WO2018143564A1

WO2018143564A1 - Variable vane pump

Info

Publication number: WO2018143564A1
Application number: PCT/KR2017/015308
Authority: WO
Inventors: 조봉현; 조영준; 조영진
Original assignee: 조봉현; 조영준; 조영진
Priority date: 2017-02-02
Filing date: 2017-12-22
Publication date: 2018-08-09
Also published as: KR101797537B1

Abstract

The present invention relates to a variable vane pump comprising: a housing which has a suction port and a discharge port positioned so as to face each other, and has an inner space provided therein; a cam ring which is installed in the housing so as to be capable of relative movement, and partitions the inner space into a pump space communicating with the suction port and the discharge port; a rotational shaft which is installed in the housing so as to be led into the pump space; a rotor which is installed on the rotational shaft so as to rotate therewith; a plurality of vanes which are provided to the rotor so as to be capable of advancing and retreating, thereby making close contact with the inner circumferential surface of the cam ring; an elastic member which is provided to the housing and applies elastic force to the cam ring in the direction of the center-of-rotation of the rotational shaft so as to enable the cam ring to be eccentric with respect to the rotational shaft; and a spacing adjustment part which is provided to the housing between the suction port and the discharge port, and has, formed between the outer circumferential surface of the cam ring and the inner circumferential surface of the housing, an inflow space into which a portion of oil discharged through the discharge port flows so as to enable the adjustment of the eccentric position of the cam ring with respect to the rotational shaft according to the rotational speed of the rotational shaft. The variable vane pump, according to the present invention, has, formed between the cam ring and the housing, the inflow space into which a portion of oil discharged from the pump flows, and thus the discharge flow rate per rotation of the pump may be increased/decreased by using the pressure of the discharged oil, and thus the pump has a relatively simple structure and has a merit of a longer service life by having enhanced durability since friction at a valve does not occur.

Description

Variable vane pump

The present invention relates to a variable vane pump, and more particularly, to a variable vane pump using the pressure of the oil discharged to reduce or reduce the discharge flow rate per rotation of the pump.

When the variable vane pump is subjected to high pressure on the external use mechanism, the cylinder ring is fixed and the stable flow rate can be discharged even if the pressure inside the pump and the pressure chamber of the first and second pressure chambers of the control valve for moving the cylinder ring are equal. Make sure

Conventional variable vane pump is integrally connected to the rotor shaft in the body, the rotor is fitted with a vane for each forward movement along the plurality of vane grooves distributed in the circumferential direction, and is formed wrapped around the outer circumference to eccentric to the rotor And a third elastic member support guide which is rotated by the carriage force in contact with the tip of the vane, and is provided to support the cylinder ring to maintain the eccentricity on one side of the outer circumferential surface of the cylinder ring, which is installed eccentrically with sliding tolerances. And a control valve supporting the cylinder ring on the other side of the outer circumferential surface of the cylinder ring.

Further, the control valve is located on one side of the valve piston moving horizontally in the side wall surrounding the side of the valve hole, a first elastic member supporting the valve piston, a first valve cap covering the side wall, and a valve piston in the side wall. And a pressure chamber that reduces wear caused by friction between the control valve and the valve hole, and between the first pressure chamber and the second pressure chamber. The valve piston is moved by the pressure difference of.

Here, the conventional variable vane pump has a U-shaped recess in the upper portion, a guide body having a through hole through which the upper and lower portions pass, an adjustment bolt for connecting the through hole through the lower portion, and the valve having the through hole formed therein. It further includes a guide member having a tapered tapered nut screwed to the end of the adjustment bolt coupled through the through holes when one side of the piston is located in the U-shaped recess to correspond to the through hole of the guide body.

In the guide member, the U-shaped recess is connected to one side of the valve piston, and the guide member supports the cylinder ring by the movement of the valve piston in a guide member moving space formed at a central portion of the control valve in a direction perpendicular to the control valve. Will be moved. That is, the pressure of the third elastic member and the pressure of the eccentric cross-sectional area difference of the cylinder ring act on the guide member having the inclination angle to move the cylinder ring.

However, in the conventional variable vane pump, a high friction force is generated by the eccentric cross-sectional pressure of the cylinder ring acting on the lower end of the pressure reducing valve through the guide member, and the high friction force reduces the durability of the pressure reducing valve, thereby reducing the service life of the pump. There is a disadvantage.

The present invention was devised to improve the above problems, and forms an inflow space through which some of the oil discharged from the pump flows between the cam ring and the housing, and uses the pressure of the discharged oil to reduce the discharge flow rate per rotation of the pump. It is an object to provide a variable vane pump to be adjusted.

