JP4583436B2 - Oil pump - Google Patents

Description

  The present invention relates to an oil pump attached to a support member with a plurality of attachment bolts.

  As this type of oil pump, for example, an oil pump described in Patent Document 1 has been proposed.

A pump body of an oil pump described in Patent Document 1 includes a substantially annular cam case that houses a pump element that is rotationally driven by a drive shaft, and a front body and a rear body that are respectively disposed on both sides in the axial direction of the cam case. The front body, the cam case, and the rear body are fastened with fastening bolts, and the mounting bolts are respectively inserted into the plurality of mounting bolt insertion holes formed in the front body. The oil pump is fixed to the support member on the side.
Japanese Patent Laid-Open No. 11-93856

  In the oil pump described in Patent Document 1, the front body is bent and deformed by the axial force of each of the mounting bolts, and the clearance between the pump element and the other components becomes too small. There is a risk of so-called seizure between elements.

  The present invention has been made in view of the above problems, and even in a state where the oil pump is attached to the support member with a plurality of mounting bolts, an appropriate clearance is ensured between the pump element and other components, An object of the present invention is to provide an oil pump that prevents so-called seizure between the pump element and other components.

The invention described in claims 1, 11, and 14, in particular, is provided on the support member via the rear cover by a plurality of mounting bolts that pass through the portion of the housing body on the side opposite to the control valve in the axial direction of the housing body. In addition to mounting , a clearance is formed between the outer surface of the rear cover on the control valve side and the support member. Of the mounting bolts, the control valve is opposite to the control valve sandwiching the drive shaft of the housing body. A gap portion is formed between the peripheral portion of the first mounting bolt through which the side portion is inserted and the rear cover facing the peripheral portion.

According to the first, eleventh and fourteenth aspects of the present invention, the amount of bending deformation of the housing body toward the support member in the vicinity of the first mounting bolt is different from that of the first mounting bolt provided on the control valve side. Since it becomes larger than the amount of deformation of the housing body around the bolt, even when the oil pump is attached to the support member by each mounting bolt, an appropriate clearance is secured between the pump element and other components, It is possible to prevent the occurrence of so-called seizure between the pump element and other components.

As shown in FIGS. 1 and 2, a housing 2 of a vane pump 1 that is a so-called variable displacement type oil pump is divided into a housing body 3 and a rear cover 4, and the housing 2 includes first to third mounting bolts 5. , 6 and 7 are fastened and fixed to the engine block 8 which is a support member on the rear cover 4 side. In the rear cover 4, projecting portions 4 d projecting toward the engine block 8 are formed in the peripheral portions of the mounting bolts 5, 6, 7, and the projecting portions 4 d are seated on the engine block 8. The mounting bolts 5, 6, 7 are inserted into the housing 2 from the housing body 3 side, and are inserted through the housing body 3 and the rear cover 4 and screwed into the engine block 8. The mounting bolts 5, 6 and 7 have the same effective diameter and are tightened with the same tightening torque, so that the mounting bolts 5, 6 and 7 have the same axial force as the housing 2. The engine block 8 is fastened.
Further, a gap is formed between the engine block 8 and the outer surface on the upper side in the drawing from the protruding portion 4 d of the rear cover 4, that is, the outer surface on the control valve 33 side described later.

  Further, a drive pulley 9 that is pivotally supported by the housing 2 is coupled to a projecting portion that projects from the housing main body 3 to the side opposite to the rear cover 4 so that the transmission pulley 10 is integrally rotatable. The vane pump 1 is rotationally driven by an engine that is a motor of a car through an endless belt 11 that is a hook member. The pulley 10 is pulled by the tension of the belt 11 in the direction of the arrow T shown in FIG.

  3 is a cross-sectional view taken along the line AA in FIG. 2 showing the vane pump 1 alone, and FIG. 4 is a cross-sectional view taken along the line BB in FIG. In FIG. 3, the state before the vane pump 1 is fixed to the engine block 8 is illustrated, and the first mounting bolt 5 is omitted for convenience.

  More specifically, as shown in FIGS. 3 and 4, a housing space 3 a for housing a pump element to be described later is recessed in the housing body 3 in the axial direction of the drive shaft 9. A rear cover 4 is assembled to the housing body 3 so as to close 3a. An annular seal ring 12 is provided between the rear cover 4 and the housing body 3 to prevent hydraulic oil leakage from the housing space 3a.

