. Also, for example, when the wheels of the saddle-ride type vehicle 200 are locked or there is a possibility that the wheels may be locked, the control device 105 executes the pressure reduction control. In these cases, the control device 105 drives the motor 90 while controlling the inlet valve 25 to an energized state, the release valve 26 to an energized state, the switching valve 28 to a de-energized state, and the pressure booster valve 29 to a de-energized state in the first hydraulic pressure circuit 12. As a result, the brake fluid in the wheel cylinder 24 of the first hydraulic circuit 12 flows through the main flow path 41 into the secondary flow path 42, reducing the hydraulic pressure in the wheel cylinder 24. The brake fluid that flows from the wheel cylinder 24 into the secondary flow path 42 then flows through the release valve 26 into the accumulator 27 and is stored in the accumulator 27. The brake fluid stored in the accumulator 27 is returned to the master cylinder 21 by a pump 50 driven by a motor 90.

[0049]

[0030] Furthermore, when the brake fluid pressure in the wheel cylinder 24 of the second hydraulic circuit 14 is excessive or there is a possibility of excessive pressure, the control device 105 executes pressure reduction control to reduce the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the second hydraulic circuit 14. At that time, the control device 105 drives the motor 90 while controlling the inlet valve 25 to an energized state, the release valve 26 to an energized state, the switching valve 28 to a de-energized state, and the pressure increase valve 29 to a de-energized state in the second hydraulic circuit 14. As a result, the brake fluid in the wheel cylinder 24 of the second hydraulic circuit 14 flows into the sub-path 42 through the main path 41, and the hydraulic pressure in the wheel cylinder 24 is reduced. Then, the brake fluid that flows from the wheel cylinder 24 into the sub-flow path 42 passes through the release valve 26 and flows into the accumulator 27, where it is stored. The brake fluid stored in the accumulator 27 is returned to the master cylinder 21 by a pump 50 driven by a motor 90.

[0050]

[0031] Furthermore, for example, when the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the first hydraulic pressure circuit 12 is insufficient or there is a possibility of such insufficiency, the control device 105 executes pressure increase control to increase the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the first hydraulic pressure circuit 12. In this case, the control device 105 controls the inlet valve 25 to a non-energized state, the release valve 26 to a non-energized state, the switching valve 28 to a conductive state, and the pressure increase valve 29 to a conductive state in the first hydraulic pressure circuit 12, while driving the motor 90. As a result, the pump 50 driven by the motor 90 causes the brake fluid in the master cylinder 21 of the first hydraulic circuit 12 to flow from the sub-flow path intermediate portion 42a through the main flow path 41 and the pressure-boosting flow path 43 into the sub-flow path 42. The brake fluid that has flowed into the sub-flow path 42 flows from the main flow path intermediate portion 41a into the main flow path 41, passes through the inlet valve 25, and flows into the wheel cylinder 24 of the first hydraulic circuit 12. As a result, the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the first hydraulic circuit 12 increases.

[0051]

[0032] Furthermore, when the brake fluid pressure in the wheel cylinder 24 of the second hydraulic circuit 14 is insufficient or there is a possibility of such insufficiency, the control device 105 executes pressure increase control to increase the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the second hydraulic circuit 14. At this time, the control device 105 controls the inlet valve 25 to a non-energized state, the release valve 26 to a non-energized state, the switching valve 28 to a conductive state, and the pressure increase valve 29 to a conductive state in the second hydraulic circuit 14, while driving the motor 90. As a result, the pump 50 driven by the motor 90 causes the brake fluid in the master cylinder 21 of the second hydraulic circuit 14 to flow through the main flow path 41 and the booster flow path 43, and from the sub-flow path intermediate portion 42a into the sub-flow path 42. The brake fluid that has flowed into the sub-flow path 42 flows from the main flow path intermediate portion 41a into the main flow path 41, and then flows through the inlet valve 25 into the wheel cylinder 24 of the second hydraulic circuit 14. This increases the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the second hydraulic circuit 14.

