WO2018051904A1

WO2018051904A1 - Variable-capacity vane pump

Info

Publication number: WO2018051904A1
Application number: PCT/JP2017/032427
Authority: WO
Inventors: 浩一朗赤塚; 裕希五味; 文彦祖父江
Original assignee: Ｋｙｂ株式会社
Priority date: 2016-09-16
Filing date: 2017-09-08
Publication date: 2018-03-22
Also published as: CN109715949A; US20190390670A1; JP2018044535A

Abstract

This vane pump (100) comprises: a rotor (2) connected to a drive shaft (1); a plurality of vanes (3) provided so as to be able to be capable of reciprocal movement in the radial direction with respect to the rotor (2); a cam ring (4) having a cam face (4a) against which slide the tips of the vanes (3) as a result of the rotation of the rotor (2), and that is provided so as to be capable of eccentric movement with respect to the rotor (2); a second pump body (20) that houses the cam ring (4); and a spring (30) that is interposed in a compressed state between the cam ring (4) and the second pump body (20), and that energizes the cam ring (4) in a direction such that that the eccentricity with respect to the rotor (2) increases. The cam ring (4) and the second pump body (20) have seating surfaces (6a, 20a) on which the spring (30) is seated, and grooves (6b, 20b) formed in the seating surfaces (6a, 20a).

Description

Variable displacement vane pump

The present invention relates to a variable displacement vane pump.

JP2013-057326A has a housing including a pump body having a U-shaped cross section having a pump storage chamber and a cover member for closing one end opening of the pump body, and is rotatably housed in the pump storage chamber, and a central portion is a drive shaft And a pump element comprising a rotor coupled to the rotor and a plurality of vanes respectively accommodated in the plurality of slits radially cut out on the outer peripheral portion of the rotor, and the pump element on the outer peripheral side with respect to the center of rotation of the rotor. And a cam ring defining a pump chamber which is a plurality of hydraulic fluid chambers together with the rotor and the adjacent vane, and housed in the pump body, in a direction to increase the eccentricity of the cam ring with respect to the rotational center of the rotor And a variable displacement vane pump including a spring, which is a biasing member for always biasing the cam ring. There.

Further, in JP2013-057326A, the cam ring is projected at a predetermined position on the outer peripheral portion, and is pivoted at an opposite position across the center of the cam ring with respect to the pivot portion constituting an eccentric rocking fulcrum and the pivot portion. It is disclosed to have an arm portion that cooperates with a spring.

In the variable displacement vane pump of JP2013-057326A, the biasing member (spring) is incorporated in a compressed state between the cam ring and the receiving member (pump body) for receiving the cam ring. Therefore, in the assembly of such a vane pump, it is necessary to compress and integrate the biasing member for biasing the cam ring in the housing member for housing the cam ring.

It is conceivable to use a jig for compressing the biasing member in the assembling operation of incorporating the biasing member into the housing member. However, even if the biasing member is incorporated into the housing member in a compressed state by the jig, the jig receives the biasing force of the biasing member, so it is difficult to pull out the jig from between the biasing member and its seating surface. As described above, the work of incorporating the biasing member is complicated, and it is desired to be performed more easily.

An object of the present invention is to improve the assemblability of a variable displacement vane pump.

According to an aspect of the present invention, there is provided a variable displacement vane pump comprising: a rotor connected to a drive shaft; a plurality of vanes reciprocably provided in a radial direction with respect to the rotor; and rotation of the rotor A cam ring which has an inner peripheral surface on which the tip of the vane slides and which is provided eccentrically with respect to the rotor, a receiving member for receiving the cam ring, and the cam ring and the receiving member in a compressed state. A biasing member for biasing the rotor in a direction to increase the amount of eccentricity with respect to the rotor, and at least one of the cam ring and the housing member includes a seating surface on which the biasing member is seated and a groove formed in the seating surface Have.