The variable vane pump according to the present invention for achieving the above object is a suction port and a discharge port are formed in a position facing each other, the inner space is provided therein, and the relative space is installed in the housing, the inner space, A cam ring partitioning the pump into a pump space communicating with the suction port and the discharge port, a rotating shaft installed in the housing to be introduced into the pump space, a rotor provided on the rotating shaft and rotating together with the rotating shaft, and retractable to the rotor. A plurality of vanes installed in close contact with the inner circumferential surface of the cam ring, installed in the housing, and an elastic member configured to provide an elastic force to the cam ring in the direction of the center of rotation of the rotation shaft so that the cam ring is eccentric with respect to the rotation shaft, the suction port and It is installed in the housing between the discharge port, the rotational speed of the rotating shaft Accordingly, a separation control unit is formed between the outer circumferential surface of the cam ring and the inner circumferential surface of the housing so that the eccentric position of the cam ring with respect to the rotation shaft is adjusted to form an inflow space into which some of the oil discharged through the discharge port flows.

The spacing control unit is positioned to be spaced apart from each other in the circumferential direction on the inner circumferential surface of the housing so that the inlet space is formed, a plurality of partition members are installed to be drawn out and retractable in the rotation axis direction from the inner circumferential surface of the housing; It is provided with a plurality of support springs to provide an elastic force to the partition member so that the end of the partition member is in contact with the outer peripheral surface of the cam ring.

The housing is formed with an inflow passage communicating with the discharge port and the inflow space so that a portion of the oil discharged from the discharge port is introduced into the inflow space, and the inflow passage is for throttling oil injected into the inflow space. An orifice portion is formed.

The partition members are installed in the housing such that the mutual separation distance decreases as the cam members are closer to the cam ring from the inner circumferential surface of the housing.

The partition member is formed to have a circular cross section, the housing is formed on the inner circumferential surface of the position adjacent to each other along the circumferential direction, each inlet is formed so that the partition member can be inserted, the inlet is to the inner peripheral surface of the housing It is preferably formed to be pulled in a direction away from the rotation axis, extending so as to be spaced apart from each other as the distance from the inner peripheral surface of the housing increases, it is formed to be curved at a predetermined curvature.

On the other hand, the housing is formed on the inner peripheral surface of the position adjacent to each other along the circumferential direction, each inlet is formed so that the partition member can be introduced, the inlet is formed to be drawn in a direction away from the rotation axis with respect to the inner peripheral surface of the housing The distance from the inner circumferential surface of the housing is extended to increase the mutual separation distance, is formed to be curved to a predetermined curvature, the partition member may be formed to be curved to a curvature corresponding to the curvature of the inlet.

The housing has a discharge passage formed in communication with the inlet space and the suction port so that the oil in the inlet space is introduced into the pump chamber, and is installed in the housing on the discharge passage so that the hydraulic pressure of the inlet space is higher than a predetermined pressure. It is preferable to further include a relief valve for opening and closing the discharge passage so that the oil in the inlet space can be discharged to the suction port.

On the other hand, the variable vane pump according to the present invention is formed to surround the outer circumferential surface of the cam ring, and further comprises a metal bearing to reduce the friction between the cam ring and the housing.

In addition, the variable vane pump according to the present invention is installed in the rotor, it is preferable to further include an elastic ring for providing an elastic force to the vanes so that the end of the vanes in contact with the inner peripheral surface of the cam ring.

The variable vane pump according to the present invention forms an inlet space through which some of the oil discharged from the pump flows between the cam ring and the housing, thereby reducing the discharge flow rate per rotation of the pump using the pressure of the discharged oil, and thus the structure is relatively simple. As the friction of the valve does not occur, the durability is improved and the service life is increased.

In addition, the variable vane pump can adjust the flow rate of the oil discharged according to the steering wheel steering as well as the rotational speed of the rotary shaft when applied to the power steering.

1 is a cross-sectional view of a variable vane pump according to the present invention.

Figure 2 is an enlarged partial cross-sectional view of the separation control of the variable vane pump of Figure 1;

3 is a partial cross-sectional view of the housing of the variable vane pump of FIG.

4 is a cross-sectional view showing a high speed rotation state of the rotating shaft of the variable vane pump of FIG.

Figure 5 is a partial cross-sectional view of the separation control unit of the variable vane pump according to another embodiment of the present invention.

Figure 6 is a partial cross-sectional view of the separation control part of the variable vane pump according to another embodiment of the present invention.

Figure 7 is a plan sectional view of a variable vane pump according to another embodiment of the present invention.

In the variable vane pump according to the present invention, a suction port and a discharge port are formed at positions facing each other, and a housing having an internal space provided therein and a relative movable inside the housing, wherein the internal space is provided at the suction port and the discharge port. A cam ring partitioned into a communicating pump space, a rotation shaft installed in the housing to be introduced into the pump space, a rotor provided on the rotation shaft and rotating together with the rotation shaft, and an inner circumferential surface of the cam ring removably installed A plurality of vanes in close contact with each other, an elastic member installed in the housing and providing an elastic force to the cam ring in a direction of the center of rotation of the rotation shaft so that the cam ring is eccentric with respect to the rotation shaft, and in the housing between the suction port and the discharge port. As installed, the image relative to the rotary shaft in accordance with the rotational speed of the rotary shaft It characterized in that it comprises a spacing control portion between the outer circumferential surface of the cam ring and the inner circumferential surface of the housing so that the eccentric position of the cam ring is adjusted, forming an inlet space in which some of the oil discharged through the discharge port is introduced.

