JP5313997B2 - Variable displacement vane pump - Google Patents

Description

  The present invention relates to a variable displacement vane pump.

  Conventionally, a technique described in Patent Document 1 is known as a variable displacement vane pump. In the variable displacement vane pump described in this publication, a pressure plate is provided on one side of the cam ring and the rotor, and the pressure plate is pressed against the cam ring and the rotor by receiving pressure from the discharge side pressure chamber. And leakage of hydraulic oil at the end face of the rotor.

JP 2007-170320 A

  The pressure plate abuts against the adapter ring at the outer peripheral portion and is restricted from moving in the axial direction. The pressure plate is provided so as to be movable relative to the drive shaft at the inner peripheral portion, so that the axial deflection amount increases toward the inner side in the radial direction. It transforms to become. The cam ring and rotor are smaller in the axial direction than the adapter ring, so that excessive sliding friction between the cam ring or rotor and the pressure plate is prevented, but when the amount of deformation of the pressure plate increases. The pressure plate comes into contact with the inner peripheral side of the cam ring. Then, the deformation of the pressure plate is restricted on the inner peripheral side of the cam ring, so that the inner portion of the cam ring from the inner peripheral side of the cam ring becomes a convex deflection toward the rotor side. Since the pressure plate is restricted on the inner peripheral side of the cam ring, the bending span is shorter than that in which the pressure plate is not restricted, and as a result, the inclination of the bending is increased. When the inclination of this deflection is large, there is a problem that the gap between the pressure plate and the rotor is increased on the outer periphery side of the rotor, and the leakage of hydraulic oil at the rotor end surface is increased.

  An object of the present invention is to provide a variable displacement vane pump capable of improving pump efficiency regardless of pump discharge pressure.

  In order to achieve the above object, in the variable displacement vane pump of the present invention, the axial distance from the pressure plate to the end surface on the axial pressure plate side of the cam ring increases from the radially outer side to the radially inner side of the cam ring. It has decided to have a taper part formed in.

  Therefore, even if the pressure plate is deformed, the interference between the pressure plate and the cam ring is suppressed, and the axial clearance between the pressure plate and the rotor can be prevented from locally increasing, and the operation at the rotor end surface can be suppressed. Liquid leakage can be suppressed.

It is an axial sectional view (II sectional view of Drawing 2) of the variable capacity type vane pump of Example 1. FIG. It is radial direction sectional drawing (II-II sectional drawing of FIG. 1) of the variable displacement vane pump of Example 1. FIG. 3 is a partially enlarged view showing a positional relationship among an adapter ring, a cam ring, and a pressure plate in Example 1. FIG. FIG. 4 is a partially enlarged sectional view taken along line III-III in FIG. 1 is a schematic view of a variable displacement vane pump according to Embodiment 1. FIG. It is the elements on larger scale showing the positional relationship of the adapter ring of Example 2, a cam ring, and a pressure plate. It is the elements on larger scale showing the positional relationship of the adapter ring of Example 3, a cam ring, and a pressure plate. It is the elements on larger scale showing the positional relationship of the adapter ring of Example 4, a cam ring, and a pressure plate. It is the elements on larger scale of the adapter ring of Example 5, a cam ring, and a pressure plate. It is the elements on larger scale of the adapter ring of Example 6, a cam ring, and a rear body.

[Outline of vane pump]
1 is an axial sectional view of the variable displacement vane pump 1 according to the first embodiment (II sectional view of FIG. 2), and FIG. 2 is a radial sectional view of the variable displacement vane pump 1 (cross section II-II of FIG. 1). Figure). FIG. 2 shows a case where the cam ring 4 is located in the most negative y-axis direction (maximum eccentricity). The variable displacement vane pump 1 according to the first embodiment supplies hydraulic fluid to a power steering device mounted on a vehicle, and a drive shaft 2 is connected to a pulley that is driven via a belt or the like to a non-illustrated engine. ing. The cross-sectional view of FIG. 2 schematically shows the oil passage configuration and the like in order to simplify the description of the pump function. The axial direction of the drive shaft 2 is the x-axis, and the direction in which the drive shaft is inserted into the pump body 10 is the positive direction. Further, the axial direction of the spring 201 (see FIG. 2) that restricts the swing of the cam ring 4 and the direction in which the cam ring 4 is urged is the y-axis negative direction and the axis that is orthogonal to the x and y axes, and the suction passage IN The side is the z-axis positive direction. The vane pump according to the first embodiment is a variable displacement vane pump that supplies hydraulic fluid to a power steering device mounted on a vehicle. The hydraulic fluid sucked from the reservoir tank RES is increased to a necessary pressure, and the necessary flow rate is increased by power steering. Supply to the device.

