JP2022139471A - Pump device - Google Patents

Abstract

To provide a pump device that can restrain abnormal wear and seizure of an opposing surface.SOLUTION: In a rear body 3 of a pump device 1, a first back pressure port 18 is provided with a ride part 45 with which a radially outer end part of a vane 1 can come into contact when moving from an open region of the first back pressure port 18 to an inside surface 3a.SELECTED DRAWING: Figure 3

Description

The present invention relates to a pump device.

Patent Document 1 describes a pump device having a rotor that is rotationally driven by a drive shaft member, a plurality of vanes provided on the outer periphery of the rotor, and a housing that accommodates the rotor.

JP 2018-127983 A

In the conventional pump device described above, when pressure imbalance occurs in the housing during operation of the pump, the housing deforms and the vanes tilt with respect to the drive shaft member. As a result, the tips of the rotating vanes enter the ports formed in the vane facing surface of the housing. Thereafter, when the tip of the vane moves from the region where the port opens to the opposing surface, the tip of the vane may catch on the end surface of the port, causing abnormal wear or seizure of the opposing surface.

One of the objects of the present invention is to provide a pump device capable of suppressing abnormal wear and seizure of the facing surface.

In the pump device according to one embodiment of the present invention, the port is provided with a ride-on portion with which the radially outer end of the vane can abut when moving from the opening region of the port to the opposing surface. there is

Therefore, according to the present invention, it is possible to suppress abnormal wear and seizure of the opposing surface.

FIG. 2 is a schematic diagram showing the structure of the pump device 1 of Embodiment 1 and the liquid passage through which the working liquid flows. 2 is a cross-sectional view of the pump device 1 taken along a plane passing through the rotation axis O of the drive shaft 6. FIG. 4 is a diagram showing the shape of the inner side surface 3a of the rear body 3 of Embodiment 1. FIG. 4 is a diagram showing the shape of an inner side surface 10a of the pressure plate 10. FIG. 4 is a cross-sectional view taken along line S5-S5 of FIG. 3 in Embodiment 1. FIG. FIG. 4 is an end view taken along line S6-S6 of FIG. 3; 5 is an end view taken along line S7-S7 of FIG. 4; FIG. FIG. 4 is a schematic vertical cross-sectional view of the pump element showing a state in which the radially outer ends of the vanes 16 are depressed into the first intake ports 18; 4 is a schematic vertical cross-sectional view of the pump element showing a state in which the radially inner end of the vane 16 has fallen into the suction side second back pressure port 42. FIG. FIG. 10 is a schematic view of a state in which a vane that has fallen into a port collides with an end surface of the port in a conventional pump device, viewed from the radially outer side of the vane. FIG. 4 is a schematic diagram showing a state in which the vane 16 that has fallen into the first intake port 18 has run over the first riding portion 45 in the pump device 1 of Embodiment 1, viewed from the radially outer side of the vane 16; 4 is a cross-sectional view taken along line S5-S5 of FIG. 3 in Embodiment 2. FIG. FIG. 11 is a diagram showing the shape of an inner side surface 3a of a rear body 3 according to Embodiment 3; 14 is an end view taken along line S14-S14 of FIG. 13; FIG.

[Embodiment 1]
FIG. 1 is a schematic diagram showing the configuration of the pump device 1 of Embodiment 1 and the liquid passage through which the hydraulic fluid flows. FIG. 2 is a cross-sectional view of the pump device 1 taken along a plane passing through the rotation axis O of the drive shaft (drive shaft member) 6. As shown in FIG. FIG. 3 is a diagram showing the shape of the inner side surface 3a of the rear body 3. As shown in FIG. FIG. 4 is a diagram showing the shape of the inner surface 10a of the pressure plate 10. As shown in FIG.
The pump device 1 of Embodiment 1 is a variable displacement vane pump, is applied to a hydraulic power steering device of a vehicle, and functions as a hydraulic fluid supply source that supplies hydraulic fluid to the power steering device.

The power steering device has a power cylinder provided in a steering gear box (not shown). The pump device 1 is driven by an internal combustion engine as a prime mover, sucks hydraulic fluid from a reservoir tank RES, and discharges the hydraulic fluid to a power cylinder.
The pump device 1 has a pump housing 4 and a pump element 5 . The pump device 1 performs a pump action by rotationally driving a pump element 5 about a rotation axis O by a drive shaft 6 . Pump housing 4 has front body 2 , rear body 3 , adapter ring 9 and pressure plate 10 . The pump housing 4 accommodates the pump element 5 in a pump element accommodation space (accommodation portion) 4a.

