JP2018091221A - Swage fixing structure for plunger pump, brake device and method for manufacturing brake device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a swage fixing structure for a plunger pump that can inhibit an increase in swage load, and to provide a brake device and a method for manufacturing a brake device.SOLUTION: A swage fixing structure for a plunger pump is provided with a groove across the whole circumference of an opening end of a cylinder storage hole for storing a plunger pump.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a caulking fixing structure for a plunger pump, a brake device, and a method for manufacturing the brake device.

  Various conventional pump devices are provided, and one of them is disclosed, for example, in Patent Document 1 below. Briefly, a caulking tool has been proposed in which a notch is provided in the caulking tool when the electromagnetic valve is attached to the housing. This notch prevents the caulking meat from escaping inward in the radial direction and provides a high pressure load in the radial direction, thereby improving the high sealing performance and long-term durability.

Special Table 2004-508200

However, in Patent Document 1, in addition to the complicated shape of the caulking tool, the caulking load increases and the housing may be deformed.
An object of the present invention has been devised in view of the prior art, and is to provide a caulking fixing structure for a plunger pump, a brake device, and a method for manufacturing the brake device that can suppress an increase in caulking load.

    In the present invention, the inner wall of the hole in which the caulking member is disposed is such that the volume of the housing that has been caulked and deformed inward from the inner wall of the hole in which the caulking member is disposed is directed toward the shear surface of the housing. Is larger than the volume of the projection space projected to the region extended in the direction of the operation axis of the plunger pump.

  Therefore, an increase in caulking load can be suppressed.

It is a figure which shows the brake device of Example 1. FIG. It is sectional drawing of the plunger pump of Example 1. FIG. It is an expanded sectional view of the plunger pump and housing of Example 1. It is a disassembled perspective view of the housing of Example 1, a motor, and a plunger pump. It is an expanded sectional view of the plunger pump and housing before caulking of Example 1. It is a principal part expanded sectional view of the plunger pump before caulking of Example 1, and a housing. It is a principal part expanded sectional view of the plunger pump and housing after caulking of Example 1. FIG. Explanatory drawing which shows the relationship between the area (volume) of the projection space of Example 1, and the area (volume) of the caulking deformation part of the housing 8 It is a figure which shows the relationship between the caulking load of Example 1, and a caulking stroke. It is a figure which shows the plunger pump discharge pulse pressure in the hydraulic pressure holding | maintenance of Example 1. FIG. It is a principal part expanded sectional view of the plunger pump before caulking of Example 2, and a housing. It is a principal part expanded sectional view of the plunger pump before caulking of Example 3, and a housing.

[Example 1]
FIG. 1 is a diagram illustrating a brake device according to a first embodiment. The brake device according to the first embodiment includes a brake pedal BP, a master cylinder unit MU, a valve unit BU, a reservoir tank RSV, and a control unit CU. The master cylinder unit MU and the valve unit BU are separate bodies, and both units are assembled with bolts to form a plurality of oil passages 8a, 8b, 11a. In addition, you may connect between both units via the steel pipe etc. not only in the structure which makes a housing directly.

  The master cylinder unit MU includes a stroke sensor S1 that detects a brake operation amount (stroke of the brake pedal BP) of the driver. The master cylinder unit MU includes a master cylinder M / C and a stroke simulator SS. The master cylinder M / C has a primary fluid chamber 7a and a secondary fluid chamber 7b, and brake fluid is supplied from the reservoir tank RSV. When the brake pedal BP is depressed, brake fluid is output from the primary fluid chamber 7a to the primary system via the primary piston 7c. At the same time, brake fluid is output from the secondary fluid chamber 7b to the secondary system via the secondary piston 7d. The primary liquid chamber 7a is connected to the wheel cylinders W / C of the left front wheel FL and the right rear wheel RR via the oil passage 8a. The secondary liquid chamber 7b is connected to the wheel cylinders W / C of the left rear wheel RL and the right front wheel FR via the oil passage 8b.

  A primary system pressure sensor S3 for detecting the primary system pressure is provided on the oil passage 8a. A secondary system pressure sensor S4 that detects the secondary system pressure is provided on the oil passage 8b. A primary cut valve 9a is provided on the oil passage 8a to shut off between the primary liquid chamber 7a and the wheel cylinder W / C, and the secondary liquid chamber 7b and the wheel cylinder W are provided on the oil passage 8b. A secondary cut valve 9b is provided to cut off between / C. The primary cut valve 9a and the secondary cut valve 9b are both normally open solenoid valves.

  The positive pressure chamber 10a and the back pressure chamber 10b of the stroke simulator SS are liquid-tightly separated from each other, so that the brake fluid cannot pass back and forth. The positive pressure chamber 10a is connected to the oil passage 25a. The oil passage 25a is connected to the secondary liquid chamber 7b. A master pressure sensor S2 that detects the master pressure is provided on the oil passage 8b upstream of the secondary cut valve 9b. The stroke simulator SS has a spring 10c in the back pressure chamber 10b, and generates an operation reaction force on the brake pedal BP according to the stroke of the piston 10d. The back pressure chamber 10b is connected to the oil passage 13a through the oil passage 11a, and is connected to the oil passage 8b through the oil passage 11a and the oil passage 11b. A stroke simulator out valve (stroke simulator adjusting valve) 12 is provided in the oil passage 11a. A stroke simulator-in valve 14 is provided in the oil passage 11b.