  The vane pump 1 includes a drive shaft 2, a rotor 3, a cam ring 4, an adapter ring 5, and a pump body 10. The drive shaft 2 is connected to the engine via a pulley and is rotatably supported by the pump body 10. The rotor 3 is a rotating body that is rotationally driven by a drive shaft, and a plurality of slits 31 that are axial grooves are formed radially on the outer periphery of the rotor 3. A plate-like vane 32 having substantially the same length in the x-axis direction as the rotor 3 is inserted into each of the slits 31 so as to advance and retract in the radial direction. Further, a back pressure chamber 33 is provided at the inner diameter side end of each slit 31, and hydraulic oil is supplied to urge the vane 32 radially outward.

  The pump body 10 is formed of a front body 11 and a rear body 12. The front body 11 has a bottomed cup shape that opens to the positive side of the x-axis, and a disc-shaped pressure plate 6 is accommodated on the bottom 111. The front body 11 and the rear body 12 are fastened and fixed by a plurality of bolts. A pump element accommodating portion 112 is formed in a space defined by the inner peripheral portion of the front body 11 and the side surface of the rear body 12. The adapter ring 5, the cam ring 4, and the rotor 3 are accommodated in the pump element accommodating portion 112 on the positive side of the pressure plate 6 in the x-axis positive direction. The rear body 12 is in liquid-tight contact with the adapter ring 5, the cam ring 4, and the rotor 3 from the x-axis positive direction side, and the adapter ring 5, the cam ring 4, and the rotor 3 are sandwiched between the pressure plate 6 and the rear body 12. In other words, the pump body 10 has a bottom portion 111 provided on one end side in the axial direction of the pump element housing portion 112 that is a cylindrical portion, and an opening is formed on the other axial end side of the cylindrical portion. It is comprised from the body 11 and the rear body 12 which obstruct | occludes the opening part of the front body 11. FIG.

  The adapter ring 5 is an annular member that is provided in the pump element accommodating portion 112 that is a cylindrical portion, and in which a cam ring accommodating portion 54 (accommodating space) is formed. The shape of the adapter ring 5 is not limited to the ring shape and may be a C ring shape as long as it has at least an arc-shaped portion so that the accommodation space is formed inside. A radial through hole 51 is provided at the end of the adapter ring 5 in the positive y-axis direction. Further, a plug member insertion hole 114 is provided at the end of the front body 11 in the positive y-axis direction, and a bottomed cup-shaped plug member 70 is inserted to ensure liquid-tightness between the front body 11 and the outside. A spring 201 is inserted into the inner periphery of the plug member 70 so as to be expandable and contractible in the y-axis direction, passes through the radial through hole 51 of the adapter ring 5 and abuts on the cam ring 4 and biases in the negative y-axis direction. The spring 201 urges the cam ring 4 in the direction in which the swing amount becomes maximum, and stabilizes the discharge amount (cam ring swing position) at the time of starting the pump where the pressure is not stable.

A cam ring housing portion 54 is formed inside the adapter ring 5. A cam ring 4 is provided in the cam ring housing 54 so as to be movable with respect to the drive shaft 2, and a plurality of pump chambers (Bz +, Bz−, By +, By− described later) are formed together with the rotor 3 and the vane 32. To do. The cam ring 4 is an annular member that is movably provided in the cam ring housing portion 54 of the adapter ring 5 and is formed so that its axial length is shorter than the axial length of the adapter ring 5. A first fluid pressure chamber A1 is formed in the cam ring housing 54 and on the outer peripheral side of the cam ring 4, and on the side where the internal volume decreases when the cam ring 4 moves in the direction in which the volumes of the plurality of pump chambers increase. Has been. A second fluid pressure chamber A2 is formed in the cam ring housing portion 54 and on the outer peripheral side of the cam ring 4, and on the side where the internal volume increases when the cam ring 4 moves in the direction in which the volumes of the plurality of pump chambers increase. Has been.
FIG. 3 is a partially enlarged view showing the positional relationship among the adapter ring, cam ring, and pressure plate of Example 1, and FIG. 4 is a partially enlarged sectional view taken along line III-III in FIG. 3 is a view of the adapter ring 5 and the cam ring 4 as viewed from the rear body 12 side, so that grooves and the like formed in the pressure plate 6 are indicated by dotted lines. The end face 4c of the cam ring 4 facing the pressure plate 6 (see the hatched area in FIG. 3) is formed so that the axial distance from the pressure plate 6 increases from the radially outer side of the cam ring 4 toward the radially inner side. A tapered portion 4 c 1 is formed over the entire circumference of the cam ring 4. A seal member 50 is provided between the adapter ring 5 and the cam ring 4 and separates the first fluid pressure chamber A1 and the second fluid pressure chamber A2 on the suction region side of the drive shaft 2. The adapter ring 5 is formed such that the inner peripheral edge 56 closer to the second fluid pressure chamber A2 than the seal member 50 has a larger radius than the inner peripheral edge 55 of the first fluid pressure chamber A1.

