JPH1026086A - Seizure preventing structure for vane pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane pump to prevent the occurrence of abnormal wear and seizure even when a side plate is bent and deformed toward the vane side at a suction section part. SOLUTION: A drive shaft is pivotally supported and low pressure ports 82 communicated with the suction region of a cam ring and high pressure ports 81 communicated with a delivery region and a high pressure chamber in a body are located between a body containing the cam ring and the cam ring and respectively symmetrically arranged in the side plate. An oil groove 8R connected to the low pressure port 82 is formed in the suction section on the vane slide side of the side plate.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane pump and, more particularly, to a structure for preventing seizure of a vane sliding portion of a side plate.

[0002]

2. Description of the Related Art A vehicle such as an automobile is provided with a power steering device using hydraulic pressure.
Conventionally, a vane pump as shown in FIGS. 5 and 6 has been employed. Reference numeral 1 denotes a vane pump body which supports a drive shaft 50 having a pulley 51 coupled to an end thereof and has a valve hole for accommodating the flow regulating valve 4. A substantially concave space is formed in the body 1 from the opening end face 1A side opposite to the pulley 51, and a pump cartridge of a vane pump including a cam ring 30 and the like in which the side plate 8 and the rotor 31 are rotatably housed. Pack 3

A fastening bolt 52 is inserted into the opening end face 1A through a bolt hole 21 of a cover, and a female screw 41 of a body is inserted.
, The cover 2 is fastened. As shown in FIG. 6, an annular seal ring groove 14 is formed at a predetermined depth on the inner periphery of the opening end face 1A, and an annular low-pressure seal ring 15 is embedded therein. The working oil in the passages 13 and 13 is sealed.

A drive shaft 5 penetrating substantially through the center of the body 1
Numeral 0 is supported by a bearing metal 18 and connected to an engine or the like via a belt (not shown) wound around a pulley 51, and the rotor 31 is rotationally driven by a drive shaft 50.
As shown in FIG. 5, inside the body 1 close to the pulley 51, a flow rate adjusting valve 4 is housed in a direction orthogonal to the drive shaft 50, and a hydraulic oil whose flow rate has been adjusted is supplied to a discharge port (not shown). From the vane pump and supplied to the power steering device.

[0005] The pump cartridge 3 is in contact with the end face 2A of the cover 2 facing the body 1, and the end of the drive shaft 50 on the rotor coupling side protrudes through the relief hole 24 at the center of the cover. A body-side end face of the pump cartridge 3;
A disc-shaped side plate 8 is interposed between the concave bottom body 1 and the space bottom, and the pump cartridge 3 is sandwiched between the side plate 8 and the cover 2.

Here, as shown in FIG. 6, the pump cartridge 3 has a drive shaft 50 at the inner periphery of the cylindrical cam ring 30.
And a vane 32 supported by the rotor 31 and in sliding contact with the inner periphery of the cam ring 30
The rotation of the cam ring 30 is restricted by a pair of dowel pins 42, 42 projecting from the body 1 side, and penetrates the cam ring 30 and the side plate 8 to keep them in a predetermined positional relationship. Attached. As shown in FIG. 5, the rotor 31 is engaged in the axial direction by a C-pin 33 provided on the drive shaft 50, and regulates the displacement of the drive shaft 50 to the right in the drawing.

On the inner periphery of the cam ring 30, the discharge area of the pump cartridge 3 faces a high-pressure port 81 formed through the side plate 8 shown in FIG. 7 to maintain a predetermined positional relationship with the high-pressure chamber 12 of the body 1. Similarly, the suction area of the pump cartridge 3 includes first and second low-pressure ports 8 formed on the side plate 8 and the cover 2.
2, 6A (see FIG. 8) while maintaining a predetermined positional relationship, so that hydraulic oil can be substantially uniformly sucked from both sides in the axial direction.

