阅读说明：本技术 叶片泵 (Vane pump ) 是由 久保康平 藤田朋之 赤塚浩一朗 牧义之 于 2020-03-03 设计创作，主要内容包括：叶片泵(100)具备：泵外壳(10),其具有收容凹部(11)；泵芯(20),其被收容于收容凹部(11),泵芯(20)具有：转子(24)；多个叶片(25),其被收装于在转子(24)上所形成的多个狭缝；凸轮环(26),其内周形成有凸轮面(26a)；第一侧面板(29),其隔着凸轮环(26)而被设置于与收容凹部(11)的底面(11a)相反的一侧,第一侧面板(29)具有朝向径向外侧突出的第一突出部(29b),泵芯(20)经由第一突出部(29b)而被卡定于泵外壳(10)。(A vane pump (100) is provided with: a pump housing (10) having a housing recess (11); a pump body (20) housed in the housing recess (11), the pump body (20) having: a rotor (24); a plurality of blades (25) which are received in a plurality of slits formed in the rotor (24); a cam ring (26) having a cam surface (26a) formed on the inner periphery thereof; and a first side plate (29) that is provided on the side opposite to the bottom surface (11a) of the housing recess (11) with the cam ring (26) therebetween, wherein the first side plate (29) has a first protruding portion (29b) that protrudes outward in the radial direction, and the pump core (20) is locked to the pump housing (10) via the first protruding portion (29 b).)

1. A vane pump that discharges a working fluid by being rotationally driven by a drive source, comprising:

a pump housing having a housing recess;

a pump core accommodated in the accommodating recess,

the pump core has:

a rotor to which a rotational driving force of the driving source is transmitted;

a plurality of vanes which are slidably housed in a plurality of slits formed radially in the rotor;

a cam ring having a cam surface formed on an inner circumference thereof, and a tip end of the vane being in sliding contact with the cam surface in accordance with rotation of the rotor;

a first side plate provided on a side opposite to a bottom surface of the housing recess with the cam ring interposed therebetween,

the first side surface plate has a first protruding portion protruding toward the radially outer side,

the pump core is clamped to the pump housing via the first protrusion.

2. The vane pump of claim 1,

the vane pump further includes an annular member fitted into an annular groove formed in an inner peripheral surface of the housing recess,

the annular member abuts against the first protruding portion on a side opposite to the bottom surface of the housing recess.

3. The vane pump of claim 2,

the pump core further has:

a second side plate provided on the opposite side of the first side plate with the cam ring interposed therebetween;

a joining pin joining the cam ring, the first side plate, and the second side plate,

the second side face plate has a second projecting portion projecting toward the radially outer side,

a first engaging groove that engages with the second protruding portion is provided along the axial direction on the inner peripheral surface of the accommodating recess.

4. The vane pump of claim 1,

a second engaging groove that engages with the first protruding portion is provided on an inner peripheral surface of the accommodating recess,

the second engagement groove has an axial groove provided along an axial direction and a circumferential groove connected to the axial groove and extending in a circumferential direction,

the pump cartridge is locked to the pump housing in a state where at least a portion of the first protrusion is engaged with the circumferential groove.

Technical Field

The present invention relates to a vane pump.

Background

JP2018-80687a discloses a vane pump including a pump casing having a housing recess and a pump core housed in the housing recess. A vane pump described in japanese patent application laid-open No. JP2018-80687a is assembled to an electric motor as a drive source.

Disclosure of Invention

In the vane pump described in japanese patent application laid-open No. JP2018-80687a, a pump core is fixed by assembling a pump housing to an electric motor. Therefore, in order to prevent the pump core from falling off the pump casing until the vane pump is assembled to the electric motor, it is necessary to assemble a fall-off prevention member such as a cover plate that covers the pump core to the pump casing.

On the other hand, when the vane pump is assembled to the electric motor, the drop-off prevention member needs to be detached from the pump housing. Since the step of attaching the separation preventing member to the pump housing and the step of detaching the separation preventing member are required in this way, the number of steps increases, and as a result, the manufacturing cost of the device having the vane pump may increase.