  One end of the drive shaft 9 is pivotally supported by the housing body 3 via a bearing 13 disposed at the end of the housing body 3 opposite to the rear cover 4, while the other end is pivotally supported by the rear cover 4. The intermediate portion of the drive shaft 9 is coupled to the rotor 14 disposed in the accommodation space 3a so as to be integrally rotatable. An oil seal 15 is disposed between the bearing 13 and the accommodating space 3a, and the oil seal 15 seals between the housing body 3 and the drive shaft 9.

  The rotor 14 is accommodated in an eccentric state with respect to the cam ring 16 on the inner peripheral side of the cam ring 16, and vanes 17 are provided in a plurality of vane slots 14a formed in the rotor 14 so as to be able to protrude and retract in the radial direction. The tip of each vane 17 is in sliding contact with the inner peripheral surface of the cam ring 16. That is, a pump element is constituted by the rotor 14, each vane 17 and the cam ring 16, and a plurality of pump chambers 18 partitioned by each vane 17 are formed between the rotor 14 and the cam ring 16 in the circumferential direction.

  The cam ring 16 is supported by a pin 19 so as to be able to swing and displace in the accommodation space 3a, and the amount of eccentricity of the cam ring 16 with respect to the rotor 14 is changed by the swinging displacement of the cam ring 16 around the pin 19. .

  An adapter ring 20 is disposed between the outer peripheral surface of the accommodation space 3 a and the cam ring 16. The inner peripheral surface of the adapter ring 20 is formed in a substantially elliptical shape in front view so as to allow the rocking displacement of the cam ring 16, and the inner peripheral surface is engaged with the pin 19. The adapter ring 20 is prevented from rotating by 19. Further, a seal member 21 is provided on the inner peripheral surface of the adapter ring 20 on the side opposite to the pin 19, and the seal member 21 is in close contact with the cam ring 16 while allowing the cam ring 16 to swing. . That is, the first and second pressure chambers 22a and 22b are separated by the seal member 21 and the pin 19 on both sides of the cam ring 16 in the oscillating displacement direction, and the pressure of the hydraulic oil introduced into the pressure chambers 22a and 22b. The cam ring 16 is oscillated and displaced.

  Further, the cam ring 16 is always urged with a return spring 23 in the left side in FIG. 4, that is, in a direction in which the eccentric amount of the cam ring 16 with respect to the rotor 14 increases, and the return spring 23 is screwed into the housing body 3 from the outer peripheral side. The plug 24 is held.

  On the other hand, a side plate 25 is arranged on the side opposite to the rear cover 4 of the adapter ring 20, and the side plate 25 closes both sides of the adapter ring 20 together with the rear cover 4. Further, a recess for forming a high pressure chamber 3b is provided between the bottom surface of the accommodation space 3a and the side plate 25, and the side plate 25 is attached to the adapter ring 20 by a pump discharge pressure introduced into the high pressure chamber 3b. It is pressed.

  The rear cover 4 is provided with a suction port 26 for sucking hydraulic oil from a tank (not shown). The suction port 26 increases the volume of each pump chamber 18 with the rotation of the rotor 14 in the internal space of the cam ring 16. The suction port 27 that opens to the suction region communicates with the suction passage 28. On the other hand, the housing body 3 is provided with a discharge port 29 for discharging hydraulic oil, and the discharge port 29 is a discharge region in which the volume of each pump chamber 18 decreases as the rotor 14 rotates in the internal space of the cam ring 16. It communicates with a discharge port 30 that is open through a discharge passage (not shown).

  Then, as the rotor 14 rotates, each pump chamber 18 rotates while increasing or decreasing its volume, and the pump is continuously operated.

  In addition, a valve hole 3c is formed in the housing body 3 on one side in the radial direction of the housing space 3a, that is, on the suction region side, along a direction orthogonal to the drive shaft 9 in a front view, and the valve hole 3c has a valve hole. A spool 31 as a body is inserted. The valve hole 3 c is closed by a plug 32 screwed into the housing body 3, and the valve hole 3 c and the spool 31 constitute a control valve 33 that is a spool valve. The control valve 33 swings the cam ring 16. In order to make it move, the oil pressure of both the pressure chambers 22a and 22b is controlled.

  The spool 31 has a first land portion 31a formed at one end thereof and a second land portion 31b formed at an intermediate portion thereof, and the high pressure chamber 33a and the land portion 31a, 31b are formed in the valve hole 3c. The intermediate pressure chamber 33b and the low pressure chamber 33c are separated.

