JP5357677B2 - Variable displacement vane pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a variable displacement vane pump achieving a reduction in machining cost of a through-hole formed in a vane. <P>SOLUTION: This variable displacement vane pump includes: a rotating part 5 having a substantially columnar peripheral surface; a plurality of vanes 6 stored to be projected from and retracted into a plurality of slits formed in the peripheral surface; a cam ring 7 arranged to surround the rotating part; and an annular wire ring 9 radially retaining the vanes. One end of the hole diameter of the through-hole 6a formed in each vane of the variable displacement pump and inserting the annular wire ring is set small and the other end thereof is set large. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a variable displacement vane pump for an automobile.

  As a conventional variable displacement vane pump, one disclosed in Patent Document 1 is known. The variable displacement vane pump disclosed in Patent Document 1 is housed in a rotatable manner having a substantially cylindrical outer peripheral surface that rotates around a rotation axis and a plurality of slits formed on the outer peripheral surface so as to protrude and retract. A plurality of vanes, a cam ring arranged so that a cylindrical inner peripheral surface surrounds the rotating portion, and a plurality of vanes are inserted into the vanes so that the tip of each vane is in sliding contact with the inner peripheral surface of the cam ring. And an annular wiring ring that is held in the radial direction.

  In addition, the annular chamber formed between the outer peripheral surface of the rotating part and the inner peripheral surface of the cam ring is partitioned into a plurality of volume chambers by a plurality of vanes whose tips are in contact with the inner peripheral surface, and the cam ring is rotated. By rotating the rotating part in a state of being eccentric with respect to the shaft, the volume chamber is periodically expanded and contracted while rotating around the rotation axis, and the fluid sucked into each volume chamber is discharged. .

JP 2001-241390 A

  In the conventional variable displacement vane pump, the cross section of the through hole through which the annular wire ring is inserted is provided in a plurality of vanes, and the through hole needs to be processed from both sides, which increases the processing cost. There are challenges.

  Then, an object of this invention is to obtain the variable capacity | capacitance vane pump which can reduce the processing cost of the through-hole of a vane.

  The present invention is characterized in that one end side of the diameter of the through hole provided in the vane of the variable capacity vane pump and through which the annular wire ring is inserted is set small and the other end side is set large.

  According to the present invention, since one end side of the hole diameter of the through hole through which the annular wire ring is inserted is set small and the other end side is set large, the through hole can be formed by processing from one direction. Cost can be reduced.

It is a block diagram which shows an example of the system by which the variable displacement vane pump concerning embodiment of this invention is used. It is the side view (partial sectional view) which looked at the internal structure of the variable capacity vane pump concerning a 1st embodiment of the present invention from the direction of a rotation axis. It is sectional drawing which follows the III-III line of FIG. FIG. 4 is an enlarged side view (partial cross-sectional view) showing an IV part of FIG. 2. It is a side view showing the rotation part of the variable capacity vane pump concerning a 1st embodiment of the present invention. It is sectional drawing which shows the principal part of the variable capacity vane pump concerning another aspect of 1st Embodiment of this invention. It is sectional drawing which follows the III-III line | wire of FIG. 2 which shows the aspect which has arrange | positioned the through-hole in the width direction center of the vane. It is sectional drawing which shows the principal part of the variable capacity vane pump concerning 2nd Embodiment of this invention. It is sectional drawing which shows the principal part of the variable displacement vane pump concerning another aspect of 2nd Embodiment of this invention.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, preferred embodiments of the invention will be described in detail with reference to the drawings. Note that similar components are included in the following embodiments. Therefore, common reference numerals are given to those similar components, and redundant description is omitted.

<First Embodiment>
1 to 5 show a first embodiment of the present invention. Among these, FIG. 1 is a block diagram illustrating an example of a system in which the variable displacement vane pump according to the present embodiment is used, and FIG. 2 is a side view of the internal configuration of the variable displacement vane pump according to the present embodiment as viewed from the rotation axis direction. FIG. 3 (partial cross-sectional view), FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2, FIG. 4 is an enlarged side view of part IV in FIG. FIG. 3 is a side view showing a rotating part of the variable capacity vane pump according to the first embodiment of the present invention. 2 is a cross-sectional view taken along line II-II in FIG. 3, FIG. 6 is a cross-sectional view showing a main part of another aspect of the first embodiment, and FIG. 7 is a through hole at the center in the width direction of the vane. It is sectional drawing which follows the III-III line | wire of FIG. 2 which shows the aspect which has arrange | positioned.