(Configuration of front body)
The front body 11 is formed with a shaft support portion 117 that supports the drive shaft 2. The shaft support 117 is formed through the bottom 111. An oil seal 2a is provided at the pulley side end of the shaft support portion 117 to ensure liquid tightness in the vane pump. On the positive side of the front body 11 in the z-axis direction, a valve receiving hole 116 for receiving a control valve 7 which is a pressure control means for controlling the amount of eccentricity of the cam ring 4 by controlling the pressure in the first fluid pressure chamber A1. And a control valve suction oil passage 115 for introducing hydraulic oil from the suction passage IN into the control valve 7, and a control pressure oil passage 113 for discharging the control pressure into the first fluid pressure chamber A1. In addition, the bottom portion 111 is formed to be recessed at a position facing the second discharge port 63 and a suction groove 111b formed at a position facing the second suction port 62 of the pressure plate 6 to be described later. It has a discharge groove 111a and a discharge passage OUT that is connected to the discharge groove 111a and sends hydraulic fluid to the power steering device. A lubricating oil passage 80 is formed in the suction groove 111b obliquely with respect to the x axis, and supplies lubricating oil to the oil seal 2a.

(Configuration of pressure plate)
The pressure plate 6 is provided in the pump element accommodating portion 112 that is a cylindrical portion, and is disposed between the adapter ring 5 and the bottom portion 111. The pressure plate 6 is a hole that is formed so that the x-axis positive side surface 61 that is in contact with the end surface on one side in the axial direction of the adapter ring 5 and the drive shaft 2 can pass therethrough. A through hole 66 is formed so as to be movable relative to the shaft 2 in the axial direction. On the side surface 61 of the pressure plate 6 in the positive x-axis direction, a second suction port 62 disposed in an arc shape above the z-axis direction and a second discharge port disposed in an arc shape below the z-axis direction. 63, and a suction-side back pressure groove 64 and a discharge-side back pressure groove 65 for introducing the discharge pressure into the back pressure chamber 33 are formed. The second suction port 62 is disposed so as to face one end surface of the cam ring 4 in the axial direction, and is formed to open to a suction region where the volumes of the plurality of pump chambers increase as the drive shaft 2 rotates. A front half second suction port 62a is formed in the first half region (second fluid pressure chamber side) of the second suction port 62 formed in a substantially semicircular shape, and a second half second suction port 62b is formed in the second half region. Has been. Further, the pressure plate 6 is biased toward the adapter ring 5 by the pressure supplied from the discharge region acting on the side surface 67 in the negative x-axis direction.

(Rear body configuration)
One end side of the rear body 12 is connected to the second suction port 62, and a suction passage 12 a for introducing the working fluid from the reservoir tank RES storing the working fluid to the first suction port 122 is formed in the z-axis direction. The suction passage 12a is formed with substantially the same diameter in the z-axis direction, and a lower end portion of the suction passage 12a is formed with an inclined surface 12a1 that is inclined toward the z-axis negative direction side in the x-axis positive direction. The height position in the z-axis direction of the end in the positive x-axis direction of the inclined surface 12a1 is formed so as to substantially coincide with the lower end in the z-axis direction of the first suction port 122 formed in the rear body. An oil passage 12d for supplying hydraulic fluid to the control valve 7 is formed above the suction passage 12a in the z-axis direction. A bottomed support hole 12c that pivotally supports the drive shaft 2 is formed in a substantially central portion of the rear body 12. A lubricating oil passage 12b communicating with the support hole 12c is formed at the lower end of the suction passage 12a to ensure lubricity in sliding between the drive shaft 2 and the support hole 12c.

  The rear body 12 has a pump forming surface 120 that is raised in a circular shape on the positive side in the x-axis direction. The pump forming surface 120 is positioned on one end side of the cam ring 4 when the other end side of the cam ring 4 is defined as the pressure plate 6 side. A first suction port 122 is formed on the pump forming surface 120 so as to face one end surface in the axial direction of the cam ring 4 and open to the suction region. Moreover, it arrange | positions so that the axial direction one end surface of the cam ring 4 may be opposed, and the 1st discharge port 123 is formed so that it may open to a discharge area | region. The outer edge shape surrounding the first suction port 122 and the first discharge port 123 is substantially the same as the outer edge shape surrounding the second suction port 62 and the second discharge port 63 facing the x-axis direction via the cam ring 4. is there. Therefore, the positional relationship with the outer peripheral edge cam ring inner peripheral edge 4b and the outer peripheral edge 4a is similarly defined. This will be described below. The pump forming surface 120 has a first suction port 122 arranged in an arc shape above the z-axis direction, a first discharge port 123 arranged in an arc shape below the z-axis direction, and a back pressure chamber. A suction-side back pressure groove 124 and a discharge-side back pressure groove 125 for introducing the discharge pressure to 33 are formed.

