JP2007016789A - Variable displacement pump - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve the problem of noise by damping vibration of a cam ring and pulsation on the pump delivery side in a variable displacement vane pump. <P>SOLUTION: This variable displacement pump has a rotor 25, the cam ring 27, a pump body 21 and a compression coil spring 61 energizing the cam ring 27 in the direction with pump capacity as a maximum in the pump body 21. A metering orifice is composed of a fixed metering orifice 53 and a variable metering orifice 59 arranged in parallel to the fixed metering orifice 53 and opened-closed by rocking of the cam ring 27. The pump has a damper orifice part 56a arranged in a flow passage connecting a high pressure side chamber and a first fluid pressure chamber 43 introducing upstream side pressure of the metering orifice, and has a damper orifice part 57 arranged in a flow passage connecting a spring chamber 54 and a second fluid pressure chamber 44 introducing downstream side pressure of the metering orifice and storing a compression coil spring 54a pressing a spool. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a variable displacement pump used in a pressure fluid utilizing device such as a power steering device that reduces the steering force of an automobile.

  Conventionally, a displacement type vane pump that is directly driven to rotate by an automobile engine has been used as a power steering device pump. Such a displacement pump increases or decreases the discharge flow rate according to the engine speed, so that the steering assist force is increased when the automobile is stopped or traveling at low speed, and the steering assist force is decreased when traveling at high speed. It has a characteristic that contradicts the steering assist force required for the device. Therefore, it is necessary to use a large-capacity pump that can secure a discharge flow rate that can obtain a necessary steering assist force even when traveling at a low speed with a low rotation speed. In addition, a flow control valve that controls the discharge flow rate to a certain amount or less is essential during high-speed traveling at a high rotational speed. For this reason, in the capacity type pump, the number of components increases, the structure and the passage configuration are complicated, and it is inevitable that the whole is increased in size and cost.

  In order to solve such problems of the displacement pump, a variable displacement vane pump capable of decreasing the discharge flow rate (cc / rev) per rotation in proportion to the increase in the rotation speed is disclosed in, for example, Patent Document 1. -Proposed by Patent Literature 4 and the like. According to these variable displacement pumps, a flow rate control valve like that of the displacement pump is not necessary, and waste of driving horsepower can be prevented, which is excellent in terms of energy efficiency. Further, since there is no return to the tank side, the oil temperature does not rise, and problems such as leakage inside the pump and a decrease in volumetric efficiency can be prevented.

  An example of such a variable displacement vane pump will be briefly described with reference to FIG. 11 showing a pump structure in Patent Document 4, for example. In the figure, 1 is a pump body, 1a is an adapter ring, and 2 is the body 1 Spring means (compression coil) that presses in the left direction in the figure with a cam ring that is swingably provided via a swing fulcrum pin 2a serving as a support shaft in an elliptical space 1b formed in the adapter ring 1a. It is biased by the spring 2b).

  A rotor 3 is housed eccentrically toward the other side so as to form a pump chamber 4 on one side in the cam ring 2. When the rotor 3 is rotationally driven by an external drive source, the vane 3a held so as to advance and retract in the radial direction is advanced and retracted. In the figure, 3b is a drive shaft of the rotor 3, and the rotor 3 is rotationally driven in a direction indicated by an arrow in the figure. Here, the pump chamber 4 is a space portion having a substantially crescent shape formed on one side of the rotor 3 in the cam ring 2, and a space portion formed from the suction side opening 7 to the discharge side opening 8 described later. It will be described as shown.

  5 and 6 are first and second fluid pressure chambers which are formed on both sides of the outer peripheral surface of the cam ring 2 in the elliptical space 1b of the adapter ring 1a provided in the body 1, and are respectively a high pressure side and a low pressure side. is there. In these chambers 5 and 6, passages 5a and 6a for guiding the fluid pressure on the downstream side of the metering throttle provided in the pump discharge side passage 11 as control pressure for swinging the cam ring 2 are spools described later. It opens through the type control valve 10.

In this example, the variable metering restrictor 12 is provided with a hole 12a opened on the side wall surface of the body 1 forming the second fluid pressure chamber 6, and a side edge of the cam ring 2 that moves so as to open and close the hole 12a. It is formed by the part 12b. For this reason, the second fluid pressure chamber 6 is in a state of fluid pressure downstream of the variable metering restrictor 12 described above, and this fluid pressure passes through the passage 6a to the low pressure side of the control valve 10. Led to the room.
Further, the pump discharge side passage on the downstream side of the variable metering throttle 12 described above is indicated by reference numeral 13.

  In FIG. 11, reference numeral 7 denotes a pump suction side opening (suction port) that opens toward the pump suction side region 4 </ b> A of the pump chamber 4, and 8 denotes an opening that faces the pump discharge side region 4 </ b> B of the pump chamber 4. This is a pump discharge side opening (discharge port). These openings 7 and 8 are provided in at least one of a pressure plate and a side plate (not shown), which are fixed walls for holding and holding the pump components including the rotor 3 and the cam ring 2 from both sides. Is formed.