Pump element 5 has rotor 7 and cam ring 8 . The rotor 7 rotates integrally with the drive shaft 6 driven by the crankshaft of the internal combustion engine. The cam ring 8 is positioned on the outer peripheral side of the rotor 7 and has a substantially annular shape. It is possible to swing in a direction in which the amount of eccentricity with respect to the center of the inner peripheral edge of the cam ring 8 and the center of the rotor 7 (rotational axis O) changes.
The adapter ring 9 is positioned on the outer peripheral side of the cam ring 8 and has a substantially annular shape. The adapter ring 9 is fixed to the outer cylindrical surface of the pump element housing space 4a.

The pressure plate 10 is positioned on the inner bottom surface 2a of the front body 2 in the pump element housing space 4a and has a substantially disk shape. A positioning pin 11 restricts the adapter ring 9 and the pressure plate 10 from rotating relative to the pump housing 4 . A plate member 12 as a cam ring support member is installed on the counterclockwise direction side of the positioning pin 11 in FIG. The plate member 12 has a pivot function for the cam ring 8 and a sealing function for sealing between the cam ring 8 and the adapter ring 9 .

A seal member 13 for sealing between the adapter ring 9 and the cam ring 8 is arranged at a position facing the plate member 12 in the radial direction (radial direction with respect to the rotation axis O) of the inner peripheral surface of the adapter ring 9. . Seal member 13 and plate member 12 form a pair of fluid pressure chambers 14a and 14b between cam ring 8 and adapter ring 9. As shown in FIG. That is, a first fluid pressure chamber 14a is formed on one radial side (right side in FIG. 1) of the cam ring 8, and a second fluid pressure chamber 14b is formed on the other radial side (left side in FIG. 1). As the cam ring 8 swings due to the pressure difference between the two fluid pressure chambers 14a and 14b, the eccentricity of the center of the inner peripheral edge of the cam ring 8 and the rotation axis O of the rotor 7 increases or decreases.

The cam ring 8 is constantly biased by a return spring 15 in a direction in which the eccentricity between the center of the inner peripheral edge of the cam ring 8 and the rotation axis O of the rotor 7 is maximized. The rotor 7 has, at its center, an insertion hole 7c through which the drive shaft 6 is inserted. In addition, the rotor 7 has a plurality of slits 7a cut along the radial direction in its outer peripheral portion. The slits 7a are arranged at equal pitches in the circumferential direction (direction around the rotation axis O). A substantially flat vane 16 is housed in each slit 7a so as to be retractable in the radial direction of the rotor 7. As shown in FIG. A plurality of pump chambers 17 are formed by each vane 16 partitioning the annular space between the cam ring 8 and the rotor 7 in the circumferential direction.

Rotation of the rotor 7 in the clockwise direction in FIG. 1 by the drive shaft 6 causes each pump chamber 17 to circulate while increasing or decreasing its volume, thereby performing pump operation. Each vane 16 is pressed against the inner peripheral surface of the cam ring 8 by the pressure of hydraulic fluid introduced into a back pressure chamber 7b formed on the inner peripheral side of each slit 7a. An inner surface (opposing surface) 3a of the rear body 3 that faces the rotor 7 in the axial direction (direction along the rotation axis O) corresponds to a suction area where the volume of each pump chamber 17 gradually expands as the rotor 7 rotates. A first suction port 18 is formed in the portion. The first suction port 18 is a groove extending in a substantially arc shape in the circumferential direction. The first intake port 18 communicates with an intake passage 19a formed in the rear body 3 via a communication hole 32 extending in the axial direction. As a result, the hydraulic fluid introduced into the suction passage 19a through the suction pipe 20 connected to the reservoir tank RES is sucked into each pump chamber 17 by the pump suction action in the suction region.