[0052]

[0033] In other words, the hydraulic control unit 100 controls the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the first hydraulic pressure circuit 12, thereby enabling pressure reduction control of the first hydraulic pressure circuit 12 (in other words, anti-lock brake control). The hydraulic control unit 100 controls the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the second hydraulic pressure circuit 14, thereby enabling pressure reduction control of the second hydraulic pressure circuit 14 (in other words, anti-lock brake control). The hydraulic control unit 100 controls the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the first hydraulic pressure circuit 12, thereby enabling pressure increase control of the first hydraulic pressure circuit 12. In addition, the hydraulic control unit 100 can control the hydraulic pressure of the brake fluid in the wheel cylinder 24 of the second hydraulic circuit 14, thereby performing pressure increase control of the second hydraulic circuit 14.

[0053]

[0034] <Configuration of hydraulic control unit> The configuration of the hydraulic control unit according to this embodiment will be described. Fig. 3 is a cross-sectional view showing the periphery of the pump 50 and motor 90 of the hydraulic control unit 100 according to the embodiment of the present invention. Fig. 4 is a cross-sectional view showing the pump 50 of the hydraulic control unit 100 according to the embodiment of the present invention. Fig. 5 is a cross-sectional view showing a part of the pump 50 of the hydraulic control unit 100 according to the embodiment of the present invention. Fig. 5 is a view showing the vicinity of the step portion 54 of the piston portion 55 of the pump 50. Fig. 5 is a view showing the vicinity of the step portion 54 when the return spring 66 is in a contracted state. 3, 4, and 5 is the pump 50 of the first hydraulic circuit 12. The configuration of the pump 50 of the second hydraulic circuit 14 is similar to the configuration of the pump 50 of the first hydraulic circuit 12.

[0054]

[0035] As described above, the hydraulic control unit 100 includes the pump 50 and the motor 90. The pump 50 and the motor 90 are mounted on a base 101 made of a metal such as an aluminum alloy.

[0055]

[0036] The motor 90 has an output shaft 91 and an eccentric portion 92. The output shaft 91 is rotated by the rotor and stator of the motor 90. Note that FIG. 3 is a diagram of the hydraulic control unit 100 cut along a cross section perpendicular to the rotation center of the output shaft 91, and the observation direction does not show the rotor and stator. The eccentric portion 92 is provided on the output shaft 91 and rotates eccentrically about the rotation center of the output shaft 91.

[0056]

[0037] The pump 50 is embedded in a recess 102 formed in a base 101. The pump 50 includes a cylinder 51, a piston 55, and a return spring 66.

[0057]

[0038] A compression chamber 52 that compresses brake fluid is formed in the cylinder 51. A discharge flow path 53 that discharges the brake fluid compressed in the compression chamber 52 is also formed in the cylinder 51. The brake fluid discharged to the discharge flow path 53 flows into the second sub-flow path 42c of the sub-flow path 42. In this embodiment, the brake fluid discharged to the discharge flow path 53 flows into the second sub-flow path 42c via the discharge flow path 68. In other words, the discharge flow path 53 communicates with the second sub-flow path 42c via the discharge flow path 68. In addition, in this embodiment, an outflow side check valve 75 is provided between the discharge flow path 68 and the discharge flow path 53 to regulate the flow of brake fluid from the discharge flow path 68 to the discharge flow path 53.

[0058]

[0039] Specifically, the pump 50 according to this embodiment includes a lid portion 67 adjacent to the cylinder 51. The lid portion 67 is embedded in a region of the recess 102 that is closer to the opening of the recess 102 than the cylinder 51. The discharge flow path 68 is formed between the cylinder 51 and the lid portion 67. In this embodiment, the discharge flow path 68 is composed of a groove formed in at least one of the end of the cylinder 51 on the lid portion 67 side and the end of the lid portion 67 on the cylinder 51 side, and a groove formed in at least one of the outer circumferential surface of the cylinder 51 and the outer circumferential surface of the lid portion 67.

[0059]

[0040] An input side end 55a, which is one end of the piston portion 55, abuts against the eccentric portion 92 of the motor 90. In other words, the input side end 55a is the end that is pressed against the motor 90 via the eccentric portion 92. Furthermore, a partition side end 55b, which is the other end of the piston portion 55, is inserted into the compression chamber 52. The partition side end 55 is the end that defines the compression chamber 52. The partition side end 55b reciprocates within the compression chamber 52. At this time, the outer peripheral surface of the partition side end 55b slides on the inner peripheral surface of the compression chamber 52.