In the body 1, a suction chamber 10 is defined between the vicinity of the upper portion of the inner peripheral surface and the outer periphery of the cam ring 30 and the side plate 8, and a low-pressure passage 9 opened at the inner peripheral bottom is formed with the suction chamber 10. On the other hand, the right end of the low-pressure passage 9 communicates with the bypass side of the flow control valve 4 that discharges the surplus flow, so that the surplus flow from the flow control valve 4 and the low-pressure hydraulic oil supplied from the suction connector 5 merge. Then, it flows into the suction chamber 10 through the low-pressure passage 9.

On the other hand, the high pressure port 81 of the side plate 8
In FIG. 5, the high-pressure chamber 12 communicates with the flow control valve 4 via a passage 11 formed obliquely upward. The hydraulic oil leaked from the pump cartridge 3 is
The air flows along the drive shaft 50 toward the pulley 51, and is guided from the lower end of the suction connector 5 to the low-pressure passage 9 through the drain passage 19 extending further toward the drive shaft 50.

Here, the side plate 8 interposed between the inner peripheral bottom portion of the body 1 and the end face of the pump cartridge 3 has a disk shape as shown in FIGS. 7A and 7B. A pair of high-pressure ports 81 is formed at a predetermined position where the end surface that is formed of parts and contacts the body 1 is 8A, the end surface that contacts the cam ring 30 is 8B, and the side plate 8 faces the discharge area of the cam ring 30. , 81 are the drive shaft 50
Is formed at a position facing the shaft hole 80 through which the hole is inserted.

Then, the end face 8 which comes into contact with the cam ring 30
B has a pair of high pressure ports 81, 81 and 90 in the circumferential direction.
An opposing step is formed below the phase of °, and this step constitutes low-pressure ports 82, 82 as first low-pressure ports. These low-pressure ports 82, 82 are provided through a gap formed between the cam ring 30 and the side plate 8 as shown in FIG.
As shown in FIG. 7, the hydraulic oil flowing into the suction chamber 10 from the low-pressure passage 9 opened at the upper part of the cam ring 30 branches off at the upper part of the cam ring 30, and the low-pressure ports 82, 82 are formed on the side of the cam ring 30 and the side plate 8. It communicates with the forked passages 13, 13 defined to go around.

[0012] As shown in FIG.
It is formed in the space between the inner wall 1D of the concave portion formed on the inner periphery of the body 1 and reaching the lower surface of the cam ring 30 and the upper semicircular portion on the outer periphery of the cam ring 30.
It gradually expands toward the zero side. On the side of the side plate 8 of the cam ring 30, the operating oil flowing from the suction chamber 10 through the forked passages 13, 13 is distributed right and left along the outer peripheral surface of the cam ring 30.
Hydraulic oil is almost uniformly sucked into the suction area of the cam ring 30 from the left-right direction in FIG. 6 through the low pressure port 82 in the side plate 8 and the end face of the cam ring 30.

A passage 8 for guiding back pressure to the base of the vane 32 is provided on an end face 8B of the side plate 8 shown in FIG.
5 are formed at a predetermined depth as substantially annular grooves, and communication between the vane back pressures is ensured by annular grooves formed on the opposed rotor side. Engagement holes 84 for engaging the dowel pins 42 are formed at predetermined positions of the side plate 8.

On the other hand, as shown in FIGS. 7 and 8, the end face 2A of the cover 2 facing the suction chamber 10 of the body 1 is moved from the position facing the low pressure passage 9 opened to the body 1 to the end face 2A. A bifurcated groove 6, 6 having a predetermined depth is formed as a low-pressure distribution groove so as to extend along the outer periphery of the abutted cam ring 30.
Is formed. The bifurcated grooves 6, 6 have a pair of low-pressure ports 6 </ b> A, 6 </ b> A on the cover side facing the suction area of the cam ring 30.
6A, the operating oil is almost uniformly sucked into the suction area of the cam ring 30 from the left and right directions. The low pressure ports 6A constitute a second low pressure port.