Two second intake ports 21a and 21b are formed in the pressure plate 10 so as to be spaced apart in the circumferential direction at positions facing the first intake port 18 on the inner surface (facing surface) 10a facing the rotor 7. there is A second discharge port 23 is formed on the inner side surface 10a in a portion corresponding to a discharge region where the volume of each pump chamber 17 is gradually reduced as the rotor 7 rotates. The second discharge port 23 is a groove extending in a substantially arc shape in the circumferential direction. The second discharge port 23 communicates with a pressure chamber 24 formed in the inner bottom surface 2a of the front body 2 via three communicating holes 39a, 39b, 39c extending in the axial direction. The pressure chamber 24 communicates with the discharge passage 19b. As a result, the hydraulic fluid discharged from each pump chamber 17 by the pump discharge action in the discharge region is discharged out of the pump housing 4 through the pressure chamber 24 and the discharge passage 19b and sent to the power cylinder of the power steering device (not shown). be done. The pressure plate 10 is pressed toward the rotor 7 by the pressure inside the pressure chamber 24 .

A first discharge port 25 having substantially the same shape as the second discharge port 23 is formed in the inner surface 3a of the rear body 3 at a position facing the second discharge port 23. As shown in FIG. A first back pressure port 40 is formed radially inside the first intake port 18 and the first discharge port 25 on the inner surface 3 a of the rear body 3 . The first back pressure port 40 is a groove extending in a substantially annular shape in the circumferential direction. The first back pressure port 40 communicates with the first discharge port 25 through two communicating holes 41a and 41b.
A suction side second back pressure port 42 and a discharge side second back pressure port 43 are formed radially inside the second suction ports 21a and 21b and the second discharge port 23 in the inner surface 10a of the pressure plate 10. ing. The two second back pressure ports 42 are grooves extending in a substantially arcuate shape in the circumferential direction. The suction side second back pressure port 42 is provided in a portion corresponding to the suction region, and the discharge side second back pressure port 43 is provided in a portion corresponding to the discharge region. The direction end protrudes to a portion corresponding to the ejection region. The suction side second back pressure port 42 communicates with the pressure chamber 24 through three communicating holes 44a, 44b, 44c extending in the axial direction.

Inside the upper end side of the front body 2, a control valve 26 for controlling the pump discharge pressure is provided in a direction perpendicular to the drive shaft 6 (horizontal direction in FIG. 1). The control valve 26 has a valve hole 28 which is a control valve housing space, a spool 29 and a spring 30 . The right opening of the valve hole 28 in FIG. 1 is closed by a plug 27 via a seal member S1. The spool 29 is accommodated in the valve hole 28 so as to be slidable in the first axis P direction. The spool 29 is a spool valve body having a substantially cylindrical shape with a bottom and having a relief hole 29a, a first land portion 29b, and a second land portion 29c. A relief valve 33 comprising a valve seat 36 , a ball 35 , a retainer 38 and a spring 37 is formed in the valve hole 34 of the spool 29 . A spring 30 biases the spool 29 toward the plug 27 side. Spring 30 is a cylindrical compression coil spring.

In the valve hole 28, a control valve first chamber 28a, a control valve second chamber 28b and a control valve third chamber 28c are separated by a spool 29. As shown in FIG. The hydraulic pressure on the upstream side of the first orifice portion A formed in the discharge passage 19b, that is, the hydraulic pressure in the pressure chamber 24 is introduced through the second orifice portion B into the control valve first chamber 28a. The control valve second chamber 28b accommodates a spring 30, and hydraulic pressure on the downstream side of the first orifice portion A is introduced through the third orifice portion C. As shown in FIG. The control valve third chamber 28c is formed on the outer peripheral side of the spool 29, and pump suction pressure is introduced from the suction passage 19a via the low pressure passage 31. As shown in FIG.

Next, the configurations of the inner side surfaces 3a and 10a of the rear body 3 and the pressure plate 10 will be described in detail with reference to FIGS. 3 and 4. FIG. The arrow in the drawing indicates the direction of rotation of the drive shaft 6. As shown in FIG.
On the inner surface 3a of the rear body 3, the radially outer edge 18a of the first intake port 18 moves from the area where the first intake port 18 opens to the inner surface 3a. A first ride-on portion 45 is provided which can come into contact when it is pressed. FIG. 5 is a cross-sectional view taken along line S5-S5 in FIG. 3, and the position of the first riding portion 45 in the axial direction gradually changes as it advances in the rotational direction of the drive shaft 6 (clockwise direction in FIG. 4). has a slope shape approaching the inner surface 3a. For convenience of explanation, a two-dimensional orthogonal coordinate system having an x-axis and a y-axis is set below. The x-axis direction is the moving direction of the cam ring 8, and the x-axis positive direction is the direction from left to right in FIG. The y-axis direction is a direction orthogonal to the x-axis direction, and the positive y-axis direction is a direction from the bottom to the top in FIG.