  The cam ring 2 is urged from the fluid pressure chamber 6 side by the compression coil spring 2b and is pressed in a direction to maintain the volume (pump capacity) in the pump chamber 4 to the maximum. Reference numeral 2c in the figure denotes a seal material provided on the outer peripheral surface of the cam ring 2 for defining the fluid pressure chambers 5 and 6 on both the left and right sides together with the swing fulcrum pin 2a.

  The spool type control valve 10 is operated by differential pressures P1 and P2 on the upstream side and the downstream side of a variable metering throttle 12 such as a metering orifice provided in the middle of the pump discharge side passages 11 and 13, and the pump discharge side By introducing the fluid pressure P3 corresponding to the flow rate of the fluid into the fluid pressure chamber 5 on the high pressure side at the outer side of the cam ring 2, a sufficient flow rate can be secured even immediately after the pump is started. .

  That is, as described above, the fluid pressure on the downstream side of the variable metering throttle 12 of the pump discharge side passages 11 and 13 is controlled by the control valve 10 and introduced into the fluid pressure chambers 5 and 6 on both sides of the cam ring 2. Thus, as shown by a black arrow or a white arrow in FIG. 11, the cam ring 2 is swung in a required direction to change the volume in the pump chamber 4, and on the pump discharge side as shown in the flow rate characteristic of FIG. The discharge flow rate can be controlled in accordance with the flow rate. Further, the flow rate control can be performed such that the flow rate on the discharge side is raised to a predetermined flow rate and maintained in accordance with the increase in the pump rotational speed, and the flow rate is decreased in the high rotational speed range of the pump.

  FIG. 11 described above shows a state from the region A to the region B in FIG. 12. When the pump rotation speed exceeds a certain value, the fluid pressure difference on the downstream side of the variable metering restrictor 12 increases, and as a result, the cam ring 2 swings to the right (in the direction indicated by the black arrow) in the figure, and when the variable metering throttle 12 is throttled, the discharge flow rate from the pump decreases according to the throttle amount, and in the region C at the minimum throttle position. As shown, a constant flow rate is maintained.

  Further, the control valve 10 is operated when the differential pressure on the downstream side of the variable metering throttle 12 becomes a predetermined value or more during a load action caused by the operation of a pressure fluid utilization device (indicated by PS in the figure). The fluid pressure P1 upstream of the variable metering restrictor 12 is introduced as a control pressure into the fluid pressure chamber 5 on the high pressure side outside the cam ring 2, and operates to prevent the cam ring 2 from swinging.

  The pump body 1 is provided with a pump suction side passage 14 extending from the tank T through the low pressure chamber of the spool type control valve 10 to the pump suction side region 4A of the pump chamber 4. The pump discharge side passage 13 pumps pressure fluid to the pump suction side (or the tank T side) via the pump suction side passage 14 when the fluid pressure on the pump discharge side becomes a predetermined pressure or more. A direct-acting relief valve 15 is provided as a pressure control valve at a position for relief on the side (tank T side).

In the variable displacement pump having the above-described structure, the fluid pressure on the downstream side of the variable metering restrictor 12 is applied to the second fluid pressure chamber 6 among the pair of fluid pressure chambers 5 and 6 for swinging the cam ring 2. It is structured to be introduced directly. That is, a variable metering throttle 12 is formed by a hole 12a provided in the side wall on the pump body 1 side constituting the second fluid pressure chamber 6 and the outer peripheral edge of the cam ring 2 that swings. It is fed to the pump discharge side passage 13 through the fluid pressure chamber 6.
JP-A-5-278622 Japanese Patent Laid-Open No. 6-200883 JP-A-7-243385 Japanese Patent Laid-Open No. 8-200239

  In the conventional variable displacement pump having the structure as described above, the cam ring 2 is attached to the pressures of the first and second fluid pressure chambers 5 and 6 and the compression coil spring 2b provided in the second fluid pressure chamber 6. The oscillating motion is controlled according to the increase / decrease of the supply flow rate of the fluid according to the pump rotation speed, and the pump capacity is controlled to be a required size. There is a problem in controlling.

  For example, the first fluid pressure chamber 5 into which the fluid pressure on the upstream side of the variable metering restrictor 12 is introduced by the control valve 10 when the pump reaches a high rotation range is partially connected via a passage 5a having a restrictor. Therefore, when the cam ring 2 swings to the first fluid pressure chamber 5 side, a required braking force is applied to the cam ring 2 by the damper function of the throttle portion of the passage 5a. Can act.

  However, the second fluid pressure chamber 6 is only provided with a compression coil spring 2b, and has a damper function for applying a braking force to the cam ring 2 as in the first fluid pressure chamber 5 side described above. Is not provided. For this reason, when the cam ring 2 swings toward the second fluid pressure chamber 6, the elastic force due to the bending of the spring 2b acts to some extent, but the braking force due to the damper function cannot be applied. Therefore, the swinging operation of the cam ring 2 toward the first and second fluid pressure chambers 5 and 6 tends to be unstable. And it is inevitable that the cam ring 2 vibrates or pulsates in the fluid pressure on the pump discharge side.

  That is, the fluid pressure on the pump discharge side flows as a jet from the hole 12a opened in the second fluid pressure chamber 6, and the cam ring 2 vibrates when it is opened and closed at the outer edge of the cam ring 2. In addition, by opening and closing the jet flow from the hole 12a at the outer edge of the cam ring 2, the pulsation increases on the pump discharge side.