  The stroke simulator out valve 12 and the stroke simulator in valve 14 are both normally closed solenoid valves. A check valve 26 is provided in parallel with the stroke simulator out valve 12. The check valve 26 permits the brake fluid to flow into the oil passage 11a when the pressure in the oil passage 11a is smaller than that of the oil passage 13a. A check valve 27 is provided in parallel with the stroke simulator-in valve 14. The check valve 27 permits the brake fluid to flow into the oil passage 15a when the pressure in the oil passage 15a is smaller than the pressure in the oil passage 11a. Between the oil passage 8a and the oil passage 15a, a primary communication valve 16a capable of switching communication / blocking between the primary system and the pump discharge system is provided. Further, a secondary communication valve 16b that can switch communication / blocking between the secondary system and the pump discharge system is provided between the oil path 8b and the oil path 15a. The primary communication valve 16a and the secondary communication valve 16b are both normally closed solenoid valves. The oil passage 15a is provided with a pump pressure sensor S5 that detects the pump discharge pressure.

The valve unit BU has a pump motor PM which is a brush motor. The pump motor PM drives the plunger pump 3, and discharges the brake fluid sucked from the reservoir tank RSV through the oil passage 17a to the oil passage 15a. A liquid reservoir 20 is provided on the suction side of the plunger pump 3 in the housing of the valve unit BU. Even when the brake fluid leaks from the oil passage 17a, the fluid reservoir 20 can function as a brake fluid supply source (to the plunger pump 3), a discharge destination (from the wheel cylinder W / C), etc. The wheel cylinder hydraulic pressure increase / decrease control can be continued.
A pressure regulating valve 21 is provided between the oil passage 15a and the oil passage 13a, and excess brake fluid discharged from the plunger pump 3 can be returned to the reservoir tank RSV via the oil passage 13a. . The pressure regulating valve 21 is a normally open type electromagnetic valve, but may be a normally closed type.
Between the oil passage 8a and the wheel cylinder W / C (FL), a left front wheel pressure increasing valve 22a for adjusting the brake fluid flowing from the oil passage 8a to the wheel cylinder W / C (FL) is provided. Further, a check valve 23a is provided in parallel with the left front wheel booster valve 22a. The check valve 23a permits the brake fluid to flow into the oil passage 8a when the pressure in the oil passage 8a is smaller than the pressure of the wheel cylinder W / C (FL). Between the wheel cylinder W / C (FL) and the oil passage 13a, a left front wheel pressure reducing valve 24a for reducing the pressure of the wheel cylinder W / C (FL) is provided.

Between the oil passage 8a and the wheel cylinder W / C (RR), a right rear wheel pressure increasing valve 22b for adjusting brake fluid flowing from the oil passage 8a to the wheel cylinder W / C (RR) is provided. Further, a check valve 23b is provided in parallel with the right rear wheel booster valve 22b. The check valve 23b permits the brake fluid to flow into the oil passage 8a when the pressure in the oil passage 8a is smaller than the pressure of the wheel cylinder W / C (RR). Between the wheel cylinder W / C (RR) and the oil passage 13a, there is provided a right rear wheel pressure reducing valve 24b for reducing the pressure of the wheel cylinder W / C (RR).
Between the oil passage 8b and the wheel cylinder W / C (RL), a left rear wheel pressure increasing valve 22c for adjusting the brake fluid flowing from the oil passage 8b to the wheel cylinder W / C (RL) is provided. Further, a check valve 23c is provided in parallel with the left rear wheel booster valve 22c. The check valve 23c permits the brake fluid to flow into the oil passage 8b when the pressure in the oil passage 8b is smaller than the pressure of the wheel cylinder W / C (RL). Between the wheel cylinder W / C (RL) and the oil passage 13a, a left rear wheel pressure reducing valve 24c for reducing the pressure of the wheel cylinder W / C (RL) is provided.
Between the oil passage 8b and the wheel cylinder W / C (FR), a right front wheel pressure increasing valve 22d for adjusting the brake fluid flowing from the oil passage 8b to the wheel cylinder W / C (FR) is provided. Further, a check valve 23d is provided in parallel with the right front wheel booster valve 22d. The check valve 23d permits the brake fluid to flow into the oil passage 8b when the pressure in the oil passage 8b is smaller than the pressure of the wheel cylinder W / C (FR). A right front wheel pressure reducing valve 24d for reducing the pressure of the wheel cylinder W / C (FR) is provided between the wheel cylinder W / C (FR) and the oil passage 13a.
Each of the pressure increasing valves 22a, 22b, 22c, and 22d is a normally open type electromagnetic valve, and each of the pressure reducing valves 24a, 24b, 24c, and 24d is a normally closed type electromagnetic valve.