In the x-axis direction, the starting end 45a of the first riding portion 45 is located on the negative x-axis side of the rotation axis O. As shown in FIG. The starting end 45a was experimented so that when the radially outer end of the vane 16 fell into the first intake port 18, it was positioned deeper than the end of the vane 16 (lower position in FIG. 5). and are set by simulation results. A terminal end 45b of the first riding portion 45 is located at the same position as the rotation axis O. As shown in FIG. That is, the terminal end 45b is located on a straight line L that passes through a point on the rotation axis O and is parallel to the y-axis. The position of the terminal end 45b is the position where the volume change rate of the pump chamber 17 is maximum. A reinforcing rib 46 is provided radially inside the first riding portion 45 . The communication hole 32 faces the first intake port 18 from the left and right sides of the rib 46 (x-axis negative direction side and x-axis positive direction side). That is, the first riding portion 45 does not overlap the communicating hole 32 in the axial direction.
FIG. 6 is an end view taken along line S6-S6 of FIG. 3. The radially inner peripheral edge 18b of the first intake port 18 has a fillet portion (second fillet) 47 formed in a fillet shape. The fillet portion 47 is fillet-processed so as to have a smaller curvature (larger radius of curvature) than the radially outer peripheral edge 18a. The fillet portion 47 is provided from one peripheral end to the other peripheral end of the first suction port 18 .

On the inner surface 10a of the pressure plate 10, the radially inner end portion of the vane 16 is located at the radially outer peripheral edge 42a of the suction side second back pressure port 42, and is the region where the suction side second back pressure port 42 opens. , there is provided a second riding portion 48 which can come into contact when moving to the inner surface 10a. FIG. 7 is an end view taken along line S7-S7 in FIG. 4, and the second riding portion 48 is a fillet portion (first fillet) formed in a fillet shape. The second ride-on portion 48 is provided from one peripheral end to the other peripheral end of the suction side second back pressure port 42 . The second riding portion 48 is filleted so as to have a smaller curvature (larger radius of curvature) than the radially inner peripheral edge 42b. Although illustration is omitted, a similar running-up portion is also provided on the radially outer peripheral edge of the discharge-side second back pressure port 43 .

Next, the effect of Embodiment 1 is demonstrated.
When the vane pump operates, the pump chamber in the discharge region of the pump chamber 17 has a higher pressure than the pump chamber in the suction region, so the front body 2 deforms due to this pressure imbalance. Specifically, in FIG. 2, the opening of the U-shaped front body 2 having a U-shaped cross section is opened, and the lower end portion in the drawing is deformed downward. Since the cam ring 8 and the adapter ring 9 are inclined with respect to the drive shaft 6 following this deformation, the vanes 16 moving along the inner peripheral surface of the cam ring 8 are inclined with respect to the inner surfaces 3a and 10a, which are sliding surfaces. do. As a result, the radially outer and inner ends of the rotating vanes 16 enter the first suction port 18 and the second suction-side back pressure port 42 formed on the inner surfaces 3a, 10a. FIG. 8 is a schematic vertical cross-sectional view of the pump element showing a state in which the radially outer ends of the vanes 16 are recessed into the first suction ports 18, and FIG. FIG. 4 is a schematic vertical cross-sectional view of a pump element showing a state of being depressed into a side second back pressure port 42;

Therefore, in the conventional pump device, as shown in FIG. 10, when the vane that has once fallen into the port rides on the opposing surface, it collides with the end face of the port. At the time of this collision, a large load is applied in the direction perpendicular to the contact surface, so repeated collisions between the vane and the end face of the port may cause abnormal wear or seizure of the opposing surface.
On the other hand, in the pump device 1 of Embodiment 1, when the radial outer end of the vane 16 moves from the opening region of the first suction port 18 to the inner surface 3a, the first suction port 18 has There is provided a first riding portion 45 that can come into contact with. In addition, the radially inner end of the vane 16 is connected to the suction side second back pressure port 42 and the discharge side second back pressure port 43 to connect the suction side second back pressure port 42 and the discharge side second back pressure port 43 together. A second run-on portion 48 is provided which can be abutted when moving from the open area of 43 to the inner surface 10a. By providing a first riding portion 45 and a second riding portion 48 for causing the vane 16 that has fallen into the first suction port 18 and the suction side second back pressure port 42 to ride on the inner side surfaces 3a and 10a, the vane 16 can be moved to the first suction port. Angular contact with the end faces of the port 18 and the suction side second back pressure port 42 can be avoided. As a result, the impact when the vane 16 rides on the inner side surfaces 3a, 10a can be reduced, so that abnormal wear and seizure of the inner side surfaces 3a, 10a can be suppressed.

