WO2017047484A1

WO2017047484A1 - Cartridge vane pump

Info

Publication number: WO2017047484A1
Application number: PCT/JP2016/076378
Authority: WO
Inventors: 義之牧; 杉原　雅道; 智行中川; 考司義村
Original assignee: Ｋｙｂ株式会社
Priority date: 2015-09-18
Filing date: 2016-09-08
Publication date: 2017-03-23
Also published as: MX2018003386A; JP2017057833A; CN107949702A; US20180252212A1; EP3327288A1

Abstract

This cartridge vane pump (100) is provided with: a body-side side plate (20) that makes contact with an end surface of a cam ring (4) and a rotor (2); first and second discharge ports (7a), (7b) that are formed in the body-side side plate (20); and an adaptor 40 in which first connecting channels (41a), (41b), which connect the first and second discharge ports (7a), (7b) formed in the body-side side plate (20) and first and second discharge channels (93a), (93b) formed in a body (90), is formed.

Description

Cartridge vane pump

The present invention relates to a cartridge type vane pump.

JP 2003-301781A describes a cartridge-type vane pump configured to be detachable from a main body fixed to a base or a frame.

In order to attach such a cartridge type vane pump to a fluid pressure device, it is necessary to make the position and shape of the discharge port provided in the side plate so as to match the discharge flow path provided in the fluid pressure device. . However, since the side plate slides with the rotor, the side plate is formed using a material having excellent durability. Since such a material has poor processability and high cost, manufacturing the side plate so as to be compatible with each of the fluid pressure devices having different discharge flow paths may cause an increase in cost.

An object of the present invention is to provide a cartridge type vane pump capable of reducing the cost while adapting the discharge port of the side plate to the discharge flow path of the fluid pressure device.

According to an aspect of the present invention, a cartridge-type vane pump that is detachably accommodated in a body of a fluid pressure device has a rotor that is connected to a drive shaft and is driven to rotate, and an opening on the outer periphery of the rotor. A plurality of slits formed in each of the slits, a vane that is slidably inserted into each slit, a cam ring having an inner peripheral cam surface with which the tip of the vane is in sliding contact, and a rotor and a vane adjacent to the cam ring. A pump chamber, a cover member that is in contact with one end surface of the rotor and the cam ring, a side plate that is in contact with the other end surface of the rotor and the cam ring, and a side plate that is formed on the side plate and discharged from the pump chamber. There is a connection flow path that connects the discharge port through which the working fluid is guided to the discharge port formed in the side plate and the discharge flow path formed in the body. Includes an adapter to be made, the.

FIG. 1 is a front view of a cartridge type vane pump according to an embodiment of the present invention. FIG. 2 is an exploded perspective view of the cartridge type vane pump according to the embodiment of the present invention as viewed from the cover member side. FIG. 3 is an exploded perspective view seen from the adapter side of the cartridge type vane pump according to the embodiment of the present invention. FIG. 4 is a sectional view in the axial direction of the cartridge type vane pump according to the embodiment of the present invention. FIG. 5 is an enlarged view of a fastening member of the cartridge type vane pump according to the embodiment of the present invention. FIG. 6 is a plan view of the adapter of the cartridge type vane pump according to the embodiment of the present invention. FIG. 7 is a rear view of the adapter of the cartridge type vane pump according to the embodiment of the present invention.

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

The cartridge type vane pump 100 according to the embodiment of the present invention is used as a fluid pressure supply source for a fluid pressure device mounted on a vehicle, for example, a power steering device or a transmission. The working fluid is hydraulic oil or other water-soluble alternative liquid.

The cartridge-type vane pump 100 (hereinafter simply referred to as “vane pump 100”) is detachably accommodated in an accommodating recess 91 formed in the body 90 of the fluid pressure device in a pre-assembled state (the state shown in FIG. 1). (See FIG. 4). The power of an engine (not shown) is transmitted to the end of the drive shaft 1, and the rotor 2 connected to the drive shaft 1 rotates.

As shown in FIGS. 1 to 4, the vane pump 100 includes a rotor 2 that is connected to the drive shaft 1 and is driven to rotate, and a plurality of slits 2 a that are radially formed with openings on the outer periphery of the rotor 2. A plurality of vanes 3 that are slidably inserted into the respective slits 2 a and are provided so as to be capable of reciprocating in the radial direction with respect to the rotor 2. The rotor 2 is housed and the tip of the vane 3 slides as the rotor 2 rotates. And a cam ring 4 having a moving inner peripheral cam surface 4a.