The invention aims to reduce the manufacturing cost of a device with a vane pump.

According to one aspect of the present invention, a vane pump that discharges a working fluid by being rotationally driven by a drive source includes: a pump housing having a housing recess; a pump body housed in the housing recess, the pump body including: a rotor to which a rotational driving force of the driving source is transmitted; a plurality of vanes which are housed in a plurality of slits in a freely sliding manner, the plurality of slits being formed in the rotor in a radial shape; a cam ring having a cam surface formed on an inner circumference thereof, and a tip end of the vane being in sliding contact with the cam surface in accordance with rotation of the rotor; and a first side plate provided on a side opposite to a bottom surface of the housing recess with the cam ring interposed therebetween, the first side plate having a first protruding portion protruding outward in a radial direction, the pump core being clamped to the pump housing via the first protruding portion.

Drawings

Fig. 1 is a sectional view of a vane pump according to a first embodiment of the present invention.

Fig. 2 is a sectional view of the vane pump taken along line II-II of fig. 1.

Fig. 3 is an enlarged sectional view of the vane pump taken along the line III-III of fig. 2.

Fig. 4 is a sectional view of a vane pump according to a second embodiment of the present invention.

Fig. 5 is a sectional view of the vane pump taken along line V-V of fig. 4.

Fig. 6 is an enlarged sectional view of the vane pump taken along line VI-VI of fig. 5.

Fig. 7 is a cross-sectional view of a modification of the vane pump according to each embodiment of the present invention.

Detailed Description

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

< first embodiment >

A vane pump 100 according to a first embodiment of the present invention will be described with reference to fig. 1 to 3. Fig. 1 is a sectional view showing a state where a vane pump 100 according to a first embodiment of the present invention is assembled to a drive source 50, fig. 2 is a sectional view showing a section along a line II-II in fig. 1, and fig. 3 is an enlarged sectional view showing a section along a line III-III in fig. 2 in an enlarged manner.

The vane pump 100 is used as a fluid pressure supply source for a fluid pressure device mounted on a vehicle, for example, a power steering device, a continuously variable transmission, and the like. The working fluid is oil or other water-soluble substitute liquid and the like. As the drive source 50 for driving the vane pump 100, an engine and an electric motor, not shown, are used.

As shown in fig. 1 and 2, the vane pump 100 includes: a pump housing 10 having a housing recess 11; and a pump core 20 housed in the housing recess 11.

The pump housing 10 has: a mounting surface 10a that is mounted to a mounting surface 52a of a housing 52 of the drive source 50; and a housing recess 11 that opens to the mounting surface 10 a. The housing recess 11 is a concave space, and has a bottom surface 11a, a first housing hole 11b formed on the bottom surface 11a side, and a second housing hole 11c formed continuously with the first housing hole 11b and having an inner diameter larger than that of the first housing hole 11 b.

The pump housing 10 is provided with a notch portion 11d, a concave high-pressure chamber 32, and a discharge passage 33, the notch portion 11d being formed so as to be recessed radially outward from the inner peripheral surface of the second housing hole 11c, the high-pressure chamber 32 being formed in the bottom surface 11a, and the discharge passage 33 being communicated with the high-pressure chamber 32 and opening in the mounting surface 10 a.

The cutout portion 11d is provided so as to face an unillustrated tank passage that opens to the mounting surface 52a of the housing 52 of the drive source 50, and the discharge passage 33 is provided so as to face an unillustrated hydraulic oil supply passage that opens to the mounting surface 52a of the housing 52 of the drive source 50. A tank passage provided in the housing 52 of the drive source 50 communicates with a tank, not shown, that stores hydraulic oil, and a hydraulic oil supply passage communicates with a fluid pressure device driven by the hydraulic oil.

The pump core 20 has: a driven shaft 1 rotationally driven by a driving source 50; a rotor 24 to which a rotational driving force of the driving source 50 is transmitted via the driven shaft 1; a plurality of vanes 25 housed in a plurality of slits formed radially in the rotor 24 so as to be slidable; and a cam ring 26 having a cam surface 26a formed on an inner periphery thereof, and a tip end of the vane 25 slidably contacts with the cam surface 26a with rotation of the rotor 24. Inside the cam ring 26, a plurality of pump chambers 27 are defined by the outer peripheral surface of the rotor 24, the cam surface 26a of the cam ring 26, and the adjacent vanes 25.