The first riding portion 45 is formed on the radially outer peripheral edge of the first suction port 18 . When the radially outer end of the vane 16 drops into the first suction port 18, the end is located near the radially outer peripheral edge of the first suction port 18, so that the radially outer end of the first suction port 18 By providing the first riding portion 45 on the peripheral edge of the first intake port, when the vane 16 rides on the inner side surface 3a, the radially outer end of the vane 16 is more reliably driven onto the first riding portion 45, and the first intake port Angular contact with the end face of 18 can be suppressed.

The second riding portion 48 is formed on the radially outer peripheral edge of the suction side second back pressure port 42 . When the radially inner end of the vane 16 falls into the suction-side second back pressure port 42, the end is located near the radially outer peripheral edge of the suction-side second back pressure port 42. By providing the second riding portion 48 on the radially outer peripheral edge of the 2-back pressure port 42, when the vane 16 rides on the inner surface 10a, the radially inner end portion of the vane 16 is more reliably held by the second riding portion 48. , thereby suppressing angular contact with the end face of the second back pressure port 42 on the suction side.

(Terminal 45b of) the first riding portion 45 is on a straight line L that passes through a point on the rotation axis O and is orthogonal to the moving direction of the cam ring 8. As shown in FIG. In other words, the first run-on portion 45 is located at a position where the volume change rate of the pump chamber 17 is maximized. This position is a position where the position of the radially outer end of the vane 16 as seen from the rotation axis O is substantially constant, regardless of the amount of eccentricity of the rotor 7 with respect to the cam ring 8 . Therefore, by providing the first riding portion 45 at this position, the influence on the pump performance (suction performance) can be minimized.

As shown in FIG. 11, the first riding portion 45 has a slope shape in which the position in the axial direction gradually approaches the inner surface 3a as it advances in the rotational direction of the drive shaft 6. As shown in FIG. By forming the first running-up portion 45 into a slope shape, the force input from the vane 16 at the time of collision with the vane 16 can be reduced to a force component divided along the shape of the slope. As a result, the load perpendicular to the contact surface when the vane 16 collides can be reduced, and the impact can be suppressed, thereby suppressing abnormal wear and seizure of the inner surface 3a.
The rear body 3 has a communication hole 32 that communicates with the first intake port 18, and the first ride-on portion 45 does not overlap the communication hole 32 in the axial direction. That is, by not providing an opening (providing a rib 46 for reinforcement) radially inwardly of the first riding portion 45 that collides with the vane 16, a decrease in the strength of the first riding portion 45 can be suppressed.

A radially inner peripheral edge of the first intake port 18 has a fillet portion 47 formed in a fillet shape. As a result, when the vane 16 falls into the first intake port 18 and rides on the inner surface 3a, the vane 16 comes into contact with the fillet portion 47, and when it collides with the vane 16, the force input from the vane 16 is transferred to the fillet portion. It can be reduced to a component force decomposed along the shape of the portion 47. As a result, angular contact between the vane 16 and the first intake port 18 can be avoided, and the load perpendicular to the contact surface when the vane 16 collides can be reduced, so wear and seizure can be suppressed.
The second riding portion 48 is a fillet portion formed in a fillet shape. As a result, when the vane 16 falls into the second back pressure port 42 on the suction side and rides on the inner surface 10a, the vane 16 comes into contact with the fillet portion. can be reduced to a force component resolved along the shape of the fillet. As a result, angular contact between the vane 16 and the suction-side second back pressure port 42 can be avoided, and the load perpendicular to the contact surface when the vane 16 collides can be reduced, so wear and seizure can be suppressed.