  If such vibration or pulsation occurs, there is a possibility that the steering force fluctuates or noise such as fluid noise increases in the power steering apparatus, and some kind of problem that can solve such a problem. It is hoped that measures will be taken.

  The present invention has been made in view of such circumstances, and the braking force by the damper function in both the first and second fluid pressure chambers that controls the movement of the cam ring that swings in the pump in a required state. The purpose of this invention is to obtain a variable displacement pump that can reduce the vibration of the cam ring and the pulsation caused by the fluid pressure on the discharge side, which have been problems in the past, and can solve the noise problem. .

  In order to achieve this object, a variable displacement pump according to the present invention includes a cam ring that is disposed in a state where the rotor is biased toward one side and forms a pump chamber with a portion near the other side of the rotor. A pump body having an internal space for swingably supporting the cam ring, an urging means for urging the cam ring in the pump body in a direction maximizing a pump capacity from the pump chamber, and the pump body The first and second fluid pressure chambers that are dividedly formed between the inner space of the cam ring and the outer peripheral portion of the cam ring via a sealing means, and into which the fluid pressure that swings the cam ring is guided, are discharged from the pump chamber. A spool type control valve which is operated by a fluid pressure on the downstream side and controls the swinging of the cam ring. In the displacement pump, the metering restrictor is a fixed metering restrictor provided in a part of the discharge side passage, and is a part of the discharge side passage, provided in parallel with the fixed metering restrictor, A high-pressure side in which the upstream pressure of the metering throttle is introduced among the pressure chambers formed on both sides of the control valve, with a variable metering throttle provided to open and close by swinging of the cam ring Among the pressure restriction chambers formed on both sides of the control valve and the damper restriction portion provided in the flow path connecting the first chamber and the first fluid pressure chamber, the downstream pressure of the metering restriction is introduced. And a damper throttle portion provided in a flow path connecting the spring chamber for accommodating the compression coil spring that presses the spool and the second fluid pressure chamber. .

  As described above, according to the variable displacement pump according to the present invention, the fixed metering restrictor and the variable metering restrictor are provided in the discharge side passage system branched into two systems, and the first is formed on both sides of the cam ring. Since the damper function is added to the second fluid pressure chamber, the damper function can be appropriately applied in both the swinging directions of the cam ring, and the vibration during the swinging of the cam ring can be appropriately damped. At the same time, the pulsation on the pump discharge side can be improved. Therefore, it is possible to reduce noise that has been a problem in the past.

  In addition, according to the present invention, when configuring a pump having a drooping type flow rate characteristic, a two-pump discharge side passage structure that passes through a fixed metering throttle and a variable metering throttle is employed. It is possible to easily adjust or change the characteristics of the supply flow rate with respect to the rotation speed of the pump.

  1 to 7 are views showing a first embodiment of a variable displacement pump according to the present invention. Here, in the first embodiment, the vane pump according to the present invention is a vane type oil pump serving as a hydraulic pressure generation source of the power steering apparatus, and the discharge flow rate is increased as the rotation speed of the pump increases. A description will be given of a pump having a so-called drooping characteristic that a predetermined flow rate is smaller than the maximum discharge flow rate and the flow rate is maintained. Moreover, in this embodiment, as shown in FIG. 2, the example provided with the direct acting type relief valve is shown.

  1 and 2, the vane type variable displacement pump generally indicated by reference numeral 20 includes a front body 21 and a rear body 22 that constitute a pump body. As shown in FIGS. 1 and 2, the front body 21 has a substantially cup shape as a whole, and a storage space 24 for storing and arranging a pump component 23 as a pump cartridge is formed therein. The rear body 22 is combined and integrally assembled so as to close the open ends of 24. The front body 21 has bearings 26a and 26b (26a on the front body 21 side and 26b on the rear body 22 side) in a state where a drive shaft 26 for rotating and driving the rotor 25 constituting the pump component 23 from the outside passes through. Is disposed rotatably. 26c is an oil seal.

Reference numeral 27 denotes a cam ring. The cam ring 27 has an inner cam surface 27 a that is fitted on the outer periphery of the rotor 25 having a vane 25 a, and a pump chamber 28 is provided between the inner cam surface 27 a and the rotor 25. Is forming. In addition, the cam ring 27 can be moved and displaced within an adapter ring 29 that is fitted in the inner wall portion of the storage space 24 so that the volume (pump capacity) of the pump chamber 28 can be varied as will be described later. Has been placed.
The adapter ring 29 is for holding the cam ring 27 in the housing space 24 of the body 21 so as to be movable and displaceable.

  2 and 3, reference numeral 30 is a pressure plate, and this pressure plate 30 is pressed against the front body 21 side of the pump cartridge (pump component 23) composed of the rotor 25, cam ring 27 and adapter ring 29 described above. And stacked. Further, the end surface of the rear body 22 is pressed against the opposite side surface of the pump cartridge as a side plate, and a required assembly state is obtained by integrally assembling the front body 21 and the rear body 22. The pump component 23 is constituted by these members.