The driven shaft 1 is a shaft-like member and includes an engagement portion 1a that engages with the rotor 24 and a coupling portion 1b that is provided to protrude from the pump core 20 toward the drive source 50. The outer peripheral surface of the engagement portion 1a is splined, and the coupling portion 1b is coupled to the drive shaft 51 of the drive source 50 via a coupling member 54 such as an oldham joint (oldham joint).

The rotor 24 is an annular member, and an engagement hole 24a that engages with the engagement portion 1a of the driven shaft 1 is formed in the center portion thereof so as to penetrate in the axial direction. The inner peripheral surface of the engagement hole 24a is spline-processed. Further, a plurality of not-shown slits are radially formed in the outer peripheral surface of the rotor 24, and the blades 25 are slidably received in the slits.

The cam ring 26 is an annular member having a cam surface 26a with a substantially elliptical shape formed on an inner peripheral surface thereof. The cam surface 26a has: two suction areas that expand the volume of the pump chamber 27 as the rotor 24 rotates; and two discharge regions that contract the volume of the pump chamber 27 in accordance with the rotation of the rotor 24.

The pump cartridge 20 further has: a first side panel 29 provided on the opposite side of the bottom surface 11a of the housing recess 11 with the cam ring 26 interposed therebetween; and a second side panel 28 provided between the cam ring 26 and the bottom surface 11a of the housing recess 11.

As shown in fig. 2, the first side plate 29 is an annular member formed such that two suction ports 29a are grooved in an arc shape. The suction port 29a is provided to correspond to a suction area of the cam ring 26, and is provided to guide the working oil to the pump chamber 27.

The second side plate 28 is a disc-shaped member formed with two circular arc-shaped through holes as discharge ports 28 a. The discharge port 28a is provided to correspond to a discharge area of the cam ring 26, and is provided to guide the hydraulic oil discharged from the pump chamber 27 to the high-pressure chamber 32. Further, the suction port that leads the working oil to the pump chamber 27 may be provided not only to the first side surface plate 29 but also to the second side surface plate 28 and the cam ring 26.

The pump core 20 has two coupling pins 30 through which the cam ring 26, the first side plate 29, and the second side plate 28 are inserted. Relative rotation of the cam ring 26, the first side plate 29, and the second side plate 28 is restricted by the two coupling pins 30, thereby positioning the suction area of the cam ring 26 and the suction port 29a of the first side plate 29, and positioning the discharge area of the cam ring 26 and the discharge port 28a of the second side plate 28.

The pump core 20 unitized by the coupling pin 30 is housed in the housing recess 11 of the pump casing 10 formed as described above.

Specifically, a part of the second side plate 28 is inserted into the first receiving hole 11b of the receiving recess 11, and the second side plate 28 defines the high-pressure chamber 32. Further, a gap of a predetermined size as a suction pressure chamber 31 is formed between the cam ring 26 and the first side plate 29 inserted into the second housing hole 11c of the housing recess 11 and the second housing hole 11 c.

The vane pump 100 in which the pump core 20 is accommodated in the accommodation recess 11 of the pump housing 10 is assembled to the drive source 50 by the pump housing 10 being fixed to the housing 52 of the drive source 50 via a plurality of bolts, not shown.

Here, as described above, in a state where the pump core 20 is housed only in the housing recess 11 of the pump housing 10, the pump core 20 may be detached from the pump housing 10 when the vane pump 100 is conveyed or when the vane pump 100 is assembled to the drive source 50.

In order to prevent the pump core 20 from dropping off the pump casing 10, a dropping-off prevention member such as a cover plate covering the pump core 20 may be assembled to the pump casing 10, but it is necessary to detach such a dropping-off prevention member from the pump casing 10 when the vane pump 100 is assembled to the drive source 50. That is, in the case where the drop-off prevention member is provided, a process of assembling the drop-off prevention member and a process of detaching the drop-off prevention member are required, and the number of processes increases, and as a result, the manufacturing cost of the device including the vane pump 100 may increase.