[0060]

[0041] The return spring 66 is provided on the outside of the piston portion 55 and presses the piston portion 55 toward the motor 90. In this embodiment, the return spring 66 presses the piston portion 55 toward the eccentric portion 92 of the motor 90. In other words, the return spring 66 presses the piston portion 55 in the direction from the partition side end 55b toward the input side end 55a. Specifically, the return spring 66 is configured to press the piston portion 55 toward the motor 90 as follows. The piston portion 55 has a step portion 64 provided on the outer periphery of the piston portion 55. The return spring 66 is in contact with a surface 64a (flat surface in FIG. 6), which is the surface of the step 64 facing the cylinder 51. More specifically, one end of the return spring 66, the piston portion side end 66a, is in contact with the surface 64a of the step 64. The other end of the return spring 66 is in contact with a part that does not move when the pump 50 is driven, such as the cylinder 51. As a result, the step 64 is pressed against the return spring 66 in the direction toward the motor 90, and the piston portion 55 is pressed against the return spring 66 in the direction toward the motor 90.

[0061]

[0042] Note that the number of parts constituting the piston portion 55 is not particularly limited, but in the present embodiment, the piston portion 55 is composed of a first piston member 56 and a second piston member 61 connected to the first piston member 56. That is, in the present embodiment, the piston portion 55 includes the first piston member 56 and the second piston member 61 which is a member separate from the first piston member 56. The first piston member 56 is a portion of the piston portion 55 that has the input end portion 55 a. The second piston member 61 is made of, for example, resin, and is a portion of the piston portion 55 that has the partition side end portion 55b. In this embodiment, the return spring 66 is provided on the outer side of the second piston member 61 of the piston portion 55. The step portion 64 is provided on the outer periphery of the second piston member 61.

[0062]

[0043] The number of parts constituting the first piston member 56 is not particularly limited, but in this embodiment, the first piston member 56 is composed of two parts. Specifically, the first piston member 56 includes a first part 57 having an input side end portion 55a, and a second part 58 connected to the first part 57 and the second piston member 61. The parts constituting the first piston member 56 are formed of, for example, resin or metal. Note that some of the parts constituting the first piston member 56 may be formed of resin, and other parts of the parts constituting the first piston member 56 may be formed of metal. For example, the first part 57 may be made of metal and the second part 58 may be made of resin.

[0063] In the present embodiment, the piston portion 55 is formed with an inlet flow path 65 through which brake fluid flowing through the internal flow path 40 toward the pump 50 flows and guides the brake fluid to the compression chamber 52. Specifically, in the present embodiment, the end of the inlet flow path 65 on the brake fluid inlet side opens to the side surface of the piston portion 55. In addition, the end of the inlet flow path 65 on the brake fluid outlet side opens to the partition side end 55 b. In other words, the end of the inlet flow path 65 on the brake fluid outlet side opens into the compression chamber 52. Then, the brake fluid that has flowed through the first sub-flow path 42b of the sub-flow path 42 toward the pump 50 flows into the inlet flow path 65 and flows out through the inlet flow path 65 into the compression chamber 52. In order to prevent the brake fluid that has flowed through the first sub-flow path 42b of the sub-flow path 42 toward the pump 50 from flowing through the outer periphery of the piston portion 55 into the arrangement space of the eccentric portion 92, in this embodiment, the space between the piston portion 55 and the base body 101 is sealed with a sealing member 87 such as an O-ring.

[0064]

[0045] Here, the brake system 10 may be provided with an inlet-side check valve 70 that regulates the flow of brake fluid backflowing from the compression chamber 52 to the internal flow path 40 (more specifically, the first sub-flow path 42b). The inlet-side check valve 70 may be provided in the first sub-flow path 42b, but in this embodiment it is provided in the inlet flow path 65. That is, in this embodiment, the piston portion 55 is provided in the inlet flow path 65 and is equipped with an inlet-side check valve 70 that regulates the flow of brake fluid from the compression chamber 52 to the internal flow path 40 (more specifically, the first sub-flow path 42b). This inlet side check valve 70 comprises a seat 73 provided in the inlet flow path 65, a ball 71 that abuts against the seat 73 and blocks the inlet flow path 65, and a spring 72 that presses the ball 71 toward the seat 73.