FIG. 1 is a plan view of a variable displacement vane pump according to a first embodiment of the present invention, showing a state in which a pump cover is removed. FIG. 2 is a cross-sectional view of the variable displacement vane pump according to the first embodiment of the present invention. FIG. 3 is a view for explaining a method of incorporating the biasing member of the variable displacement vane pump according to the first embodiment of the present invention, and shows a state before incorporating the biasing member. FIG. 4 is a view for explaining the method of incorporating the biasing member of the variable displacement vane pump according to the first embodiment of the present invention, and is an enlarged view showing the biasing member housed in the housing member. FIG. 5 is a view for explaining the method of incorporating the biasing member of the variable displacement vane pump according to the first embodiment of the present invention, and is an enlarged view showing a state where the biasing member is seated. FIG. 6 is an enlarged view showing a first modified example of the variable displacement vane pump according to the first embodiment of the present invention. FIG. 7 is an enlarged view showing a second modified example of the variable displacement vane pump according to the first embodiment of the present invention. FIG. 8 is a plan view of a variable displacement vane pump according to a second embodiment of the present invention, showing a state in which the pump cover is removed. FIG. 9 is a view for explaining the method of incorporating the biasing member of the variable displacement vane pump according to the second embodiment of the present invention, and is an enlarged view showing the biasing member housed in the housing member. FIG. 10 is a view for explaining the method of incorporating the biasing member of the variable displacement vane pump according to the second embodiment of the present invention, and is an enlarged view showing a state in which the cam ring is housed in the housing member. FIG. 11 is a view for explaining the method of incorporating the biasing member of the variable displacement vane pump according to the second embodiment of the present invention, and is an enlarged view showing a state where the biasing member is seated.

Hereinafter, embodiments of the present invention will be described with reference to the attached drawings.

First Embodiment
First, the overall configuration of a variable displacement vane pump (hereinafter simply referred to as a "vane pump") 100 according to a first embodiment of the present invention will be described with reference to Figs.

The vane pump 100 is used as a fluid pressure source mounted on a vehicle, for example, a fluid pressure supply source such as a continuously variable transmission.

In the vane pump 100, the power of an engine (not shown) is transmitted to the end of the drive shaft 1, and with the rotation of the rotor 2 connected to the drive shaft 1, the working oil as a working fluid is sucked and discharged. . The rotor 2 rotates counterclockwise as shown by the arrow in FIG.

As shown in FIG. 1 and FIG. 2, the vane pump 100 accommodates the plurality of vanes 3 provided reciprocably in the radial direction with respect to the rotor 2 and the rotor 2 and rotates the vanes 3 as the rotor 2 rotates. A cam ring 4 having a cam surface 4a which is an inner peripheral surface on which the tip slides, a cam ring 4 which can be eccentric to the center of the rotor 2, a first pump body 10 through which the drive shaft 1 is inserted, and a housing member for housing the cam ring 4 And a pump cover 15 provided so as to sandwich the second pump body 20 together with the first pump body 10 and sealing the opening of the second pump body 20. The drive shaft 1 is rotatably supported by the first pump body 10, as shown in FIG.

As shown in FIG. 1, slits 7 opened on the outer peripheral surface of the rotor 2 are radially formed at predetermined intervals. The vanes 3 are inserted into the slits 7 so as to be capable of reciprocating. In the slit 7, a back pressure chamber 8 into which the discharge pressure is introduced is partitioned by the base end of the vane 3.

The vanes 3 are pressed in the direction of coming out of the slit 7 by the pressure of the hydraulic fluid introduced to the back pressure chamber 8, and the tip end portion abuts on the cam surface 4 a of the cam ring 4. As a result, inside the cam ring 4, a plurality of pump chambers 9 are defined by the outer peripheral surface of the rotor 2, the cam surface 4 a of the cam ring 4, and the adjacent vanes 3.

The cam ring 4 has a substantially annular main body portion 5 having a cam surface 4 a which is an inner circumferential surface in sliding contact with the tip end of the vane 3, and a lever portion 6 extending in the radial direction from the main body portion 5. A proximal end of the lever portion 6 is connected to the main body portion 5, and a substantially planar seating surface 6a on which a spring 30 described later is seated is formed at the distal end.

In addition, the cam ring 4 has a suction area for expanding the volume of the pump chamber 9 divided between the vanes 3 sliding on the cam surface 4 a as the rotor 2 rotates, and a discharge area for reducing the volume of the pump chamber 9 And. Thus, each pump chamber 9 expands and contracts as the rotor 2 rotates.