  As shown in FIG. 1, the variable displacement vane pump 1 according to this embodiment can be used as a hydraulic pressure supply source for a belt-driven continuously variable transmission system (belt CVT system 100). The hydraulic oil discharged from the variable displacement vane pump 1 is passed through the control valve 200 to each part of the belt CVT system 100 (primary pulley 101, secondary pulley 102, forward clutch 103, reverse brake 104, torque converter 105, lubrication / cooling. System 106).

  In the control valve 200, there are various electric, manual and hydraulic valves (shift control valve 201, secondary valve 202, secondary pressure solenoid valve 203, line pressure solenoid valve 204, pressure regulator valve 205, manual valve 206, A lockup / select switching solenoid valve 207, a clutch regulator valve 208, a select control valve 209, a lockup solenoid valve 210, a torque converter regulator valve 211, a lockup control valve 212, a select SW valve 213, and the like.

  The electric valve included in the control valve 200 is controlled by the control unit 300 for the belt CVT system 100.

  As shown in FIG. 2, the variable displacement vane pump 1 according to the present embodiment includes a pump part 2 and a control valve part 3, both of which are in the pump body 4. Is formed. The pump unit 2 is configured as a variable displacement vane pump, and the control valve unit 3 is configured as a spool valve.

  The pump unit 2 is housed in a substantially cylindrical housing recess 4a formed in the pump body 4, and includes a rotating unit 5 having a substantially columnar outer peripheral surface 5a that rotates about a rotation axis Ax, and an outer peripheral surface 5a. A plurality of vanes 6 accommodated in respective 11 slits 5b formed at equal intervals along each of the axial direction and the radial direction, and a cam ring 7 disposed so as to surround the rotating portion 5. And an adapter ring 8 that is arranged so as to surround the cam ring 7 and is inserted into the receiving recess 4a, and a plurality of vanes 6 that are inserted into the inner peripheral surface 7a of the cam ring 7 in the radial direction. And an annular wire ring 9 for energizing and holding the vane 6. The adapter ring 8 is prevented from rotating in the housing recess 4a by a locking means (not shown).

  Then, a plurality of annular chambers R formed between the outer peripheral surface 5 a of the rotating part 5 and the inner peripheral surface 7 a of the cam ring 7 are provided by a plurality of vanes 6 whose tips are brought into sliding contact with the inner peripheral surface 7 a of the cam ring 7. The volume chamber V is partitioned.

  Further, in the present embodiment, the rotating portion 5 is rotated in a state where the cam ring 7 is arranged eccentrically to the left and upward in FIG. 2 with respect to the rotation axis Ax, thereby rotating the volume chamber V around the rotation axis Ax. It is configured to periodically expand and contract and discharge the fluid sucked into each volume chamber V.

  The rotating unit 5 is spline-coupled to the shaft 13 and rotates together with the shaft 13. The rotation axis Ax is also the rotation axis of the shaft 13. In the present embodiment, the rotation direction of the rotating unit 5 and the shaft 13 is the clockwise direction of FIG.

  In the present embodiment, the slits 5b are formed radially along the radial direction of the rotation axis Ax, and are formed at positions that divide the rotating portion 5 into 11 equal parts in the circumferential direction. A substantially cylindrical pressurizing chamber 5c is formed on the back side (rotation axis Ax side) of the slit 5b, and in the suction process, the pressurizing chamber 5c is connected to the suction side to suck and discharge the hydraulic oil. In the process, the hydraulic oil sucked in communication with the pressurizing chamber 5c and the discharge port side is discharged to the discharge side, and the high pressure discharge pressure is applied to the root of the vane 6 to push the vane 6 radially outward so that the cam ring. 7 is pressed against the inner peripheral surface 7a. In addition, the said pressurization is not essential.