A back pressure chamber 5 into which the discharge pressure of the pump is guided is defined on the base end side of the slit 2a. The vane 3 is pressed in the direction of coming out of the slit 2 a by the pressure of the back pressure chamber 5, and the tip part comes into contact with the inner peripheral cam surface 4 a of the cam ring 4. As a result, a plurality of pump chambers 6 are defined inside the cam ring 4 by the outer peripheral surface of the rotor 2, the inner peripheral cam surface 4 a of the cam ring, and the adjacent vanes 3.

The cam ring 4 is an annular member having an inner circumferential cam surface 4 a that is substantially elliptical, and includes a suction region that expands the volume of the pump chamber 6 as the rotor 2 rotates and a discharge region that contracts the volume of the pump chamber 6. Have Each pump chamber 6 expands and contracts as the rotor 2 rotates. The vane pump 100 is a so-called balanced vane pump in which the cam ring 4 has two suction regions and two discharge regions. The cam ring 4 is formed with notches 4e that communicate the outside and the inside of the cam ring 4 on both end faces at positions corresponding to the two suction regions.

The vane pump 100 has a cover-side side plate 10 that abuts on one end surface (upper side in FIGS. 1 and 4) of the rotor 2 and the cam ring 4, and the other end surface (lower side in FIGS. 1 and 4) of the rotor 2 and the cam ring 4. It further includes a body-side side plate 20 that abuts and a cover 30 that abuts against the cover-side side plate 10 and is fixed to the body 90 of the fluid pressure device. A cover member is constituted by the cover side plate 10 and the cover 30.

The cover side plate 10 and the body side plate 20 are disposed so as to sandwich the rotor 2 and the cam ring 4. The cover chamber side plate 10 and the body side plate 20 sandwich the both end surfaces of the rotor 2 and the cam ring 4 to seal the pump chamber 6.

As shown in FIG. 3, the cover-side side plate 10 is formed so as to cut out a part of the outer edge portion, and has a suction port 11 that guides hydraulic oil into the pump chamber 6 and positions corresponding to the two discharge regions. Each includes a discharge recess 12 and a through hole 13 through which the drive shaft 1 is inserted.

The suction port 11 is formed at a position corresponding to two suction areas. Each suction port 11 is formed in an arc shape with the through hole 13 as the center. The suction port 11 communicates with the tank through a suction space 70 formed in an annular shape between the cam ring 4 shown in FIG. 4 and the body 90 of the fluid pressure device, and a suction flow path 92 formed in the body 90.

The discharge recess 12 is formed in a groove shape and at positions corresponding to the two discharge areas. Each discharge recess 12 is formed in an arc shape centered on the through hole 13. The discharge recess 12 is provided so as to face first and second through

holes

21a and 21b formed in a body side plate 20 to be described later with the vane 3 interposed therebetween. Since the discharge recess 12 communicates with the first and second through

holes

21 a and 21 b through the pump chamber 6, the same pressure as the first and second through

holes

21 a and 21 b acts on the discharge recess 12. Therefore, the force acting on the vane 3 due to the pressure in the first and second through

holes

21 a and 21 b is offset by the pressure of the discharge recess 12, and the vane 3 can be prevented from being pressed against the cover-side side plate 10.

As shown in FIG. 2, the body side plate 20 is formed on the slidable contact surface 20a in which the other end surface of the rotor 2 is in slidable contact with the two discharge regions, and is operated on the pump chamber 6. First and second through

holes

21 a and 21 b that discharge oil, a through hole 22 through which the drive shaft 1 is inserted, and a suction recess 23 that allows the suction space 70 and the pump chamber 6 to communicate with each other.

The first and second through

holes

21 a and 21 b are provided at symmetrical positions with the through hole 22 as the center. The first and second through

holes

21 a and 21 b are formed in an arc shape with the through hole 22 as the center, and are formed through the body side plate 20.

The suction recess 23 is formed on the sliding contact surface 20a so as to correspond to the two suction regions. The outer peripheral edge of each suction recess 23 reaches the outer peripheral surface of the body side plate 20 and is formed in a concave shape that opens radially outward.

An outer notch 26 and an inner notch 27 which are grooves extending from the first and second through

holes

21a and 21b toward the rear in the rotation direction of the rotor 2 are formed on the sliding contact surface 20a of the body side plate 20. The outer notch 26 is disposed on the outer peripheral side of the inner notch 27 and is longer in the rotational direction of the rotor 2 than the inner notch 27.

Both the outer notch 26 and the inner notch 27 are formed in a tapered shape in which the dimension in the radial direction of the rotor 2 decreases as going from the first and second through

holes

21a, 21b to the rear in the rotational direction of the rotor 2. Further, the outer notch 26 and the inner notch 27 are disposed on the outer peripheral side of the outer peripheral surface of the rotor 2 and on the inner peripheral side of the inner peripheral cam surface 4 a of the cam ring 4.