As shown in FIG. 2, an accommodation recess 10 a is formed in the first pump body 10 at a position facing the rotor 2 and the cam ring 4. In the housing recess 10a, a side plate 11 is disposed to be in contact with one side surface (right side surface in FIG. 2) of the rotor 2 and the cam ring 4. The side plate 11 is formed to be substantially flush with the end face of the first pump body 10 facing the second pump body 20. A pump cover 15 is disposed in contact with the other side surface (left side surface in FIG. 1) of the rotor 2 and the cam ring 4. The side plate 11 and the pump cover 15 are disposed in a state in which both side surfaces of the rotor 2 and the cam ring 4 are sandwiched, and the pump chamber 9 is sealed. In the present embodiment, although the pump cover 15 abuts on the other side of the rotor 2 and the cam ring 4 to seal the pump chamber 9, the pump cover 15 is provided with a side plate which abuts on the other side of the rotor 2 and the cam ring 4. The pump chamber 9 may be sealed with this side plate.

The pump cover 15 communicates with a suction port 16 opening in an arc corresponding to the suction area of the pump chamber 9 and a tank (not shown), and leads hydraulic oil of the tank to the pump chamber 9 through the suction port 16 The suction passage 17 is formed. Further, a discharge port 12 which is opened in an arc shape corresponding to the discharge area of the pump chamber 9 is formed in the side plate 11 so as to penetrate therethrough.

In the first pump body 10, a high pressure chamber 13 is formed, into which hydraulic fluid discharged from the pump chamber 9 in the discharge area is introduced. The hydraulic oil discharged from the pump chamber 9 is led to the high pressure chamber 13 through the discharge port 12 formed in the side plate 11. The hydraulic oil led to the high pressure chamber 13 is supplied to an external hydraulic device through a discharge passage (not shown) formed in the first pump body 10 and communicating with the high pressure chamber 13.

The vane pump 100 sucks the working oil from the tank through the suction port 16 and the suction passage 17 in each pump chamber 9 in the suction area of the cam ring 4 in accordance with the rotation of the rotor 2, and each pump room 9 in the discharge area of the cam ring 4. The hydraulic fluid is discharged to the outside through the discharge port 12 and the discharge passage. Thus, the vane pump 100 supplies and discharges the hydraulic oil by the expansion and contraction of each pump chamber 9 accompanying the rotation of the rotor 2.

The second pump body 20 is a receiving member for receiving the cam ring 4 and also functions as an adapter ring for swingably supporting the cam ring 4. As shown in FIG. 1, a support pin 21 for supporting the cam ring 4 is provided on the inner peripheral surface of the second pump body 20. The cam ring 4 swings around the support pin 21 inside the second pump body 20 and is eccentric to the center of the rotor 2. Thus, the support pin 21 is a pivot point of the cam ring 4.

On the inner peripheral surface of the second pump body 20, the first restricting portion 22 for restricting the movement of the cam ring 4 in the direction of decreasing the eccentricity with respect to the rotor 2 and the movement of the cam ring 4 in the direction of increasing the eccentricity with respect to the rotor 2 And the second restricting portion 23 which restricts the pressure. That is, the first restricting portion 22 defines the minimum eccentricity of the cam ring 4 with respect to the rotor 2, and the second restricting portion 23 defines the maximum eccentricity of the cam ring 4 with the rotor 2.

At a position axially symmetrical with the support pins 21 on the inner peripheral surface of the second pump body 20, a seal material 24 in contact with the outer peripheral surface of the main body 5 of the cam ring 4 is attached when the cam ring 4 swings.

Thus, in the outer peripheral accommodation space on the outer side of the cam ring 4 which is between the outer peripheral surface of the cam ring 4 and the inner peripheral surface of the second pump body 20, the first fluid pressure chamber is formed by the support pin 21 and the seal member 24. 25 and the second fluid pressure chamber 26 are divided. Not limited to this, an adapter ring is provided separately from the second pump body 20, and the first fluid pressure chamber 25 and the second fluid pressure chamber 26 may be provided between the outer peripheral surface of the cam ring 4 and the inner peripheral surface of the adapter ring. And may be divided.