Thus, the cam ring 30 is axially sandwiched between the forked passages 13 formed by the gap between the upper semicircular portion of the outer periphery of the cam ring 30 housed in the body 1 and the inner periphery of the body 1. By the ports 82, 82 formed by the steps formed in the side plate 8 and the bifurcated grooves 6, 6 formed in the cover 2, the pump cartridge 3 is provided with a pair of horizontally arranged two end faces of the cam ring 30. The low-pressure ports 82, 82 and 6A, 6A make it possible to substantially evenly suck the hydraulic oil from the front and rear in the axial direction.

The end surface 2A of the cover 2 has a substantially annular vane back pressure groove 23 at a predetermined position corresponding to the base end of the vane 32 in the rotor 31, similarly to the side plate 8. Vane back pressure groove 83 of side plate 8
The back pressure is guided to the base end of the vane 32 also on the cover 2 side via the.

[0017]

In the vane pump described in the prior art, the back side of the side plate 8 always faces the pressure of the high pressure chamber 12, but the vane side 8B slides on the low pressure port 82. Since the pressure received between the portion and the portion slidably provided in the high-pressure port 81 is different, the pressure difference between the back side and the vane side varies depending on the location, and becomes maximum in the suction section adjacent to the low-pressure port. Since the side plate may not be a uniform disk, the portion of the suction section bends most to the vane side, and abnormal wear and seizure are likely to occur.

An object of the present invention is to provide a vane pump capable of preventing abnormal wear and seizure even if the side plate is bent and deformed toward the vane at the suction section.

[0019]

Means for Solving the Problems To solve the above-mentioned problems, a first means adopted by the present invention is to "support a driving shaft and interpose a cam ring between a body and a cam ring. A low-pressure port communicating with the suction area of the cam ring and a high-pressure port communicating with the discharge area and the high-pressure chamber in the body are each provided with a low-pressure port in the suction section on the side of the vane sliding contact of the side plate. An oil groove connected to the port was provided. " A second means is that "an oil groove connected to the low-pressure port is provided in a manner bypassing the low-pressure port in a suction section of the side plate on the side of the vane sliding contact". The third means is that "an oil groove connected to a high-pressure port is provided in a suction section of the side plate on the side of the vane sliding contact". A fourth means is that “an oil groove connected to the high-pressure port is provided in the suction section of the side plate on the side of the vane sliding contact so as to bypass the high-pressure port”.

[0020]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A vane pump according to the present invention will be described below with reference to the embodiments shown in FIGS. The same parts as those described in the related art are denoted by the same part numbers, and the operation of the vane pump and the operation and effect of the side plate, which is a main part according to the present invention, are described in the same parts as in the related art described above. Is omitted. The difference between the side plate according to the present invention and the conventional side plate is that an oil groove for lubrication is provided on a sliding contact surface with the vane in the suction section.

In the first embodiment of the present invention shown in FIG. 1A, the inclined surface 82A of each of the low pressure ports 82, 82 is provided.
Thus, at least one oil groove 8R having an inclination angle θ is continuously provided with respect to a radial line 8C passing through the center of rotation of the rotor 31. When the vane 32 shown in FIG. 6 rotates in the direction of the arrow, as the side surface of the vane slides on the sliding contact surface 8B of the vane provided with the oil groove 8R, the hydraulic oil is lifted from the low pressure port 82 and the oil groove 8R. And the sliding surface of the vane is replenished, so that the sliding surface is always lubricated with fresh hydraulic oil.
Moreover, since the lubricating oil is discharged to the high pressure port 81, the lubricated surface is constantly washed away with fresh hydraulic oil, so that even if abrasion powder is generated, there is no stagnation, abnormal wear and seizure. Can be prevented.

The reason why the oil groove 8R is inclined with respect to the radial line 8C is that the sliding range of the side surface of the vane with respect to the oil groove 8R is expanded, and the effect of scraping the sliding surface using the rotation of the vane is used. This facilitates the supply of hydraulic oil.
Further, by gradually decreasing one or both of the groove depth and the groove width of the oil groove 8R from the starting end side to the end side in the illustrated rotation direction, the supply of the hydraulic oil to the sliding contact surface can be more reliably performed. It can be.