  The pressure plate 30 and the rear body 22 serving as a side plate stacked on the pressure plate 30 via a cam ring 27 are positioned in the rotational direction by a swing fulcrum pin 31 described later or an appropriate detent means (not shown). It is assembled and fixed integrally in the state. The swing fulcrum pin 31 functions as a shaft support portion and a positioning pin for enabling the cam ring 27 to swing, and also has a sealing function for defining a fluid pressure chamber for swinging the cam ring 27.

  Reference numeral 33 denotes a pump discharge side pressure chamber formed on the bottom side of the storage space 24 of the front body 21, and the pump discharge side pressure acts on the pressure plate 30 by the pressure chamber 33. Reference numeral 34 denotes a pump discharge side opening formed in the pressure plate 30 so as to guide the pressure oil from the pump chamber 28 to the pump discharge side pressure chamber 33.

  Although not shown, a pump suction side opening 35 (showing an opening position with respect to the pump chamber 28 in FIG. 1) is provided in a part of the rear body 22, and the suction side fluid flowing from the tank T through the suction side opening 35. Passes through a pump suction side passage (both not shown) formed in the body 22 from a suction side port provided in a part of the rear body 22, and enters the pump chamber 28 from a pump suction side opening 35 that opens at an end surface of the rear body 22. To be supplied. In FIG. 3, reference numeral 35 a denotes a groove facing the pump suction side opening 35.

  Reference numeral 40 denotes a control valve comprising a valve hole 41 and a spool 42 formed above the front body 21 in a direction perpendicular to the shaft 26. By means of this control valve 40, first and second fluid pressure chambers 43, 44 which are formed separately on both sides of the cam ring 27 in the adapter ring 29 by the rocking fulcrum pin 31 and a sealing material 45 provided at the axial target position. It is comprised so that the fluid pressure introduced into may be controlled.

Although not shown, a passage 51 (shown by a broken line in FIG. 1) from the pump discharge side pressure chamber 33 is connected to one end side of the valve hole 41.
A passage 52 is formed along the axial direction of the spool 42. A fixed metering restrictor 53 is provided on a part of the passage 52, here on the spring chamber 54 side having a spring 54 a provided on the other end side of the spool 42. A pump discharge side port 55 is formed at the outer end of the spring chamber 54 via a passage hole 55a, and feeds pressure oil to a power steering device as a hydraulic equipment (not shown).

  As described above, the spool 42 is configured to introduce the fluid pressure on the downstream side of the fixed metering restrictor 53 to the first and second fluid pressure chambers 43 and 44 according to the number of rotations of the pump. Has been. The fluid pressure on the upstream side of the fixed metering restrictor 53 is configured to be introduced through a passage hole 56 that opens toward one end in the valve hole 41 of the control valve 40. The passage hole 56 is blocked by a land 42a in an initial state in which the spool 42 is located on the left side in FIG. 1, and at this time, a pump suction opening in this portion through an annular groove in the center of the spool 42. The side (pressure of the tank T) is introduced through a gap passage 42b between the land 42a and the small diameter portion.

Further, as the spool 42 moves to the left in the drawing due to the differential pressure of the downstream fluid pressure above the fixed metering restrictor 53 and a variable metering restrictor described later, the spool 42 is separated from the pump suction side described above. The upstream fluid pressure is introduced into the first fluid pressure chamber 43 through the passage hole 56. Control of the supply fluid pressure to the passage hole 56 by the control valve 40 is as shown in FIGS. 6A, 6B, 7A, and 7B corresponding to FIG.
A part of the passage hole 56 is configured as a damper throttle 56a.

  On the other hand, the fluid pressure on the downstream side of the fixed metering throttle 53 acts on the second fluid pressure chamber 44 through a passage hole 57 that opens to a part of the discharge port 55 and functions as a damper throttle.

  A part of the pump discharge side passage, in this embodiment, a passage by three small holes 58 formed in the pressure plate 30 is formed separately from the discharge side passage 51 from the pump discharge side pressure chamber 33. The second fluid pressure chamber 44 is open. The variable metering diaphragm 59 is formed by the open ends of the small holes 58 and the peripheral edge of the outer peripheral edge of the cam ring 27. The fluid pressure passing through the variable metering restrictor 59 passes through the second fluid pressure chamber 44 and the notch portion of the adapter ring 29 and opens from the passage hole 57 to the discharge port 55.

  1 and 2, reference numeral 61 denotes a compression coil spring that biases the cam ring 27, and the compression coil spring 61 is disposed in a circular space facing a part of the second fluid pressure chamber 44. The circular space is formed in a cylindrical portion of a plug member 63 screwed so as to close a hole portion 62 formed from the outside of the front body 21, and a plunger damper having one end opened in the cylindrical portion. 64 is in contact with the outer peripheral portion of the cam ring 27 by the elastic force of the spring 61, and is always configured to apply a biasing force by the spring 61 to the cam ring 27 regardless of the swinging motion of the cam ring 27. Yes. In the figure, reference numeral 64a denotes an O-ring as a sealing material that seals between the outer peripheral portion of the plunger damper 64 and the tubular portion of the plug member 63.