Further, if the pump core 200 can rotate within the pump housing 10 within the housing recess 11 about the driven shaft 1, the discharge pressure becomes unstable, and the pump efficiency may decrease. Therefore, in a state where the vane pump 100 is assembled to the drive source 50, the pump core 20 needs to be fixed to the pump housing 10 so as not to rotate within the accommodation recess 11 centering on the driven shaft 1.

In order to restrict the rotation of the pump core 20, it is conceivable that the end of the coupling pin 30 is inserted into a hole formed on the bottom surface 11a of the pump housing 10 and a hole formed on the housing 52 of the drive source 50. However, in any case, it is difficult to observe the positions of the coupling pin 30 and the hole when the coupling pin 30 is inserted into the hole, and it is difficult to smoothly insert the coupling pin 30 into the hole, resulting in a reduction in the efficiency of the assembly work. Further, it is necessary to form holes into which the coupling pins 30 are inserted into the pump housing 10 and the housing 52 of the drive source 50 with high accuracy. Therefore, in the case where the rotation of the pump core 20 is restricted by this method, the manufacturing cost of the apparatus having the vane pump 100 may be increased.

Therefore, in the present embodiment, the pump core 20 is prevented from dropping off from the pump housing 10 without attaching or detaching the drop-off prevention member or the like by providing a structure in which the pump core 20 is locked to the pump housing 10. In the present embodiment, the rotation stopper of the pump element 20 is provided at a visible position, so that the rotation of the pump element 20 is restricted and the assembly of the pump element 20 into the pump housing 10 is facilitated.

Hereinafter, a structure in which the pump core 20 is locked to the pump housing 10 will be described.

The vane pump 100 further includes a retainer ring 40 as an annular member, and the retainer ring 40 is fitted into an annular groove 11e formed in an inner peripheral surface of the second housing hole 11c of the housing recess 11 so that the pump core 20 is engaged with the pump housing 10.

Further, the first side plate 29 is provided with two arcuate first protruding portions 29b protruding radially outward from the outer peripheral surface at two locations with the driven shaft 1 interposed therebetween. The outer diameter of the outer peripheral surface of the first projection 29b is set smaller than the inner diameter of the second housing hole 11 c. Therefore, the pump body 20 including the first projecting portion 29b projecting radially outward is housed in the housing recess 11.

When the snap ring 40 is fitted into the annular groove 11e in a state where the pump core 20 is accommodated in the accommodating recess 11 of the pump housing 10, the snap ring 40 abuts against the first protrusion 29b on the side opposite to the bottom surface 11 a.

In this way, the first projecting portion 29b of the first side plate 29 is locked by the snap ring 40 fitted into the annular groove 11e formed in the pump housing 10, and therefore, the pump core 20 is prevented from falling off from the pump housing 10.

Therefore, it is not necessary to attach or detach the drop-off prevention member to or from the pump housing 10 in order to prevent the pump core 20 from dropping off from the pump housing 10, and therefore, the assembling property of the vane pump 100 to the drive source 50 can be improved.

Next, a structure for restricting the rotation of the pump core 20 will be described.

As shown in fig. 2 and 3, the second side plate 28 is provided with a second protruding portion 28b that protrudes outward in the radial direction from the outer peripheral surface. On the other hand, an axial groove 11f as a first engaging groove that engages with the second protrusion 28b is provided along the axial direction of the driven shaft 1 on the inner peripheral surface of the first housing hole 11b into which the second side plate 28 is inserted.

When the pump element 20 is inserted into the housing recess 11 of the pump housing 10 such that the second protruding portion 28b engages with the axial groove 11f formed in the pump housing 10, the second protruding portion 28b abuts against the axial groove 11f to restrict the pump element 20 from rotating within the housing recess 11 about the driven shaft 1. By preventing the pump core 20 from rotating in the housing recess 11 in this way, the discharge pressure of the vane pump 100 can be stabilized, and the pump efficiency can be improved.