  The intermediate pressure chamber 33b formed on one side of the first land portion 31a is provided with a return spring 34 for urging the spool 31 toward the other side, and a meter formed in a discharge passage (not shown). The hydraulic pressure downstream of the ring throttle is introduced. A high pressure chamber 33a formed on the other side of the second land portion 31b is supplied with hydraulic pressure upstream of a metering throttle (not shown), while a low pressure chamber 33c formed between the land portions 31a and 31b. Communicates with the suction passage 28 via the low-pressure passage 35, and pump suction pressure is introduced.

  The spool 31 is operated by changing the differential pressure between the high pressure chamber 33a and the intermediate pressure chamber 33b in accordance with the change in the pump discharge amount, and the low pressure chamber 33c or the first pressure chamber 22a is moved according to the position of the spool 31. While the hydraulic pressure of the high pressure chamber 33a is selectively introduced, the hydraulic pressure of the low pressure chamber 33c or the intermediate pressure chamber 33b is selectively introduced into the second pressure chamber 22b. In other words, the cam ring 16 swings due to the differential pressure between the pressure chambers 22a and 22b, and the pump displacement changes as the amount of eccentricity between the cam ring 16 and the rotor 14 changes. In other words, the pump discharge amount is controlled by the control valve 33.

  On the other hand, in the front view shown in FIG. 4, the first mounting bolt insertion hole 2 a through which the first mounting bolt 5 is inserted in the housing 2 on the side opposite to the control valve 33 of the housing space 3 a, that is, on the discharge region side of the housing space 3 a. Are drilled along the axial direction of the drive shaft 9. Specifically, the axis of the first mounting bolt insertion hole 2a intersects with a virtual line C that is orthogonal to the axis of the control valve 33 and intersects with the axis of the drive shaft 9 in a front view.

  Similarly, in the front view shown in FIG. 4, the second and third mounting bolt insertion holes 2b and 2c through which the second and third mounting bolts 6 and 7 are inserted on both sides of the imaginary line C of the housing 2 are respectively drive shafts. 9 is drilled along the axial direction. Specifically, the axes of the second and third mounting bolt insertion holes 2 b and 2 c intersect with a virtual line D that is orthogonal to the virtual line C and intersects with the axis of the drive shaft 9 in a front view. Each mounting bolt insertion hole 2a, 2b, 2c is formed so as to penetrate the housing body 3 and the rear cover 4.

  Further, similarly in the front view shown in FIG. 4, the first fastening bolt 37 disposed between the control valve 33 and the second mounting bolt 6, and the first mounting bolt 5 and the second mounting bolt 6 are disposed. The second fastening bolt 38, the third fastening bolt 39 disposed between the first mounting bolt 5 and the third mounting bolt 7, and the fourth fastening disposed between the control valve 33 and the third mounting bolt 7. The housing body 3 and the rear cover 4 are fastened by the bolt 40. More specifically, the first to fourth fastening bolts 37, 38, 39, and 40 are inserted into four regions of the housing 2 that are divided by virtual lines C and D in the front view shown in FIG. Fourth fastening bolt insertion holes 2d, 2e, 2f, 2g are formed, respectively.

  More specifically, the effective diameter of each of the fastening bolts 37, 38, 39, 40 is smaller than each of the mounting bolts 5, 6, 7, and the first mounting bolt 5 is the second, third fastening of the housing body 3. The counter-control valve 33 side is inserted through the bolts 38 and 39. Further, the mounting bolts 5, 6, 7 and the fastening bolts 37, 38, 39, 40 are respectively arranged on the radially outer side than the seal ring 12.

  FIG. 5 is a front view showing the rear cover 4 in FIG. 3 alone.

As shown in FIG. 5 in addition to FIG. 3, the rear cover 4 is formed on a seating surface 4a on which a seating surface 3d on the housing body 3 side is seated, and on the counter-control valve 33 side of the seating surface 4a. Formed between the offset surface 4b offset from the surface 4a on the side opposite to the housing main body 3 and the offset surface 4b and the seating surface 4a, intersects with the axis of the first mounting bolt insertion hole 2a in a front view, and And a stepped portion 4c along an imaginary line E parallel to the axis of the control valve 33. Thus, a gap 41 is formed between the seating surface 3d of the housing body 3 and the offset surface 4b of the rear cover 4 so as to communicate with the first mounting bolt insertion hole 2a. In other words, the counter-control valve 33 side of the seating surface 4a of the rear cover 4 is cut away from the virtual line E. In the peripheral portion of the seating surface 4a of the rear cover 4 around the second and third mounting bolt insertion holes 2b and 2c, the seating surface 3d on the housing body 3 side is seated on the seating surface 4a.