The second pump body 20 is formed with a spring chamber 27 in which a coil spring (hereinafter, simply referred to as a "spring") 30 as a biasing member is accommodated. The spring chamber 27 communicates with the first fluid pressure chamber 25. Further, the tip of the lever portion 6 is accommodated in the spring chamber 27. A spring 30 as a biasing member is interposed between the lever portion 6 of the cam ring 4 and the second pump body 20 in a compressed state. Specifically, the spring 30 is seated on a seating surface 20a which is a wall surface which divides the spring chamber 27 in the second pump body 20 at one end (lower end in FIG. 1), and the other end (upper end in FIG. 1) is a lever portion The seat 6 is seated on a seating surface 6 a formed at the tip of the seat 6. The spring 30 biases the lever portion 6 of the cam ring 4 in a direction in which the amount of eccentricity of the cam ring 4 with respect to the rotor 2 is increased.

The first fluid pressure chamber 25 communicates with a suction passage 17 (see FIG. 2) for sucking in the hydraulic oil from the tank. The discharge pressure of the pump chamber 9 whose pressure is controlled by a control valve (not shown) is led to the second fluid pressure chamber 26. Since the pressure of the hydraulic fluid introduced to the second fluid pressure chamber 26 is higher than the pressure of the suction passage 17, a thrust in the direction of decreasing the amount of eccentricity with respect to the rotor 2 acts on the cam ring 4 due to the pressure difference. Accordingly, the cam ring 4 swings around the support pin 21 so that the thrust due to the pressure difference between the first fluid pressure chamber 25 and the second fluid pressure chamber 26 and the biasing force of the spring 30 are balanced. When the cam ring 4 swings with the support pin 21 as a fulcrum, the amount of eccentricity of the cam ring 4 with respect to the rotor 2 changes, and the displacement of the pump chamber 9 changes.

When the thrust due to the pressure difference between the first fluid pressure chamber 25 and the second fluid pressure chamber 26 is larger than the biasing force of the spring 30, the amount of eccentricity of the cam ring 4 with respect to the rotor 2 becomes smaller, and the displacement of the pump chamber 9 is reduced. Becomes smaller. On the other hand, when the thrust due to the pressure difference between the first fluid pressure chamber 25 and the second fluid pressure chamber 26 is smaller than the biasing force of the spring 30, the amount of eccentricity of the cam ring 4 with respect to the rotor 2 becomes large. The discharge capacity of the chamber 9 is increased. Thus, in the vane pump 100, the amount of eccentricity of the cam ring 4 with respect to the rotor 2 is changed by the pressure difference between the first fluid pressure chamber 25 and the second fluid pressure chamber 26 and the biasing force of the spring 30, Changes.

As shown in FIG. 1, in the seating surface 6 a of the spring 30 in the lever portion 6 of the cam ring 4 and the seating surface 20 a of the spring 30 in the second pump body 20,

grooves

6 b, 20b are formed. The groove 6b formed in the lever portion 6 is formed along the central axis direction (vertical direction in the drawing of FIG. 1) of the rotor 2 and is an end surface of the lever portion 6 on the pump cover 15 side (end surface facing the pump cover 15) Open to Further, the groove 20 b formed in the second pump body 20 is formed along the central axis direction of the rotor 2 and opens at the end face of the second pump body 20 on the pump cover 15 side. The position facing the spring 30 is a position where the

grooves

6 b and 20 b face part of the spring 30.

Next, a method of manufacturing the vane pump 100 will be described with reference to FIGS. 3 to 5. In the following, a method of incorporating the spring 30 into the second pump body 20 will be mainly described.

Before the spring 30 is incorporated into the second pump body 20, the second pump body 20 is placed on the first pump body 10, and as shown in FIG. , Vane 3 and cam ring 4 are incorporated.

In this state, as shown in FIG. 4, the spring 30 is axially held by the jig T capable of axially holding the spring 30 and compressed, and the spring 30 in the compressed state is the lever portion 6 of the cam ring 4. And housed between the second pump body 20. The jig T includes, for example, as shown in FIG. 4, a pair of holding portions having a circular cross section, and is configured such that the distance between the holding portions is expanded and contracted by an external force. That is, the jig T is configured such that the holding portions approach and separate from each other by an external force.