The axial groove 11f is formed such that one end thereof opens into a notch portion 11d formed so as to open from the inner circumferential surface of the second housing hole 11c toward the radially outer side. Therefore, the pump core 20 can be inserted into the housing recess 11 of the pump casing 10 while visually checking the engagement of the second protrusion 28b with the axial groove 11 f.

In this way, since the rotation of the pump core 20 is restricted by the structure of the portion that is easily confirmed when the pump core 20 is assembled to the pump housing 10, the assemblability of the pump core 20 to the pump housing 10 can be improved even when the structure that restricts the rotation of the pump core 20 is provided.

The position where the axial groove 11f is provided is not limited to the region where the notch 11d is formed, and may be provided at any position as long as the inner circumferential surface of the first housing hole 11b is easily recognized when the pump core 20 is inserted into the housing recess 11 of the pump housing 10. In this case, in order to avoid interference with the second receiving hole 11c, the outer diameter of the outer peripheral surface of the second protrusion 28b is set to be smaller than the inner diameter of the second receiving hole 11 c.

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

The vane pump 100 incorporated in the drive source 50 discharges the working oil by being rotationally driven by the drive source 50. Specifically, the rotation of the drive shaft 51 of the drive source 50 is transmitted to the driven shaft 1 via the joint member 54, and the rotor 24 engaged with the driven shaft 1 is rotationally driven. When the rotor 24 is rotationally driven, each pump chamber 27 expands and contracts in accordance with the profile of the cam surface 26 a.

The hydraulic oil stored in the tank is sucked into the expanding pump chamber 27 through a tank passage formed in the housing 52 of the drive source 50, the cutout portion 11d communicating with the tank passage, the suction pressure chamber 31 communicating with the cutout portion 11d, and the suction port 29a communicating with the suction pressure chamber 31.

On the other hand, the pressurized hydraulic oil is supplied from the contracted pump chamber 27 to the fluid pressure device via the discharge port 28a formed in the second side plate 28, the high pressure chamber 32 communicating with the discharge port 28a, the discharge passage 33 communicating with the high pressure chamber 32, and the hydraulic oil supply passage formed in the housing 52 of the drive source 50 communicating with the discharge passage 33. Thus, the vane pump 100 sucks the hydraulic oil from the drive source 50 side and discharges the hydraulic oil to the drive source 50 side.

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

In the vane pump 100, the pump core 20 is held in the housing recess 11 because the pump core 20 is locked to the pump housing 10 via the first protruding portion 29b provided on the first side plate 29. Therefore, the pump core 20 is prevented from being detached from the pump housing 10 until the vane pump 100 is assembled to the drive source 50, and the vane pump 100 can be assembled to the drive source 50 as it is. Since it is not necessary to assemble or disassemble the components for preventing the dropping-off, the manufacturing cost of the device having the vane pump 100 can be reduced as a result.

In the vane pump 100, the second protrusion 28b provided on the second side plate 28 engages with the axial groove 11f formed in the pump casing 10, and therefore, the pump core 20 is restricted from rotating within the housing recess 11 about the driven shaft 1. By preventing the pump core 20 from rotating in the housing recess 11 in this way, the discharge pressure of the vane pump 100 can be stabilized, and the pump efficiency can be improved. Further, since the rotation of the pump core 20 is restricted by the structure of the portion that is easily confirmed when the pump core 20 is assembled to the pump housing 10, the assemblability of the pump core 20 to the pump housing 10 can be improved even when the structure that restricts the rotation of the pump core 20 is provided.

< second embodiment >

Next, a vane pump 200 according to a second embodiment of the present invention will be described with reference to fig. 4 to 6. Hereinafter, description will be given mainly on differences from the first embodiment, and in the drawings, the same reference numerals are given to the components having the same functions as those of the vane pump 100 according to the first embodiment, and description thereof will be omitted. Fig. 4 is a sectional view of a vane pump 200 according to a second embodiment of the present invention, fig. 5 is a sectional view showing a section along the line V-V of fig. 4, and fig. 6 is an enlarged sectional view showing a section along the line VI-VI of fig. 5 in an enlarged manner.