That is, by forming a gap 41 in the axial direction of the first mounting bolt 5 between the peripheral portion of the first mounting bolt 5 in the housing body 3 and the rear cover 4, each mounting bolt 5 , 6, 7 is tightened. The amount of deformation of the housing body 3 toward the engine block 8 due to the axial force of each of the mounting bolts 5, 6, 7 in the state is from the peripheral portions of the housing body 3 around the second and third mounting bolts 6, 7. Also, the peripheral portion of the first mounting bolt 5 in the housing body 3 is set to be larger.

  Here, since the respective mounting bolts 5, 6, and 7 are unevenly distributed on the side opposite to the control valve 33 in the housing body 3, the respective mounting bolts are assumed to be similar to each other as in the technique described in Patent Document 1 described above. Assuming that the oil pump is attached to the support member with the structure described above, the part on the control valve side of the housing body is the part on the counter-control valve side due to the axial force of each mounting bolt in the tightening state of each mounting bolt. Will be greatly deformed. That is, in the portion of the housing on the side opposite to the control valve, the deformation of the housing body is suppressed by the contact between the protruding portion of the rear cover and the engine block, while in the portion of the housing on the control valve side, the rear cover and the engine are suppressed. Since the blocks are separated from each other, the portion on the control valve side of the housing body is greatly bent and deformed as compared with the portion on the counter-control valve side. As a result, the clearance between the rear cover and the rotor becomes too small on the control valve side, and so-called seizure may occur between the two.

  On the other hand, in the present embodiment, the offset surface 4b is formed in the peripheral portion of the rear cover 4 around the first mounting bolt insertion hole 2a, so that the shaft is interposed between the offset surface 4b and the seating surface 3d of the housing body 3. While the gap 41 is provided in the direction, the seating surface 3d on the rear cover 4 side is seated on the seating surface 4a in the peripheral portion of the rear cover 4 around the second and third mounting bolt insertion holes 2b and 2c. . Therefore, the rigidity of the portion of the housing 2 on the side opposite to the control valve 33 is lowered by the gap 41, and the portion is positively bent and deformed toward the engine block 8 side when the mounting bolts 5, 6, and 7 are tightened. When the mounting bolts 5, 6 and 7 are tightened, the amount of deformation of the housing body 3 around the first mounting bolt 5 toward the engine block 8 is such that the housing body around the second and third mounting bolts 6 and 7 3 is larger than the amount of bending deformation toward the engine block 8 side. As a result, a moment is generated in the housing body 3 in a direction in which the control valve 33 side of the housing body 3 is separated from the rear cover 4, and an appropriate clearance is secured between the rotor 14 and the rear cover 4. Sticking can be prevented.

  The details of the first embodiment have been described above. The operational effects of the first embodiment will be described below.

  In the first embodiment, a housing body that pivotally supports a drive shaft that rotationally drives the pump element, and a housing space that houses the pump element is recessed in the axial direction, and the housing space of the housing body is closed. And a control valve that is provided on one side of the housing body in the radial direction of the housing space and that controls the pump discharge amount. The oil pump includes a plurality of at least the housing body that is inserted in the axial direction. For mounting to the support member on the rear cover side with the mounting bolt, in the tightened state of each mounting bolt, the housing body supporting member side in the vicinity of the first mounting bolt that passes through the counter-control valve side of the housing body among the mounting bolts The amount of bending deformation to the side of the other mounting bolts provided on the control valve side than the first mounting bolts Since it is set to be larger than the bending deformation amount of the main body, a moment in the direction in which the control valve side of the housing body is separated from the rear cover is generated in the housing body in the tightening state of each mounting bolt. . Thereby, even in the above-described mounting bolt tightened state, an appropriate clearance is ensured between the pump element and the rear cover, and so-called seizure between them can be prevented.