A pair of first back pressure grooves 24a are formed in the sliding contact surface 20a of the body side plate 20 at symmetrical positions with the through hole 22 as a center, and the through holes 22 are formed with respect to the pair of first back pressure grooves 24a. A pair of second back pressure grooves 24b are formed at positions shifted by approximately 90 ° from the center.

The first back pressure groove 24 a is formed in an arc shape with the through hole 22 as the center, and communicates with the back pressure chamber 5. The first back pressure groove 24a communicates the plurality of back pressure chambers 5 opened to the first back pressure groove 24a.

The second back pressure groove 24 b is formed in an arc shape with the through hole 22 as the center, and communicates with the back pressure chamber 5. The second back pressure groove 24b communicates the plurality of back pressure chambers 5 opened to the second back pressure groove 24b.

As shown in FIG. 3, the body-side side plate 20 opens to the end surface opposite to the sliding contact surface 20a, and communicates with the first and second through

holes

21a and 21b. 25b, the first and

second arc grooves

25a, 25b and the second back pressure groove 24b, the communication hole 28 formed through the body side plate 20, the first and second arc grooves 25a, O-

rings

83a and 83b as sealing members that surround and seal the outer periphery of 25b. The O-

rings

83a and 83b are mounted in grooves formed on the outer periphery of the first and

second arc grooves

25a and 25b of the body side plate 20 and compressed between the body side plate 20 and an adapter 40 described later. Provided in the state.

The first and

second arc grooves

25a and 25b are formed in an arc shape with the through hole 22 as the center. A first through hole 21a and a communication hole 28 are opened at the bottom surface of the first arc groove 25a, and a second through hole 21b and a communication hole 28 are opened at the bottom surface of the second arc groove 25b. Accordingly, the first through hole 21a and the communication hole 28 communicate with each other through the first arc groove 25a, and the second through hole 21b and the communication hole 28 communicate with each other through the second arc groove 25b. In the vane pump 100, the first through hole 21a and the first arc groove 25a constitute the first discharge port 7a, and the second through hole 21b and the second arc groove 25b constitute the second discharge port 7b.

The cover 30 is formed with a through hole 31 that supports the end of the drive shaft 1 via a sleeve. The cover 30 is fixed to the body 90 by inserting bolts (not shown) through a plurality of through holes 33 formed in the outer peripheral portion of the cover 30.

The vane pump 100 includes first and

second discharge ports

7a and 7b formed in the body side plate 20 and two first and

second discharge passages

93a and 93b (see FIG. 4) formed in the body 90. It further includes an adapter 40 in which first and second

connection flow paths

41a and 41b are respectively connected.

As shown in FIG. 4, the adapter 40 includes a main body portion 40b having an abutment surface 40a that abuts on the body side plate 20 and an annular surface 40f that faces a bottom surface of a third recess 91c of an accommodation recess 91 described later. A cylindrical portion 40c having a smaller diameter than the main body portion 40b and extending in the axial direction from the main body portion 40b, and a boss portion 40d extending into the cylindrical portion 40c from the main body portion 40b and forming a support hole 42 for supporting the end of the drive shaft 1. And an annular groove 47 formed in the annular surface 40f of the main body portion 40b.

The main body 40b is formed in a disc shape. An annular O-ring 81 that prevents leakage of hydraulic fluid between the main body 40b and the body 90 is provided on the outer periphery of the main body 40b.

The cylindrical portion 40c is formed coaxially with the main body portion 40b and has an internal space 40e inside. An annular O-ring 82 that blocks communication between the first connection flow path 41a and the second connection flow path 42b is provided on the outer periphery of the cylindrical portion 40c.

The first connection channel 41a is formed so as to penetrate the main body portion 40b between the contact surface 40a and the annular surface 40f, and connects the first discharge port 7a and the first discharge channel 93a. Specifically, the first connection channel 41a includes an arc-shaped first opening 44a that opens to the contact surface 40a, a groove 47 that opens to the annular surface 40f, and a first opening 44a and a groove 47. And a through hole 45a that communicates with each other. The first opening 44 a is formed at a position facing the first arc groove 25 a of the body side plate 20. The through hole 45a is formed in an arc shape along the outer peripheral surface of the cylindrical portion 40c (see FIGS. 6 and 7). Since the concave groove 47 is formed in an annular shape, even if the first connection flow path 41a of the vane pump 100 and the first discharge flow path 93a of the fluid pressure device are not provided at positions facing each other, the first discharge flow If the path 93 a is open toward the concave groove 47, the first connection flow path 41 a and the first discharge flow path 93 a communicate with each other through the concave groove 47.