A part of the plunger damper 64 is formed with a damper throttle 65 having a small hole that communicates the inside of the spring 61 and the second fluid pressure chamber 44. Instead of the damper aperture 65, a bleed hole 63a that opens to the atmosphere is provided in a part of the plug member 63, and a damper function is obtained by the spring 61 and the plunger damper 64 by the function of the bleed hole 63a. You may comprise.
The damper diaphragm 65 described above may be formed with a hole diameter of about 0.6 mm, for example. Further, an O-ring is interposed on the outer periphery of the plunger damper 64 and seals this portion. This O-ring also has an effect of suppressing the vibration of the cam ring 27.

2 is a relief valve provided in a part of the rear body 22, and is connected to a part of the pump discharge side passage by opening the second fluid pressure chamber 44, and the fluid pressure on the pump discharge side is adjusted to the rear body. 22 is configured to be able to escape to the pump suction side via a passage 48a provided in the motor 22.
In the vane type variable displacement pump 20 as described above, configurations other than those described above are as conventionally known, and a specific description thereof is omitted here.

  According to the variable displacement pump 20 having the structure described above, the discharge-side passages 51, 52, 55a, 58, 57 from the pump discharge-side pressure chamber 33 are provided with a fixed metering restrictor 53 and a variable metering restrictor 59. It is a system. Further, the control pressure controlled by the control valve 40 based on the fluid pressure on the upstream side of the metering throttles 53 and 59 and the fluid pressure (tank pressure) on the pump suction side is one side in the swing direction of the cam ring 27. 1 fluid pressure chamber 43. On the other hand, the fluid pressure on the downstream side of the metering throttles 53 and 59 is introduced into the second fluid pressure chamber 44 on the other side in the swing direction of the cam ring 27.

  According to such a structure, the cam ring 27 is swung in a required state in accordance with the magnitude of the flow rate on the pump discharge side, and the supply flow rate to the pump discharge side is a constant amount or the pump rotation speed as shown in FIG. It can be maintained at an arbitrary amount below a certain amount with an increase in.

  Here, in FIG. 5, when the pump rotation reaches the middle speed range from the low speed, the supply flow rate changes as indicated by ab and c. At this time, as shown in FIGS. 6A and 6B, the control valve 40 is pumped through the first fluid pressure chamber 43 via the passage hole 56 and the damper throttle 56a when the pump rotation is slow. The fluid pressure (tank pressure) on the suction side is guided, and a constant amount determined by the differential pressure obtained by the throttle amounts of both metering throttles 53 and 59 is maintained.

  When the pump rotational speed reaches the high speed range, the spool 42 of the control valve 40 moves left as shown in FIGS. 7A and 7B, and the passage hole 56 to the first fluid pressure chamber 43 is metered by the throttle. Switch to fluid pressure upstream of 53,59. Accordingly, the cam ring 27 swings toward the second fluid pressure chamber 44 provided with the spring 61, whereby the variable metering restrictor 59 is gradually closed.

  When the small hole 58 constituting the variable metering restrictor 59 is completely closed by the outer edge of the cam ring 27, the control valve 40 is controlled by the differential pressure on the downstream side of the fixed metering restrictor 53. The determined flow rate can be maintained (indicated by de in FIG. 5). Such a flow rate characteristic is a so-called drooping characteristic.

  Here, when the relationship between the small hole 58 constituting the variable metering restrictor 59 and the opening amount due to the displacement of the outer edge portion of the cam ring 27 is changed, the flow rate characteristic is changed as shown by a one-dot chain line in FIG. Can do.

  In this embodiment, the three small holes 58 described above are used, and the variable metering diaphragm 59 formed thereby is smaller than the opening amount of a variable diaphragm of a type widely known in the past. The variable metering diaphragm 59 is not limited to the three small holes 58 that are opened and closed at the outer edge of the cam ring 2 as shown in FIGS. 1 to 4 described above, but includes one or more small holes. It can be constituted by a hole 58.

The swing amount of the cam ring 27 is, for example, about 1.9 mm in the current product, and if a plurality of small holes 58 (the total opening amount is equivalent to one) is provided, the diaphragm is reduced by a small displacement of the cam ring 27. Since it can be opened and closed, it is convenient in setting pump performance. In this embodiment, for example, as the three small holes 58, one small hole 58 having a diameter of 1 mm (the front end side in the displacement direction of the cam ring 27) and two small holes 58 having a diameter of 1.1 mm (the rear of the displacement direction). However, the present invention is not limited to this. As described above, in order to change the characteristics, the diameter of these holes can be changed as appropriate, the opening position can be shifted so as to line up with the moving direction of the cam ring 27, or the opening amount can be changed along this moving direction. Good.
Further, the small hole 58 is not limited to a circular shape, and may be a square hole, a modified hole, or the like.

  Further, the first and second fluid pressure chambers 43 and 44 for swinging the cam ring 27 are connected to the control valve 40 and the pump discharge side passage (discharge side port 55) via damper throttles 56a and 57. From the above, when the cam ring 27 swings with the pressure difference of the fluid pressure on the upstream and downstream of the metering throttles 53 and 59 in the middle of the discharge side passage due to increase or decrease of the pump rotation speed, A required braking force can be applied in the swing direction.