[0065]

[0046] There is no particular limitation on the method for fixing the pump 50 configured as described above to the base 101. In this embodiment, the pump 50 is fixed to the base 101 as follows. The base 101 has a step 103 on the inner surface of the recess 102. The cylinder 51 of the pump 50 has a step 54 that protrudes from the outer surface and abuts against the step 103 of the base 101. The base 101 also has a plastically deformed portion 104 formed by plastically deforming the periphery of the opening of the recess 102. The cover portion 67 and the cylinder 51 of the pump 50 are sandwiched between the step portion 103 and the plastically deformed portion 104, and the pump 50 is fixed to the base body 101. Note that FIG. 3 shows the base body 101 before the plastically deformed portion 104 is formed. For this reason, the plastically deformed portion 104 is shown by an imaginary line in FIG. 3.

[0066]

[0047] The pump 50 according to this embodiment includes a holder 85 that holds the cylinder 51 and the piston portion 55. By including the holder 85 in the pump 50, at least some of the components of the pump 50 can be unitized. The unitized parts of the pump 50 can then be inserted into the recess 102 of the base 101 at one time. Therefore, the hydraulic control unit 100 including the holder 85 is easier to manufacture than assembling the pump 50 by inserting the components of the pump 50 into the recess 102 one by one. This holder 85 is equipped with a filter 86 through which brake fluid flows into the inlet flow path 65 formed in the piston portion 55. By providing the holder 85 with the filter 86, foreign matter can be prevented from entering the compression chamber 52, and the occurrence of scratches inside the compression chamber 52 can be prevented, thereby improving the reliability of the hydraulic control unit 100.

[0067]

[0048] In the pump 50 configured in this manner, as the outer peripheral surface of the eccentric portion 92 of the motor 90 approaches the compression chamber 52, the piston portion 55 is pushed so as to be inserted into the compression chamber 52. This reduces the volume of the compression chamber 52. Furthermore, as the outer peripheral surface of the eccentric portion 92 of the motor 90 moves away from the compression chamber 52, the piston portion 55, which is pressed toward the eccentric portion 92 by the return spring 66, maintains a state in which the input side end 55 a abuts against the eccentric portion 92. As a result, the piston portion 55 moves in accordance with the outer peripheral surface of the eccentric portion 92 of the motor 90, in other words, moves in accordance with the eccentric rotational motion of the eccentric portion 92 of the motor 90, and operates to escape from the compression chamber 52. Therefore, the volume of the compression chamber 52 increases.

[0068]

[0049] When brake fluid flows into the first sub-flow path 42b of the sub-flow path 42, the brake fluid in the first sub-flow path 42b flows into the inlet flow path 65 formed in the piston portion 55. For example, during pressure reduction control, the brake fluid in the wheel cylinder 24 flows into the inlet flow path 65 through the main flow path 41 and the first sub-flow path 42b. During pressure increase control, the brake fluid in the master cylinder 21 flows into the inlet flow path 65 through the main flow path 41, the pressure increase flow path 43, and the first sub-flow path 42b.

[0069]

[0050] At this time, when the volume of the compression chamber 52 is increasing, the hydraulic pressure of the brake fluid present on the compression chamber 52 side relative to the inlet check valve 70 is low. Therefore, the brake fluid that has flowed into the inlet flow path 65 moves the ball 71 away from the seat 73, opening the inlet check valve 70. As a result, the brake fluid that has flowed into the inlet flow path 65 passes through the inlet check valve 70 and flows into the compression chamber 52. On the other hand, when the volume of the compression chamber 52 is decreasing, the hydraulic pressure of the brake fluid present on the compression chamber 52 side relative to the inlet check valve 70 increases. Therefore, the brake fluid that has flowed into the inlet flow path 65 cannot move the ball 71 away from the seat 73. As a result, the inlet check valve 70 is closed, and the brake fluid that has flowed into the inlet flow path 65 does not flow into the compression chamber 52.