Next, from the state where the spring 30 is compressed by the jig T, the force for holding (compressing) the spring 30 by the jig T is weakened to extend the spring 30. Then, both ends of the spring 30 are respectively seated on the seating surface 20 a of the second pump body 20 and the seating surface 6 a of the lever portion 6 of the cam ring 4. At this time, the jig T is inserted into the groove 6 b of the lever portion 6 and the groove 20 b of the second pump body 20 as shown in FIG. 5. As described above, the

grooves

6b and 20b formed on the seating surfaces 6a and 20a of the lever portion 6 and the second pump body 20 are jig insertion grooves into which a jig T for compressing the spring 30 is inserted. is there.

Next, the jig T is extracted from the

grooves

6 b and 20 b in the seating surfaces 6 a and 20 a of the lever portion 6 and the second pump body 20. Here, the depths of the

grooves

6 b and 20 b are each formed larger than the thickness (outer diameter) of the jig T along the axis of the spring 30. For this reason, as shown in FIG. 5, in the state where the jig T is accommodated in the

grooves

6b and 20b, gaps are formed between the

grooves

6b and 20b and the jig T, respectively. Since the jig T is accommodated in the

grooves

6 b and 20 b, the jig T is not pinched by the spring 30, the lever portion 6, the spring 30 and the second pump body 20. Therefore, both end portions of the spring 30 are reliably seated on the seating surfaces 6a and 20a. Further, since the seating surfaces 6a and 20a of the lever portion 6 and the second pump body 20 receive the biasing force of the spring 30, and the biasing force is not applied to the jig, the jig T can be easily removed from the

grooves

6b and 20b. It can be extracted. Therefore, the spring 30 can be easily incorporated between the second pump body 20 and the lever portion 6, and the assembling performance of the vane pump 100 can be improved.

Next, a modification of the first embodiment will be described.

In the first embodiment, the first pump body 10 rotatably supporting the drive shaft 1 and the second pump body 20 which is a housing member for housing the cam ring 4 are separately formed. On the other hand, the first pump body 10 and the second pump body 20 may be integrally formed.

Further, in the first embodiment, the

single grooves

6b and 20b are formed on the seating surface 6a of the lever portion 6 and the seating surface 20a of the second pump body 20, respectively. On the other hand, the number and the shape of the

grooves

6 b and 20 b can be arbitrarily configured in accordance with the shape of the jig T. For example, two or

more grooves

6b and 20b may be provided on the seating surfaces 6a and 20a. Moreover, you may form

groove

6b, 20b of the magnitude | size which can insert two or more jig | tool T into

seating surface

6a, 20a.

Further, in the first embodiment, the

grooves

6 b and 20 b are formed on both the seating surface 6 a of the lever portion 6 and the seating surface 20 a of the second pump body 20. On the other hand, the groove 20 b may be formed only on the seating surface 20 a of the second pump body 20. In this case, as shown in FIG. 6, the lever portion 6 is formed so that a space for inserting the jig T is divided between the lever portion 6 and the second pump body 20. The lever portion 6 and the spring 30 are integrally held by the jig T in a state where the spring 30 is seated on the seating surface 6 a of 6. In this state, the cam ring 4 and the spring 30 may be accommodated together in the second pump body 20. After that, the holding force is reduced and the spring 30 is seated on the second pump body 20 so that the jig T on the second pump body 20 side is inserted into the groove 20b formed in the seating surface 20a of the second pump body 20. Seat on face 20a. Thus, the jig T can be easily pulled out and the spring 30 can be incorporated into the second pump body 20 in a compressed state. That is, the jig on the side of the lever portion 6 in a state where the amount of eccentricity of the cam ring 4 is maximum, in which the end face 6c of the lever portion 6 opposite to the seating surface 6a is closest to the wall portion of the second pump body 20. It may be configured such that T does not contact the inner peripheral surface of the second pump body 20 so that withdrawal of the jig T is not impeded by the second pump body 20.