  Here, the damper diaphragm 56a described above may have a hole diameter of about 1.2 mm, for example. Further, the passage hole 57 serving as a damper throttle located on the downstream side of the variable metering throttle 59 may be formed with a hole diameter of about 2 mm, for example.

  According to such a structure, an appropriate braking force can be applied when swinging toward the first and second fluid pressure chambers 43 and 44, so that the cam ring 27 vibrates or pulsates on the pump discharge side. The cam ring 27 can be smoothly swung in a required state so as not to occur. Note that the above-described passage hole 57 serving as the damper throttle is only required to be downstream of the fixed metering throttle 53, and can be communicated with the spring chamber 54 side of the control valve 40, for example.

In this embodiment, the urging force of the compression coil spring 61, which is the urging means, is applied to the cam ring via the plunger damper 62. Therefore, the urging force and the braking force are appropriately applied to the cam ring 27 to smoothly Can be obtained more effectively.
Here, in order to appropriately control the movement of the plunger damper 62, the air bleed hole 63a is provided, and the space on the side where the spring 61 is provided is opened to the atmosphere through a predetermined restriction, thereby further improving the effect. Can be improved.

FIG. 8 shows a case where the variable displacement pump 20 in the first embodiment described above is changed from the drooping type to the constant flow type, and is a side sectional view corresponding to FIG.
In this embodiment, unlike the above-described drooping type, there is no need for a variable metering throttle, so the small hole 58 that opens to the second fluid pressure chamber 44 in the pressure plate 30 is omitted. Further, the fixed metering throttle 53 of the spool 42 in the control valve 40 may be formed with an appropriate throttle diameter in accordance with required pump characteristics.

  Although not shown, a passage hole 57 for guiding the fluid pressure downstream of the fixed metering throttle 53 provided in the spool 42 of the control valve 40 to the second fluid pressure chamber 44 is formed with a diameter that functions as a throttle portion. Or it is good to provide an aperture part in the part.

  Of course, even with such a structure, the damper effect on the cam ring 27 can be exerted even on the second fluid pressure chamber 44 side by the plunger damper 64 and the passage hole 57 serving as a damper throttle. Therefore, even with the pump having such a structure, the vibration during the swinging operation of the cam ring 27 can be attenuated, the pulsation on the pump discharge side can be reduced, and the noise can be suppressed, as in the above-described embodiment.

  In the structure of this embodiment, in the variable displacement pump 20, parts other than those constituting the variable metering restrictor are shared between the drooping type and the constant flow type. There is an advantage that the response to the change of the specification can be simplified.

  9 and 10 show a second embodiment of the variable displacement pump 20 according to the present invention having a drooping type flow rate characteristic. In these drawings, the same or corresponding parts as those in FIGS. 1 to 7 described above are denoted by the same reference numerals and detailed description thereof is omitted.

  Similarly to the first embodiment, the second embodiment also has a variable capacity having a so-called drooping characteristic in which the flow rate on the pump discharge side is reduced from the maximum flow rate as the rotational speed increases. It is a shape pump.

  In this embodiment, unlike the first embodiment described above, the variable metering diaphragm 70 is provided by utilizing the movement of the plunger damper 64 that is interlocked with the swing of the cam ring 27.

  More specifically, as shown in FIGS. 9 and 10, the pump body 21 is provided with a passage 71 branched from the discharge side passage 51 from the pump discharge side pressure chamber 33 to the control valve 40 side. The passage 71 is recessed in the outer peripheral portion of the plunger damper 64 through a passage hole 73 formed in a radial direction from a passage portion 72 formed by a space between the plug member 63 accommodating the compression coil spring 61 and the body 21. It communicates with the outer end side of the annular groove 74 provided.

  The inner end side of the annular groove 74 is formed from a passage portion 76 formed of a space formed in a part of the outer periphery of the tubular portion of the plug member 63 via a small-diameter hole 75 in a radial direction different from the passage hole 73. 21 communicates with the pump discharge side port 55 through a passage hole 77 formed in 21.

  The variable metering diaphragm 70 is formed by the annular groove 74 and the small diameter hole 75 of the plunger damper 64 described above. That is, when the plunger damper 64 moves as the cam ring 27 swings, the small-diameter hole 75 is gradually closed, so that the variable metering restrictor 70 is partitioned from the second fluid pressure chamber 44. Is formed.

  Here, as for the small-diameter hole 75, the selection of the hole diameter becomes even more free as compared with the case where the variable metering diaphragm is opened and closed by the displacement accompanying the swing of the cam ring 27. That is, the hole diameter can be made smaller than the small hole in the first embodiment described above, and the selection range of the supply flow rate characteristic with respect to the rotation speed of the pump is widened. In addition, the damper effect can be more effectively caused.

  Further, in such a structure, even if the cam ring 27 vibrates, the influence thereof does not directly affect the variable metering diaphragm 70, so that the occurrence of pulsation can be reduced. Such an advantage becomes even more effective by providing the variable metering restrictor 70 at a position separated from the second fluid pressure chamber 44 as described above.

  Further, in the above-described embodiment, the flow rate characteristic of the pump is changed by changing the small hole 58 provided in the pressure plate 30, and therefore there is a problem that the pressure plate cannot be shared. In this embodiment, this problem is eliminated, and the pressure plate 30 can be used as a standard part.