[0070]

[0051] The brake fluid that flows into the compression chamber 52 is compressed as the volume of the compression chamber 52 decreases. When the hydraulic pressure of the brake fluid in the compression chamber 52 reaches a level that allows the outlet check valve 75 to open, the brake fluid in the compression chamber 52 is pressure-fed to the second sub-flow path 42c of the sub-flow path 42 through the discharge flow path 53 and the discharge flow path 68. For example, during pressure reduction control, the brake fluid that flows into the second sub-flow path 42c passes through the main flow path 41 and is returned to the master cylinder 21. During pressure increase control, the brake fluid that flows into the second sub-flow path 42c passes through the main flow path 41 and flows into the wheel cylinder 24.

[0071]

[0052] Conventional hydraulic control units have a return spring disposed in the compression chamber. Therefore, in conventional hydraulic control units, when the diameter of the compression chamber is reduced, the diameter of the return spring also needs to be reduced. However, reducing the diameter of the return spring weakens the pressing force on the piston, making it difficult for the piston to move in accordance with the operation of the motor. As a result, the pump's pumping capacity decreases, making it difficult to move the desired volume of brake fluid. To solve this problem, it is necessary to lengthen the return spring and increase the pressing force on the piston. However, this also increases the length of the compression chamber, making it impossible to reduce the size of the hydraulic control unit. As such, it has been difficult to reduce the size of conventional hydraulic control units.

[0072]

[0053] On the other hand, in the hydraulic control unit 100 according to this embodiment, the return spring 66 is provided outside the compression chamber 52. Therefore, in the hydraulic control unit 100 according to this embodiment, the return spring 66 can be selected without being limited by the size of the compression chamber 52. Therefore, in the hydraulic control unit 100 according to this embodiment, the compression chamber 52 can be made smaller while suppressing a decrease in the pressing force of the return spring 66. Therefore, the hydraulic control unit 100 according to this embodiment can be made smaller than conventional hydraulic control units.

[0073]

[0054] In a conventional hydraulic control unit, the return spring is guided by the inner wall surface of the compression chamber. Therefore, in the hydraulic control unit 100 according to this embodiment, the return spring 66 is disposed outside the compression chamber 52, which eliminates the function of guiding the return spring 66. This raises concerns that the return spring 66 may move in its radial direction while the hydraulic control unit 100 is in operation. For example, in the hydraulic control unit 100 according to this embodiment, there may be concerns that the return spring 66 may move in its radial direction and interfere with surrounding components.

[0074]

[0055] However, the hydraulic control unit 100 according to this embodiment can also suppress movement of the return spring 66 in the radial direction of the return spring 66. This is because the piston portion 55 of the hydraulic control unit 100 according to this embodiment is provided with an expanded diameter portion 62. This expanded diameter portion 62 is provided opposite to the inner circumferential portion of the piston portion side end portion 66 a of the return spring 66. Moreover, the diameter of the expanded diameter portion 62 increases as it approaches the step portion 64 with which the piston portion side end portion 66 a abuts. When the piston portion 55 has the expanded diameter portion 62, for example, the gap between the inner peripheral portion of the piston portion side end 66 a of the return spring 66 and the outer peripheral surface of the piston portion 55 is smaller (or the piston portion side end 66 a of the return spring 66 and the expanded diameter portion 62 are more likely to come into contact with each other) compared to when the piston portion 55 does not have the expanded diameter portion 62. Therefore, in the hydraulic control unit 100 according to this embodiment, the expanded diameter portion 62 can prevent the piston portion side end 66 a of the return spring 66 from moving in the radial direction of the return spring 66. As a result, the hydraulic control unit 100 according to this embodiment can also prevent the return spring 66 from moving in the radial direction of the return spring 66 by using the expanded diameter portion 62.

[0075]

[0056] As described above, in this embodiment, the piston portion 55 is made up of the first piston member 56 and the second piston member 61. As described above, in this embodiment, the step portion 64 is provided on the outer periphery of the second piston member 61. In this case, the expanded diameter portion 62 is provided on the outer periphery of the second piston member 61.