Hereinafter, a variable vane pump according to an exemplary embodiment of the present invention will be described in detail with reference to the accompanying drawings. As the inventive concept allows for various changes and numerous embodiments, particular embodiments will be illustrated in the drawings and described in detail in the text. However, this is not intended to limit the present invention to a specific disclosed form, it should be understood to include all modifications, equivalents, and substitutes included in the spirit and scope of the present invention. In describing the drawings, similar reference numerals are used for similar elements. In the accompanying drawings, the dimensions of the structures are shown in an enlarged scale than actual for clarity of the invention.

Terms such as first and second may be used to describe various components, but the components should not be limited by the terms. The terms are used only for the purpose of distinguishing one component from another. For example, without departing from the scope of the present invention, the first component may be referred to as the second component, and similarly, the second component may also be referred to as the first component.

The terminology used herein is for the purpose of describing particular example embodiments only and is not intended to be limiting of the invention. Singular expressions include plural expressions unless the context clearly indicates otherwise. In this application, the terms "comprise" or "have" are intended to indicate that there is a feature, number, step, action, component, part, or combination thereof described on the specification, and one or more other features. It is to be understood that the present invention does not exclude the possibility of the presence or the addition of numbers, steps, operations, components, parts, or combinations thereof.

Unless defined otherwise, all terms used herein, including technical or scientific terms, have the same meaning as commonly understood by one of ordinary skill in the art. Terms such as those defined in the commonly used dictionaries should be construed as having meanings consistent with the meanings in the context of the related art and shall not be construed in ideal or excessively formal meanings unless expressly defined in this application. Do not.

1 to 4 illustrate a variable vane pump 100 according to the present invention.

Referring to the drawings, the variable vane pump 100 includes a housing 200 having an inlet 201 and an outlet 202 formed at positions facing each other, an inner space 203 provided therein, and the housing 200. Cam ring 310 and the pump space 311 partitioning the inner space 203 into a pump space 311 communicated with the suction port 201 and the discharge port 202, which is installed to be movable relative to the inside. A rotary shaft 320 installed in the housing 200 to be inserted into the rotor, a rotor 330 installed on the rotary shaft 320 to rotate together with the rotary shaft 320, and a retractable installation on the rotor 330. And a plurality of vanes 340 in close contact with the inner circumferential surface of the cam ring 310, and installed in the housing 200, so that the cam ring 310 is eccentric with respect to the rotation shaft 320. An elastic member 350 which provides an elastic force in the direction of the center of rotation of the rotary shaft 320, the suction port 201 and Installed in the housing 200 between the outlet 202, the cam ring 310 of the cam ring 310 is adjusted so that the eccentric position of the cam ring 310 with respect to the rotation shaft 320 in accordance with the rotation speed of the rotation shaft 320 Between the outer circumferential surface and the inner circumferential surface of the housing 200, there is provided a separation control unit 360 for forming an inlet space 363, a portion of the oil discharged through the discharge port 202 is introduced.

The housing 200 has a suction port 201 and a discharge port 202 formed on either side of the front or rear surface. In this case, the suction port 201 and the discharge port 202 are formed at positions opposite to each other with respect to the center of the inner space 203. The inner space 203 formed inside the housing 200 is formed in a circular shape, and is preferably formed in communication with the suction port 201 and the discharge port 202.

On the other hand, the housing 200 is in communication with the discharge port 202 is formed with a first internal flow path 204 through which the oil discharged through the discharge port 202 flows. At this time, one side of the housing 200 is formed with a first connector 205 is connected to the device using the discharged oil, such as a worm gear cylinder, the first inner passage 204 is formed in the first connector 205 It is formed in communication.

In addition, the housing 200 is formed with a second internal flow passage 206 communicating with the suction port 201. On the other side of the housing 200 is formed a second connector 207 is connected to the oil supply means, such as an oil tank, the second internal flow path 206 is formed in communication with the second connector 207.

On the other hand, although the housing 200 is not shown in the figure, the front and rear surfaces of the body ring so as to close the front and rear of the annular body ring provided with the inner space 203, the front and rear surfaces are opened. And a plurality of body plates each having a suction port 201 and a discharge port 202 formed therein.

In addition, the housing 200 is installed on the open front and rear surfaces of the cam ring 310, a plurality of fixing plates (not shown) formed with the first and second communication ports communicated with the suction port 201 and the discharge port 202. It may be further provided.