As shown in FIG. 4, the second connection flow path 41b is formed to penetrate the main body portion 40b and communicate with the internal space 40e of the cylindrical portion 40c, and connects the second discharge port 7b and the second discharge flow path 93b. To do. Specifically, the second connection flow path 41b includes an arc-shaped second opening 44b that opens to the contact surface 40a, an internal space 40e of the cylindrical portion 40c, and an interior of the second opening 44b and the cylindrical portion 40c. And a through hole 45b communicating with the space 40e. The second opening 44b is formed at a position facing the second arc groove 25b of the body side plate 20. The through hole 45b is formed in an arc shape along the outer peripheral surface of the boss portion 40d (see FIGS. 6 and 7). The second connection flow path 41 b communicates with a second discharge flow path 93 b formed in the body 90.

Next, a method for assembling the vane pump 100 will be described.

First, the dowel pin 60 is press-fitted into the insertion hole 34 formed in the cover 30. Then, the dowel pins 60 are sequentially inserted into the through holes 15 formed in the cover side plate 10, the through holes 4 c formed in the cam ring 4, and the through holes 29 b formed in the body side plate 20, and finally It is inserted into the insertion hole 46 formed in the adapter 40. As a result, the cover 30, the cover side plate 10, the cam ring 4, the body side plate 20, and the adapter 40 are stacked. The drive shaft 1, the rotor 2, and the vane 3 are incorporated into the cam ring 4 when the cam ring 4 is inserted. In this way, the dowel pin 60 penetrates the cam ring 4 and is supported at both ends by the cover 30 and the adapter 40, and the relative rotation of the cover 30, the cover side plate 10, the body side plate 20 and the adapter 40 with respect to the cam ring 4. To prevent. That is, the dowel pin 60 functions as a positioning of these members during assembly, and also functions as a rotation stopper that prevents relative rotation of the cover side plate 10 and the body side plate 20 with respect to the cam ring 4 after assembly.

The cover 30, the cover side plate 10, the cam ring 4, the body side plate 20, and the adapter 40 stacked in this way are integrally held by two head pins 50 as coupling members. The head pin 50 will be specifically described below.

As shown in FIGS. 2 and 3, the head pin 50 includes a shaft portion 51 whose tip is fixed to an engagement hole 43 formed in the adapter 40, and a restricting portion that is larger in diameter than the shaft portion 51 and formed at the proximal end. 52. The shaft portion 51 includes a through hole 32 formed in the cover 30, a through hole 14 formed in the cover side plate 10, a through hole 4 b formed in the cam ring 4, and a through hole formed in the body side plate 20. 29a is penetrated and a front-end | tip is press-fitted in the engagement hole 43. FIG. Thus, the cover 30, the cover side plate 10, the cam ring 4, and the body side plate 20 are held in an integrated state between the restriction portion 52 of the head pin 50 and the adapter 40. Two head pins 50 are provided at symmetrical positions around the drive shaft 1. The head pin 50 may be fixed to the adapter 40 by providing a male screw at the tip of the shaft 51 and screwing with a female screw formed in the engagement hole 43.

Thus, the vane pump 100 is held in an integrated state by the head pins 50. Accordingly, when the vane pump 100 is attached to the body 90, specifically, when the vane pump 100 is transported to be attached to the body 90, or when the vane pump 100 is attached to the accommodating recess 91 of the body 90, the vane pump 100 is separated. Can be prevented. Therefore, the mounting property is improved. Further, when the vane pump 100 is removed from the body 90, the vane pump 100 is held in an integrated state, and therefore can be easily removed.

When the vane pump 100 is attached to the body 90 of the fluid pressure device, specifically, when the vane pump 100 is housed in the housing recess 91 of the body 90 and the cover 30 is fixed to the body 90, as shown in FIG. In addition, a gap S exists between the cover 30 and the restriction portion 52 of the head pin 50. When the vane pump 100 is driven and a high pressure is generated in the pump chamber 6, the vicinity of the center of the cover 30 may be bent so as to be bent (deform). In the vane pump 100, since the gap S exists between the cover 30 and the restriction portion 52 of the head pin 50, such a deflection of the cover 30 can be allowed. That is, since the cover 30 is bent and a force for pulling out the head pin 50 does not act on the restricting portion 52 of the head pin 50, the head pin 50 is prevented from being detached or damaged. Thus, since the vane pump 100 is hold | maintained at the state integrated with the head pin 50, when removing the vane pump 100, the vane pump 100 does not fall apart.

In the above embodiment, the description has been given by taking the case where there are two head pins 50 as an example. However, the present invention is not limited to this, and the head pins 50 may be more (about 3 to 6) as long as a space can be secured. As the number of head pins 50 increases, the holding force for maintaining the state in which the vane pump 100 is integrated is improved accordingly. Conversely, if the number of head pins 50 is small, the size can be reduced accordingly. By providing two head pins 50 at symmetrical positions with the drive shaft as the center, a minimum number of head pins 50 can be stably held. Further, the head pin 50 is configured such that the tip portion thereof is press-fitted into the engagement hole 43, so that it is not necessary to thread the head pin 50 and the engagement hole 43.