Further, as shown in FIG. 7, the groove 20 b is formed only in the seating surface 20 a of the second pump body 20, and a seating member 31 separate from the lever portion 6 is provided between the lever portion 6 and the spring 30. It is also good. In this case, the spring 30 and the seating member 31 are held together by the jig T and inserted into the second pump body 20. In this state, the spring 30 is extended so that the jig T is inserted into the groove 20b of the second pump body 20, thereby seating one end of the spring 30 on the seating surface 20a of the second pump body 20 The member 31 is brought into contact with the lever portion 6. A sufficient gap is provided between the jig T and the second pump body 20 so as not to interfere with each other, and the jig T engages with the seating member 31 and the spring via the seating member 31. Hold 30. Therefore, the withdrawal of the jig T is not hindered by the second pump body 20. Therefore, the jig T can be easily pulled out from the groove 20 b and between the seating member 31 and the second pump body 20. Even in this case, the same effect as that of the above embodiment can be obtained. On the contrary, while the groove 6 b is formed only in the seating surface 6 a of the lever portion 6, the seating member 31 may be provided between the spring 30 and the second pump body 20. The seating member 31 will be described in detail in a second embodiment described later. As described above, if at least one of the cam ring 4 and the second pump body 20 has the seating surfaces 6a and 20a and the

grooves

6b and 20b, the same effect as that of the above embodiment can be obtained.

According to the first embodiment described above, the following effects can be obtained.

In the vane pump 100, the spring 30 compressed in the second pump body 20 by the jig T is extended so that the jig T is accommodated in the

grooves

6b and 20b, and is seated on the seating surfaces 6a and 20a. The spring 30 is incorporated into the second pump body 20 by pulling out the jig T from the

grooves

6 b and 20 b. Thus, the formation of the

grooves

6b and 20b in the seating surfaces 6a and 20a prevents the jig T from being pinched between the spring 30 and the seating surfaces 6a and 20a. It does not receive a biasing force. Therefore, the jig T can be easily pulled out of the second pump body 20, and the spring 30 can be easily incorporated into the second pump body 20. Therefore, the assemblability of the vane pump 100 is improved.

Second Embodiment
Next, a second embodiment of the present invention will be described with reference to FIGS. In the following, differences from the first embodiment will be mainly described, and the same components as those of the vane pump 100 of the first embodiment will be assigned the same reference numerals and descriptions thereof will be omitted.

In the first embodiment, the spring 30 is seated on the seating surface 6 a of the lever portion 6 and on the seating surface 20 a of the second pump body 20. Further, in the seating surface 6 a of the lever portion 6 and the seating surface 20 a of the second pump body 20,

grooves

6 b and 20 b are formed. On the other hand, in the second embodiment, a seating member 31 separate from the cam ring 4 is provided between the spring 30 and the lever portion 6, and the spring 30 is seated on the seating member 31. In the second embodiment, the

grooves

6 b and 20 b in which the jig T is accommodated are not formed in the lever portion 6 and the second pump body 20. In such a point, the second embodiment is different from the first embodiment.

As shown in FIG. 8, the vane pump 200 according to the second embodiment further includes a seating member 31 formed separately from the cam ring 4 and provided between the spring 30 and the lever portion 6.

The seating member 31 has an abutting portion 32 that abuts on the lever portion 6 of the cam ring 4 and a disk portion that faces the spring 30.

The disc portion has a seating portion 33 on which the spring 30 is seated, and an engagement portion 34 for the jig T to be engaged. The engagement portion 34 is formed so as to radially and outwardly extend from the seat portion 33 in an annular manner. The engaging portion 34 forms a gap larger than the width (outside diameter) of the jig T with the lever portion 6. In other words, the thickness of the contact portion 32 (the length along the axial direction of the spring 30) such that a gap larger than the width of the jig T is formed between the engagement portion 34 and the lever portion 6 Is set.

Next, a method of manufacturing the vane pump 200 will be described. Hereinafter, as in the first embodiment, a method of incorporating the spring 30 will be mainly described.

When the spring 30 is incorporated in the vane pump 200, unlike the first embodiment, the spring 30 and the seating member 31 are incorporated into the second pump body 20 earlier than the cam ring 4. Thereafter, as shown in FIG. 9, the seating member 31, the spring 30, and the outer wall portion of the second pump body 20 are held by the jig T. Specifically, the two jigs T provided on one side are engaged with the engaging portion 34 of the seating member 31, and the two jigs T provided on the other side are provided on the outer wall surface of the second pump body 20. The seating member 31, the spring 30, and the second pump body 20 are held in contact with each other by the jig T. Thereby, the spring 30 is compressed by the holding force transmitted to the engaging portion 34 of the seating member 31 and the wall portion of the second pump body 20 through the jig T.