  More specifically, in the first embodiment, the second and third mounting bolts are provided on both sides of an imaginary line connecting the axis of the first mounting bolt and the axis of the drive shaft in the housing body in a front view. Each is inserted in the axial direction, and a gap is formed in the axial direction of the first mounting bolt between the peripheral portion of the first mounting bolt and the rear cover in the housing body. As a result, in the tightening state of each of the mounting bolts, the amount of bending deformation of the housing body around the first mounting bolt toward the support member becomes larger than the amount of bending deformation of the housing body around the second and third mounting bolts. .

  More specifically, in the first embodiment, a rotor that is rotationally driven by a drive shaft, a plurality of vanes that are provided in the rotor so as to be able to protrude and retract in a radial direction, and the rotor that is extrapolated to the rotor. A plurality of pump chambers are formed together with each vane, and a cam ring that is movable in a direction in which the amount of eccentricity with the rotor increases or decreases, and a drive shaft that rotationally drives the rotor are pivotally supported. A housing main body in which a housing space for housing the cam ring is recessed in the axial direction, a pressure plate arranged in a position closer to the bottom of the housing space than the cam ring in the housing space, and a rear cover for closing the housing space of the housing body A pair of pressure chambers formed on both sides of the cam ring in the moving direction, and one side of the housing body in the radial direction of the housing space And a control valve that controls the hydraulic pressure in both the pressure chambers to change the amount of eccentricity between the cam ring and the rotor. A support member on the rear cover side having a mounting bolt and second and third mounting bolts that are inserted in the axial direction on both sides of an imaginary line connecting the axis of the first mounting bolt and the axis of the drive shaft of the housing body. A gap is formed in the axial direction of the first mounting bolt between the peripheral portion of the first mounting bolt in the housing body and the rear cover. As a result, as described above, an appropriate clearance is secured between the rotor and the rear cover, and so-called seizure between them can be prevented.

  In the first embodiment, a substantially annular seal ring for preventing hydraulic oil leakage from the housing space is provided between the housing main body and the rear cover, and the gap is formed on the radially outer side of the seal ring. Since the portion is formed, the hydraulic oil does not leak from the accommodation space.

  In the first embodiment, the first mounting bolt is disposed between the control valve and the second mounting bolt in the front view and fastens the housing body and the rear cover in the axial direction, and the first mounting bolt in the front view. Between the first mounting bolt and the second mounting bolt, and between the first mounting bolt and the third mounting bolt when viewed from the front, and between the housing main body and the rear cover. A third fastening bolt that is fastened in the axial direction; and a fourth fastening bolt that is disposed between the control valve and the third mounting bolt in a front view and fastens the housing body and the rear cover in the axial direction. The mounting bolt is inserted through the counter-control valve side of the housing body from the second fastening bolt and the third fastening bolt in the front view. Since the housing body communicates with a mounting bolt insertion hole through which the first mounting bolt is inserted, the housing body is more effectively moved to the support member side of the housing body in the vicinity of the first mounting bolt when the mounting bolts are tightened. Can be made larger than the amount of bending deformation of the housing body around the second and third mounting bolts.

  Furthermore, in the first embodiment, a transmission pulley is coupled to a protrusion of the drive shaft that protrudes from the housing body to the side opposite to the rear cover, and the tension is applied to the winding member wound around the pulley. Since the pulley is pulled to the first mounting bolt side, a moment for separating the control valve side of the housing body from the rear body is generated in the housing body by the traction force of the winding member, and the pump body and the rear cover are separated from each other. So-called seizure can be more effectively prevented.

  And in 1st Embodiment, since the 1st attachment bolt has penetrated the discharge area | region side in which the volume of a pump chamber reduces with rotation of the said rotor among housing bodies, the vibration of an oil pump is suppressed. This is preferable.

  In the first embodiment described above, the effective diameter of the first mounting bolt is made larger than the effective diameters of the second and third mounting bolts, and the tightening torque of the first mounting bolt is set to the second and third torques. By making it larger than the tightening torque of the mounting bolt, the first mounting bolt can be configured to fasten the housing body and the support member with a larger axial force than the second and third mounting bolts. In this case, the amount of bending deformation of the housing body around the first mounting bolt toward the support member side is compared with the amount of bending deformation of the housing body around the second and third mounting bolts in each mounting bolt tightened state. Thus, the so-called seizure between the pump element and the rear cover can be more effectively prevented.

  In the first embodiment, power is transmitted to the oil pump by means of pulleys and belts. Needless to say, power may be transmitted to the oil pump using sprockets and chains.