In the second embodiment of the present invention shown in FIG. 1B, at least one oil groove 8S connected to each low-pressure port 82 is machined so as to coincide with the radius line 8C, and the side plate is formed. Since the fixed turntable need only be intermittently rotated by a certain angle, machining of the oil groove by the NC board or the like is relatively easy.

In the third embodiment of the present invention shown in FIG. 2A, the slopes 82A of the low pressure ports 82, 82
Oil groove 8 connected to the low pressure port in a manner bypassing the low pressure port
T is provided. The circular arc portion of the oil groove 8T may be concentric with the rotation center of the rotor, or may have any shape in which the radius of the circular arc with respect to the rotation center of the rotor gradually decreases or increases from the start side Ra to the end side Rb. In the latter, the width of the vane in the radial direction with respect to the sliding contact surface of the vane is increased, so that the supply range can be expanded. In any case, since fresh working oil is supplied to the sliding contact surface of the vane from the starting side below the oil groove 8T toward the upper end side, abnormal wear and seizure can be prevented.

In the fourth embodiment of the present invention shown in FIG. 2B, an oil groove 8 that detours from the inclined surface 82A of the low pressure port 82 is used.
U is formed in an arc shape. Since the oil groove 8U has an arc shape, machining using a cylindrical tooth-shaped milling tool or the like is easy. Both the oil grooves shown in FIGS. 2A and 2B can be formed as a single detour oil groove, so that machining with an NC board or the like is relatively easy. Further, by gradually decreasing one or both of the groove depth and the groove width of the oil groove from the starting side to the end side in the illustrated rotation direction, the supply of the working oil to the sliding contact surface is further ensured. be able to.

Next, in the fifth embodiment of the present invention shown in FIG. 3A, the starting end side of the oil groove 8W is open to the high pressure ports 83, 83 connected to the discharge side of the vane pump.
Since the oil groove 8W is inclined by the inclination angle φ with respect to the radial line 8C passing through the center of rotation of the rotor in the radial direction, the effect of scraping hydraulic oil to the vane sliding contact surface is the same as in the first embodiment shown in FIG. In addition, since the hydraulic oil is guided from the high pressure port, the sliding surface of the vane can be forcibly lubricated.

In the sixth embodiment of the present invention shown in FIG. 3 (B), the oil groove 8X is machined in accordance with the radius line 8C passing through the center of rotation of the rotor, and the machining is relatively easy. Since the oil groove 8X is open to the high-pressure port 83, the vane sliding contact surface can be forcibly lubricated.

In the seventh embodiment of the present invention shown in FIG. 4 (A), the oil groove 8Y is connected to the high pressure port 83 so as to bypass the high pressure port 83. Also in this case, as the vane rotates, fresh hydraulic oil is forcibly supplied to the sliding contact surface of the vane from the starting side below the oil groove 8Y to the upper end side, so that abnormal wear and seizure are caused. Can be prevented. In this case, since the oil groove is formed as a single bypass oil groove, machining with an NC board or the like is relatively easy. The arc portion of the oil groove 8T may be concentric with the rotation center of the rotor, or may have any shape in which the radius of the arc with respect to the rotation center of the rotor gradually decreases or increases from the start side Rc to the end side Rd. However, in the latter, the width of the vane in the radial direction with respect to the sliding contact surface of the vane is increased, so that the supply range can be expanded.

In the eighth embodiment of the present invention shown in FIG. 4B, an oil groove 8Z bypassing the high pressure port 83 is formed in an arc shape. Since the oil groove 8Z has an arc shape, processing is easy.