The basic configuration of the vane pump 200 is the same as that of the vane pump 100 according to the first embodiment. The difference mainly lies in that, in the vane pump 100 according to the first embodiment, the pump core 20 is locked to the pump casing 10 via the snap ring 40, whereas in the vane pump 200, the pump core 20 is directly locked to the pump casing 10.

As in the vane pump 100 according to the first embodiment, the vane pump 200 includes: a pump housing 10 having a housing recess 11; and a pump core 20 housed in the housing recess 11.

The pump body 20 has a first side surface plate 129 provided on the opposite side of the bottom surface 11a of the housing recess 11 with the cam ring 26 interposed therebetween, and the first side surface plate 129 is provided with two suction ports 129a and an arcuate first projecting portion 129b projecting radially outward from the outer peripheral surface.

The first protruding portion 129b is provided at two places with the driven shaft 1 interposed therebetween, and the outer diameter of the outer peripheral surface of the first protruding portion 129b is set to be larger than the inner diameter of the second receiving hole 11 c.

On the other hand, an axial groove 11g and a circumferential groove 11h as second engagement grooves that engage with the first protrusion 129b are formed on the inner circumferential surface of the second housing hole 11c of the housing recess 11 of the pump housing 10.

The axial groove 11g is a groove formed along the axial direction of the driven shaft 1, and the circumferential groove 11h is a groove formed from an end of the axial groove 11g in the circumferential direction toward the rotation direction of the vane pump 200 indicated by an arrow a in fig. 5.

As shown in fig. 6, the width GW1 in the circumferential direction of the axial groove 11g is set to be larger than the width W1 in the circumferential direction of the first protrusion 129b, and the width GW2 in the axial direction of the circumferential groove 11h is set to have a slightly smaller portion than the width W2 in the axial direction of the first protrusion 129 b. Specifically, the width GW2 in the axial direction of the circumferential groove 11h is gradually narrowed as it is away from the axial groove 11g, and is set to a size of a degree to which the first protrusion 129b is fitted.

In the vane pump 200 configured as described above, after the first protrusion 129b is inserted into the axial groove 11g in the axial direction from the attachment surface 10a side, the pump core 20 is rotated in the rotation direction of the vane pump 200 about the driven shaft 1, and at least a part of the first protrusion 129b is engaged with the circumferential groove 11h, whereby the pump core 20 can be directly engaged with the pump housing 10.

In this way, since the first protrusion 129b of the first side panel 129 is fitted into the circumferential groove 11h formed in the pump housing 10, the pump core 20 is prevented from falling off from the pump housing 10.

In addition, since the first protrusion 129b is fitted into the circumferential groove 11h formed in the pump housing 10, the pump core 20 is restricted from moving within the housing recess 11, and is prevented from moving in the direction in which the vane pump 200 is rotationally driven by the end surface of the circumferential groove 11 h. By preventing the pump core 20 from rotating about the driven shaft 1 in the housing recess 11 in this way, the discharge pressure of the vane pump 200 can be stabilized, and the pump efficiency can be improved.

Further, the anti-slip pin 41 inserted into the pump casing 10 after the first protrusion 129b is fitted into the circumferential groove 11h may be provided at a position opposite to the circumferential groove 11h with the first protrusion 129b interposed therebetween. By disposing the anti-slip pin 41 in the direction in which the first protrusion 129b slips off from the circumferential groove 11h in this manner, the rotation of the pump core 20 about the driven shaft 1 can be reliably restricted.

As shown in fig. 5, the axial groove 11g is formed so as to be open at one end on the mounting surface 10 a. Therefore, the pump core 20 can be inserted into the housing recess 11 of the pump casing 10 while visually checking the engagement of the first protrusion 129b with the axial groove 11g and the circumferential groove 11 h.

Since the locking of the pump core 20 to the pump housing 10 and the restriction of the rotation of the pump core 20 are performed by the structure of the portion that is easily confirmed when the pump core 20 is assembled to the pump housing 10, the assemblability of the pump core 20 to the pump housing 10 can be improved.

The operation of the vane pump 200 having the above-described configuration is the same as that of the vane pump 100 according to the first embodiment, and therefore, the description thereof is omitted.