Next, as shown in FIG. 10, the cam ring 4 is inserted into the second pump body 20 while the spring 30 is in a compressed state. Thereafter, the holding force of the jig T is weakened to bring the contact portion 32 of the seating member 31 into contact with the lever portion 6 as shown in FIG. Furthermore, the jig T is pulled out of the second pump body 20. At this time, the jig T on one side (the seating member 31 side) does not contact the inner peripheral surface of the lever portion 6 and the second pump body 20. Therefore, the jig T can be easily pulled out, and the spring 30 can be easily incorporated into the second pump body 20 by pulling out the jig T.

As described above, in the second embodiment, by providing the seating member 31, the jig T can be assembled when the spring 30 is assembled, even if the

grooves

6b and 20b are not formed in the lever portion 6 and the second pump body 20. It can be pulled out easily.

Next, a modification of the second embodiment will be described.

In the second embodiment, the seating member 31 is provided only between the spring 30 and the lever portion 6. In addition to this, a seating member 31 may be provided between the spring 30 and the second pump body 20. In this case, as in the second embodiment, the

grooves

6b and 20b are not formed in both of the lever portion 6 and the second pump body 20, while the cam ring 4 is firstly mounted as in the first embodiment. The spring 30 can be housed in the second pump body 20 by being accommodated by the jig T together with the two seating members 31 and housed in the second pump body 20.

Moreover, in the said 2nd Embodiment, the seating member 31 has the seating part 33 and the engaging part 34 which are integrally formed as a disk part. Not limited to this, in the state where the abutting portion 32 and the cam ring 4 abut on each other, the jig T engaged with the engaging portion 34 and the cam ring 4 and the second pump body 20 abut each other. If it is formed so as not to be formed, it can be formed in any shape. In other words, the seating member 31 is formed in an arbitrary shape as long as the jig T engaged with the engagement portion 34 and the cam ring 4 and the second pump body 20 are formed so as not to be in contact with each other. can do.

According to the above second embodiment, the following effects can be obtained.

In the vane pump 200, the spring 30 compressed by the jig T through the seating member 31 in the second pump body 20 is extended so that the seating member 31 abuts on the lever portion 6 of the cam ring 4, and then the jig T The spring 30 is incorporated into the second pump body 20 by pulling out the second pump body 20. As described above, the jig T compresses the spring 30 via the seating member 31, and the jig T is not pinched between the spring 30 and the seating surfaces 6a and 20a. Thus, the jig T can be easily pulled out of the second pump body 20, and the spring 30 can be easily incorporated into the second pump body 20. Therefore, the assemblability of the vane pump 200 is improved.

Hereinafter, the configuration, operation, and effects of the embodiment of the present invention will be collectively described.

In the vane pump 100, the rotor 2 connected to the drive shaft 1, the plurality of vanes 3 provided to be reciprocally movable in the radial direction with respect to the rotor 2, and the tips of the vanes 3 slide as the rotor 2 rotates. Interposed in a compressed state between the cam ring 4 and the second pump body 20, the cam ring 4 having the cam surface 4a and being provided eccentrically with respect to the rotor 2, the second pump body 20 accommodating the cam ring 4 And the cam ring 4 and the second pump body 20 are provided with

seating surfaces

6a and 20a on which the spring 30 is seated, and the seating surface 6a. , 20a, and

grooves

6b, 20b.

Further, in the vane pump 100, the

grooves

6b and 20b are jig insertion grooves into which a jig T for compressing the spring 30 is inserted, and are formed at positions facing the spring 30.

Further, in the vane pump 100, the cam ring 4 is formed on the main body portion 5 on which the cam surface 4a on which the tip of the vane 3 slides is formed, and the lever portion 6 extending in the radial direction from the main body portion 5 And.

In these configurations, the spring 30 compressed in the second pump body 20 by the jig T is extended so that the jig T is accommodated in the

grooves

6b and 20b, and is seated on the seating surfaces 6a and 20a, Thereafter, the spring 30 is incorporated into the second pump body 20 by pulling out the jig T from the

grooves

6 b and 20 b. Thus, the formation of the

grooves

6b and 20b in the seating surfaces 6a and 20a prevents the jig T from being pinched between the spring 30 and the seating surfaces 6a and 20a. Since the biasing force is not received, the jig T can be easily pulled out of the second pump body 20. Thus, the spring 30 can be easily incorporated into the second pump body 20. Therefore, the assemblability of the vane pump 100 is improved.