The cam ring 310 is formed in an annular shape in which the pump space 311 is provided, and has an outer diameter smaller than the inner diameter of the housing 200 so that the cam ring 310 can be installed to be movable relative to the inside of the housing 200. At this time, the front and rear surfaces of the cam ring 310 is opened so that the pump space 311 can communicate with the suction port 201 and the discharge port 202, the housing 200 is in contact with the inner surface of the housing 200, respectively. It is preferably formed to have a front and rear width corresponding to the front and rear width of the inner space (203).

On the other hand, the outer circumferential surface of the cam ring 310 is provided with a metal bearing 312 to reduce the friction between the cam ring 310 and the housing 200. The metal bearing 312 is formed in an annular shape provided with a hollow so that the inner circumferential surface is in contact with the outer circumferential surface of the cam ring 310. The metal bearing 312 rotatably supports the cam ring 310, and a bearing such as an oilless bearing, a needle bearing, or a ball bearing is preferably applied.

The rotating shaft 320 extends in the front-rear direction and is installed in the housing 200 to penetrate the inner space 203. At this time, the rotating shaft 320 is rotatably supported by the housing 200, it is preferably installed to pass through the center of the inner space (203). In addition, although the rotation shaft 320 is not shown in the drawing, the driving means for generating a rotational force, such as an engine or a motor of the vehicle is connected to the end.

The rotor 330 is installed on the rotating shaft 320 exposed to the pump space 311, it is preferable to extend a predetermined length in the front and rear direction. In addition, the rotor 330 is formed so that the plurality of vane grooves are spaced apart from each other along the circumferential direction so that the vanes 340 can pass through the outer circumferential surface. The vane groove extends along the radial direction of the rotor 330 or the rotating shaft 320. That is, the vane groove is formed so as to be penetrated a predetermined depth in the direction of the center of rotation of the rotor 330 from the outer peripheral surface of the rotor 330.

In addition, although the rotor 330 is not shown in the drawing, the mounting grooves are formed in an annular shape so that the elastic ring 330 may be installed on the front or rear surface, respectively. The installation groove is formed in an annular shape having a predetermined radius with respect to the rotation center of the rotor 330, it is formed to pass through the vane grooves.

A plurality of elastic rings 333 are respectively installed on the front or rear of the rotor 330, it is formed of a metallic material having a predetermined elasticity. The elastic ring 333 is formed in an annular shape having an outer diameter smaller than the inner diameter of the body ring of the housing 300 and larger than the outer diameter of the rotating shaft 320, although not shown in the figure, one side is cut out. Elastic rings 333 are installed in the installation grooves formed on the front and rear surfaces of the rotor 330, it is installed in the vanes through the vane groove communicated with the installation groove. In addition, the elastic ring 333 is formed with a plurality of irregularities along the outer circumferential surface.

A plurality of vanes 340 are inserted into the vane grooves of the rotor 330, one end of which is in contact with the inner circumferential surface of the cam ring 310, and the other end of the vane 340 is inserted into the vane grooves of the rotor 330. At this time, although not shown in the drawings, the front and rear edges of the other end of the vane 340 is provided with an insertion groove (not shown) so that the elastic rings 333 are respectively inserted to elastically support the vane 340. The insertion groove may extend a predetermined length from one end of the vane 340 toward the other end.

The elastic ring 333 is inserted into the insertion groove formed at the front and rear edges of the vane 340, and the elastic ring 333 provides an elastic force so that one end of the vane 340 contacts the inner circumferential surface of the cam ring 310. Since the state in which one end of the vane 340 is in contact with the inner circumferential surface of the cam ring 310 is maintained by the elastic ring 333, the variable vane pump 100 may pump oil even if the rotating shaft 320 rotates at a low speed. .

The elastic member 350 is installed on the inner circumferential surface of the housing 200 between the discharge port 202 and the suction port 201, and the one end is supported on the outer circumferential surface of the cam ring 310, and the other end is supported on the housing 200. do. The elastic member 350 is applied to the coil spring having a predetermined elasticity to provide the cam ring 310 in the direction of the center of rotation of the rotation axis 320 from the inner peripheral surface of the housing 200. The cam ring 310 is eccentrically supported with respect to the rotor 330 by the elastic force of the elastic member 350.

The space adjusting part 360 includes a plurality of partition members 361 provided on the inner circumferential surface of the housing 200 at a position adjacent to the elastic member 350, and end portions of the partition members 361 abut on the outer circumferential surface of the cam ring 310. And a plurality of support springs 362 providing an elastic force.

The partition member 361 is formed to have a front and rear width corresponding to the front and rear width of the inner space 203 so as to partition the inflow space 363 in the space between the cam ring 310 and the housing 200. The predetermined length extends in the radial direction of 320. In this case, an inlet 364 is formed on the inner circumferential surface of the housing 200 to allow the partition members 361 to be introduced therein. The inlet 364 has a front and rear width corresponding to the front and rear width of the partition member 361, and is formed to be pulled in a direction away from the rotation shaft 320 with respect to the inner circumferential surface of the housing 200. The inlet 364 is formed on the inner circumferential surface of the housing 200 to be spaced apart from each other along the circumferential direction.