  6 and 7 are diagrams showing a second embodiment of the present invention. FIG. 6 is a view corresponding to FIG. 3 of the first embodiment described above, and FIG. 7 is a side view showing a state where the vane pump 1 shown in FIG. 6 and 7, the same or corresponding parts as those of the first embodiment described above are denoted by the same reference numerals.

  In the second embodiment shown in FIG. 6, an inclined surface 4e is provided on the rear cover 4 in place of the offset surface 4b in the first embodiment, and other portions are the same as those in the first embodiment. It is constituted similarly. The inclined surface 4e is inclined toward the counter-control valve 33 side so as to be separated from the seating surface 3d of the housing body 3, and the gap portion 42 is directed to the counter-control valve 33 side with the shaft of the first mounting bolt insertion hole 2a. It is formed so as to gradually increase in the direction, that is, the axial direction of the first mounting bolt 5. As shown in FIG. 7, in the tightened state of the mounting bolts 5, 6, and 7, the gap 42 is crushed by the bending deformation of the housing body 3, and the inclined surface 4e on the rear cover 4 side and the seating on the housing body 3 side The surface 3d is in close contact with the surface 3d, thereby improving the appearance quality of the vane pump 1.

  That is, in the second embodiment, the gap is formed so as to gradually increase in the axial direction of the first mounting bolt toward the counter-control valve side, and is the same as the first embodiment described above. The effect is obtained.

  FIG. 8 is a diagram showing a third embodiment of the present invention, and is an exploded side view of the housing 2. In FIG. 8, the same or corresponding parts as those in the first embodiment described above are denoted by the same reference numerals.

  In the third embodiment of the present invention, as shown in FIG. 8, a shim plate 43 is interposed between the housing body 3 and the rear cover 4 in the first embodiment, and the housing body 3 and the rear cover 4 Are separated in the axial direction by the thickness of the shim plate 43, and the shim plate 43 is sandwiched between the seating surface 3d on the housing main body side and the seating surface 4a on the rear cover 4 side.

  FIG. 9 is a front view showing the shim plate 43 in FIG. 8 alone.

  As shown in FIG. 9, the shim plate 43 has a low pressure passage 35 in addition to the second and third mounting bolt insertion holes 2b, 2c and the first to fourth fastening bolt insertion holes 2d, 2e, 2f, 2g. In addition, the lower edge portion 43a is formed in a substantially straight shape when viewed from the front, and the first mounting bolt insertion portion 43b is formed in a substantially semicircular shape when viewed from the front through which the first mounting bolt 5 is inserted. Has been. That is, in the assembled state of the vane pump 1, the shim plate 43 overlaps only on the control valve 33 side with respect to the shaft center of the first mounting bolt insertion hole 2 a in the housing body 3 and the rear cover 4 in a front view, and the lower edge of the shim plate 43. A gap 41 similar to that of the first embodiment described above is formed on the side of the portion 43a. In other words, the shim plate 43 is cut out at a portion of the seating surface 3d of the housing body 3 corresponding to the counter-control valve 33 side with respect to the axis of the first mounting bolt insertion hole 2a.

  That is, in the third embodiment, a shim plate is interposed between the housing main body and the rear cover, and a notch serving as the gap is formed in the periphery of the first mounting bolt in the shim plate. As a result, the housing body and the rear cover are spaced apart in the axial direction to form the gap, so that substantially the same effect as in the first embodiment can be obtained.

  In the third embodiment, the cutout portion serving as the gap is formed in the peripheral portion of the first mounting bolt of the shim plate. However, the thin portion may be formed in place of the cutout portion. It goes without saying that the effect of can be obtained.

  FIG. 10A is a diagram showing a modification of the shim plate in the third embodiment, and FIG. 10B is a diagram showing another modification of the shim plate in the third embodiment. It is.

  The shim plate 44 in the modified example shown in FIG. 10 (a) is formed with a notch 44a that is notched from the lower edge of the shim plate 44 to the lower edge of the first mounting bolt insertion hole 2a. The notch 44 a has a tapered shape that becomes wider toward the lower edge side of the shim plate 44. Therefore, since the gap is formed between the housing main body 3 and the rear cover 4 with the notch 44a in the assembled state of the vane pump 1, substantially the same effect as the first embodiment can be obtained.