  As shown in FIG. 3, the vane 6 is configured as a substantially rectangular plate-like member. In this embodiment, the tip portion corresponds to the inner peripheral surface 7 a of the cam ring 7, for example, an inner peripheral surface. The curved surface is formed with a curvature smaller than the curvature of 7a.

  The cam ring 7 is formed in an annular shape having a constant radius, and the tip of the rotating vane 6 comes into sliding contact with the inner peripheral surface 7a.

  The outer peripheral surface 8a of the adapter ring 8 is formed in a substantially cylindrical surface, while the inner peripheral surface 8b is formed in a substantially flat cylindrical surface that is long and flat at the upper left and lower right in FIG. More specifically, the inner peripheral surface 8b has three planar facing surfaces 8c, 8d, and 8e on the lower left diagonal, the upper left diagonal, and the upper right diagonal in FIG. 2, and the concave curved surface 8f, 8g and 8h are formed. Then, as shown in FIG. 2, in the state where the cam ring 7 is located at the most obliquely upper left position in the inner peripheral surface 8b, a gap is formed between the concave curved surfaces 8f and 8g and the outer peripheral surface 7b of the cam ring 7. These gaps become the pressurizing chamber 10.

  In FIG. 2, a semi-cylindrical groove 8i is formed on the facing surface 8e located obliquely upward to the right, and a slightly shallow groove 7c is formed on the outer peripheral surface 7b of the cam ring 7 facing the groove 8i. The pin 11 is accommodated in the concave grooves 8i and 7c so as to be sandwiched between the concave grooves 8i and 7c. The cam ring 7 is configured to swing around the pin 11 as a fulcrum inside the inner peripheral surface 8 b of the adapter ring 8.

  A coil spring 12 as an urging mechanism for urging the cam ring 7 diagonally to the left in FIG. 2 is interposed on the opposite side of the pressurizing chamber 10 with respect to the rotation axis Ax (inclined to the right in FIG. 2). Thus, a compression reaction force that opposes the pressurization from the pressurizing chamber 10 is applied to the cam ring 7. In the present embodiment, a spring receiver 8j that receives the coil spring 12 is formed on the inner periphery of the adapter ring 8, and one end of the coil spring 12 is in contact with the outer peripheral surface 7b of the cam ring 7, The other end is supported by a spring receiver 8 j on the inner periphery of the adapter ring 8.

  Furthermore, a concave groove 8k having a substantially rectangular cross section is formed on the opposing surface 8e located on the opposite side of the pin 11 with respect to the rotation axis Ax (left obliquely downward in FIG. 2). In the concave groove 8k, A substantially rod-shaped seal member 14 is inserted. The end surface on the protruding side (upper side in FIG. 2) of the seal member 14 is in contact with the outer peripheral surface 7b of the cam ring 7, and when the cam ring 7 swings, the seal member 14 is placed on the outer peripheral surface 7b of the cam ring 7. It comes in sliding contact. In this embodiment, the seal member 14 and the pin 11 seal the crescent-shaped counter chamber 15 in a side view on the side where the pressurizing chamber 10 and the coil spring 12 are disposed.

  In the present embodiment, as shown in FIG. 2, the pressurizing chamber 10 and the opposing chamber 15 are connected to each other via a fluid passage 4 c formed in the pump body 4 and a communication passage 8 m formed in the adapter ring 8. A fluid is introduced from the control valve unit 3.