  Further, in the second embodiment, unlike the first embodiment described above, the pump flow characteristic is changed only by replacing the plug member 63 and the plunger damper 64 for assembling the spring 61. There is an advantage that the disassembling work of the main body is not necessary.

The present invention is not limited to the above-described embodiment structure, and the shape, structure, and the like of each part of the variable displacement pump 20 can be freely modified and changed as appropriate, and various modifications can be considered.
In each of the above-described embodiments, the fixed metering diaphragm 53 and the variable metering diaphragm 59 are simply described as “throttles”, but this is a choke even if such a throttle portion is an orifice. Because it is good.

  As described above, according to the variable displacement pump according to the present invention, the fixed metering restrictor and the variable metering restrictor are provided in the discharge side passage system branched into two systems, and the first is formed on both sides of the cam ring. Since the damper function is added to the second fluid pressure chamber, the damper function can be appropriately applied in both the swinging directions of the cam ring, and the vibration during the swinging of the cam ring can be appropriately damped. At the same time, the pulsation on the pump discharge side can be improved. Therefore, it is possible to reduce noise that has been a problem in the past.

  In addition, according to the present invention, when configuring a pump having a drooping type flow rate characteristic, a two-pump discharge side passage structure that passes through a fixed metering throttle and a variable metering throttle is employed. It is possible to easily adjust or change the characteristics of the supply flow rate with respect to the rotation speed of the pump.

Further, according to the present invention, pulsation can be reduced by providing one system of the discharge side passage of the pump so as to pass through the control valve.
Moreover, the variable displacement pump having the above-described advantages can be easily configured with the same size as the conventional one.

  Further, according to the present invention, since the variable metering throttle is provided in the plunger damper portion, vibration during the swinging operation of the cam ring is not directly transmitted to the variable metering throttle, so that the pressure fluid passing through the variable metering throttle Occurrence of pulsation can be reduced. Moreover, since such a plunger damper can be easily added as required, a conventional type pump can be easily modified.

  For example, the embodiment described above is expressed in the form described in the scope of claims.

A cam ring that forms a pump chamber between the rotor and a portion closer to the other side of the rotor, and a rocking fulcrum pin provided on a part of the outer peripheral surface of the cam ring. A pump body having an internal space that is swingably supported as a fulcrum; an urging means for urging the cam ring in the pump body in a direction that maximizes a pump capacity from the pump chamber; and an interior of the pump body Pressures discharged from the pump chamber, and first and second fluid pressure chambers that are dividedly formed between the outer peripheral portion of the cam ring in the space and through which a fluid pressure that swings the cam ring is guided. A variable displacement potentiometer equipped with a spool type control valve which is operated by a fluid pressure on the downstream side above a metering throttle provided in the middle of the fluid discharge side passage and which controls the swing of the cam ring. The cam ring is swung by a fixed metering throttle provided in a part of the discharge side passage and a part of the passage branched from the discharge side passage upstream of the fixed metering throttle. And a variable metering throttle provided so as to be opened and closed by the control valve, and the fluid pressure on the upstream side of the fixed metering throttle and the fixed metering throttle is controlled by the control valve to control the first metering through the damper throttle. A flow path for introducing the fluid pressure chamber into the first fluid pressure chamber, and a flow path for introducing the fluid pressure downstream of the fixed metering throttle and the variable metering throttle into the second fluid pressure chamber via the damper throttle portion. A variable displacement pump characterized by that.
This variable displacement pump has been described with reference to FIGS.

The variable displacement pump according to paragraph 0073, wherein the discharge side passage is connected to one end of a valve hole that slidably supports the spool of the control valve, and the discharge side passage is formed in the spool along the axial direction. Forming a passage hole to be configured, connecting the other end of the valve hole to a pump discharge side port provided in the pump body, and providing the fixed metering throttle in a part of the passage hole in the spool. A variable displacement pump.
This variable displacement pump has been described with reference to FIGS.

In the variable displacement pump according to Paragraph 0073 or Paragraph 0074, the variable passage pump may be configured such that the branch passage is opened by an opening that is opened and closed at a side wall portion of the second fluid pressure chamber at an outer edge portion of the cam ring. A variable displacement pump characterized by comprising a metering throttle.
This variable displacement pump has been described with reference to FIGS.

The variable displacement pump according to paragraph 0075, wherein the opening of the branch passage to the second fluid pressure chamber is configured by a plurality of small holes.
This variable displacement pump has been described with reference to FIGS.

In the variable displacement pump according to Paragraph 0073, Paragraph 0074, Paragraph 0075 or Paragraph 0076, a plunger damper having the urging means provided therein is provided in the second fluid pressure chamber, and the plunger damper is disposed on the cam ring side. A variable displacement pump characterized in that it is in contact with the part.
This variable displacement pump has been described with reference to FIGS.

In the variable displacement pump according to paragraphs 0073 and 0074, a plunger damper having the urging means provided therein is provided in the second fluid pressure chamber, and the plunger damper is brought into contact with a side portion of the cam ring. A variable metering throttle that opens and closes a part of the branch passage by a movement of a plunger damper that moves in accordance with the swinging of the cam ring is provided at a position separated from the second fluid pressure chamber. Variable displacement pump.
This variable displacement pump has been described with reference to FIGS.