  The control unit CU controls the primary cut valve 9a and the secondary cut valve 9b in the closing direction and closes the stroke simulator in valve 14 during normal braking in which each wheel generates a braking force according to the amount of brake operation by the driver. The valve direction is controlled, the stroke simulator out valve 12 is controlled in the valve opening direction, the primary communication valve 16a and the secondary communication valve 16b are controlled in the valve opening direction, the pressure regulating valve 21 is controlled in the valve closing direction, and the pump motor Activate PM. Thereby, desired brake fluid can be sent from the reservoir tank RSV to each wheel cylinder W / C via the oil passage 17a → the plunger pump 3 → the oil passage 15a → the oil passage 8a and the oil passage 8b. At this time, a desired braking force is obtained by feeding back the detected values of the primary system pressure sensor S3, the secondary system pressure sensor S4, and the pump pressure sensor S5 so that the rotation of the pump motor PM and the pressure regulating valve 21 become the target pressure. Is obtained. In addition, the brake fluid sent from the secondary fluid chamber 7b of the master cylinder M / C is guided to the positive pressure chamber 10a of the stroke simulator SS, and the piston 10d moves, whereby a reaction force acts on the spring 10c, and the brake pedal A reaction force according to the operation is created. Accordingly, it is possible to generate an appropriate braking force and a reaction force and a stroke of the brake pedal BP during the braking operation.

  In the first embodiment, when the brake fluid leaks from the piping of the master cylinder M / C, a brake operation amount of the driver is generated when a failure occurs in which the stroke of the brake pedal BP is excessive with respect to the master pressure from the normal time. Accordingly, the boost control of the wheel cylinder W / C by the pump motor PM is continued. The target hydraulic pressure of the wheel cylinder W / C is calculated from the detected values of the stroke sensor S1 and the master pressure sensor S2 as in the normal case. Therefore, if the stroke S of the brake pedal BP or the master pressure Pmc is output, the target hydraulic pressure is not affected. Accordingly, the boost control of the wheel cylinder W / C can be performed in the same manner as normal without affecting the wheel cylinder W / C pressure.

  FIG. 2 is a cross-sectional view of the plunger pump of the first embodiment, and FIG. 3 is an enlarged cross-sectional view of the pump portion of the first embodiment. The axis (axis) of the rotation shaft of the pump motor PM substantially coincides with the axis O of the cam housing hole 81. The cam accommodation hole 81 accommodates the rotation drive shaft 300 which is the rotation shaft and drive shaft of the plunger pump 3 and the cam unit 30. The rotation drive shaft 300 is a drive shaft of the plunger pump 3. The rotation drive shaft 300 is connected and fixed to the rotation shaft of the pump motor PM so that its axis extends on the extension of the rotation shaft of the pump motor PM, and is rotated by the pump motor PM. The axis of the rotary drive shaft 300 substantially coincides with the axis O. The rotary drive shaft 300 rotates around the axis O together with the rotary shaft of the pump motor PM. The cam unit 30 is provided on the rotation drive shaft 300. The cam unit 30 includes a cam 301, a drive member 302 (outer ring), and a plurality of rolling elements 303. The cam 301 is a cylindrical eccentric cam, and has an axis P that is eccentric with respect to the axis O of the rotary drive shaft 300. The axis P extends substantially parallel to the axis O. The cam 301 swings while rotating around the axis O integrally with the rotation drive shaft 300. The drive member 302 (outer ring) has a cylindrical shape and is disposed on the outer peripheral side of the cam 301. The axis of the drive member 302 (outer ring) substantially coincides with the axis P. The drive member 302 (outer ring) can rotate around the axis P with respect to the cam 301. The drive member 302 (outer ring) is an eccentric bearing having the same configuration as the outer ring of the rolling bearing. The plurality of rolling elements 303 are disposed between the outer peripheral surface of the cam 301 and the inner peripheral surface of the drive member 302 (outer ring). The rolling element 303 is a needle roller and extends along the axial direction of the rotation drive shaft 300.

  The plunger pump 3 is a fixed cylinder type radial plunger pump, and includes a housing 8, a rotary drive shaft 300, a cam unit 30, and a plurality (five) of pump units 3A to 3E. The pump units 3 </ b> A to 3 </ b> E are plunger pumps (piston pumps) as reciprocating pumps, and operate by rotation of the rotary drive shaft 300. As the plunger (piston) 36 reciprocates, the brake fluid is sucked and discharged as hydraulic fluid. The cam unit 30 has a function of converting the rotary motion of the rotary drive shaft 300 into the reciprocating motion of the plunger 36. When the configurations of the pump units 3A to 3E are distinguished from each other, suffixes A to E are added to the reference numerals. Each plunger 36 is arranged around the cam unit 30 and is accommodated in the cylinder accommodation hole 82, respectively. An axis 360 of the plunger 36 substantially coincides with the axis of the cylinder accommodation hole 82 and extends in the radial direction of the rotary drive shaft 300. In other words, the plungers 36 are provided by the number of cylinder accommodation holes 82 (five), and extend in the radial direction with respect to the axis O. The plungers 36 </ b> A to 36 </ b> E are arranged substantially evenly in the direction around the rotation drive shaft 300 (hereinafter simply referred to as the circumferential direction), that is, at substantially equal intervals in the rotation direction of the rotation drive shaft 300. The axes 360A to 360E of the plungers 36A to 36E are in the same plane. These plungers 36A to 36E are driven by the same rotation drive shaft 300 and the same cam unit 30.