  In the pump unit 2 having the above configuration, the volume chamber V also rotates as the rotating unit 5 rotates. At this time, since the cam ring 7 is eccentric leftward and obliquely upward in FIG. 2 with respect to the rotation axis Ax, the annular chamber R is wide at the upper left and lower at the lower right in FIG. When applied to the CVT system 100, the gear shift state). Accordingly, as each volume chamber V rotates together with the rotating portion 5 and the vane 6 in the clockwise direction of FIG. 2, the volume chamber V is narrowest in the diagonally lower right portion of FIG. 2 and moves through the lower side of FIG. Become wider. Furthermore, it is the widest in the upper left direction of FIG. 2 and becomes narrower as it moves downward in the right direction through the upper side of FIG. Therefore, in the pump unit 2 according to the present embodiment, in FIG. 2, below the center line L including the rotation axis Ax (a straight line perpendicular to the rotation axis Ax and including the rotation axis Ax and the center C of the cam ring 7). The volume of the volume chamber V increases, and the volume of the volume chamber V decreases on the upper side. A discharge opening 4f that faces the volume chamber V corresponding to a section in which the volume chamber V shrinks is formed on a side surface 4e of the housing recess 4a of the pump body 4 (a surface that is lateral to the moving direction of the vane 6). Is formed, and a suction opening 4g facing the volume chamber V is formed corresponding to a section in which the volume chamber V expands. Accordingly, the volume chamber V periodically expands and contracts as it rotates, and the suction opening 4g in the suction stroke section I moves from right to left below the center line L in FIG. 2 including the rotation axis Ax. Then, the fluid is sucked in via a discharge stroke, and the fluid is discharged through the discharge opening 4f in the discharge stroke section O that moves from the left to the right above the center line L.

  In the above configuration, when the pressure of the fluid in the pressurizing chamber 10 increases, the cam ring 7 pushed by the pressure of the fluid moves obliquely downward to the right in FIG. 2 (for example, when applied to the belt CVT system 100). , Constant speed running state). As a result, the amount of eccentricity δ between the center C of the cam ring 7 and the rotation axis Ax decreases, and the difference in volume between when the volume chamber V is reduced and when the volume chamber V is reduced is reduced. Discharge amount) is reduced. On the other hand, when the pressure of the fluid in the pressurizing chamber 10 decreases, the force by which the cam ring 7 is pressed obliquely downward to the right in FIG. 2 by the fluid pressure decreases, and the cam ring 7 is pushed back to the left by the coil spring 12. Move to the left. Then, the amount of eccentricity δ between the center C of the cam ring and the rotation axis Ax becomes large, and the difference in volume between the time when the volume chamber V is reduced and the time when the volume chamber V is enlarged becomes large, so that the discharge capacity from the pump unit 2 increases. . Therefore, in this embodiment, the discharge capacity of the pump unit 2 can be changed by appropriately changing the pressure of the fluid introduced into the pressurizing chamber 10. For example, when applied to the belt CVT system 100, it is possible to perform control such that the discharge amount is increased during gear shifting and the discharge amount is decreased during constant speed traveling as necessary. In the present embodiment, fluid is also introduced into the facing chamber 15, and the pump is driven by the pressure of the fluid in the pressurizing chamber 10 and the facing chamber 15 and the biasing force (compression reaction force) of the coil spring 12 as the biasing means. The discharge capacity of the part 2 changes.

  In the present embodiment, a housing groove 5 d capable of housing the annular wire ring 9 is formed on the outer periphery of the rotating portion 5 along the circumferential direction. The annular wire ring 9 is made of an elastic wire having a circular cross section and is formed in a substantially circular shape, and is provided with a vane retaining crimping portion 9 a at both ends, and the free diameter of the wire ring 9 is initially assembled to the vane 6. The size is set to be relatively larger than the diameter at the time. When the wire ring 9 is compressed in the radial direction when incorporated in the pump portion 2 and contracted in a concentric state with the inner peripheral surface 7a of the cam ring 7, each vane 6 is repelled by the repulsive force of the wire ring 9 itself. Can be biased radially outward.

  As shown in FIG. 3, a through hole 6 a extending in the thickness direction of the vane 6 is formed in the vicinity of the tip of each vane 6. As shown in FIG. 4, the through-hole 6a is formed at one end in the axial direction, and is formed at the small diameter portion 6b into which the wire ring 9 is inserted, and at the other end side in the axial direction, and the large through which the wire ring 9 is loosely fitted. The diameter portion 6c is formed in a conical shape that gradually increases in diameter from the small diameter portion 6b toward the large diameter portion 6a.