1 shows a first embodiment when a variable displacement pump according to the present invention has a drooping type flow rate characteristic, and shows a cross section of a main part of the pump in a state of low rotation (immediately before ab in FIG. 5). FIG. It is sectional drawing of the one side cut | disconnected by the II-II line of FIG. FIG. 3 is a side view of a pressure plate disposed on one side of a cam ring in the variable displacement pump of FIGS. 1 and 2. It is a figure for demonstrating the relationship by rocking | fluctuation operation | movement of the three small holes drilled in the pressure plate, and the outer peripheral part of a cam ring. FIG. 3 is a characteristic diagram for explaining a supply flow rate with respect to a pump rotation speed in the variable displacement pump of FIGS. 1 and 2. (A) is sectional drawing of the control valve part for demonstrating the control pressure to the 1st fluid pressure chamber by the control valve at the time of low rotation of a pump (just before ab of FIG. 5), (b) is the It is a principal part enlarged view. (A) is sectional drawing of the control valve part for demonstrating the control pressure to the 1st fluid pressure chamber by the control valve at the time of low rotation of a pump (be of FIG. 5), (b) is the principal part. It is an enlarged view. FIG. 3 is a cross-sectional view corresponding to FIG. 2 for explaining a pump structure when the variable displacement pump having a drooping type flow rate characteristic in FIGS. 1 and 2 is used as a constant flow rate type. The variable displacement pump according to the present invention shows a second embodiment in the case of having a drooping type flow rate characteristic, (a) is a cross-sectional view of the main part of the pump in a state of low rotation, (b) is It is the principal part enlarged view. It is sectional drawing of the one side cut | disconnected by the XX line of Fig.9 (a). It is operation | movement explanatory drawing in the state at the time of the low rotation which shows the conventional variable displacement pump. It is a characteristic view explaining the supply flow rate with respect to the pump rotation speed in the pump of FIG.

Explanation of symbols

  20 ... Vane type variable displacement pump (variable displacement vane pump), 21 ... Front body (pump body), 22 ... Rear body (pump body), 23 ... Pump components, 24 ... Storage space, 25 ... Rotor, 25a ... Vane, 26 ... Drive shaft (rotating shaft), 27 ... Cam ring, 28 ... Pump chamber, 29 ... Adapter ring, 30 ... Pressure plate, 31 ... Oscillating fulcrum pin, 33 ... Pump discharge side pressure chamber, 34 ... Pump discharge side Opening 35, pump suction side opening, 40 ... spool type control valve, 41 ... valve hole, 42 ... spool, 42a ... land portion, 42b ... gap passage, 43, 44 ... first and second fluid pressure chambers, 45 ... Sealing material, 48 ... Relief valve, 51 ... Discharge side passage, 53 ... Fixed metering throttle, 55 ... Pump discharge side port, 55a ... Passage 56 ... passage hole, 56a ... damper throttle, 57 ... passage hole (damper throttle), 58 ... small hole (variable metering throttle), 59 ... variable metering throttle, 61 ... compression coil spring (biasing means), 62 ... 63, plug member, 63a ... bleed hole, 64 ... plunger damper, 64a ... O-ring, 64b ... opening, 65 ... damper throttle, 70 ... variable metering throttle, 71 ... branch passage on the pump discharge side, 72 ... A passage part, 73 ... a passage hole, 74 ... an annular groove, 75 ... a small diameter hole, 76 ... a passage part, 77 ... a passage hole, 78 ... a passage hole serving as a damper throttle part, 79 ... a damper throttle, T ... a tank.

Claims (1)

A cam ring which is arranged in a state where the rotor is biased toward one side and forms a pump chamber with a portion near the other side of the rotor;
A pump body having an internal space for swingably supporting the cam ring;
A biasing means for biasing the cam ring in the pump body in a direction that maximizes a pump capacity from the pump chamber;
A first fluid pressure chamber and a second fluid pressure chamber, which are dividedly formed between the outer periphery of the cam ring in the internal space of the pump body and through which a fluid pressure for swinging the cam ring is guided via a sealing means;
A variable valve equipped with a spool-type control valve that is operated by a fluid pressure on the downstream side and controls the swing of the cam ring above a metering throttle provided in the middle of the discharge side passage of the pressure fluid discharged from the pump chamber. For displacement pumps,
A fixed metering throttle provided in a part of the discharge side passage,
A part of the discharge-side passage, which is provided in parallel with the fixed metering throttle, and is configured by a variable metering throttle provided to be opened and closed by swinging of the cam ring,
Among the pressure chambers formed on both sides of the control valve, a damper throttle provided in a flow path connecting the high pressure side chamber into which the upstream pressure of the metering throttle is introduced and the first fluid pressure chamber And
Of the pressure chambers formed on both sides of the control valve, a pressure downstream of the metering throttle is introduced, and a spring chamber that houses a compression coil spring that presses the spool, and the second fluid pressure chamber A variable displacement pump comprising a damper throttle portion provided in a flow path to be connected.

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