  The pump portion 3A includes a cylinder sleeve 31, a filter member 32, a plug member 33 that is a caulking member, a guide ring 34, a first seal ring 351, a second seal ring 352, a plunger 36, and a return spring. 37, a suction valve 38, and a discharge valve 39, which are installed in the cylinder accommodation hole 82. The cylinder sleeve 31 has a bottomed cylindrical shape, and a through hole 311 passes through the bottom portion 310. The cylinder sleeve 31 is fixed to the cylinder accommodation hole 82. The axis of the cylinder sleeve 31 substantially coincides with the axis 360 of the cylinder accommodation hole 82. An end 312 on the opening side of the cylinder sleeve 31 is disposed in the medium diameter portion 822 (suction port 823), and the bottom portion 310 is disposed in the large diameter portion (discharge port) 821. The filter member 32 has a bottomed cylindrical shape, and a hole 321 passes through the bottom 320, and a plurality of openings penetrates the side wall. A filter is installed in the opening. An end 323 on the opening side of the filter member 32 is fixed to an end 312 on the opening side of the cylinder sleeve 31. The bottom part 320 is disposed in the small diameter part 820. The axis of the filter member 32 substantially coincides with the axis 360 of the cylinder accommodation hole 82. There is a gap between the outer peripheral surface where the opening of the filter member 32 opens and the inner peripheral surface of the cylinder accommodation hole 82 (suction port 823). The first communication fluid path communicates with the suction port 823 and the gap. The plug member 33 has a columnar shape, and has a bottomed cylindrical discharge chamber 330 and a discharge passage 331 on one axial end side thereof. The discharge passage 331 extends in the radial direction, connects the discharge chamber 330 and the outer peripheral surface of the plug member 33, and communicates with the discharge port 821. One end side in the axial direction of the plug member 33 is fixed to the bottom 310 of the cylinder sleeve 31. The axial center of the plug member 33 substantially coincides with the axial center 360 of the cylinder accommodation hole 82. The plug member 33 is fixed to the large diameter portion 821 and closes the opening of the cylinder accommodation hole 82 on the outer peripheral surface of the housing 8. The second communication liquid path communicates with the discharge port 821 and the discharge passage 331 of the plug member 33. The guide ring 34 has a cylindrical shape, and is fixed to the cam housing hole 81 side (small diameter portion 820) with respect to the filter housing 32 in the cylinder housing hole 82. The axis of the guide ring 34 substantially coincides with the axis 360 of the cylinder accommodation hole 82. The first seal ring 351 is installed between the guide ring 34 and the filter member 32 in the cylinder accommodation hole 82 (small diameter portion 820).

  The plunger 36 has a cylindrical shape, and has an end surface (hereinafter referred to as a plunger end surface) 361 on one side in the axial direction, and a flange portion 362 on the outer periphery on the other side in the axial direction. The plunger end surface 361 has a planar shape extending in a direction substantially perpendicular to the axis 360 of the plunger 36 and has a substantially circular shape centering on the axis 360. The plunger 36 has an axial hole 363 and a radial hole 364 therein. The axial hole 363 extends on the axial center 360 and opens on the end surface of the plunger 36 on the other axial direction side. The radial hole 364 extends in the radial direction of the plunger 36, opens on the outer peripheral surface on one side in the axial direction than the flange portion 362, and connects to the one axial direction side of the axial hole 363. A check valve case 365 is fixed to the other end of the plunger 36 in the axial direction. The check valve case 365 has a bottomed cylindrical shape made of a thin plate, has a flange portion 366 on the outer periphery of the end portion on the opening side, and a plurality of holes 368 pass through the side wall portion and the bottom portion 367. The end of the check valve case 365 on the opening side is fitted to the end of the plunger 36 on the other side in the axial direction. The second seal ring 352 is installed between the flange portion 366 of the check valve case 365 and the flange portion 362 of the plunger 36. The other axial direction other side of the plunger 36 is inserted into the inner peripheral side of the cylinder sleeve 31, and the flange portion 362 is guided and supported by the cylinder sleeve 31. The axial direction one side of the plunger 36 from the radial hole 364 is on the inner peripheral side (hole 321) of the bottom portion 320 of the filter member 32, the inner peripheral side of the first seal ring 351, and the inner peripheral side of the guide ring 34. Inserted and guided and supported by these. The axial center 360 of the plunger 36 substantially coincides with the axial center of the cylinder sleeve 31 and the like (cylinder housing hole 82). An end (plunger end surface 361) on one side in the axial direction of the plunger 36 protrudes into the cam housing hole 81.

  The return spring 37 is a compression coil spring and is installed on the inner peripheral side of the cylinder sleeve 31. One end of the return spring 37 is installed on the bottom portion 310 of the cylinder sleeve 31, and the other end is installed on the flange portion 366 of the check valve case 365. The return spring 37 always urges the plunger 36 toward the cam housing hole 81 with respect to the cylinder sleeve 31 (cylinder housing hole 82). The suction valve 38 includes a ball 380 as a valve body and a return spring 381, which are accommodated on the inner peripheral side of the check valve case 365. A valve seat 369 is provided around the opening of the axial hole 363 on the end surface on the other axial side of the plunger 36. When the ball 380 is seated on the valve seat 369, the axial hole 363 is closed. The return spring 381 is a compression coil spring, one end of which is installed on the bottom 367 of the check valve case 365 and the other end of which is installed on the ball 380.