  On the other hand, another modification shown in FIG. 10 (b) is one in which a U-shaped hole 45a having a substantially U shape in plan view is formed on the outer peripheral side of the first mounting bolt insertion hole 2a in the shim plate 45. In the assembled state of the vane pump 1, a gap is formed between the housing body 3 and the rear cover 4 with a U-shaped hole 45a. Therefore, also in this modified example, substantially the same effect as that of the first embodiment can be obtained.

The side view of the vane pump which showed the 1st Embodiment of this invention and was attached to the engine block. The front view of the vane pump in FIG. AA sectional view of Drawing 2 showing a vane pump alone. BB sectional drawing of FIG. The front view which shows the rear cover in FIG. 3 alone. The figure which shows the 2nd Embodiment of this invention and is equivalent to FIG. 3 in 1st Embodiment. The side view which shows the state by which the vane pump shown in FIG. 6 was fastened with the engine block. The disassembled side view of the vane pump which shows the 3rd Embodiment of this invention. The front view which shows the shim plate in FIG. 8 alone. The figure which shows the modification of the 3rd Embodiment of this invention.

Explanation of symbols

1 ... Vane pump (oil pump)
DESCRIPTION OF SYMBOLS 3 ... Housing main body 3a ... Accommodating space 4 ... Rear cover 5 ... 1st installation bolt 6 ... 2nd installation bolt 7 ... 3rd installation bolt 8 ... Engine block (support member)
DESCRIPTION OF SYMBOLS 9 ... Drive shaft 10 ... Pulley 11 ... Belt (wrapping member)
12 ... Seal ring 14 ... Rotor (pump element)
16 ... Cam ring (pump element)
17 ... Vane (pump element)
22a ... first pressure chamber 22b ... second pressure chamber 25 ... side plate 33 ... control valve 37 ... first fastening bolt 38 ... second fastening bolt 39 ... third fastening bolt 40 ... fourth fastening bolt 41 ... gap 42 ... Cavity 43 ... Shim plate 44 ... Shim plate 44a ... Notch 45 ... Shim plate

Claims (19)