[0076]

[0057] In this way, by providing the return spring 66 outside the compression chamber 52 and providing the piston portion 55 with the expanded diameter portion 62, the hydraulic control unit 100 can be made smaller and radial movement of the return spring 66 can be suppressed. However, from the viewpoint of further improving the reliability of the hydraulic control unit 100, it is desirable to sufficiently increase the stability of the pressing force of the return spring 66. Here, it is conceivable that the expanded diameter portion 62 may cause the piston portion side end 66a of the return spring 66 to get caught on the expanded diameter portion 62, which may prevent the stability of the pressing force of the return spring 66 from being sufficiently increased. In response to this, it is preferable that the hydraulic control unit b100 according to this embodiment has the following configuration.

[0077]

[0058] Preferably, a gap 63 is formed between the inner circumferential portion of the piston portion side end 66a of the return spring 66 and the expanded diameter portion 62. This prevents the piston portion side end 66a of the return spring 66 from getting caught on the expanded diameter portion 62 when the return spring 66 expands or contracts, thereby sufficiently stabilizing the pressing force of the return spring 66. As a result, the reciprocating motion of the piston portion 55 of the pump 50 is stabilized, further improving the reliability of the hydraulic control unit 100. Therefore, the hydraulic control unit 100 configured in this manner can both suppress radial movement of the return spring 66 and sufficiently increase the stability of the pressing force of the return spring 66.

[0078] Preferably, in the reciprocating direction of the piston portion 55 (left-right direction on the paper in FIGS. 3 to 5 ), the distance L between the end 62 a on the compartment-side end 55 b side of the expanded diameter portion 62 and the step portion 64 is less than 1.5 times the diameter d of the wire rod 66 b of the return spring 66. This prevents the wire rod 66 b from the piston portion-side end 66 a of the return spring 66 from being caught on the expanded diameter portion 62 after the second turn when the return spring 66 expands or contracts. Therefore, the pressing force of the return spring 66 is sufficiently stable when the return spring 66 expands or contracts. As a result, the reciprocating motion of the piston portion 55 of the pump 50 is stabilized, further improving the reliability of the hydraulic control unit 100. Therefore, the hydraulic control unit 100 configured in this manner can simultaneously suppress the radial movement of the return spring 66 and sufficiently increase the stability of the pressing force of the return spring 66.

[0079] Preferably, the expanded diameter portion 62 has a tapered shape. The tapered expanded diameter portion 62 has a smoothly changing diameter, so that a shape that the return spring 66 can easily get caught on is not formed on the outer circumferential surface. This prevents the return spring 66 from getting caught on the expanded diameter portion 62 when the return spring 66 expands or contracts, and therefore the pressing force of the return spring 66 is sufficiently stabilized. As a result, the reciprocating motion of the piston portion 55 of the pump 50 is stabilized, further improving the reliability of the hydraulic control unit 100. Therefore, the hydraulic control unit 100 configured in this manner can both suppress radial movement of the return spring 66 and sufficiently increase the stability of the pressing force of the return spring 66.

[0080] When the inlet-side check valve 70 is configured to include the seat 73 and the ball 71 as described above, the seat 73 is preferably disposed in an area on the input-side end 55a side with respect to the end 62a of the expanded diameter portion 62. In other words, the seat 73 is disposed in a position facing the expanded diameter portion 62, or on the side farther from the compression chamber 52 than the end 62a. By disposing the seat 73 in this manner, the thickness of the piston portion 55 around the seat 73 can be sufficiently ensured. This makes it possible to sufficiently increase the strength of the piston portion 55 around the seat 73 with which the ball 71 abuts. In a conventional configuration in which the piston portion 55 does not have the expanded diameter portion 62, it is difficult to ensure a sufficient thickness of the piston portion 55 around the seating portion 73 by adjusting the arrangement of the seating portion 73. In contrast, in the present embodiment, the diameter of the expanded diameter portion 62 increases as it approaches the step portion 64, so it is possible to ensure a sufficient thickness by adjusting the arrangement of the seating portion 73. Therefore, in the hydraulic control unit 100 having the expanded diameter portion 62, such a configuration is particularly effective from the viewpoint of sufficiently increasing the strength of the piston portion 55 around the seating portion 73.