  The return spring 381 always urges the ball 380 toward the valve seat 369 with respect to the check valve case 365 (plunger 36). The discharge valve 39 includes a ball 390 as a valve body and a return spring 391, which are accommodated in the discharge chamber 330 of the plug member 33. A valve seat 313 is provided around the opening of the through hole 311 in the bottom 310 of the cylinder sleeve 31. When the ball 390 is seated on the valve seat 313, the through hole 311 is closed. The return spring 391 is a compression coil spring, one end of which is installed on the bottom surface of the discharge chamber 330 and the other end is installed on the ball 390. The return spring 391 always urges the ball 390 toward the valve seat 313.

  Inside the cylinder housing hole 82, the space R1 closer to the cam housing hole 81 than the flange portion 362 of the plunger 36 is a space on the suction side communicating with the first communication liquid path. Specifically, from the gap between the outer peripheral surface of the filter member 32 and the inner peripheral surface (suction port 823) of the cylinder housing hole 82, a plurality of openings of the filter member 32, and the outer peripheral surface of the plunger 36 and the filter member A space that passes through the gap between the inner peripheral surface of 32 and reaches the radial hole 364 and the axial hole 363 of the plunger 36 functions as a suction side space R1. The suction-side space R1 is prevented from communicating with the cam housing hole 81 by the first seal ring 351.

  Inside the cylinder accommodation hole 82, a space R3 between the cylinder sleeve 31 and the plug member 33 is a discharge-side space communicating with the second communication liquid path. Specifically, the space from the discharge passage 331 of the plug member 33 to the discharge port 821 functions as the discharge side space R3. On the inner peripheral side of the cylinder sleeve 31, the volume of the space R2 between the flange portion 362 of the plunger 36 and the bottom portion 310 of the cylinder sleeve 31 changes due to the reciprocating movement (stroke) of the plunger 36 with respect to the cylinder sleeve 31. This space R2 communicates with the suction side space R1 by opening the suction valve 38, and communicates with the discharge side space R3 by opening the discharge valve 39.

  The plunger 36 of the pump unit 3A reciprocates to perform a pumping action. That is, when the plunger 36 strokes toward the cam housing hole 81 (axial center O), the volume of the space R2 increases and the pressure in R2 decreases. When the discharge valve 39 is closed and the suction valve 38 is opened, the brake fluid as the working fluid flows from the suction side space R1 into the space R2, and from the first communication fluid path through the suction port 823, the space R2 Brake fluid is supplied to When the plunger 36 strokes away from the cam housing hole 81, the volume of the space R2 decreases, and the pressure in R2 increases. When the suction valve 38 is closed and the discharge valve 39 is opened, the brake fluid flows out from the space R2 through the through hole 311 to the discharge side space R3, and to the second communication liquid path through the discharge port 821. Brake fluid is supplied. The other pump units 3B to 3E have the same configuration. The brake fluid discharged from each pump unit 3A to 3E to the second communication fluid path is collected in one discharge fluid path 13, and is commonly used in two systems of hydraulic circuits.

  FIG. 4 is an exploded perspective view of the housing 8, the motor PM, and the plunger pump 3 according to the first embodiment.

  Here, as shown in FIG. 4, the five plunger pumps 3A to 3E as the caulking members are respectively plugged into the five cylinder housing holes 82A to 82E provided in the housing 8 with the plug members 33 as the caulking members. The plunger pumps 3A to 3E are fixed to the housing 8 by being inserted so as to be positioned on the opening end sides of the cylinder housing holes 82A to 82E and caulking the opening ends of the cylinder housing holes 82A to 82E of the housing 8. doing. After the drive shaft 300 of the electric motor PM is inserted into the cam accommodation hole 81, the electric motor PM is fixed to the housing 8.

FIG. 5 is an enlarged cross-sectional view of the plunger pump and the housing before caulking of the first embodiment, and FIG. 6 is an enlarged cross-sectional view of a main part of the plunger pump and the housing before caulking of the first embodiment.
As shown in FIGS. 5 and 6, the plunger pump 3 is accommodated in the cylinder accommodation hole 82 so that the plug member 33 as the caulking member is positioned on the opening end side. In particular, on the outer surface of the plug member 33, a cylindrical contact portion 33d that comes into contact with the inner wall 82a of the cylinder housing hole 82, an inclined portion 33a that continues to the contact portion 33d in the upward direction in the figure, and a continuous diameter reduction. A stepped portion 33c and a horizontal portion 33b are formed. A space 500 formed by the stepped portion 33c, the inclined portion 33a, and the inner wall 82a of the cylinder accommodating hole 82 becomes a region for accommodating almost the entire deformation due to caulking of the housing 8. The shape of the stepped portion 33c is formed in consideration of the volume of deformation of the housing 8.
Further, since the stepped portion 33c can be gradually reduced in diameter by forming the inclined portion 33a, the meat deformed by caulking of the housing 8 is likely to come into contact with the stepped portion 33c.
A circumferential groove 80 a is formed in the reference surface 80 d of the housing 8 on the outer periphery of the opening end portion of the cylinder accommodation hole 82 of the housing 8. Thereby, an end 80b as a protrusion is formed. Reference numeral 400 denotes a commonly used cylindrical caulking punch. The flat pressing surface of the caulking punch 400 is disposed so as to face the entire circumferential groove 80a formed in the cylinder housing hole 82 and the end surface of the housing 8 and the end 80b on the inner wall 82a side, and moves downward in the figure. The plunger pump 3 is caulked and fixed to the housing 8 by deforming the end 80b of the housing 8.