As described in the first to eighth embodiments, the oil groove connected to the low pressure port or the high pressure port, or the oil groove connected to the low pressure port or the high pressure port so as to bypass the low pressure port or the high pressure port is provided. Thereby, the sliding surface is effectively lubricated, so that the bending to the vane sliding contact side caused by the pressure difference between the back surface of the side plate facing the high pressure port and the vane sliding side of the suction section facing the low pressure port is prevented. Abnormal abrasion and image sticking caused by this can be reliably prevented. Further, by gradually decreasing one or both of the groove depth and the groove width of the oil groove from the start side to the end side with respect to the illustrated rotation direction, the supply of the working oil to the sliding contact surface is further ensured. be able to. The oil groove of the present invention may be any shape such as rectangular, trapezoidal, semicircular, semielliptical, V-shaped, etc., as long as the above purpose can be achieved.

[0031]

As described in detail above, in the present invention,
By providing an oil groove connected to the low-pressure port or high-pressure port, or an oil groove connected to the low-pressure port or high-pressure port so as to bypass the low-pressure port or high-pressure port, the sliding contact surface can be effectively lubricated. In addition, abnormal wear and seizure caused by bending to the vane sliding contact side caused by a pressure difference between the back surface of the side plate facing the high pressure port and the pressure difference between the vane sliding contact side of the suction section facing the low pressure port are reliably prevented. Can be. In addition, these oil grooves and bypass grooves can be easily added to the conventional side plate, and there is no need to change the mold and the assembly process. Can be.

[Brief description of the drawings]

FIG. 1A is a plan view of a side plate of a side plate according to a first embodiment of the present invention, which is in sliding contact with a vane. (B) It is a top view by the side of a vane sliding contact of a side plate concerning a 2nd embodiment of the present invention.

FIG. 2A is a plan view of a side plate of a side plate according to a third embodiment of the present invention, which is in sliding contact with a vane. (B) It is a top view by the side of a vane sliding contact of a side plate concerning a 4th embodiment of the present invention.

FIG. 3A is a plan view of a side plate of a side plate according to a fifth embodiment of the present invention, which is in sliding contact with a vane. (B) It is a top view by the side of a vane sliding contact of a side plate concerning a 6th embodiment of the present invention.

FIG. 4A is a plan view of a side plate of a side plate according to a seventh embodiment of the present invention, which is in sliding contact with a vane. (B) It is a top view by the side of a vane sliding contact of a side plate concerning an 8th embodiment of the present invention.

FIG. 5 is a sectional view of a vane pump according to the related art.

FIG. 6 is an end view of a conventional vane pump with a cover removed.

FIG. 7A is a plan view of the side plate according to the related art on the side of the vane sliding contact. (B) It is HH arrow sectional drawing of the side plate which concerns on a prior art.

FIG. 8A is a plan view of a cover according to the related art on a side where a vane slides. (B) It is DD sectional drawing of the cover which concerns on a prior art.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Body 8 Side plate 8C Radial line 8R, 8S which passes through the center of rotation of rotor 8R, 8S Oil groove connected to low pressure port 8T, 8U Oil groove connected to low pressure port so as to bypass low pressure port 8W, 8X Oil groove connected to high pressure port 8Y, 8X 8Z Oil groove connected to high pressure port in a manner bypassing high pressure port 12 High pressure chamber in body 30 Cam ring 50 Drive shaft 82 Low pressure port 83 High pressure port

Claims (20)