[0081] [ 0 0 6 2 ]

[0082] <Modification> Fig. 6 is a diagram illustrating a modification of a hydraulic control unit according to an embodiment of the present invention, and is a cross-sectional view showing a portion of a pump. Fig. 6 is a diagram showing the vicinity of a step 54 of a piston 55 of a pump 50. The shape of the expanded diameter portion 62 is not limited to a tapered shape as long as the diameter increases toward the step 64. For example, as shown in Fig. 6, the expanded diameter portion 62 may have a shape in which the diameter increases in a stepped manner toward the step 64. In the hydraulic control unit 100 configured in this manner, the expanded diameter portion 62 can also prevent the piston portion side end 66a of the return spring 66 from moving in the radial direction of the return spring 66. In other words, the hydraulic control unit 100 configured in this manner can also prevent the return spring 66 from moving radially of the return spring 66 by the expanded diameter portion 62.

[0083]

[0063] Fig. 7 is a diagram illustrating a modified example of a hydraulic control unit according to an embodiment of the present invention, and is a cross-sectional view showing a portion of a pump. Fig. 7 shows the vicinity of a step 54 of a piston 55 of a pump 50. In the hydraulic control unit 100 shown in Figs. 1 to 6, the surface 64a of the step 64 against which the piston-portion-side end 66a of the return spring 66 a abuts is flat. On the other hand, in the hydraulic control unit 100 shown in Fig. 7, the piston 55 has a groove 64b on the surface 64a of the step 64, into which the piston-portion-side end 66a of the return spring 66 is inserted. The hydraulic control unit 100 configured in this manner can better prevent the piston portion side end 66a of the return spring 66 from moving in the radial direction of the return spring 66. In other words, the hydraulic control unit 100 configured in this manner can better prevent the return spring 66 from moving in the radial direction of the return spring 66. On the other hand, when the surface 64a of the step portion 64 is a flat surface, the radial dimension of the step portion 64 can be more reduced compared to when a groove portion 64 is provided on the surface 64a, so the hydraulic control unit can be made more compact.

[0084]

[0064] <Effects of the hydraulic pressure control unit> The effects of the hydraulic pressure control unit according to this embodiment will be described.

[0085]

[0065] The hydraulic control unit 100 according to this embodiment is a hydraulic control unit for a brake system 10 mounted on a saddle-ride type vehicle 200. The hydraulic control unit 100 includes a base 101 having an internal flow path 40 that connects a wheel cylinder 24 and a master cylinder 21, and a pump 50 that moves brake fluid in the internal flow path 40. The pump 50 includes a cylinder 51 having a compression chamber 52 that compresses the brake fluid, and a partition-side end 55b at one end of the pump 50, which is pressed by a motor 90 that is the drive source of the pump 50, and a partition-side end 55c at the other end of the pump 50, which is pressed by a compression chamber 52.

[0086] a piston portion 55 inserted into the compression chamber 52 to define the compression chamber 52, and a partition-side end portion 55 b reciprocating within the compression chamber 52; and a return spring that presses the piston portion 55 toward the motor 90.

[0087] Furthermore, the return spring 66 is provided on the outside of the piston portion 55. The piston portion 55 is provided with a stepped portion 64 that is provided on the outer periphery of the piston portion 55 and against which a piston portion side end 66 a, which is one end of the return spring 66, abuts and is pressed by the return spring 66 in the direction toward the motor 90, and an enlarged diameter portion 62 that is provided opposite the inner periphery of the piston portion side end 66 a of the return spring 66 and whose diameter increases as it approaches the stepped portion 64.

[0088]

[0066] As described above, the hydraulic control unit 100 configured in this manner can be made smaller than conventional hydraulic control units, and the enlarged diameter portion 62 can also prevent the return spring 66 from moving in the radial direction of the return spring 66.

[0089]

[0067] Although the hydraulic control unit 100 according to this embodiment has been described above, the hydraulic control unit according to the present invention is not limited to the description of this embodiment. The hydraulic control unit according to the present invention may be implemented in a manner that implements only a part of this embodiment. For example, the hydraulic control unit according to the present invention may be configured not to perform the above-described pressure increase control. In this case, the hydraulic control unit according to the present invention does not include the switching valve 28, the pressure increase valve 29, and the pressure increase flow path 43, which are necessary for pressure increase control.