  FIG. 7 is an enlarged cross-sectional view of a main part of the plunger pump and the housing after caulking in the first embodiment.

  a is a shearing surface generated after caulking by the caulking punch 400. The deformation of the housing 8 deformed by the caulking punch 400 comes into contact with the inclined portion 33a and the stepped portion 33c of the outer peripheral surface of the plug member 33 and is accommodated in the space 500, and the plunger pump 3 is caulked to the housing 8. It is fixed.

  FIG. 8 is an explanatory diagram showing the relationship between the area (volume) of the projection space and the area (volume) of the caulking deformation of the housing 8 according to the first embodiment.

A projection space in which the inner wall 82a of the cylinder housing hole 82 in which the plunger pump 3 is disposed is projected to a line c extending in the operation axis direction of the plunger pump 3 with the shearing surface a generated after caulking by the caulking punch 400 inward. The area B (that is, the volume) of deformation due to caulking of the housing 8 accommodated in the space 500 is larger than the area A (that is, the volume). That is, A <B.
This is because the end 80b is easily deformed by the circumferential groove 80a formed on the end surface of the housing 8, and the meat deformed by caulking of the housing 8 is easily brought into contact with the stepped portion 33c by the inclined portion 33a. Furthermore, since the caulking load is distributed as a component force by the inclined portion 33a, the caulking load can be reduced.

  FIG. 9 is a diagram illustrating the relationship between the caulking load and the caulking stroke in Example 1 and the comparative example.

The solid line is Example 1 and the broken line is a comparative example in which the circumferential groove 80a, the step portion 33c and the inclined portion 33a are not formed, and shows the relationship between the caulking load and the caulking stroke. It can be seen that the maximum caulking load of Example 1 is reduced by 30% or more compared to the comparative example, and the stroke is also reduced.
The final stroke of Example 1 and the comparative example is small because of the springback.

  FIG. 10 is a diagram illustrating the discharge pulse pressure of the plunger pump during the hydraulic pressure holding of Example 1 and the comparative example.

  It can be seen that the variation in Example 1 is smaller than that of the comparative example in which the circumferential groove 80a, the step portion 33c, and the inclined portion 33a are not formed. As the variation is smaller, it is possible to suppress the deterioration of volume efficiency and sound vibration.

Next, the function and effect will be described.
The pump device and the brake device according to the first embodiment have the following effects.
(1) A circumferential groove 80a is provided on the outer periphery of the open end of the inner wall 82a of the cylinder housing hole 82 of the housing 8 with which the caulking punch 400 comes into contact with the reference surface 8d, and the end 80b as a protrusion is deformed. I try to make it easier.
Therefore, an increase in caulking load can be suppressed. Thereby, since the fixing force and the sealing performance of the plunger pump 3 can be obtained with a low caulking load, adverse effects on the plunger pump 3 (variation in discharge performance due to deformation of the housing 8) can be suppressed.
In addition, since it is only necessary to additionally process the entire circumferential groove 80a, it is possible to suppress a decrease in productivity, and it is not necessary to complicate the shape of the caulking punch 400.

(2) The plug member 33 of the plunger pump 3 is provided with a step portion 33c that shrinks inward with respect to the inner wall 82a of the cylinder housing hole 82 so that the caulked deformed housing 8 abuts.
Therefore, the stepped portion 33c formed on the plug member 33 of the plunger pump 3 is matched with the caulking shape of the housing 8, so that the caulking deformation can be performed with a low load.

(3) The plug member 33 of the plunger pump 3 includes a stepped portion 33c that shrinks inward with respect to the inner wall 82a of the cylinder housing hole 82. The stepped portion 33c is formed in the cylinder housing hole 82 in the direction perpendicular to the operating axis of the plunger pump 3. The inner wall 82a is provided with an inclined portion 33a that gradually shrinks inward.
Therefore, when the housing 8 is caulked and deformed, the flesh of the housing 8 that has flowed is likely to come into contact with the stepped portion 33c, thereby forming a space 500 formed by the stepped portion 33c, the inclined portion 33a, and the inner wall 82a of the cylinder housing hole 82. It becomes easy to fill and high fixing force is obtained.

(4) The stepped portion 33c is formed so that the space 500 formed by the stepped portion 33c and the inclined portion 33a of the plug member 33 of the plunger pump 3 and the inner wall 82a of the cylinder housing hole 82 can be accommodated by the caulking deformation volume of the housing 8. Form a shape.
Therefore, by matching the shape of the stepped portion 33c with the deformed shape of the housing 8, the space 500 can be filled with a lower load.

[Example 2]
FIG. 11 is a cross-sectional view of the plunger pump and the housing before caulking according to the second embodiment.
Unlike the first embodiment, a convex portion 80c as a protrusion is provided on the reference surface 80d of the housing 8 at the open end of the inner wall 82a of the cylinder accommodating hole 82 of the housing 8 instead of the entire circumferential groove 80a.
Similarly to the first embodiment, the inner wall 82a of the cylinder housing hole 82 in which the plunger pump 3 is arranged with the shearing surface a generated after caulking by the caulking punch 400 inward is arranged in the operation axis direction of the plunger pump 3. The area B (that is, the volume) of deformation due to caulking of the housing 8 accommodated in the space 500 becomes larger than the area A (that is, the volume) of the projection space projected up to the line c.
Since the other configuration is the same as that of the first embodiment, members that are the same as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and description thereof is omitted.