[Supply of hydraulic oil to first and second fluid pressure chambers]
Next, the effect | action regarding supply of hydraulic fluid is demonstrated. A through hole 52 is provided on the z-axis positive direction side of the adapter ring 5 and on the y-axis negative direction side of the seal member 50. Each of the through holes 52 communicates with the control valve 7 via an oil passage 113 provided in the front body 11, and connects the first fluid pressure chamber A 1 on the y-axis negative direction side and the control valve 7. The oil passage 113 opens into a valve housing hole 116 that houses the control valve 7, and a control pressure is introduced into the first fluid pressure chamber A1 as the pump is driven. By providing the through hole 52 provided in the adapter ring 5 in the center of the axial width of the adapter ring 5, the outer peripheral surface of the adapter ring 5 becomes a sealing surface to reduce leakage.

  The control valve 7 is connected to the discharge groove 111 a via the oil passages 21 and 22. An orifice 8 is provided on the oil passage 22, and a discharge pressure that is an upstream pressure of the orifice 8 and a downstream pressure of the orifice 8 are introduced into the control valve 7. The position of the control valve 7 is controlled by the differential pressure at this time and the urging force of the valve spring 7a to generate a control pressure. This is because the control pressure is introduced into the first fluid pressure chamber A1, and this control pressure is generated based on the suction pressure and the discharge pressure, so that control pressure ≧ suction pressure. On the other hand, the second fluid pressure chamber A2 is a gap formed between the inner periphery of the adapter ring and the outer periphery of the cam ring, and a portion communicating with the second suction port 62 and the first suction port 122 (hereinafter referred to as communication channel). Inhalation pressure is introduced into the. This communication path always opens to the second fluid pressure chamber A2 regardless of the swinging position of the cam ring 4, whereby the second fluid pressure chamber A2 becomes the suction pressure. Accordingly, the suction pressure is always introduced into the second fluid pressure chamber A2, and thereby the variable displacement vane pump 1 is controlled only by the hydraulic pressure P1 in the first fluid pressure chamber A1. On the other hand, the hydraulic pressure P2 in the second fluid pressure chamber A2 is not controlled and always P2 = suction pressure, so that the second fluid pressure chamber A2 can obtain a stable pressure, and is stable by preventing hydraulic disturbance. The swing control of the cam ring 4 can be executed.

[Eccentric operation of cam ring]
The biasing force in the y-axis positive direction that the cam ring 4 receives from the pressure P1 of the first fluid pressure chamber A1 can be larger than the sum of the hydraulic pressure P2 of the second fluid pressure chamber A2 and the biasing force in the negative y-axis direction received from the spring 201. For example, the cam ring 4 moves in the positive y-axis direction while rolling on the support plate 40. By this movement, the volume of the pump chamber By + on the y-axis positive direction side is increased, and the volume of the pump chamber By− on the y-axis negative direction side is decreased.
When the volume of the pump chamber By− on the negative y-axis side decreases, the amount of oil supplied from the suction side to the discharge side per unit time decreases, and the differential pressure between the upstream pressure and the downstream pressure of the orifice 8 decreases. . Thereby, the control valve 7 is pushed back by the valve spring 7a, and the control pressure of the control valve 7 is lowered. Therefore, if the pressure P1 of the first fluid pressure chamber A1 also decreases and cannot fully resist the sum of the urging forces in the y-axis negative direction, the cam ring 4 moves to the y-axis negative direction side.
When the urging forces in the positive and negative directions of the y axis become substantially equal, the forces in the y axis direction acting on the cam ring 4 are balanced and the cam ring 4 stops. As a result, when the oil amount increases, the differential pressure of the orifice 8 increases, and the control valve 7 pushes the valve spring 7a to increase the valve control pressure. Therefore, contrary to the above, the cam ring 4 moves in the positive y-axis direction. Actually, the cam ring 4 does not cause movement hunting, and the eccentric amount of the cam ring 4 is determined so that the flow rate set by the orifice diameter of the orifice 8 and the spring 7a is constant.

(Operation of taper part)
Next, the operation of the tapered portion 4c1 formed on the cam ring 4 will be described. FIG. 5 is a schematic diagram of the variable displacement vane pump according to the first embodiment. FIG. 5A shows the relationship of each component when the pump discharge pressure is low in the configuration of the first embodiment. FIG. 5B shows each configuration when the pump discharge pressure is high in the configuration of the first embodiment. FIG. 5C shows the relationship between the components in a state where the pump discharge pressure is high in the configuration of the comparative example having no tapered portion. In order to simplify the description, the description will be limited to the rotor 3, the cam ring 4, the adapter ring 5, the pressure plate 6, and the rear body 12.