The vane pump 100 assembled in this way is fixed to the body 90 by being attached to the housing recess 91 of the body 90 and screwing the bolt inserted into the through hole 33 of the cover 30 into the body 90.

Next, the housing recess 91 of the body 90 will be described.

As shown in FIG. 4, the housing recess 91 of the body 90 includes, in order from the bottom surface side, a first recess 91 a in which the second discharge channel 93 b opens on the bottom surface and a diameter larger than that of the first recess 91 a. The second recess 91b in which one discharge channel 93a is opened, the third recess 91c having a larger diameter than the second recess 91b and into which the main body 40b of the adapter 40 is inserted, and having a larger diameter than the third recess 91c. And a fourth recess 91d in which the suction space 70 described above is formed between the vane pump 100 and the vane pump 100.

When the vane pump 100 is housed in the housing recess 91, the cylindrical portion 40c of the adapter 40 is fitted into the first recess 91a, and the main body 40b of the adapter 40 is fitted into the third recess 91c. At this time, the annular surface 40f of the main body portion 40b faces the bottom surface of the third recess 91c. Thereby, by the 2nd recessed part 91b, the 3rd recessed part 91c, the main-body part 40b of the adapter 40, and the outer periphery of the cylindrical part 40c, ie, the bottom face of the 2nd recessed part 91b and the 3rd recessed part 91c, and the main-body part 40b of the adapter 40 An annular high pressure chamber 94 is defined between them. The high pressure hydraulic oil discharged from the pump chamber 6 is guided to the high pressure chamber 94 through the first through hole 21 a, the first arc groove 25 a, the first opening 44 a, the through hole 45 a, and the concave groove 47. The hydraulic fluid guided into the high pressure chamber 94 flows out to the first discharge flow path 93a.

The body-side side plate 20, the cam ring 4, and the cover-side side plate 10 are accommodated in the fourth recess 91d, and the fourth recess 91d is closed by attaching the cover 30 to the body 90. Between the fourth recess 91d and the vane pump 100 (the body side plate 20, the cam ring 4, and the cover side plate 10), an annular suction space 70 that communicates with the suction flow path 92 is formed.

Next, the operation of the vane pump 100 will be described.

Rotating the drive shaft 1 with the power of a drive device such as an engine (not shown) causes the rotor 2 to rotate. As the rotor 2 rotates, the pump chamber 6 located in the two suction areas expands. As a result, the hydraulic oil in the tank is sucked into the pump chamber 6 through the suction flow path 92, the suction space 70, the notch 4 e, the suction port 11, and the suction recess 23. Further, the pump chamber 6 located in the two discharge regions contracts as the rotor 2 rotates. As a result, the hydraulic oil in the pump chamber 6 in the one discharge region flows into the first discharge port 7a (the first through hole 21a and the first arc groove 25a), the first connection flow path 41a (the first opening 44a, Through the through hole 45a and the concave groove 47), the high pressure chamber 94, and the first discharge flow passage 93a, hydraulic oil in the pump chamber 6 in the other discharge region is supplied to a hydraulic device (not shown) and is discharged into the second discharge region. Through the port 7b (second through-hole 21b and second arc groove 25b), second connection flow path 41b (second opening 44b, through-hole 45b, and internal space 40e) and second discharge flow path 93b, hydraulic pressure not shown. Supplied to the equipment. In the vane pump 100, each pump chamber 6 repeats suction and discharge of hydraulic oil twice while the rotor 2 rotates once.

Part of the hydraulic oil discharged to the first and

second discharge ports

7a and 7b (first and

second arc grooves

25a and 25b) enters the back pressure chamber 5 through the communication hole 28 and the second back pressure groove 24b, respectively. The base end portion 3b of the vane 3 is pressed toward the inner peripheral cam surface 4a. Therefore, the vane 3 is urged in the direction protruding from the slit 2 a by the fluid pressure of the back pressure chamber 5 that presses the base end portion 3 b and the centrifugal force that works in accordance with the rotation of the rotor 2. As a result, the tip 3 a of the vane 3 rotates while being in sliding contact with the inner peripheral cam surface 4 a of the cam ring 4, so that the hydraulic oil in the pump chamber 6 flows into the tip 3 a of the vane 3 and the inner peripheral cam surface 4 a of the cam ring 4. The liquid is discharged from the pump chamber 6 without leaking from between the two.