In this case, the inlet openings 364 are rotated on the shaft 320 so that the partition members 361 may be installed in the housing 200 such that the separation distances decrease from the inner circumferential surface of the housing 200 to the cam ring 310. It is preferable to extend linearly so as to be farther away from each other. The space between the partition members 361, the inner surface of the housing 200, and the outer circumferential surface of the cam ring 310 forms the inflow space 363.

On the other hand, when the discharge of the oil proceeds through the discharge port 202, the discharge chamber in which the oil is discharged is generated in the space communicating with the discharge port of the pump space 311, the cam ring 310 is eccentric with respect to the rotating shaft 320 Therefore, an area difference between an upper portion and a lower portion of the discharge chamber occurs based on the rotation shaft 320. Based on the drawing shown in FIG. 1, the lower portion of the discharge chamber has a larger volume than the upper portion of the discharge chamber. Accordingly, the inner surface of the cam ring 310 corresponding to the lower portion of the discharge chamber is larger than the inner surface of the cam ring 310 corresponding to the upper portion of the discharge chamber, and the cam ring 310 corresponding to the lower portion of the discharge chamber. An area obtained by subtracting the inner surface area of the cam ring 310 corresponding to the upper portion of the discharge chamber from the inner surface area of the eccentric cross section is defined. In this case, the partition members 361 are installed in the housing 200 such that the area between the partition members 361 is smaller than the eccentric cross-sectional area. In addition, the partition members 361 are preferably installed in the housing 200 at a position adjacent to a portion having a larger area among the upper portion or the lower portion of the discharge chamber based on the rotation shaft 320. That is, referring to FIG. 1, the partition members 361 are provided on the lower inner side surface of the housing adjacent to the lower portion of the larger discharge chamber.

The support springs 362 are respectively installed at the inlets 364 to provide elastic force so that the partition member 361 protrudes from the inner circumferential surface of the housing 200. Meanwhile, in the illustrated example, the support spring 362 has a structure in which a leaf spring is applied, but the support spring 362 is not limited thereto, but a coil spring may be applied.

In this case, the housing 200 has an inflow passage 208 which communicates with the outlet 202 and the inlet space 363 so that some of the oil discharged from the outlet 202 can flow into the inlet space 363. Is formed. In this case, one end of the inflow passage 208 communicates with the inflow space 363 between the partition members 361, and the other end thereof is formed to communicate with the first internal passage 204. In addition, an orifice portion 211 for throttling oil injected into the inflow space 363 is formed in the housing 200 on the inflow passage 208. The orifice portion 211 is formed at one end of the inflow passage 208. Some of the oil discharged through the first internal passage 204 flows into the inflow passage 208 through the orifice portion 211.

Although not shown in the figure, the orifice portion 211 is provided with a chamber having a larger cross-sectional area than that of the inflow passage 208. The oil introduced through the inflow passage 208 decreases in flow velocity as it flows into the chamber of the orifice portion 211, but friction occurs between the chamber inner wall surface of the orifice portion 211 and the oil, and the pressure is generated by the generated friction. Losses occur and the oil pressure decreases. On the other hand, the orifice portion 211 is not limited thereto, and any structure can be used to reduce the pressure of oil.

In addition, the housing 200 has a discharge passage 209 is formed in communication with the inlet space 363 and the suction port 201 so that the oil in the inlet space 363 can be introduced into the pump chamber. In this case, when the hydraulic pressure of the inflow space 363 is greater than or equal to a predetermined pressure, the oil in the inflow space 363 may be discharged to the suction port 201 in the housing 200 on the discharge flow path 209. A relief valve 212 for opening and closing the discharge passage 209 is provided. The relief valve 212 is a safety valve generally used in the prior art and a detailed description thereof will be omitted. The relief valve 212 prevents the hydraulic pressure in the inflow space 363 from being higher than a predetermined pressure, thereby preventing damage to the pump and occurrence of defects due to a sudden increase in hydraulic pressure.

Referring to the operation of the variable vane pump 100 according to the present invention configured as described above in detail.

The cam ring 310 is eccentrically set from the rotation shaft 320 by the elastic force of the elastic member 350. When the rotating shaft 320 is rotated, the rotor 330 installed on the rotating shaft 320 is also rotated, and the oil is pumped to the pump space 311 through the suction port 201 by the vanes 340 installed on the rotor 330. It is introduced and discharged to the outside through the discharge port 202.

When the oil is discharged through the discharge port 202, discharge pressure is generated in the discharge chamber, which is a part of the pump space 311 communicated with the discharge port, and the discharge pressure is applied to the inner surface of the cam ring 310 corresponding to the discharge chamber. Works. At this time, since the lower portion of the discharge chamber has a larger area than the upper portion of the discharge chamber based on the rotation shaft 320, the force acts downward on the cam ring 310 based on the drawing.