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

In the vane pump 200, the pump core 20 is held in the housing recess 11 because the pump core 20 is locked to the pump housing 10 via the first protrusion 129b provided on the first side plate 129. Therefore, the pump core 20 is prevented from being detached from the pump housing 10 until the vane pump 200 is assembled to the drive source 50, and the vane pump 200 can be assembled to the drive source 50 as it is. Since it is not necessary to assemble or disassemble the components for preventing the dropping-off, the manufacturing cost of the device having the vane pump 200 can be reduced as a result.

In the vane pump 200, the first protrusion 129b provided on the first side plate 129 engages with the circumferential groove 11h formed in the pump housing 10, and therefore, the pump core 20 is restricted from rotating within the housing recess 11 about the driven shaft 1. By preventing the pump core 20 from rotating in the housing recess 11 in this way, the discharge pressure of the vane pump 200 can be stabilized, and the pump efficiency can be improved.

In the vane pump 200, the pump core 20 is locked to the pump casing 10 only by engaging the first protrusion 129b provided on the first side plate 129 with the circumferential groove 11h formed in the pump casing 10, and the rotation of the pump core 20 in the housing recess 11 is restricted. In this way, in the vane pump 200, the pump core 20 can be prevented from dropping off the pump casing 10 by a simple configuration, and the discharge pressure of the vane pump 200 can be stabilized to improve the pump efficiency.

Next, modifications of the above embodiments will be described.

In each of the above embodiments, the pump core 20 includes the driven shaft 1 coupled to the drive shaft 51 of the drive source 50. Alternatively, as shown in fig. 7, the pump core 20 may not have the driven shaft 1. In this case, the engagement portion 51a formed at the tip end of the drive shaft 51 of the drive source 50 directly engages with the engagement hole 24a of the rotor 24. In this case, since the second side plate 28 is not provided with a through hole through which the driven shaft 1 is inserted, the shapes of the second side plate 28 and the high-pressure chamber 32 can be simplified.

Fig. 7 shows a configuration in which the drive shaft 51 of the drive source 50 directly engages with the engagement hole 24a of the rotor 24 in the first embodiment, and the drive shaft 51 of the drive source 50 can directly engage with the engagement hole 24a of the rotor 24 in the second embodiment as well.

In the first embodiment, two first protruding portions 29b are provided, but the number of first protruding portions 29b is not limited to two, and may be three or more. Similarly, in the second embodiment, two first protruding portions 129b are provided, but the number of first protruding portions 129b is not limited to two, and may be three or more.

In the first embodiment, the first projecting portion 29b is formed in an arc shape, but the shape of the first projecting portion 29b is not limited thereto, and any shape may be used as long as it projects radially outward from the outer peripheral surface of the first side surface plate 29 and can be brought into contact with the snap ring 40. Similarly, in the second embodiment, the first protrusion 129b is formed in an arc shape, but the shape of the first protrusion 129b is not limited thereto, and any shape may be used as long as it protrudes radially outward from the outer peripheral surface of the first side surface plate 129 and can be locked in the circumferential groove 11 h.

The structure, operation, and effects of the embodiments of the present invention configured as above will be summarized.

The vane pumps 100 and 200 include: a pump housing 10 having a housing recess 11; a pump body 20 housed in the housing recess 11, the pump body 20 including: a rotor 24 to which a rotational driving force of the driving source 50 is transmitted; a plurality of vanes 25 housed in a plurality of slits formed radially in the rotor 24 so as to be slidable; a cam ring 26 having a cam surface 26a formed on an inner periphery thereof, and a tip end of the vane 25 slidably contacting the cam surface 26a with rotation of the rotor 24; the first side plates 29 and 129 are provided on the opposite side of the bottom surface 11a of the housing recess 11 with the cam ring 26 interposed therebetween, the first side plates 29 and 129 have first protruding portions 29b and 129b that protrude outward in the radial direction, and the pump core 20 is locked to the pump housing 10 via the first protruding portions 29 and 129 b.