When the vane pump 100 is housed in the housing recess 91 of the body 90, the main body 40 b of the adapter 40 is in contact with the bottom surface of the third recess 91 c of the housing recess 91. Furthermore, O-

rings

83a and 83b are provided in a compressed state between the adapter 40 and the body side plate 20. Accordingly, the body side plate 20 is always pressed against the end surface of the rotor 2 by the elastic force of the O-

rings

83a and 83b, so that leakage of hydraulic oil from between the body side plate 20 and the rotor 2 can be prevented. Therefore, the discharge efficiency of the vane pump 100 is improved. As described above, the O-

rings

83a and 83b always urge the body side plate 20 to the end surface of the rotor 2 in addition to the function as a sealing member that surrounds and seals the outer periphery of the first and

second arc grooves

25a and 25b. It has a function as an urging member to be performed.

When high-pressure hydraulic oil is discharged from the pump chamber 6, the pressure of the hydraulic oil in the first and

second arc grooves

25a and 25b also becomes high. As a result, the body side plate 20 is pressed against the end surface of the rotor 2. Further, high-pressure hydraulic oil is introduced from the pump chamber 6 into the high-pressure chamber 94 through the first discharge port 7a and the first connection flow path 41a. Accordingly, the adapter 40 is separated from the bottom surface of the third recess 91c and pressed against the body side plate 20 by the pressure of the hydraulic oil in the high pressure chamber 94. Thereby, the adapter 40 urges the body side plate 20 toward the rotor 2 by the high pressure hydraulic oil guided to the high pressure chamber 94, and presses the body side plate 20 against the end surface of the rotor 2.

When the pump chamber 6 is at a high pressure, the body side plate 20 cannot be pressed sufficiently toward the rotor 2 only by the elastic force of the O-

rings

83a and 83b. However, when the pump chamber 6 is at a high pressure, the body side plate 20 is operated by the pressure of the hydraulic oil in the first and

second arc grooves

25a and 25b and the adapter in addition to the urging force by the elasticity of the O-

rings

83a and 83b. It is pressed against the rotor 2 also by the pressure of the hydraulic oil acting on 40. Therefore, it is possible to prevent leakage of hydraulic oil from between the body side plate 20 and the rotor 2 even at high pressure.

Further, in a state where the high-pressure hydraulic oil is guided into the internal space 40e or the high-pressure chamber 94, the adapter 40 is pressed against the body side plate 20 so that the O-

rings

83a and 83b are connected to the adapter 40 and the body side plate 20 with each other. Compressed strongly between. Thereby, even if the hydraulic oil in the 1st, 2nd circular-

arc groove

25a, 25b becomes high pressure, it can prevent that O-

ring

83a, 83b protrudes from a groove | channel.

According to the above embodiment, the following effects are obtained.

The vane pump 100 includes a body side plate 20 that contacts the other end surfaces of the rotor 2 and the cam ring 4, first and

second discharge ports

7 a and 7 b formed on the body side plate 20, and a first formed on the body 90. And adapters for forming first and second

connection flow paths

41a and 41b for connecting the second

discharge flow paths

93a and 93b. By appropriately changing the adapter 40, the positions of the first and

second discharge ports

7a and 7b formed in the body side plate 20 and the first and second

discharge flow paths

93a and 93b formed in the body 90 are changed. The first and

second discharge ports

7a and 7b can be connected to the first and second

discharge flow paths

93a and 93b regardless of the deviation or the difference in shape. Furthermore, since the first and

second discharge channels

93a and 93b of the body 90 do not have to be formed in accordance with the shape and position of the first and

second arc grooves

25a and 25b, the degree of design freedom is improved.

The cartridge type vane pump is installed in various fluid pressure devices. For this reason, the arrangement of the first and

second discharge channels

93a and 93b may differ depending on the fluid pressure device. The body-side side plate 20 is made of an iron-based sintered metal having excellent durability because it slides on the rotor 2. Such an iron-based sintered metal is poor in workability and high in material itself. Therefore, if it is manufactured in conformity with the positions of the first and second

discharge flow paths

93a and 93b, the cost increases. Therefore, in the vane pump 100, the first and

second discharge ports

7a and 7b formed in the body side plate 20 and the first and

second discharge channels

93a and 93b formed in the body 90 are connected to the body. The adapter 40 is configured as an adapter 40 different from the side side plate 20 and is formed of an aluminum alloy having excellent workability. Thereby, even if arrangement | positioning and shape of the 1st, 2nd

discharge flow paths

93a and 93b of a fluid pressure apparatus differ, the body side side plate 20 can be shared. Further, by using an aluminum alloy, the processing time can be shortened, so that the adapter 40 can be easily manufactured and the material cost can be suppressed, so that an increase in cost can be suppressed. Moreover, the weight reduction of the vane pump 100 can be achieved by using an aluminum alloy whose specific gravity is lighter than iron. Further, since the body side plate 20 is formed of iron-based sintered metal, durability is improved and seizure with the rotor 2 is prevented.