[Embodiment 2]
Since the basic configuration of the second embodiment is the same as that of the first embodiment, only the parts that differ from the first embodiment will be described.
12 is a cross-sectional view taken along line S5-S5 of FIG. 3 in Embodiment 2. FIG. The first riding portion 45 of the second embodiment is formed in an R shape (curved line shape) connecting the end surface of the first intake port 18 and the inner surface 3a. Therefore, as in the first embodiment, when the vane 16 collides with the vane 16, the force input from the vane 16 can be reduced to a component force decomposed along the R shape. By reducing the load, the impact can be suppressed, and abnormal wear and seizure of the inner surface 3a can be suppressed.

[Embodiment 3]
Since the basic configuration of the third embodiment is the same as that of the first embodiment, only the parts that differ from the first embodiment will be described.
13A and 13B are diagrams showing the shape of the inner surface 3a of the rear body 3 according to Embodiment 3. FIG. 14 is an end view taken along the line S14-S14 of FIG. 13. FIG. The run-on portion 45 of the third embodiment is a fillet portion formed in a fillet shape, and has a smaller curvature than the fillet portion 47 . Therefore, as in the first embodiment, when the vane 16 collides with the vane 16, the force input from the vane 16 can be reduced to a component force resolved along the shape of the fillet portion. By reducing the vertical load, the impact can be suppressed, and abnormal wear and seizure of the inner surface 3a can be suppressed.

[Other embodiments]

Although the embodiment for carrying out the present invention has been described above, the specific configuration of the present invention is not limited to the configuration of the embodiment, and design changes, etc. within the scope of the invention may be made. is also included in the present invention.
The present invention can also be applied to a fixed displacement vane pump, and the same effects as those of the embodiment can be obtained.
The riding portion provided on the back pressure port may be tapered.

Technical ideas that can be grasped from the above-described embodiments will be described below.
In one aspect of the pump device, the pump device has a first end and a second end that are a pair of ends in the axial direction when the direction along the axis of rotation is defined as the axial direction. a drive shaft member; a rotor that rotates by the drive shaft member and has an insertion hole through which the drive shaft member is inserted; a slit; When the direction is the radial direction, a cam ring is provided outside the rotor in the radial direction, is formed in an annular shape, and forms a plurality of pump chambers together with the rotor and the vanes; , a port, and a facing surface, wherein the accommodating portion accommodates the rotor, the vanes, and the cam ring, and the port is arranged in the circumferential direction when the direction around the rotation axis is defined as the circumferential direction. opening in a region of the plurality of pump chambers where the volume of the pump chamber increases as the drive shaft member rotates or in a region where the volume of the pump chamber decreases as the drive shaft member rotates; The facing surface abuts the end surface of the rotor in the axial direction, and the radially outer end of the vane moves toward the facing surface from the region where the port opens. and the housing provided with a riding portion that can abut against the housing.

Preferably, in the above aspect, a first fluid pressure chamber and a second fluid pressure chamber are formed in the accommodating portion, and the first fluid pressure chamber extends radially outward of the cam ring in the radial direction. The second fluid pressure chamber is provided in a portion whose volume decreases as the amount of eccentricity between the rotation axis of the drive shaft member and the center of the inner peripheral edge of the cam ring increases. and a space provided radially outside of the cam ring in the radial direction, the volume of which increases as the amount of eccentricity between the rotation axis of the drive shaft member and the center of the inner peripheral edge of the cam ring increases. The cam ring is provided movably in the accommodating portion based on the pressure difference between the first fluid pressure chamber and the second fluid pressure chamber.

In another preferred aspect, in any one of the above aspects, the riding portion is formed on the radially outer peripheral edge of the port.
According to still another preferred aspect, in any one of the above aspects, the riding portion has a first fillet formed in a fillet shape.
According to still another preferred aspect, in any one of the above aspects, the riding portion is formed at a position where the rate of change in volume of the pump chamber is maximized.
In still another preferred aspect, in any one of the above aspects, the riding portion has a slope shape in which the position in the axial direction gradually approaches the facing surface as it advances in the rotational direction of the drive shaft member.