In the state where the pump discharge pressure is low, the pressure pressure applied to the pressure plate 6 toward the adapter ring 5 is small, so that the components including the pressure plate 6 are not significantly deformed. Therefore, the plate gap between the end face 4c of the cam ring 4 and the pressure plate 6 is maintained in a narrow state, and an appropriate sealing property is secured, so that stable pump performance can be exhibited.
In a state where the pump discharge pressure is high, the pressure pressure applied to the pressure plate 6 toward the adapter ring 5 increases, and the pressure plate 6 is bent toward the adapter ring 5 side. At this time, as shown in FIG. 5C, when the inner peripheral end of the cam ring 4 is formed at substantially the same height as the outer peripheral end, the pressure plate 6 with the inner peripheral end serving as a fulcrum. Will occur. That is, if there is no unnecessary contact between the pressure plate 6 and the cam ring 4, no fulcrum is generated, and therefore the clearance between the pressure plate 6 and the rotor 3 is narrowed. However, it has been found that the fulcrum causes deformation in the direction in which the clearance becomes wider, and the clearance between the pressure plate 6 and the rotor 3 is unnecessarily widened.
Therefore, in the first embodiment, the tapered portion 4c1 is formed on the inner periphery of the cam ring 4 as shown in FIG. Thereby, even if the pressure plate 6 bends to the adapter ring 5 side, the inner peripheral side end portion of the cam ring 4 is lower than the outer peripheral side end portion, so that a fulcrum is generated between the pressure plate 6 and the cam ring 4. The pressure plate 6 can be flexed stably, the clearance between the pressure plate 6 and the rotor 3 can be kept uniform, the proper sealing performance is maintained, and the stable pump performance can be exhibited. . In the case of Example 1, since the taper portion 4c1 is formed over the entire inner circumference side of the cam ring 3, processing is easy.

As described above, the effects listed below can be obtained in the first embodiment.
(1) It has a pump element accommodating portion 112 (hereinafter referred to as a cylindrical portion) and a bottom portion 111 provided on one axial end side of the cylindrical portion, and an opening is formed on the other axial end side of the cylindrical portion. The front body 11 and the rear body 12 provided on the front body 11 and closing the opening of the front body 11, the drive shaft 2 pivotally supported by the pump body 10, and the tubular portion An adapter ring 5 provided with at least an arc-shaped portion so as to form an accommodation space therein, and movably provided in the accommodation space of the adapter ring 5. An annular cam ring 4 formed to be shorter than the length in the direction, and a plurality of slits 31 provided in the drive shaft 2 and disposed in the cam ring 4 and extending substantially in the radial direction are arranged in the circumferential direction. The formed rotor 3, the vane 32 that is provided in the slit 31 so as to be movable forward and backward, and forms a plurality of pump chambers together with the cam ring 4 and the rotor 3, and the pump body 10. A suction passage IN that communicates with a suction region that increases in volume, a discharge passage OUT that is provided in the pump body 10 and communicates with a discharge region that decreases in volume among a plurality of pump chambers as the rotor 3 rotates, and a cylinder An x-axis positive side surface 61 (contact portion) that is provided in the shape portion, is disposed between the adapter ring 5 and the bottom portion 111 and contacts an end surface on one side of the adapter ring 5 in the axial direction, and the drive shaft 2 A through-hole 66 formed so as to be capable of penetrating, the hole being formed to be movable relative to the drive shaft 2 in the axial direction, and pressure supplied from the discharge region is Direction A space formed between the pressure plate 6 biased toward the adapter ring side by acting on the one side surface, and the accommodation space of the adapter ring 5 and the cam ring 4, and the amount of eccentricity of the cam ring 4 increases. The first fluid pressure chamber A1 provided on the side where the volume decreases with the movement of the cam ring 4 to the side to be moved, the second fluid pressure chamber A2 provided on the side where the volume increases, and the first fluid pressure chamber A1 or By controlling the pressure of the second fluid pressure chamber A2, a control valve 7 (control means) for controlling the eccentric amount of the cam ring 4 and the cam ring 4 are provided on the cam ring 4 and an end face 4c on one axial side of the cam ring 4 is the cam ring 4 The taper portion 4c1 is formed so that the axial distance from the pressure plate 6 increases from the radially outer side toward the radially inner side.

  A tapered surface 4c1 that is inclined in the same direction as the deformation of the pressure plate 6 is formed on the end surface 4c on the one axial side of the cam ring. Therefore, the deformation of the pressure plate 6 causes the pressure plate 6 and the cam ring 4 to Even if the axial clearance between them decreases, interference between the pressure plate and the cam ring is suppressed. As a result, the deformation of the pressure plate becomes gentle (the inclination of the bending deformation becomes small), and it is possible to suppress the axial gap between the pressure plate 6 and the rotor 3 from becoming locally large. Thereby, the leakage of the hydraulic fluid in a rotor end surface can be suppressed.

  Further, the tapered portion 4 c 1 is disposed on the radially inner side of the cam ring 4. In other words, the place that is most likely to come into contact with the deflection of the pressure plate 6 is the inner peripheral side of the cam ring 4. By providing the taper portion 4c1 on the inner peripheral side, the contact between the cam ring 4 and the pressure plate 6 can be suppressed. Further, since the outer peripheral side of the cam ring 4 is less likely to come into contact with the pressure plate 6 than the inner peripheral side, it is possible to improve the sealing performance of the cam ring end surface by not providing the tapered portion.