[Claims] 1. A low-pressure port that supports a drive shaft and is interposed between a body containing a cam ring and a cam ring and communicates with a suction region of the cam ring, and a discharge region and a high-pressure chamber in the body. High pressure port that communicates with
An oil groove connected to a low-pressure port is provided in a suction section of a symmetrically provided side plate on a vane sliding contact side, and a seizure prevention structure for a vane pump is provided. 2. The seizure prevention structure for a vane pump according to claim 1, wherein the oil groove connected to the low pressure port is provided to be inclined with respect to a radial line passing through the rotation center of the rotor. 3. The structure for preventing seizure of a vane pump according to claim 1, wherein the oil groove connected to the low pressure port is provided so as to coincide with a radius line passing through the rotation center of the rotor. 4. A groove according to claim 1, wherein one or both of the groove depth and the groove width of the oil groove connected to the low-pressure port gradually decreases from the starting side to the terminal side of the groove.
2. The seizure prevention structure for the vane pump according to 1. 5. A low-pressure port which supports the drive shaft and is interposed between the body containing the cam ring and the cam ring and communicates with a suction area of the cam ring, and also has a discharge area and a high-pressure chamber in the body. High pressure port that communicates with
A seizure prevention structure for a vane pump, wherein oil grooves connected to the low-pressure port are provided in the suction sections on the side of the vane sliding contact of the symmetrically provided side plates so as to bypass the low-pressure port. 6. An anti-seizing structure for a vane pump according to claim 5, wherein an oil groove connected to the low-pressure port so as to bypass the low-pressure port is provided concentrically with respect to the rotation center of the rotor. . 7. The burn-in of the vane pump according to claim 5, wherein the radius of the oil groove connected to the low-pressure port so as to bypass the low-pressure port gradually decreases from the start side to the end side. Prevention structure. 8. The burn-in of a vane pump according to claim 5, wherein the radius of the oil groove connected to the low-pressure port in a manner bypassing the low-pressure port gradually increases from the starting side to the end side. Prevention structure. 9. The structure for preventing seizure of a vane pump according to claim 5, wherein the oil groove connected to the low-pressure port is formed in an arc shape so as to bypass the low-pressure port. 10. An oil groove connected to a low-pressure port in a manner bypassing the low-pressure port, wherein one or both of the groove depth and the groove width gradually decreases from the starting side to the terminal side. , 7, 8 or 9. 11. A low-pressure port, which supports the drive shaft and is interposed between the body containing the cam ring and the cam ring and communicates with a suction area of the cam ring, and also has a discharge area and a high-pressure chamber in the body. A seizure prevention structure for a vane pump, wherein an oil groove connected to a high pressure port is provided in a suction section on a side of a vane sliding contact of a side plate provided with symmetrically connected high pressure ports. 12. The seizure prevention structure for a vane pump according to claim 11, wherein the oil groove connected to the high pressure port is provided to be inclined with respect to a radial line passing through the rotation center of the rotor. 13. The seizure prevention structure for a vane pump according to claim 11, wherein the oil groove connected to the high pressure port is provided so as to coincide with a radial line passing through the rotation center of the rotor. 14. A groove according to claim 11, wherein one or both of a groove depth and a groove width of the oil groove connected to the high-pressure port is gradually reduced from the starting end to the end of the groove.
Or a seizure prevention structure for a vane pump according to item 13. 15. A low pressure port which supports the drive shaft and is interposed between the body containing the cam ring and the cam ring and communicates with a suction area of the cam ring, and also has a discharge area and a high pressure chamber in the body. An oil groove connected to the high pressure port is provided in a suction section on the side of the vane sliding contact of the side plate in which the high pressure ports communicating with each other are symmetrically provided. Construction. 16. The seizure prevention structure for a vane pump according to claim 15, wherein an oil groove connected to the high pressure port so as to bypass the high pressure port is provided concentrically with respect to the rotation center of the rotor. . 17. The oil groove connected to the high pressure port in a manner bypassing the high pressure port has a radius with respect to the rotation center of the rotor,
The structure for preventing seizure of a vane pump according to claim 15, wherein the structure gradually decreases from the start side to the end side. 18. A radius of the oil groove connected to the high pressure port in a manner bypassing the high pressure port with respect to the rotation center of the rotor,
The seizure prevention structure for a vane pump according to claim 15, wherein the structure gradually increases from the starting end side to the end side. 19. The seizure prevention structure for a vane pump according to claim 15, wherein the oil groove connected to the high pressure port is formed in an arc shape so as to bypass the high pressure port. 20. A method according to claim 15, wherein one or both of the groove depth and the groove width of the oil groove connected to the high pressure port in a manner bypassing the high pressure port gradually decreases from the starting side to the terminal side. , 17, 18 or 19, the structure for preventing seizure of the vane pump.