Further, in the vane pump 200, the rotor 2 connected to the drive shaft 1, the plurality of vanes 3 provided to reciprocate in the radial direction with respect to the rotor 2, and the tips of the vanes 3 slide as the rotor 2 rotates. In a compressed state between the cam ring 4 and the second pump body 20, the cam ring 4 having the moving cam surface 4a and being provided eccentrically with respect to the rotor 2, the second pump body 20 accommodating the cam ring 4 and A spring 30 is interposed and biases the cam ring 4 in a direction in which the amount of eccentricity with respect to the rotor 2 increases, and a seating member 31 provided between the spring 30 and the cam ring 4 and on which the spring 30 is seated.

Further, in the vane pump 200, the seating member 31 engages the abutment portion 32 that abuts the cam ring 4, the seating portion 33 on which the spring 30 is seated, and the engagement portion 34 for engaging the jig T that compresses the spring 30. And the jig T engaged with the engagement portion 34 and the cam ring 4 and the second pump body 20 are not in contact with each other when the contact portion 32 and the cam ring 4 are in contact with each other. Be done.

In such a configuration, the spring 30 compressed by the jig T through the seating member 31 in the second pump body 20 is extended so that the seating member 31 abuts on the cam ring 4 and then the jig T is pulled out. Thus, the spring 30 is incorporated into the second pump body 20. As described above, the jig T compresses the spring 30 via the seating member 31, and the jig T is not pinched between the spring 30 and the seating surface 6a. It can be easily pulled out of the pump body 20. Thus, the spring 30 can be easily incorporated into the second pump body 20. Therefore, the assemblability of the vane pump 200 is improved.

As mentioned above, although the embodiment of the present invention was described, the above-mentioned embodiment showed only a part of application example of the present invention, and in the meaning of limiting the technical scope of the present invention to the concrete composition of the above-mentioned embodiment. Absent.

The present application claims priority based on Japanese Patent Application No. 2016-182110 filed on September 16, 2016 to the Japan Patent Office, and the entire contents of this application are incorporated herein by reference.

Claims

A variable displacement vane pump,
A rotor connected to the drive shaft,
A plurality of vanes reciprocably provided in the radial direction with respect to the rotor;
A cam ring having an inner circumferential surface on which the tip of the vane slides as the rotor rotates, and provided eccentrically to the rotor;
An accommodating member for accommodating the cam ring;
And a biasing member interposed in a compressed state between the cam ring and the receiving member and biasing the cam ring in a direction in which the amount of eccentricity with respect to the rotor increases.
A variable displacement vane pump, wherein at least one of the cam ring and the housing member has a seating surface on which the biasing member is seated, and a groove formed in the seating surface.
A variable displacement vane pump according to claim 1, wherein
The groove is a jig insertion groove into which a jig for compressing the biasing member is inserted, and the variable displacement vane pump is formed at a position facing the biasing member.
A variable displacement vane pump according to claim 1, wherein
The cam ring is a variable displacement type having a main body on which the inner peripheral surface on which the tip of the vane slides is formed, and a lever on which the seating surface is provided by extending radially from the main body. Vane pump.
A variable displacement vane pump,
A rotor connected to the drive shaft,
A plurality of vanes reciprocably provided in the radial direction with respect to the rotor;
A cam ring having an inner circumferential surface on which the tip of the vane slides as the rotor rotates, and provided eccentrically to the rotor;
An accommodating member for accommodating the cam ring;
An urging member interposed in a compressed state between the cam ring and the receiving member, and urging the cam ring in a direction in which the amount of eccentricity with respect to the rotor becomes large;
A variable displacement vane pump comprising: a seating member provided between the biasing member and the cam ring and on which the biasing member is seated.
The variable displacement vane pump according to claim 4, wherein
The seating member includes an abutment portion abutting on the cam ring, a seating portion on which the biasing member is seated, and an engaging portion for engaging a jig for compressing the biasing member.
The variable displacement vane pump is configured such that the jig engaged with the engagement portion, the cam ring, and the housing member do not abut each other when the contact portion and the cam ring abut.