In this configuration, the pump core 20 is held in the housing recess 11 because the pump core 20 is locked to the pump housing 20 via the first protruding portions 29b and 129b provided on the first side panels 29 and 129. Therefore, the pump core 20 is prevented from being detached from the pump housing 10 until the vane pumps 100 and 200 are assembled to the drive source 50, and the vane pumps 100 and 200 can be assembled to the drive source 50 as they are. Since it is not necessary to assemble or disassemble the dropping prevention member to or from the pump casing 10, the manufacturing cost of the device having the vane pumps 100 and 200 can be reduced as a result.

The vane pump 100 further includes a snap ring 40 fitted into an annular groove 11e formed in the inner peripheral surface of the housing recess 11, and the snap ring 40 abuts against the first protrusion 29b on the side opposite to the bottom surface 11a of the housing recess 11.

In this configuration, the snap ring 40 fitted into the pump housing 10 abuts against the first projection 29b, and therefore the pump core 20 is held in the housing recess 11. In this way, with a simple configuration, it is possible to prevent the pump core 20 from falling off the pump casing 10 until the vane pump 100 is assembled to the drive source 50, and to assemble the vane pump 100 to the drive source 50 as it is. Therefore, it is not necessary to assemble or disassemble the dropping prevention member to or from the pump housing 10, and as a result, the manufacturing cost of the device having the vane pump 100 can be reduced.

In addition, the pump cartridge 20 further includes: a second side panel 28 provided on the opposite side of the first side panel 29 with the cam ring 26 interposed therebetween; and a connecting pin 30 for connecting the cam ring 26, the first side plate 39, and the second side plate 28, wherein the second side plate 28 has a second protruding portion 28b protruding outward in the radial direction, and an axial groove 11f engaging with the second protruding portion 28b is provided along the axial direction on the inner circumferential surface of the housing recess 11.

In this configuration, since the second protrusion 28b provided on the second side plate 28 is engaged with the axial groove 11f formed in the pump housing 10, the pump core 20 is restricted from rotating within the housing recess 11 about the driven shaft 1. By preventing the pump core 20 from rotating in the housing recess 11 in this way, the discharge pressure of the vane pump 100 can be stabilized, and the pump efficiency can be improved. Further, since the rotation of the pump core 20 is restricted by the structure of the portion that is easily confirmed when the pump core 20 is assembled to the pump housing 10, the assemblability of the pump core 20 to the pump housing 10 can be improved even when the structure that restricts the rotation of the pump core 20 is provided.

Further, second engagement grooves 11g, 11h that engage with the first protrusion 129b are provided on the inner peripheral surface of the housing recess 11, the second engagement grooves have an axial groove 11g provided along the axial direction and a circumferential groove 11h that is continuous with the axial groove 11g and extends in the circumferential direction, and the pump element 20 is locked to the pump casing 10 in a state where at least a part of the first protrusion 129b engages with the circumferential groove 11 h.

In this configuration, since the first protrusion 129b engages with the circumferential groove 11h formed in the pump housing 10, the pump core 20 is held in the housing recess 11. In this way, with a simple configuration, it is possible to prevent the pump core 20 from falling off the pump housing 10 until the vane pump 200 is assembled to the drive source 50, and to assemble the vane pump 200 to the drive source 50 as it is. Therefore, it is not necessary to assemble or disassemble the dropping prevention member to or from the pump housing 10, and as a result, the manufacturing cost of the device having the vane pump 200 can be reduced.

In this configuration, since the first protrusion 129b provided on the first side plate 129 engages with the circumferential groove 11h formed in the pump housing 10, the pump core 20 is restricted from rotating within the housing recess 11 about the driven shaft 1. By preventing the pump core 20 from rotating in the housing recess 11 in this way, the discharge pressure of the vane pump 200 can be stabilized, and the pump efficiency can be improved.

Although the embodiments of the present invention have been described above, the above embodiments are merely some of application examples of the present invention, and the technical scope of the present invention is not limited to the specific configurations of the above embodiments.

The application claims priority based on Japanese patent application 2019-69818, which was filed on the sun on 1/4/2019 with the patent office, and the entire content of the application is incorporated by reference in the present specification.