  Next, Example 2 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 6 is a partially enlarged view showing a positional relationship among the adapter ring, the cam ring, and the pressure plate according to the second embodiment. In the first embodiment, the tapered portion 4 c 1 is formed over the entire circumference of the cam ring 4. On the other hand, the second embodiment is different in that the tapered portion 4c2 is provided only in the range where the suction region is formed in the circumferential range of the cam ring 4.

That is, the variable displacement vane pump in the embodiment introduces the pressure regulated by the control valve 7 into the first fluid pressure chamber A1. This pressure is a value controlled so as to change between the suction pressure that is the pressure in the suction region and the discharge pressure that is the pressure in the discharge region, and can be said to be not as high as the discharge pressure. In addition, a suction pressure is always introduced into the second fluid pressure chamber A2, which can be said to be lower than the discharge pressure. At this time, when considering the differential pressure between the inner periphery and the outer periphery of the cam ring in the suction region, neither the first fluid pressure chamber A1 nor the second fluid pressure chamber A2 located on the outer periphery of the cam ring is so high. Since it is low, the differential pressure is relatively small. Therefore, even if the tapered portion 4c2 is formed on the end surface of the cam ring 4 and the sealing surface between the pressure plate 6 and the cam ring 4 is reduced, the amount of leakage does not increase excessively.
However, considering the differential pressure between the cam ring inner periphery and the outer periphery in the discharge region, the first fluid pressure chamber A1 and the second fluid pressure chamber A2 located on the cam ring outer periphery are not so high, but the cam ring inner periphery is the discharge pressure. Since it is high, the differential pressure is relatively large. Therefore, if a taper portion is formed on the end surface of the cam ring 4 and the sealing surface is reduced, the amount of leakage may increase.

As described above, in the second embodiment, the following operational effects can be obtained.
(2) The control valve 7 (control means) controls the pressure of the first fluid pressure chamber A1 so that the pressure changes between the suction pressure that is the pressure in the suction region and the discharge pressure that is the pressure in the discharge region. The suction pressure is always introduced into the second fluid pressure chamber A2, and the tapered portion 4c2 is provided only in the range where the suction region is formed in the circumferential range of the cam ring 4.

  The pressure difference between the inner and outer circumferences of the cam ring is relatively large in the discharge region (the first fluid pressure chamber A1 side in the discharge region has a large leak amount when the first fluid pressure chamber A1 is at the suction pressure, and the second fluid pressure chamber side is always at the suction pressure. Therefore, the amount of leakage in the discharge region can be reduced by eliminating the taper of the discharge region and ensuring a large seal width at the cam ring end face. Since the pressure difference between the inner and outer circumferences of the cam ring is relatively small in the suction region, leakage of the rotor end surface due to the provision of the tapered portion can be suppressed. Even if the pressure plate 6 is pressed by the discharge pressure, the force that pushes back the pressure plate 6 also acts in the discharge region, so that the deformation of the pressure plate 6 is also suppressed, and the local deformation accompanying the contact is also suppressed. Leakage can be suppressed.

  Next, Example 3 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 7 is a partially enlarged view showing the positional relationship among the adapter ring, the cam ring, and the pressure plate according to the third embodiment. In the first embodiment, the tapered portion 4 c 1 is formed with a uniform radial width over the entire circumference of the cam ring 4. On the other hand, in Example 3, the tapered portion 4c3 is provided so that the radial width of the range where the discharge region is formed is smaller than the range where the suction region is formed in the circumferential range of the cam ring 4. Is different. That is, in the range of the suction region, the leak at the inner and outer periphery of the cam ring is small and the deformation amount of the pressure plate 6 is large, so the radial width of the tapered portion 4c31 is set large. On the other hand, in the range of the discharge region, the leak on the inner and outer peripheries of the cam ring is large and the deformation amount of the pressure plate 6 is small, so the radial width of the tapered portion 4c32 is set small.

As described above, the following operational effects can be obtained in the third embodiment.
(3) The control valve 7 (control means) controls the pressure of the first fluid pressure chamber A1 so that the pressure changes between the suction pressure that is the pressure in the suction region and the discharge pressure that is the pressure in the discharge region. The suction pressure is always introduced into the second fluid pressure chamber A2, and the taper portion 4c3 has a smaller radial width in the range in which the discharge region is formed in the circumferential range of the cam ring 4 than in the range in which the suction region is formed. (See 4c31, 4c32).
The pressure difference between the cam ring inner and outer periphery is as described in the second embodiment. Therefore, by making the radial width of the tapered portion 4c32 on the discharge region side smaller than the radial width of the tapered portion 4c31 on the suction region side, the seal width is secured while obtaining the effect of the tapered portion on the discharge region side. Can do.

(4) The tapered portion 4 c 32 in the range where the discharge region is formed is disposed on the radially inner side of the cam ring 4.
The place most easily touched by the bending of the pressure plate 6 is the inner peripheral side of the cam ring 4. By providing the tapered portion 4c32 on the inner peripheral side, the contact between the cam ring and the pressure plate can be suppressed. Further, since the outer peripheral side of the cam ring 4 is less likely to come into contact with the pressure plate 6 than the inner peripheral side, it is possible to improve the sealing performance of the cam ring end surface by not providing the tapered portion.