Next, the function and effect will be described.
A projecting portion 80c as a projecting portion is provided at the open end portion of the inner wall 82a of the cylinder accommodating hole 82 of the housing 8 so as to be easily deformed.
Therefore, an increase in caulking load can be suppressed. Thereby, since the fixing force and the sealing performance of the plunger pump 3 can be obtained with a low caulking load, adverse effects on the plunger pump 3 (variation in discharge performance due to deformation of the housing 8) can be suppressed.
In addition, since it is only necessary to provide the housing 8 with a protrusion 80c as a protrusion on the reference surface 80d, the productivity can be suppressed and the shape of the caulking punch 400 is complicated. There is no need to do.
Other functions and effects are the same as those of the first embodiment.

Example 3
FIG. 12 is an enlarged cross-sectional view of the plunger pump and the housing before caulking according to the third embodiment.
Unlike the first embodiment, the entire circumferential groove 80a at the open end of the inner wall 82a of the cylinder accommodation hole 82 of the housing 8 is omitted.
Similarly to the first embodiment, the inner wall 82a of the cylinder housing hole 82 in which the plunger pump 3 is arranged with the shearing surface a generated after caulking by the caulking punch 400 inward is arranged in the operation axis direction of the plunger pump 3. The area B (that is, the volume) of deformation due to caulking of the housing 8 accommodated in the space 500 becomes larger than the area A (that is, the volume) of the projection space projected up to the line c.
Since the other configuration is the same as that of the first embodiment, members that are the same as those of the first embodiment are denoted by the same reference numerals as those of the first embodiment, and description thereof is omitted.

Next, the function and effect will be described.
(1) The plug member 33 of the plunger pump 3 is provided with a step portion 33c that shrinks inward with respect to the inner wall 82a of the cylinder housing hole 82 so that the caulked deformed housing 8 abuts.
Therefore, the stepped portion 33c formed on the plug member 33 of the plunger pump 3 is matched with the caulking shape of the housing 8, so that the caulking deformation can be performed with a low load.

(2) The plug member 33 of the plunger pump 3 includes a stepped portion 33c that shrinks inward with respect to the inner wall 82a of the cylinder housing hole 82. The stepped portion 33c is in the cylinder housing hole 82 in the direction perpendicular to the operating axis of the plunger pump 3. An inclined portion 33a is provided as an inclined portion that gradually decreases inward with respect to the inner wall 82a.
Therefore, when the housing 8 is caulked and deformed, the flesh of the housing 8 that has flowed is likely to come into contact with the stepped portion 33c, thereby forming a space 500 formed by the stepped portion 33c, the inclined portion 33a, and the inner wall 82a of the cylinder housing hole 82. It becomes easy to fill and high fixing force is obtained.
Further, since only the inclined portion 33a is formed between the stepped portion 33c and the contact portion 33d of the plug member 33, a decrease in productivity can be suppressed, and there is no need to complicate the shape of the caulking punch 400.

(3) The step portion 33c is formed so that the space 500 formed by the step portion 33c and the inclined portion 33a of the plug member 33 of the plunger pump 3 and the inner wall 82a of the cylinder housing hole 82 can be accommodated in the caulking deformation volume of the housing 8. Form a shape.
Therefore, by matching the shape of the stepped portion 33c with the deformed shape of the housing 8, the space 500 can be filled with a lower load.

[Other Examples]
As mentioned above, although demonstrated based on each Example, it is included in this invention even if it is another structure.
For example, in each embodiment, the plunger pump has been described as the caulking member. However, any member that can be caulked and fixed to the housing 8 such as an electromagnetic valve is applicable. Further, the inclined portion 33a may be formed in a horizontal plane.

The technical idea that can be grasped from the embodiment described above will be described below.
In one aspect of the pump device and the brake device, the plunger pump is fixed by caulking and fixing the plunger pump accommodated in the hole provided in the housing by caulking and deforming the housing to the caulking member. Structure,
In the direction perpendicular to the operation axis of the plunger pump in the caulked deformation region,
The volume of the housing deformed by caulking inside the inner wall of the hole in which the caulking member is disposed,
The inner surface of the hole where the caulking member is disposed is larger than the volume of the projection space projected to the region extending in the direction of the operation axis of the plunger pump with the shearing surface of the housing facing inward.
In a more preferred aspect, in the above aspect, the caulking member includes a stepped portion that shrinks inward with respect to the inner wall of the hole in a direction perpendicular to the operation axis of the plunger pump, and the stepped portion is deformed by the caulking. The housing comes into contact.
In still another preferred aspect, in the above aspect, the step portion includes an inclined portion that gradually decreases inward with respect to the inner wall of the hole in a direction perpendicular to the operation axis of the plunger pump.
In still another preferred aspect, in any one of the above aspects, the volume of the housing that is caulked and deformed inside the inner wall of the hole in which the caulking member is disposed is formed by the stepped portion and the inner wall of the hole. Fits into the space.
In still another preferred aspect, in any one of the above aspects, the open end portion of the cylinder accommodation hole is formed with a protrusion that a cylinder jig contacts.
In still another preferred aspect, in the above aspect, the protrusion is formed by processing a recess with respect to a reference surface of the housing.
In still another preferred aspect, in any one of the above aspects, the protrusion is formed by processing as a protrusion with respect to a reference surface of the housing.
In still another preferred embodiment, in any of the above embodiments, the pressing surface of the caulking punch is flat.