According to still another preferable aspect, in any one of the above aspects, the riding portion has a curved cross section along the rotation direction of the drive shaft member.
According to still another preferred aspect, in any one of the above aspects, the housing has a communication hole that communicates with the port, and the riding portion does not overlap the communication hole in the axial direction.
According to still another preferred aspect, in any one of the above aspects, the ride-on portion is positioned on a line that includes the rotation axis and is perpendicular to the moving direction of the cam ring.
In yet another preferred aspect, in any of the above aspects, the radially inner peripheral edge of the port has a second fillet formed in a fillet shape, the second fillet being greater than the first fillet. also has a large curvature.

From another point of view, in one aspect, the pump device includes a drive shaft member having a first end and a second end which are a pair of ends in the axial direction when the direction along the axis of rotation is defined as the axial direction. a rotor that rotates by the drive shaft member and has an insertion hole through which the drive shaft member is inserted; a slit; vanes that are provided in the slit so as to move back and forth; A cam ring, which is provided outside the rotor in the radial direction when viewed as a direction, is formed in an annular shape and forms a plurality of pump chambers together with the rotor and the vanes, a housing, a housing, and a port. , a back pressure port, and a facing surface, the accommodating portion accommodates the rotor, the vanes, and the cam ring, and the port extends in the circumferential direction when the direction around the rotation axis is defined as the circumferential direction. In the direction, among the plurality of pump chambers, it opens in a region where the volume of the pump chamber increases as the drive shaft member rotates or in a region where the volume of the pump chamber decreases as the drive shaft member rotates. the back pressure port is connected in the circumferential direction to a back pressure chamber formed inside the slit in the radial direction, the facing surface is in contact with the end surface of the rotor in the axial direction, The back pressure port is provided with a riding portion that can contact when the radially inner end portion of the vane moves from the opening region of the back pressure port to the facing surface, and the housing.

Preferably, in the above aspect, a first fluid pressure chamber and a second fluid pressure chamber are formed in the accommodating portion, and the first fluid pressure chamber extends radially outward of the cam ring in the radial direction. The second fluid pressure chamber is provided in a portion whose volume decreases as the amount of eccentricity between the rotation axis of the drive shaft member and the center of the inner peripheral edge of the cam ring increases. and a space provided radially outside of the cam ring in the radial direction, the volume of which increases as the amount of eccentricity between the rotation axis of the drive shaft member and the center of the inner peripheral edge of the cam ring increases. The cam ring is provided movably in the accommodating portion based on the pressure difference between the first fluid pressure chamber and the second fluid pressure chamber.

In another preferred aspect, in any one of the above aspects, the riding portion is formed on the peripheral edge of the back pressure port.
In still another preferred aspect, in any one of the above aspects, the riding portion has a first fillet formed in a fillet shape.
In yet another preferred aspect, in any one of the above aspects, the riding portion has a tapered shape.

1 pumping device
2 Front body (housing)
3 Rear body (housing)
3a inner surface (opposing surface)
4 pump housing
4a Pump element accommodation space (accommodation part)
6 drive shaft (drive shaft member)
7 rotor
7a slit
7b Back pressure chamber
7c insertion hole
8 cam ring
9 Adapter ring (housing)
10 Pressure plate (housing)
10a inner side (facing side)
14a First fluid pressure chamber
14b Second fluid pressure chamber
16 vanes
17 Pump room
18 1st intake port
32 Through hole
42 Suction side 2nd back pressure port
45 1st run-up section
48 2nd riding part

Claims (15)