  Next, Example 4 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 8 is a partially enlarged view showing the positional relationship among the adapter ring, the cam ring, and the pressure plate according to the fourth embodiment. In the first embodiment, the tapered portion 4 c 1 is formed with a uniform radial width over the entire circumference of the cam ring 4. On the other hand, the fourth embodiment is different in that a tapered portion is provided in each of the circumferential range of the cam ring 4 in the range where the suction region is formed and the range where the discharge region is formed. Specifically, the rotation direction start end portion and the end portion of the suction side taper portion 4c41 formed in the suction region are a confinement region formed between the rotation direction end portion of the suction region and the rotation direction start end portion of the discharge region. It has notches 4c41a and 4c41b formed so that the radial width and the axial depth gradually decrease toward the side. Further, the discharge side taper portion 4c42 formed in the discharge region has a notch 4c42a formed so that the radial width and the axial depth gradually decrease toward the closed region side at the rotation direction start end portion. . Further, the radial width of the suction side taper portion 4c41 is formed to be larger than the radial width of the discharge side taper portion 4c42.

  Thus, the pressure fluctuation before and behind the confinement region can be suppressed by forming a so-called notch shape in the rotation direction start end or end portion of the taper portion. Further, by forming the notch-shaped portion into a shape in which the radial width gradually decreases along the inner peripheral surface of the cam ring 4, a portion where the taper portion is formed (suction region or discharge region) and a taper portion are formed. The cam ring inner peripheral surface 4b and the vane 32 can be smoothly slid at the boundary between the non-applied portion (the confinement region).

As described above, the following operational effects can be obtained in the fourth embodiment.
(5) The suction side taper portion 4c41 and the discharge side taper portion 4c42 (taper portion) are provided in a range where the suction region is formed or a range where the discharge region is formed in the circumferential range of the cam ring 4, and the rotation of the taper portion The direction start end or end portion is formed between the rotation direction start end portion of the suction region and the rotation direction end portion of the discharge region, or between the rotation direction start end portion of the confinement region or discharge region and the rotation direction end portion of the suction region. It is formed so that the radial width or the axial depth gradually decreases toward the formed confinement region side.
Therefore, pressure fluctuations before and after the closed region can be suppressed, and sliding between the cam ring inner peripheral surface and the vane 32 at the boundary portion of the closed region can be made smooth.

Next, Example 5 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 9 is a partially enlarged view of the adapter ring, the cam ring, and the pressure plate according to the fifth embodiment. In the first embodiment, the tapered portion 4 c 1 is formed with a uniform radial width over the entire circumference of the cam ring 4. On the other hand, the fifth embodiment is different in that the suction side taper portion 4c51 is formed in the suction region and the discharge side taper portion 4c52 is formed in the discharge region. The radial width of the suction side taper portion 4c51 is y1, the axial width is z1, and the radial length of the cam ring end surface is x1. Similarly, the radial width of the discharge-side tapered portion 4c52 is y2, the axial width is z2, and the radial length of the cam ring end face is x2.
At this time, in the suction side taper portion 4c51 where the differential pressure between the inner and outer peripheries of the cam ring is small, sealing performance can be obtained even if x1 is small. Therefore, by making y1 large, contact due to deformation of the pressure plate 6 can be reliably avoided. . Furthermore, by increasing z1, contact is avoided even when the pressure plate 6 is largely deformed. In particular, since the deformation of the pressure plate 6 tends to be large in the suction region, it is effective to increase y1 and z1.
On the other hand, in the discharge side taper portion 4c52 where the differential pressure between the inner and outer circumferences of the cam ring is large, by increasing x2 and decreasing y1 in order to ensure the sealing performance, the sealing performance is ensured and contact with the deformation of the pressure plate 6 is also achieved. To avoid. Further, by increasing z2, contact with the deformation of the pressure plate 6 is avoided. Since the deformation of the pressure plate 6 is smaller in the discharge region than in the suction region, y2 and z2 are made smaller than y1 and z1, in other words, the axial depth of z2 is made smaller than z1. Sealing performance can be secured while avoiding contact. In addition, what is necessary is just to combine the magnitude relationship of x, y, z suitably.

As described above, in the fifth embodiment, the following operational effects can be obtained.
(6) The control valve 7 (control means) controls the pressure of the first fluid pressure chamber A1 so that the pressure changes between the suction pressure that is the pressure in the suction region and the discharge pressure that is the pressure in the discharge region. The suction pressure is always introduced into the second fluid pressure chamber A2, and the taper portion has a range (z2) in which the discharge region is formed rather than the range (z1) in which the suction region is formed in the circumferential range of the cam ring 4. It is formed so that the axial depth is small.
The pressure difference at the inner and outer periphery of the cam ring is the same as that described in the second embodiment. Therefore, by making the axial depth z2 of the discharge side taper portion 4c52 smaller than the axial depth z1 of the suction region, the clearance on the cam ring end face is reduced while avoiding contact on the discharge region side, and the sealing performance is improved. Can be maintained.