When the vane pump 100 is started, since the pressure on the discharge side is low, the body side plate 20 cannot be pressed sufficiently against the end surface of the rotor 2 depending on the pressure on the discharge side. Thereby, the hydraulic oil in the pump chamber 6 leaks from between the body-side side plate 20 and the rotor 2, and the discharge efficiency of the pump decreases. Therefore, in the vane pump 100, the O-

rings

83a and 83b are compressed and provided between the adapter 40 and the body side plate 20. Thereby, the body side plate 20 is pressed against the end surface of the rotor 2 by the elastic force of the O-

rings

83a and 83b, so that leakage between the body side plate 20 and the rotor 2 can be prevented even at a low pressure. Furthermore, since the O-

rings

83a and 83b also function as seal members for the first and

second arc grooves

25a and 25b, the number of parts can be reduced.

Further, since the body side plate 20 is constantly pressed against the end face of the rotor 2 by the elastic force of the O-

rings

83a and 83b, it is not necessary to generate a force for pressing the body side plate 20 against the rotor 2 by the head pin 50. Therefore, the head pins 50 can be made thinner or the number thereof can be reduced.

In the vane pump 100, by providing the O-

rings

83a and 83b, a dimensional error of each member constituting the vane pump 100 can be allowed. Specifically, the sum of the axial dimensions of the drive shaft 1 of the body 40 b of the adapter 40, the body side plate 20, the cam ring 4, the cover side plate 10, and the portion inserted into the housing recess 91 of the cover 30. Is smaller than the depth to the bottom surface of the third recess 91c, it is possible to allow only the amount of compression of the O-

rings

83a and 83b.

In addition, it can replace with O-

ring

83a, 83b, and can also provide an urging member between the main-body part 40b of the adapter 40, and the bottom face of the 3rd recessed part 91c of the body 90, for example. In this case, the urging member is not limited to the O-ring but may be a member such as a disc spring.

In the vane pump 100, an annular high-pressure chamber 94 into which high-pressure hydraulic oil discharged from the pump chamber 6 is guided is defined between the adapter 40 and the bottom surface of the body 90. Since the high pressure discharged from the pump chamber 6 acts on the entire annular surface 40f of the main body 40b, the body side plate 20 can be strongly pressed against the end surface of the rotor 2.

In the vane pump 100, the main body portion 40b of the adapter 40 is formed in a disc shape, and the cylindrical portion 40c is formed in a cylindrical shape. Thereby, the O-

rings

81 and 82 provided in the main body portion 40b and the cylindrical portion 40c can be formed in an annular shape. Therefore, the shapes of the O-

rings

81 and 82 are simplified, and the O-

rings

81 and 82 can be easily manufactured. Furthermore, if the main body portion 40b and the cylindrical portion 40c are formed coaxially, the processing of the adapter 40 can be simplified and the processing accuracy can be improved.

Further, since the O-ring 81 is provided on the outer periphery of the cylindrical portion 40c, it is not necessary to seal the cylindrical portion 40c against the bottom surface of the first concave portion 91a of the body. do not need. Thereby, processing time can be shortened. Further, since the O-

rings

81 and 82 are provided on the outer circumferences of the main body portion 40b and the cylindrical portion 40c, respectively, it is possible to prevent the O-

rings

81 and 82 from dropping off when the vane pump 100 is attached to the body 90.

The configuration, operation, and effect of the embodiment of the present invention configured as described above will be described together.

The cartridge-type vane pump 100 includes a rotor 2 that is connected to a drive shaft 1 and is driven to rotate, a plurality of slits 2 a that are radially formed with openings on the outer periphery of the rotor 2, and are slidable in the slits 2 a. A vane 3 to be inserted; a cam ring 4 having an inner circumferential cam surface 4a in which the tip of the vane 3 is in sliding contact; a pump chamber 6 partitioned between the rotor 2 and the vane 3 adjacent to the cam ring 4; And a cover member (cover 30 and cover-side side plate 10) fixed to the body 90, a body-side side plate 20 contacting the rotor 2 and the other end surface of the cam ring 4, and a body First and

second discharge ports

7a and 7b formed in the side side plate 20 through which the working fluid discharged from the pump chamber 6 is guided; First and second

connection flow paths

41a and 41b connecting the first and

second discharge ports

7a and 7b formed at the rate 20 and the first and second

discharge flow paths

93a and 93b formed in the body 90 are provided. Adapter 40 to be formed.