  The through-hole 6a is arranged so that the small diameter portion 6b is located on the low pressure suction side and the large diameter portion 6c is located on the high pressure discharge side. Contrary to FIG. 4, as shown in FIG. 6, the through hole 6 a may be arranged so that the small diameter portion 6 b is located on the high pressure discharge side and the large diameter portion 6 c is located on the low pressure suction side. Since the area where high pressure is applied to the through hole 6a is smaller in the configuration of FIG. 4, the configuration of FIG. 4 is more suitable for reducing leakage of hydraulic oil through the through hole 6a.

  Further, as shown in FIG. 7, the through hole 6 a is preferably formed on the tip side of the center in the width direction of the vane 6 a and the center in the length direction (radial direction of the rotating portion) of the vane 6 a. is there. When the through hole 6a is formed on either side in the width direction, when the vane 6 protrudes, there is a risk that the protrusion of the vane 6 on the opposite side to the through hole 6a may be delayed. By setting the through-hole 6a at the center in the width direction, the protrusion delay in the width direction can be prevented. Further, when the through-hole 6a is formed on the base end side with respect to the center in the length direction of the vane 6, the amount of protrusion of the vane is reduced, so that the discharge amount is reduced.

  The housing groove 5d on the outer periphery of the rotating part 5 and the through hole 6a of the vane 6 are provided at positions shifted by a predetermined dimension D in the axial direction from the axial center of the rotating part 5 (the center in the width direction of the vane 6). ing. Since the axial length of the rotating part 5 is the same as the width dimension of the vane 6, the axial center of the rotating part 5 is the same as the center of the vane 6 in the width direction.

  Since the wire ring 9 is inserted into the small diameter portion 6b of each vane 6, when the vane 6 passes through the boundary between the high pressure and the low pressure, the gap between the small diameter portion 6b and the b wire ring 9 becomes minute, and the hydraulic oil The amount of leakage can be minimized. Further, since the wire ring 9 is loosely fitted to the large diameter portion 6c of each vane 6, the annular wire ring 9 can move within the large diameter portion 6c of the through hole 6a of the vane 6 as the rotating portion 5 rotates. 6 and the wire ring 9 can be prevented from interfering with each other, so that the vane 6 can project and retract smoothly in the slit 5b of the rotating portion 5, and the wear of the wire ring 9 can be suppressed.

  As described above, in the present embodiment, the through holes 6a of the plurality of vanes 6 are offset to the position shifted by the predetermined dimension D from the center of the vane 6 in the width direction. In this case, when the through hole 6a of the vane 6 is significantly deviated from the predetermined position, that is, the position of the through hole 6a is located on the opposite side of the center in the width direction of the vane 6, Since the assembly can be easily noticed, the plurality of vanes 6 can be reliably incorporated into the slits 5b of the rotating unit 5 with the front and back directions being correct. Therefore, since the small diameter portions 6b of the plurality of through holes 6a can be arranged at regular intervals when incorporated in the pump portion 2, the compression is performed when the wire ring 9 is compressed in the radial direction by the small diameter portions 6b. The variation in the amount can be suppressed, and as a result, the urging force of the vane 6 toward the outside in the radial direction of the vane 6 can be effectively utilized, and the durability of the wire ring 9 itself can be improved.

  Moreover, in this embodiment, since the through-hole 6a of each vane 6 is comprised from the small diameter part 6b formed in the one end of an axial direction, and the large diameter part 6c formed in the other end side of an axial direction. The through hole 6a can be provided by processing from one side (the large diameter portion 6c side), and the cost can be reduced as compared with the conventional one that requires processing from both sides in the axial direction.

  In addition, in the state where the through hole 6a is not offset and is arranged at the center in the width direction of the vane 6, if the direction of the front and back of the vane 6 is reversed and reversed, the assembling property is deteriorated, even if assembled. However, the wire ring 9 becomes zigzag, the diameter of the wire ring 9 is reduced, and the amount of protrusion of the vane is reduced. As a result, the cam ring is not contacted and the pump discharge amount is reduced.

  When the through hole 6a is a straight hole having a constant hole diameter, the variable displacement pump changes the inclination angle of the vane 6 in accordance with the eccentricity of the cam ring 7, so that a bending stress is applied to the wire ring 9 each time. In order to release this bending stress, the hole diameter of the through hole 6a must be increased. However, as the hole diameter increases, the amount of hydraulic oil leakage increases and the pump efficiency decreases.