A housing body that pivotally supports a drive shaft that rotationally drives the pump element, and a housing space that houses the pump element is recessed in the axial direction;
A rear cover for closing the housing space of the housing body;
A control valve that is provided on one side of the housing body in the radial direction of the housing space and controls the pump discharge amount;
An oil pump comprising:
The portion of the housing body on the side opposite to the control valve is attached to the support member via the rear cover with a plurality of mounting bolts inserted in the axial direction of the housing body, and the outer surface of the rear cover on the control valve side and the support In those where a gap is formed between the members ,
Among the mounting bolts, there is a gap between the peripheral portion of the first mounting bolt through which the portion of the housing body opposite to the control valve across the drive shaft is inserted and the rear cover facing the peripheral portion. An oil pump characterized in that a portion is formed.   2. The oil pump according to claim 1, wherein the gap is formed so as to gradually increase in the axial direction of the first mounting bolt toward the counter-control valve side.   A substantially annular seal ring for preventing hydraulic oil leakage from the housing space is provided between the housing body and the rear cover, and the gap is formed on the radially outer side of the seal ring. The oil pump according to claim 1. A first fastening bolt that is disposed between the control valve and the second mounting bolt in a front view and fastens the housing body and the rear cover in the axial direction;
A second fastening bolt that is disposed between the first mounting bolt and the second mounting bolt in a front view and fastens the housing body and the rear cover in the axial direction;
A third fastening bolt that is disposed between the first mounting bolt and the third mounting bolt in a front view and fastens the housing body and the rear cover in the axial direction;
A fourth fastening bolt that is disposed between the control valve and the third mounting bolt in a front view and fastens the housing body and the rear cover in the axial direction;
With
2. The oil pump according to claim 1, wherein the first mounting bolt is inserted through the counter-control valve side of the housing body from the second fastening bolt and the third fastening bolt in a front view.   2. The oil pump according to claim 1, wherein the gap is formed by axially separating a shim plate interposed between the housing main body and the rear cover.   The oil pump according to claim 5, wherein a cutout portion serving as the gap portion is formed in a peripheral portion of the first mounting bolt in the shim plate. The oil pump according to claim 4 , wherein the oil pump is fixed to the support member.
An oil pump characterized in that the first mounting bolt fastens the housing body and the support member with a larger axial force than the second and third mounting bolts.   The oil pump according to claim 7, wherein the first mounting bolt has an effective diameter larger than that of the second and third mounting bolts.   The oil pump according to claim 7, wherein the first mounting bolt is tightened with a tightening torque larger than that of the second and third mounting bolts. The oil pump according to claim 1, wherein the oil pump is fixed to the support member.
A transmission pulley or sprocket is coupled to a protruding portion of the drive shaft that protrudes from the housing body to the rear cover side, and the pulley or sprocket is first driven by the tension of a winding member wound around the pulley or sprocket. An oil pump characterized by being pulled to the mounting bolt side. A housing body that pivotally supports a drive shaft that rotationally drives the pump element, and a housing space that houses the pump element is recessed in the axial direction;
A rear cover that closes the housing space of the housing body;
A control valve that is provided on one side of the housing body in the radial direction of the housing space and controls the pump discharge amount;
An oil pump comprising:
A first mounting bolt that is inserted axially through the non-control valve side of the housing body, and both sides of an imaginary line that connects the axis of the first mounting bolt and the axis of the drive shaft of the housing body when viewed from the front. second inserting direction, a third mounting bolt, is attached to the support member through the rear cover by at which a gap is formed between the supporting member and the control valve side of the outer surface of the rear cover ,
An oil pump characterized in that a gap is formed in the axial direction of the first mounting bolt between the peripheral portion of the first mounting bolt in the housing body and the rear cover.   12. The oil pump according to claim 11, wherein the gap is formed so as to gradually increase in the axial direction of the first mounting bolt toward the counter-control valve side.   A substantially annular seal ring for preventing hydraulic oil leakage from the housing space is provided between the housing body and the rear cover, and the gap is formed on the radially outer side of the seal ring. The oil pump according to claim 13. A rotor driven to rotate by a drive shaft;
A plurality of vanes provided in the rotor so as to be movable in and out in the radial direction;
A cam ring that is extrapolated to the rotor and forms a plurality of pump chambers together with the rotor and each vane, and is movable in a direction in which the amount of eccentricity with the rotor increases or decreases,
A housing body that pivotally supports the drive shaft, and a housing space for housing the rotor and cam ring is recessed in the axial direction;
A rear cover that closes the housing space of the housing body;
A side plate arranged on the side opposite to the rear cover of the cam ring;
A pair of pressure chambers formed on both sides of the cam ring in the moving direction;
A control valve that is provided on one side of the housing body in the radial direction of the housing space and controls the hydraulic pressure of the two pressure chambers to change the amount of eccentricity between the cam ring and the rotor;
In an oil pump with
A first mounting bolt that is inserted axially through the non-control valve side of the housing body, and both sides of an imaginary line that connects the axis of the first mounting bolt and the axis of the drive shaft of the housing body when viewed from the front. gap between the second and third mounting bolts, together adapted to be mounted to the support member through the rear cover by the support member and the control valve side of the outer surface of the rear cover to be inserted in the direction Is formed ,
Oil pump, characterized in that the air gap in the axial direction of the first mounting bolt is formed between the peripheral portion and the rear cover of the first mounting bolt out of the housing body.   15. The oil pump according to claim 14, wherein the gap is formed so as to gradually increase in the axial direction of the first mounting bolt toward the counter-control valve side.   A substantially annular seal ring for preventing hydraulic oil leakage from the housing space is provided between the housing body and the rear cover, and the gap is formed on the radially outer side of the seal ring. The oil pump according to claim 14.   The oil pump according to claim 16, wherein the gap portion communicates with a mounting bolt insertion hole through which the first mounting bolt is inserted in the housing body. A first fastening bolt that is disposed between the control valve and the second mounting bolt in a front view and fastens the housing body and the rear cover in the axial direction;
A second fastening bolt that is disposed between the first mounting bolt and the second mounting bolt in a front view and fastens the housing body and the rear cover in the axial direction;
A third fastening bolt that is disposed between the first mounting bolt and the third mounting bolt in a front view and fastens the housing body and the rear cover in the axial direction;
A fourth fastening bolt that is disposed between the control valve and the third mounting bolt in a front view and fastens the housing body and the rear cover in the axial direction;
With
15. The oil pump according to claim 14, wherein the first mounting bolt is inserted through the opposite side of the housing body from the second fastening bolt and the third fastening bolt in a front view.   15. The oil pump according to claim 14, wherein the first mounting bolt is inserted through the discharge region side of the housing body where the volume of the pump chamber decreases as the rotor rotates.

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