At this time, some of the oil discharged into the inflow space 363 formed by the separation control unit 360 is introduced, the oil flowing into the inflow space 363 is decompressed through the orifice portion 211. In addition, since the outer surface of the cam ring 310 corresponding to the inflow space 363 has an area smaller than the eccentric cross-sectional area, the force acting on the inner surface of the cam ring 310, that is, the eccentric cross-sectional area, is the oil in the inflow space 363. Greater than the force generated by

As a result, a pressure difference is generated between the eccentric cross-sectional area of the discharge chamber inside the cam ring 310 and the inflow space 363, and the force acts in the direction adjacent to the inner surface of the housing by the pressure difference. The cam ring 310 is supported relative to the housing 200 so that the initial eccentric position is maintained by the tension of the elastic member 350.

At this time, when the rotation speed of the rotary shaft 320 increases, the pressure of the oil discharged to the outside of the pump space 311 increases in proportion to the increased rotation speed. Accordingly, a pressure difference between the inflow space 363 of the separation controller 360 and the pump space 311 inside the cam ring 310 is relatively large. That is, the difference between the pressure acting on the inner surface of the cam ring 310 corresponding to the discharge chamber and the pressure acting on the outer surface of the cam ring 310 corresponding to the inflow space 363 is greater, and the cam ring 310 The elastic member 350 is moved in the compression direction. At this time, the cam ring 310 is moved to the lower side as shown in FIG.

According to the movement of the cam ring 310 described above, the discharge chamber volume which is a part of the pump space 311 communicated with the discharge port 202 is reduced. That is, when the discharge pressure is increased, the cam ring 30 is moved to the lower side based on the drawing. In this case, the discharge chamber is reduced in the upper region but increased in the lower region to increase the eccentric cross-sectional area. However, as the cam ring 310 moves, the volume of the suction chamber, which is a part of the pump space 311 communicated with the suction port 201, decreases, and thus the discharge flow rate discharged to the outside of the pump decreases.

At this time, since the partition members 361 are supported to be inclined to each other, the area of the outer circumferential surface of the cam ring 310 between the partition members 361, that is, the inflow space 363 is closer to the inner surface of the housing 200. The hydraulic working area of the oil introduced into the tank increases. Therefore, as the cam ring 310 is adjacent to the inner side of the housing 200, the force acting on the cam ring 310 by the oil filled in the inflow space 363 increases, so that the oil according to the speed increase of the rotation shaft 320 is increased. The rate of reduction of the discharge flow rate can be adjusted. That is, the rate of decrease of the discharge flow rate due to the increase of the speed of the rotary shaft 320 in the low speed rotation state of the rotary shaft 320 is greater than the rate of decrease of the discharge flow rate due to the increase of the speed of the rotary shaft 320 in the high speed rotation state of the rotary shaft 320. When the variable vane pump 100 is applied to a power steering apparatus for a lane, the steering feeling of the steering wheel according to the speed of the vehicle may be prevented from being changed rapidly in a high speed state of the vehicle.

On the other hand, when the variable vane pump 100 according to the present invention is applied to a vehicle power steering device, the oil discharged from the variable vane pump 100 according to the steering or non-steering of the handle for the same rotational speed of the rotary shaft 320 The discharge amount of is adjusted. That is, when steering the handle, the oil discharged from the housing 200 is supplied to the cylinder installed on the steering shaft of the vehicle, the variable vane pump 100 is in a constant pressure state. At this time, since the pressure of the pump space 311 inside the cam ring 310 and the pressure of the inflow space 363 of the separation control unit 360 are not relatively large, the cam ring 310 is rotated by the elastic member 350. ), A relatively large amount of oil is discharged per rotation of the rotating shaft 320 by maintaining the eccentric state. Since a relatively large amount of oil is pumped from the variable vane pump 100, the driver can steer the handle more easily.

In addition, when the driver does not steer the handle, the oil discharged from the variable vane pump 100 is in a dynamic pressure state because the oil is bypassed in a state in which the flow to the cylinder installed on the drive shaft of the vehicle is blocked, where the cam ring 310 Pressure inside the pump space 311 is greater than the pressure of the inlet space 363 of the separation control unit 360. At this time, the pressure difference between the pressure of the pump space 311 in the cam ring 310 and the inflow space 363 of the separation control unit 360 is greater than when steering the handle. Therefore, the cam ring 310 is moved in the direction in which the elastic member 350 is compressed by the pressure difference. As the cam ring 310 moves, the volume of the pump space 311, that is, the suction chamber, between the suction port 201 and the discharge port 202 decreases, and the flow rate of oil discharged per revolution of the rotating shaft 320 decreases. do.

As described above, the variable vane pump 100 according to the present invention may adjust the discharge flow rate of oil according to steering and non-steering of the handle even if the rotation speed of the rotating shaft 320 does not change. There is an advantage to save the power to drive 100).