[0090] [Explanation of symbols]

[0091] [ 0 0 6 8 ]

[0092] ! Fuselage, 2 handles, 3 front wheels, 3 a rotor, 4 rear wheels, 4 a rotor, 1 0

[0093]

Claims

[Document name] Scope of claims

1. A hydraulic control unit (100) for a brake system (10) mounted on a saddle-ride type vehicle (200), comprising: a base (101) in which an internal flow path (40) for communicating a wheel cylinder (24) with a master cylinder (21) is formed; and a pump (50) for moving brake fluid in the internal flow path (40), wherein the pump (50) comprises a cylinder (51) in which a compression chamber (52) for compressing the brake fluid is formed, and a pump (50) having an input side end (55a) which is one end pressed by a motor (90) which is a drive source of the pump (50) and a partition side end (55b) which is the other end pressed by a partition side end (55c) which is connected to the compression chamber (52). a piston portion (55) inserted into the motor (90) to define the compression chamber (52), the end portion (55b) of the piston portion (55) reciprocating within the compression chamber (52), and a return spring that presses the piston portion (55) toward the motor (90). The return spring (66) is provided outside the piston portion (55), and the piston portion (55) is provided on the outer periphery of the piston portion (55), and the return spring (66) is provided with a stepped portion (64) against which a piston portion-side end (66a) that is one end of the return spring (66) comes into contact and which is pressed by the return spring (66) in a direction toward the motor (90), and an expanded diameter portion (62) that is provided opposite to the inner periphery of the piston portion-side end (66a) of the return spring (66), and the diameter of which increases as it approaches the stepped portion (64). To ( 1 0 0 ).

2. A hydraulic control unit (100) according to claim 1, wherein a gap (63) is formed between the inner peripheral portion of the piston portion side end (66a) of the return spring (66) and the expanded diameter portion (62).

3. A hydraulic control unit (100) according to claim 1, wherein a distance (L) between an end (62a) of the expanded diameter portion (62) on the compartment-side end (55b) side and the step portion (64) in the reciprocating direction of the piston portion (55) is less than 0.5 times a diameter (d) of a wire rod (66b) of the return spring (66).

4. A hydraulic control unit (100) according to any one of claims 1 to 3, wherein the enlarged diameter portion (62) has a tapered shape.

5. The hydraulic control unit (100) according to any one of claims 1 to 3, wherein the diameter of the enlarged diameter portion (62) is increased in a stepped manner as it approaches the step portion (64).

6. A hydraulic control unit (100) according to any one of claims 1 to 3, wherein a surface (64a) of the step portion (64) against which the piston portion side end portion (66a) abuts is a flat surface. [Claim ?] The piston portion (55) has a groove portion (64b) in which the piston portion side end portion (66a) of the step portion (64) is inserted, on a surface (64a) with which the piston portion side end portion (66a) of the step portion (64) abuts. The hydraulic control unit (100) according to any one of claims 1 to 3, comprising:

8. The piston portion (55) is formed with an inflow passage (65) into which brake fluid flowing through the internal passage (40) toward the pump (50) flows and which guides the brake fluid to the compression chamber (52), and the piston portion (55) is provided with an inflow-side check valve (70) that is provided in the inflow passage (65) and that regulates the flow of brake fluid from the compression chamber (52) toward the internal passage (40), and the inflow-side check valve (70) has a seat (73) provided in the inflow passage (65) and a ball (71) that abuts against the seat (73) and closes the inflow passage (65). ), and the seating portion (73) is provided at the end (65b) of the enlarged diameter portion (62) on the compartment side end (55b). The hydraulic control unit (100) according to any one of claims 1 to 3, wherein the hydraulic control unit (100) is arranged in an area on the input side end (55a) side with respect to the input side end (55b).

9. The hydraulic control unit (100) according to any one of claims 1 to 3, wherein the piston portion (55) comprises a first piston member (56) having the input side end portion (55a) and a second piston member (61) that is a separate member from the first piston member (56) and has the partition side end portion (55b), the return spring (66) is provided on the outside of the second piston member (61) of the piston portion (55), and the stepped portion (64) and the expanded diameter portion (62) are provided on the outer periphery S of the second piston member (61).

10. A straddle-type vehicle (200) equipped with a hydraulic pressure control unit (100) according to any one of claims 1 to 3.

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