  Next, Example 6 will be described. Since the basic configuration is the same as that of the first embodiment, only different points will be described. FIG. 10 is a partially enlarged view of the adapter ring, the cam ring, and the rear body according to the sixth embodiment. In Example 1, the taper portion 4c1 is formed on the surface where the cam ring 4 and the pressure plate 6 face each other. On the other hand, the sixth embodiment is different in that a tapered portion is formed on the surface where the cam ring 4 and the rear body 12 face each other.

  That is, as shown in FIG. 5B, when the hydraulic pressure increases, the pressure plate 6 is deformed, but the rear body 12 is also deformed at the same time. At this time, the outer periphery of the cam ring 4 and the pump forming surface 120 of the rear body 12 may come into contact with each other. Therefore, the rear-side tapered portion 4c6 is formed on the outer periphery of the cam ring 4 so that the axial distance from the pump forming surface 120 decreases from the radially outer side toward the radially inner side. Thereby, the contact between the cam ring 4 and the rear body 12 can be avoided, and the sealing performance can be ensured by making the gap uniform. In addition, the taper part in any one of Examples 1-5 can be suitably formed in the end surface by the side of the pressure plate 6 of the cam ring 4 of Example 6. FIG.

As described above, the effects listed below can be obtained in the sixth embodiment.
(6) The cam ring 4 is provided on the other axial side of the cam ring 4 (rear body 12 side), and is formed such that the axial distance from the rear body 12 decreases from the radially outer side of the cam ring 4 toward the radially inner side. A rear taper portion 4c6.
The rear body 12 is deformed so that the inner peripheral side protrudes outwardly by the pressure of the pump chamber in the discharge region (see FIG. 5B). By making the cam ring end face shape conform to this convex deformation, the gap between the cam ring end face and the pump forming surface 120 of the rear body 12 can be made uniform, and leakage at the cam ring end face can be suppressed. .

DESCRIPTION OF SYMBOLS 1 Variable displacement type vane pump 2 Drive shaft 3 Rotor 4 Cam ring 4a Cam ring outer periphery 4b Cam ring inner periphery 4c1 Tapered part 5 Adapter ring 6 Pressure plate 7 Control valve 10 Pump body 11 Front body 12 Rear body 12a Suction passage 31 Slit 32 Vane 33 Back pressure Chamber 50 Seal member 62 Second suction port 68 Axial negative side surface 112 Pump element accommodating portion (tubular portion)
120 Pump formation surface 122 First suction port A1 First fluid pressure chamber A2 Second fluid pressure chamber B Pump chamber IN Suction passage OUT Discharge passage

Claims (1)

A cylindrical portion and a bottom portion provided on one axial end side of the cylindrical portion; a front body having an opening formed on the other axial end side of the cylindrical portion; and the front body, A pump body composed of a rear body that closes the opening of the front body;
A drive shaft supported by the pump body;
An adapter ring provided in the cylindrical portion and having at least an arc-shaped portion so as to form an accommodation space therein;
An annular cam ring that is movably provided in the accommodation space of the adapter ring and is formed so that an axial length is shorter than an axial length of the adapter ring;
A rotor provided on the drive shaft, disposed in the cam ring, and formed by arranging a plurality of slits extending in a substantially radial direction in the circumferential direction;
A vane provided in the slit so as to freely advance and retract, and forms a plurality of pump chambers together with the cam ring and the rotor;
A suction passage that is provided in the pump body and communicates with a suction region in which the volume of the plurality of pump chambers increases with rotation of the rotor;
A discharge passage which is provided in the pump body and communicates with a discharge region whose volume decreases among the plurality of pump chambers as the rotor rotates;
An abutting portion provided in the cylindrical portion, disposed between the adapter ring and the bottom portion, abutting against an end surface on one axial side of the adapter ring, and the drive shaft being formed to be able to pass therethrough. A through hole formed so that the hole can move relative to the drive shaft in the axial direction, and pressure supplied from the discharge region is applied to the surface on the one side in the axial direction. A pressure plate biased toward the adapter ring by acting;
A space formed between the accommodation space of the adapter ring and the cam ring, the first being provided on the side where the volume decreases as the cam ring moves toward the side where the eccentric amount of the cam ring increases. A fluid pressure chamber and a second fluid pressure chamber provided on the side of increasing volume;
Control means for controlling the amount of eccentricity of the cam ring by controlling the pressure of the first fluid pressure chamber or the second fluid pressure chamber;
A tapered portion provided on the cam ring and formed such that an axial distance from the pressure plate increases as an end surface on one axial side of the cam ring moves from a radially outer side to a radially inner side of the cam ring;
A variable displacement vane pump characterized by comprising:

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