On the other hand, the variable vane pump 100 according to the present invention is provided with an elastic ring 333 inside the rotor 330 to provide elastic force to the vanes 340, even if the rotating shaft 320 rotates at a low speed vane 340 The end of the field can be in close contact with the inner circumferential surface of the cam ring 310, the operation reliability is relatively high. In addition, since the cam ring 310 is provided with a metal bearing 312 on the outer circumferential surface of the cam ring 310, even if the rotating shaft 320 rotates at a high speed, the cam ring 310 is caused by friction between the inner contact surface of the cam ring 310 and one end of the vane 340. By rotating at a constant speed in the metal bearing 312, the frictional speed between the cam ring 310 internal surface and the upper end of the vane 340 is reduced.

On the other hand, Figure 5 shows a partition member 410 according to another embodiment of the present invention.

Elements having the same function as in the above-described drawings are denoted by the same reference numerals.

Referring to the drawings, the partition member 410 is formed to have a circular cross section. At this time, the inlet 412 is formed to be drawn in the direction away from the rotation axis 320 with respect to the inner peripheral surface of the housing 200, and extends so as to increase the mutual separation distance away from the inner peripheral surface of the housing 200, It is formed to bend to a predetermined curvature.

As the cam ring 310 is adjacent to the inner surface of the housing 200 by the partition members 410 described above, an area of the outer circumferential surface of the cam ring 310 between the partition members 410 increases. At this time, since the partition members 410 are bent and supported by the inlet 412, the change in the outer circumferential surface area of the cam ring 310 between the partition members 410 according to the speed of the rotation shaft 320 is not directly proportional to the cam ring ( As the 310 is adjacent to the inner surface of the housing 200, the rate of change of the outer surface of the cam ring 310 between the partition members 410 increases.

Therefore, when the variable vane pump 100 is applied to a vehicle power steering device, in the high speed rotation state of the rotation shaft 320, the reduction rate of the discharge flow rate according to the increase in speed is more than in the case of the partition member shown in the embodiment of FIG. 1. Since it is small, the steering steering of the vehicle according to the speed of the vehicle is prevented from being changed suddenly, thereby providing the driver with a more comfortable driving feeling at high speed.

Meanwhile, as illustrated in FIG. 6, the restraining member 361 may not be formed to have a circular cross section, but may be formed to have a curvature corresponding to the curvature of the inlet 362.

On the other hand, Figure 7 shows a variable vane pump 500 according to another embodiment of the present invention.

Referring to the drawings, the variable vane pump 500 further includes a leakage preventing unit 510 for preventing oil from leaking between the housing 200 and the rotation shaft 320. In this case, the housing 200 has a recess 505 is formed at both ends in the longitudinal direction of the rotor 330, that is, the inner surfaces of the rotor 330 opposite to the front and rear surfaces thereof. At this time, the recess groove 505 is formed on the inner surface of the body plate 210 of the housing 200, extends in an annular shape having a predetermined radius around the rotation axis 320, from the inner surface of the body plate 210 It is preferably formed to be drawn in a predetermined depth along the longitudinal direction of the rotary shaft (320). At this time, the leakage preventing member 511 is formed on the inner surface of the body plate 210 between the vane groove and the rotation shaft 320 of the rotor 330 to be installed between the vane groove and the rotation shaft 320 of the rotor 330. It is.

In addition, fixing keys 506 are provided in the interior recesses 505 of the body plate 210 to prevent rotation of the leakage preventing member 511 of the leakage preventing unit 510 to be described later. The fixing key 506 extends a predetermined length along the longitudinal direction of the rotation shaft 320, one end is fixed to the body plate 210, the other end is introduced into the advance groove 505.

Meanwhile, when a plurality of fixing plates having first and second communication holes communicating with the suction port 201 and the discharge port 202 are installed on the front and rear surfaces of the cam ring 310 in the housing 200, the fixing is performed. Preferably, the recess groove 505 is formed on the inner surface of the plate.

The leakage preventing part 510 is provided at the longitudinal end of the rotor 330, that is, the front and rear surfaces of the rotor 330 to prevent the oil in the pump space from leaking between the rotation shaft 320 and the housing 200. A plurality of oil leakage preventing members 511 which are installed on the inner surface of the housing 200 facing each other in a longitudinal direction of the rotation shaft 320 and are hollowed so that the rotation shaft 320 can be inserted therein; A plurality of contact springs provided on the leakage preventing member 511 to provide an elastic force to the leakage preventing member 511 such that the leakage preventing member 511 may be in close contact with the longitudinal end of the rotor 330. 512).

The leakage preventing member 511 is inserted into the recesses 505 of the body plate 210, respectively, and is formed in an annular shape in which the hollow is provided. One end of the leakage preventing member 511 is inserted into the advance groove 505, the other end is installed on the body plate 210 to be in contact with the front or rear of the rotor 330. In addition, the leakage preventing member 511 is preferably formed of a metallic or non-metallic material having a predetermined wear resistance and strength.