M / C master cylinder
PM pump motor (actuator)
RSV reservoir tank
SS stroke simulator
W / C wheel cylinder
3 Plunger pump
31 Cylinder sleeve
33 Plug member (caulking member)
33a Slope
33b Horizontal part
33c Stepped part
36 Plunger (piston)
39 Discharge valve
8 Housing
80a Groove all around
80b end (protrusion)
80c Convex (protrusion)
80d Reference plane
82 Cylinder receiving hole
82a Inner wall of cylinder receiving hole
300 Rotating drive shaft (Rotating shaft)
301 cams
302 Drive member (eccentric cam)
330 Discharge chamber
331 Discharge passage
390 ball (ball valve)
400 Caulking punch

Claims (13)

A plunger pump caulking and fixing structure for fixing a plunger pump accommodated in a hole provided in the housing by caulking and deforming the housing to a caulking member,
In the direction perpendicular to the operation axis of the plunger pump in the caulked deformation region,
The volume of the housing deformed by caulking inside the inner wall of the hole in which the caulking member is disposed,
Plunger having a volume larger than a projection space projected from an inner wall of the hole in which the caulking member is disposed to an area extending in an operation axis direction of the plunger pump toward a shear surface of the housing inward. The caulking fixing structure of the pump. In the caulking and fixing structure of the plunger pump according to claim 1,
The caulking member includes a stepped portion that shrinks inward with respect to the inner wall of the hole in a direction perpendicular to the operation axis of the plunger pump,
The plunger pump caulking and fixing structure, wherein the caulking deformed housing contacts the stepped portion. In the caulking fixing structure of the plunger pump according to claim 2,
The plunger pump caulking fixing structure is characterized in that the step portion includes an inclined portion that gradually shrinks inward with respect to the inner wall of the hole in a direction perpendicular to the operation axis of the plunger pump. In the caulking fixing structure of the plunger pump according to claim 2,
Caulking and fixing of the plunger pump, wherein the volume of the housing that is caulked and deformed inside the inner wall of the hole in which the caulking member is disposed fits in a space formed by the stepped portion and the inner wall of the hole. Construction. A plunger pump;
A plug member arranged in an operating axis direction of the plunger pump;
A hole for accommodating the plunger pump and the plug member, and a fluid passage through which the brake fluid discharged by the plunger pump flows, and the plunger pump is fixed by being caulked and deformed by the plug member. A housing,
In the direction perpendicular to the operation axis of the plunger pump in the caulked deformation region,
The volume caulked and deformed inward from the inner wall of the hole in which the plug member is disposed is directed toward the inner surface of the plunger pump in the direction of the operation axis of the plunger pump, with the shear surface facing inward. A housing having a structure larger than the volume of the projection space projected to the extended region;
A brake device comprising: The brake device according to claim 5,
The plug member includes a stepped portion that contracts inward with respect to the inner wall of the hole in a direction perpendicular to the operation axis of the plunger pump.
The brake device, wherein the caulked deformed housing abuts on the stepped portion. The brake device according to claim 6,
The brake device according to claim 1, wherein the step portion includes an inclined portion that gradually decreases inward with respect to the inner wall of the hole in a direction perpendicular to the operation axis of the plunger pump. The brake device according to claim 6,
The brake device according to claim 1, wherein a volume of the housing that is caulked and deformed inward from an inner wall of the hole in which the plug member is disposed is contained in a space formed by the stepped portion and the inner wall of the hole. A first step of processing a liquid path, a hole, and a protrusion provided on an outer periphery of the opening of the hole into a housing;
A second step of disposing a plunger pump in the hole for discharging brake fluid into the fluid path;
A third step of disposing a plug member on the opening side with respect to the plunger pump in the operation axis direction of the plunger pump;
The volume of the inner housing in the direction perpendicular to the operating axis of the plunger pump that moves by pressing the protrusion from the operating axis direction of the plunger pump is pressed by a caulking punch from the volume of the housing that the caulking punch crushes. A fourth step of fixing the plunger pump to the housing by caulking the housing to the plug member,
A method for manufacturing a brake device comprising: In the manufacturing method of the brake equipment according to claim 9,
The plug member includes a stepped portion that contracts inward with respect to the inner wall of the hole in a direction perpendicular to the operation axis of the plunger pump.
In the fourth step, the brake device manufacturing method is characterized in that the housing is caulked so as to contact the stepped portion. In the manufacturing method of the brake equipment according to claim 9,
In the first step, the protrusion is formed as a recess with respect to a reference surface of the housing in which the hole is provided,
In the fourth step, the concave portion is pressed from the direction of the operating axis of the plunger pump with the caulking punch, and the method for manufacturing a brake device is characterized in that: In the manufacturing method of the brake equipment according to claim 9,
In the first step, the protrusion is formed as a protrusion with respect to a reference surface of the housing in which the hole is provided,
In the fourth step, the bump is pressed from the direction of the operation axis of the plunger pump with the caulking punch. In the manufacturing method of the brake equipment according to claim 9,
In the fourth step, the brake device manufacturing method is characterized in that the projection is pressed from the direction of the operation axis of the plunger pump by a flat pressing surface formed on the caulking punch.

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