A pump device,
a drive shaft member having a first end and a second end which are a pair of ends in the axial direction when the direction along the axis of rotation is defined as the axial direction;
a rotor rotated by the drive shaft member and having an insertion hole through which the drive shaft member is inserted and a slit;
a vane provided in the slit so as to be able to move forward and backward;
a cam ring, which is provided outside the rotor in the radial direction when the radial direction of the rotation axis is the radial direction, is formed in an annular shape, and forms a plurality of pump chambers together with the rotor and the vanes;
a housing having a receptacle, a port, and a facing surface;
the accommodating portion accommodates the rotor, the vanes, and the cam ring;
When the direction around the rotation axis is defined as a circumferential direction, the port is defined in the plurality of pump chambers in the circumferential direction as a region where the volume of the pump chamber increases with rotation of the drive shaft member or the drive shaft member. opening in a region where the volume of the pump chamber decreases as the shaft member rotates,
the facing surface abuts the end surface of the rotor in the axial direction;
The port is provided with a ride-on portion with which the radially outer end of the vane can come into contact when moving from the opening region of the port to the facing surface,
the housing;
A pumping device comprising: A pump device according to claim 1,
A first fluid pressure chamber and a second fluid pressure chamber are formed in the accommodating portion,
The first fluid pressure chamber is a space provided radially outside of the cam ring in the radial direction, and the amount of eccentricity between the rotational axis of the drive shaft member and the center of the inner peripheral edge of the cam ring is It is provided in the part where the volume decreases as it increases,
The second fluid pressure chamber is a space provided radially outside of the cam ring in the radial direction, and the amount of eccentricity between the rotational axis of the drive shaft member and the center of the inner peripheral edge of the cam ring is It is provided in the part where the volume increases as it increases,
The cam ring is provided movably within the accommodating portion based on a pressure difference between the first fluid pressure chamber and the second fluid pressure chamber,
pump device. 3. A pumping device according to claim 2,
The riding portion is formed on the outer peripheral edge of the port in the radial direction,
pump device. A pump device according to claim 3, wherein
The riding portion has a first fillet formed in a fillet shape,
pump device. 3. A pumping device according to claim 2,
The riding portion is formed at a position where the volume change rate of the pump chamber is maximized,
pump device. A pump device according to claim 5, wherein
The riding portion has a slope shape in which the position in the axial direction gradually approaches the facing surface as it advances in the rotational direction of the drive shaft member,
pump device. A pump device according to claim 5, wherein
The riding portion has a curved cross section along the direction of rotation of the drive shaft member.
pump device. A pump device according to claim 5, wherein
The housing has a communication hole that communicates with the port,
The riding portion does not overlap the communicating hole in the axial direction,
pump device. 3. A pumping device according to claim 2,
The riding portion is positioned on a straight line that passes through a point on the rotation axis and is perpendicular to the moving direction of the cam ring.
pump device. 5. A pumping device according to claim 4,
the radially inner peripheral edge of the port has a second fillet formed in a fillet shape;
the second fillet has a greater curvature than the first fillet;
pump device. A pump device,
a drive shaft member having a first end and a second end which are a pair of ends in the axial direction when the direction along the axis of rotation is defined as the axial direction;
a rotor rotated by the drive shaft member and having an insertion hole through which the drive shaft member is inserted and a slit;
a vane provided in the slit so as to be able to move forward and backward;
a cam ring, which is provided outside the rotor in the radial direction when the radial direction of the rotation axis is the radial direction, is formed in an annular shape, and forms a plurality of pump chambers together with the rotor and the vanes;
a housing having a housing, a port, a back pressure port, and a facing surface;
the accommodating portion accommodates the rotor, the vanes, and the cam ring;
When the direction around the rotation axis is defined as a circumferential direction, the port is defined in the plurality of pump chambers in the circumferential direction as a region where the volume of the pump chamber increases with rotation of the drive shaft member or the drive shaft member. opening in a region where the volume of the pump chamber decreases as the shaft member rotates,
the back pressure port is connected in the circumferential direction to a back pressure chamber formed inside the slit in the radial direction;
the facing surface abuts the end surface of the rotor in the axial direction;
The back pressure port is provided with a riding portion that can contact when the radially inner end portion of the vane moves from the opening region of the back pressure port to the facing surface,
the housing;
A pumping device comprising: 12. A pumping device according to claim 11, wherein
A first fluid pressure chamber and a second fluid pressure chamber are formed in the accommodating portion,
The first fluid pressure chamber is a space provided radially outside of the cam ring in the radial direction, and the amount of eccentricity between the rotational axis of the drive shaft member and the center of the inner peripheral edge of the cam ring is It is provided in the part where the volume decreases as it increases,
The second fluid pressure chamber is a space provided radially outside of the cam ring in the radial direction, and the amount of eccentricity between the rotational axis of the drive shaft member and the center of the inner peripheral edge of the cam ring is It is provided in the part where the volume increases as it increases,
The cam ring is provided movably within the accommodating portion based on a pressure difference between the first fluid pressure chamber and the second fluid pressure chamber,
pump device. 13. A pumping device according to claim 12, wherein
The riding portion is formed on a peripheral edge of the back pressure port,
pump device. 14. A pumping device according to claim 13,
The riding portion has a first fillet formed in a fillet shape,
pump device. 14. A pumping device according to claim 13,
The riding portion has a tapered shape,
pump device.

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