In addition, a fixing groove is formed at one end of the leakage preventing member 511 so that the fixing key 506 installed on the body plate 210 may be inserted. The fixing groove extends a predetermined length from one end of the leakage preventing member 511 toward the other end.

A plurality of contact springs 512 are installed between the body plate 210 and the leakage preventing member 511 to provide an elastic force so that the other end of the leakage preventing member 511 is in close contact with the front or rear of the rotor 330. At this time, the contact spring 512 is preferably a plate spring is applied.

The variable vane pump 500 according to the present invention configured as described above is prevented from leaking between the housing 200 and the rotating shaft 320 by the leak preventing unit 510, even if the rotation speed of the rotating shaft 320 is slow. There is an advantage that it is possible to discharge a certain amount stably.

The description of the presented embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the scope of the invention. Thus, the present invention should not be limited to the embodiments set forth herein but should be construed in the broadest scope consistent with the principles and novel features set forth herein.

(none)

Claims

A housing having a suction port and a discharge port formed at positions facing each other, and having an internal space provided therein;

A cam ring which is installed to be movable relative to the inside of the housing and divides the internal space into a pump space communicating with the suction and discharge ports;

A rotating shaft installed in the housing to be drawn into the pump space;

A rotor installed on the rotating shaft and rotating together with the rotating shaft;

A plurality of vanes mounted on the rotor so as to be able to move forward and close to the inner circumferential surface of the cam ring;

An elastic member installed in the housing and providing an elastic force to the cam ring in the direction of the center of rotation of the rotation shaft such that the cam ring is eccentric with respect to the rotation shaft;

Installed in the housing between the suction port and the discharge port, and discharged through the discharge port between the outer peripheral surface of the cam ring and the inner peripheral surface of the housing so that the eccentric position of the cam ring with respect to the rotating shaft is adjusted according to the rotational speed of the rotary shaft And a spacing control unit forming an inflow space into which some of the oil is introduced.

The spacing control unit

A plurality of partition members disposed on the inner circumferential surface of the housing so as to be spaced apart from each other along the circumferential direction, the plurality of partition members installed to be pulled out and retractable from the inner circumferential surface of the housing;

And a plurality of support springs providing elastic force to the partition member such that an end portion of the partition member contacts an outer circumferential surface of the cam ring.
The method of claim 1,

The housing has an inlet flow passage communicating with the outlet and the inlet space so that some of the oil discharged from the outlet can be introduced into the inlet space, and the inlet flow path reduces the pressure of the oil injected into the inlet space. Variable vane pump having an orifice portion for making.
The method of claim 1,

The partition member is a variable vane pump is installed in the housing so that the mutual separation distance is reduced closer to the cam ring from the inner peripheral surface of the housing.
The method of claim 1,

The partition member is formed to have a circular cross section,

The housings each have an inlet opening on the inner circumferential surface of the position adjacent to each other along the circumferential direction so that the partition member can be retracted,

The inlet is formed to be drawn in the direction away from the axis of rotation with respect to the inner peripheral surface of the housing, the variable vane pump is formed so as to be extended at a predetermined curvature, so as to extend the mutual separation distance away from the inner peripheral surface of the housing.
The method of claim 1,

The housings each have an inlet opening on the inner circumferential surface of the position adjacent to each other along the circumferential direction so that the partition member can be retracted,

The inlets are formed to be drawn in a direction away from the rotation axis with respect to the inner circumferential surface of the housing, extended to increase the mutual separation distance as the distance from the inner circumferential surface of the housing is increased, is formed to be curved at a predetermined curvature,

The partition member is a variable vane pump formed to be curved to the curvature corresponding to the curvature of the inlet.
The method according to claim 1 or 2,

The housing has a discharge passage formed in communication with the inlet space and the suction port so that the oil in the inlet space can be introduced into the pump chamber,

And a relief valve installed in the housing on the discharge passage to open and close the discharge passage so that the oil in the inlet space can be discharged to the suction port when the hydraulic pressure of the inlet space is higher than a predetermined pressure. .
The method of claim 1,

And a metal bearing formed to surround an outer circumferential surface of the cam ring and reducing friction between the cam ring and the housing.
The method of claim 1,

And an elastic ring installed on the vanes, the elastic ring providing elastic force to the vanes so that the end portions of the vanes may contact the inner circumferential surface of the cam ring.
The method of claim 1,

In order to prevent oil in the pump space from leaking between the rotating shaft and the housing, the pump may be retractably installed along the longitudinal direction of the rotating shaft on an inner side surface of the housing opposite to the longitudinal end of the rotor. Leakage preventing member is formed so that the hollow;

And a close contact spring installed on the leak preventing member and providing an elastic force to the leak preventing member so that the leak preventing member is in close contact with the longitudinal end of the rotor.