According to this configuration, by appropriately changing the adapter 40, the first and second discharge channels 93a formed in the body 90 and the first and

second discharge ports

7a and 7b formed in the body side plate 20 are formed. The first and

second discharge ports

7a and 7b and the first and second

discharge flow paths

93a and 93b can be connected regardless of the positional shift and the shape difference from the first and

second discharge channels

7a and 93b. Furthermore, the body side plate 20 on which the rotor 2 slides can be shared. Accordingly, the first and

second discharge ports

7a and 7b of the body side plate 20 can be adapted to the first and second

discharge flow paths

93a and 93b of the fluid pressure device, and the cost can be reduced.

The cartridge-type vane pump 100 further includes urging members (O-

rings

83a and 83b) that constantly urge the body side plate 20 toward the rotor 2.

According to this configuration, the body side plate 20 is constantly urged toward the rotor 2 by the urging members (O-

rings

83a and 83b), so that leakage from between the body side plate 20 and the rotor 2 is prevented. it can. Therefore, the discharge efficiency of the pump is improved.

Further, in the cartridge type vane pump 100, the urging members (O-

rings

83a and 83b) are compressed between the adapter 40 and the body side plate 20 and are formed on the body side plate 20 in the first, It is a sealing member that surrounds and seals the outer periphery of the

second discharge ports

7a and 7b.

According to this configuration, the seal members (O-

rings

83a and 83b) that prevent leakage from the first and

second discharge ports

7a and 7b function as urging members (O-

rings

83a and 83b). Thereby, the number of parts can be reduced.

Further, in the cartridge type vane pump 100, the adapter 40 is a circle to which the high-pressure working fluid discharged from the pump chamber 6 is guided between the adapter 40 and the bottom surface of the body 90 in a state where the cartridge type vane pump 100 is accommodated in the body 90. An annular high-pressure chamber 94 is defined, and the body side plate 20 is urged toward the rotor 2 by a high-pressure working fluid guided to the high-pressure chamber 94.

According to this configuration, when the pressure is high, the body side plate 20 is biased toward the rotor 2 by the high pressure working fluid guided to the high pressure chamber 94. Leakage between the two can be prevented.

Further, in the cartridge type vane pump 100, the body side plate 20 is made of sintered metal, and the adapter 40 is made of aluminum alloy.

According to this configuration, the body side plate 20 is formed of an iron-based sintered metal, so durability is improved and seizure with the rotor 2 is prevented. Further, since the adapter 40 is formed of an aluminum alloy that is lighter than an iron-based sintered metal, the weight can be reduced. Furthermore, since the aluminum alloy has good workability, the adapter 40 can be easily manufactured.

The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

In the vane pump 100, two discharge ports are provided, but one discharge port may be provided. Further, the cover 30 may be formed integrally with the cover side plate 10. If the high pressure chamber 94 is formed, the concave groove 47 may not be formed.

The body 90 is provided with two discharge channels (first and

second discharge channels

93a and 93b), but there may be one discharge channel. In this case, for example, the first and second

connection flow paths

41 a and 41 b can be merged in the high-pressure chamber 94 by not providing the adapter 40 with the cylindrical portion 40 c.

This application claims priority based on Japanese Patent Application No. 2015-185584 filed with the Japan Patent Office on September 18, 2015, the entire contents of which are incorporated herein by reference.

Claims

A cartridge type vane pump that is detachably accommodated in a body of a fluid pressure device,
A rotor coupled to the drive shaft and driven to rotate;
A plurality of slits formed radially with openings on the outer periphery of the rotor;
A vane slidably inserted into each of the slits;
A cam ring having an inner circumferential cam surface with which the tip of the vane is in sliding contact;
A pump chamber defined between the rotor and the vane adjacent to the cam ring;
A cover member that contacts the one end surface of the rotor and the cam ring and is fixed to the body;
A side plate in contact with the other end face of the rotor and the cam ring;
A discharge port formed in the side plate and through which a working fluid discharged from the pump chamber is guided;
A cartridge-type vane pump comprising: an adapter having a connection flow path connecting the discharge port formed in the side plate and a discharge flow path formed in the body.
The cartridge type vane pump according to claim 1,
A cartridge-type vane pump further comprising a biasing member that constantly biases the side plate toward the rotor.
The cartridge type vane pump according to claim 2,
The cartridge-type vane pump, wherein the urging member is a seal member that is compressed between the adapter and the side plate and seals the outer periphery of the discharge port formed on the side plate.
The cartridge type vane pump according to claim 1,
The adapter defines an annular high-pressure chamber to which a high-pressure working fluid discharged from the pump chamber is guided with the bottom surface of the body in a state where the cartridge-type vane pump is accommodated in the body. A cartridge-type vane pump that urges the side plate toward the rotor by a high-pressure working fluid guided to the high-pressure chamber.
The cartridge type vane pump according to claim 1,
The side plate is formed of sintered metal,
The adapter is a cartridge type vane pump formed of an aluminum alloy.