Second Embodiment
FIG. 8 is a cross-sectional view showing a main part of the variable displacement vane pump according to the embodiment, and FIG. 9 is a cross-sectional view showing a main part of another aspect of the first embodiment. Note that the pump section of the variable displacement vane pump 1A according to the present embodiment can be the same as that of the first embodiment. Therefore, the description thereof is omitted below.

  In the present embodiment, a through hole 6d formed in the vicinity of the tip of each vane 6 is formed at one end in the axial direction, a small diameter portion 6e into which the wire ring 9 is inserted, and formed at the other end side in the axial direction. 9 is the same as the first embodiment in that it is composed of a large-diameter portion 6f into which 9 is loosely fitted.

  However, in this embodiment, the large-diameter portion 6f has a conical portion whose diameter gradually increases from the end portion of the small-diameter portion 6e, and a large-diameter portion extending from the large-diameter end portion of the conical portion toward the other end in the axial direction. Divided into cylindrical parts.

  The through hole 6a is arranged so that the small diameter portion 6e is located on the low pressure suction side and the large diameter portion 6f is located on the high pressure discharge side. In contrast to FIG. 8, as shown in FIG. 9, the through hole 6 d may be arranged so that the small diameter portion 6 e is positioned on the high pressure discharge side and the large diameter portion 6 f is positioned on the low pressure suction side. However, since the area where high pressure is applied to the through-hole 6d can be narrower in the configuration of FIG. 8, the configuration of FIG. 8 is more suitable for reducing the leakage of hydraulic oil through the through-hole 6d. is there.

  In such a configuration, since the wire ring 9 is inserted into the small diameter portion 6b (slightly larger in diameter than the wire ring 9) of each vane 6, when the vane 6 passes the boundary between the high pressure and the low pressure, the small diameter portion 6b, In addition, the gap between the wire rings 9 becomes very small, and the amount of hydraulic oil leakage can be minimized. Further, since the wire ring 9 is loosely fitted to the large diameter portion 6c of each vane 6, the annular wire ring 9 can move within the large diameter portion 6c of the through hole 6a of the vane 6 as the rotating portion 5 rotates. 6 and the wire ring 9 can be prevented from interfering with each other, so that the vane 6 can project and retract smoothly in the slit 5b of the rotating portion 5, and the wear of the wire ring 9 can be suppressed.

  Also according to this embodiment described above, the same effect as in the first embodiment can be obtained.

  The preferred embodiments of the present invention have been described above. However, the present invention is not limited to the above embodiments, and various modifications can be made. For example, the configuration of the through hole formed in the vicinity of the tip of each vane is not limited to the above embodiment, and various modifications can be made.

DESCRIPTION OF SYMBOLS 1,1A Variable capacity vane pump 5 Rotating part 5a Outer peripheral surface 5b Slit 6 Vane 6a Through hole 6b Small diameter part 6c Large diameter part 6d Through hole 6e Small diameter part 6f Large diameter part 7 Cam ring 7a Inner peripheral surface 9 Wire ring 13 Rotating shaft

Claims (2)

A rotating part having a substantially cylindrical outer peripheral surface that rotates around a rotation axis, a plurality of vanes accommodated in each of a plurality of slits formed on the outer peripheral surface, and surrounding the rotating part a cam ring disposed, is inserted into the through hole of the vane, in the variable capacitance vane pump comprising an annular wiring for retaining the vanes in the radial direction so that the tip of the vane slides over each of the cam ring inner peripheral surface ,
The through hole of the vane is formed on one end side in the axial direction of the through hole, and the small-diameter portion in which the wiring is fitted, is formed on the other end side in the axial direction of the through hole, the wiring is loosely A variable displacement vane pump characterized by comprising a large diameter portion. 2. The variable displacement vane pump according to claim 1, wherein the wiring and the through hole of the vane are provided at positions shifted by a predetermined dimension from the axial center of the rotating portion.

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