WO2014129311A1 - 可変容量型ベーンポンプ - Google Patents
可変容量型ベーンポンプ Download PDFInfo
- Publication number
- WO2014129311A1 WO2014129311A1 PCT/JP2014/052682 JP2014052682W WO2014129311A1 WO 2014129311 A1 WO2014129311 A1 WO 2014129311A1 JP 2014052682 W JP2014052682 W JP 2014052682W WO 2014129311 A1 WO2014129311 A1 WO 2014129311A1
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- WIPO (PCT)
- Prior art keywords
- rotor
- suction port
- angle
- pump
- variable displacement
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
- F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
- F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/32—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
- F04C2/332—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2250/00—Geometry
- F04C2250/10—Geometry of the inlet or outlet
Definitions
- the present invention relates to a variable displacement vane pump used as a fluid pressure supply source.
- JP2003-97454A describes a variable displacement vane pump.
- the variable displacement vane pump includes a rotor in which the vane is accommodated, a cam ring having an inner peripheral cam surface with which the tip of the vane is slidably contacted and swinging around a support pin, and a slidable contact with one axial end of the rotor.
- a side plate has a suction port for guiding the working fluid to the pump chamber defined between the rotor and the cam ring, and a discharge port for guiding the working fluid discharged from the pump chamber in an arc shape. It is formed.
- a suction section in which the pump chamber communicates with the suction port, a discharge section in which the pump chamber communicates with the discharge port, and a transition section located between the suction port and the discharge port are formed in the side plate. .
- the pump chamber moves to these sections in the order of the suction section, the transition section, the discharge section, and the transition section according to the rotation of the rotor.
- the pump chamber located in one transition section communicates with the discharge port, and at the same time, the pump chamber located in the other transition section communicates with the suction port.
- An object of the present invention is to provide a variable displacement vane pump capable of suppressing generation of noise due to pressure fluctuations of a working fluid discharged from a discharge port.
- a variable displacement vane pump used as a fluid pressure supply source, the rotor being driven to rotate by the power of the power source, and a plurality of radially formed openings provided on the outer periphery of the rotor.
- the side member provided in contact, the pump chamber defined between the rotor, the cam ring, and the vane adjacent to the side member, and the side member on the region side where the volume of the pump chamber expands as the rotor rotates.
- An arc-shaped suction port that guides the working fluid sucked into the pump chamber and an arc-shaped side member that contracts the volume of the pump chamber as the rotor rotates
- a discharge port that guides the working fluid discharged from the chamber, and the side member includes a first transition section that is a section from the end of the suction port to the start end of the discharge port, and from the end of the discharge port to the start end of the suction port.
- a second transition section, and the angle from the start end to the end of the suction port centered on the rotor is a pressure increase timing at which the pump chamber starts to communicate with the start end of the discharge port from the first transition section.
- There is provided a variable displacement vane pump that is set so as to deviate from the low pressure timing at which the other pump chamber starts to communicate with the starting end of the suction port from the second transition section.
- FIG. 1 is a front view showing a variable displacement vane pump according to an embodiment of the present invention.
- FIG. 2 is a front view showing a state in which the rotor and the vane are arranged on the side plate according to the embodiment of the present invention.
- FIG. 3A is a front view showing the side plate when the number of vanes is an odd number.
- FIG. 3B is a front view showing the side plate when the number of vanes is an odd number.
- FIG. 4A is a front view showing the side plate when the number of vanes is an even number.
- FIG. 4B is a front view showing the side plate when the number of vanes is an even number.
- FIG. 5 is a front view showing a state in which the rotor and the vanes are arranged on the side plate in the comparative example.
- FIG. 1 is a front view of a variable displacement vane pump 100 (hereinafter simply referred to as “vane pump 100”) in the present embodiment, and is a view seen from the axial direction of the shaft 1 with the pump cover removed.
- vane pump 100 variable displacement vane pump 100
- the vane pump 100 is used as a fluid pressure supply source for a fluid pressure device mounted on a vehicle, for example, a power steering device or a continuously variable transmission.
- the working fluid is oil or other water-soluble alternative liquid.
- the vane pump 100 is driven by, for example, an engine (not shown) and the like, and the rotor 2 connected to the shaft 1 rotates in a clockwise direction as indicated by an arrow in FIG.
- the vane pump 100 is provided with a pump body 3, a shaft 1 rotatably supported by the pump body 3, a rotor 2 connected to the shaft 1 and driven to rotate, and a reciprocating motion in the radial direction with respect to the rotor 2.
- a plurality of slits 2a having openings on the outer peripheral surface are radially formed at predetermined intervals.
- the vane 4 is slidably inserted into each slit 2a.
- a back pressure chamber 2b is formed which is partitioned by the base end portion of the vane 4 which is the end opposite to the direction in which the vane 4 protrudes from the slit 2a and into which the working fluid is guided.
- the vane 4 is pressed in the direction protruding from the slit 2a by the pressure of the back pressure chamber 2b.
- the pump body 3 is formed with a pump housing recess 3 a for housing the adapter ring 6.
- a side plate 20 is disposed on the bottom surface of the pump housing recess 3a so as to come into contact with one side in the axial direction of the rotor 2, the cam ring 5 and the adapter ring 6 (the back side in FIG. 1).
- the opening of the pump housing recess 3a is sealed by a pump cover (not shown) that contacts the other side (front side in FIG. 1) of the rotor 2, the cam ring 5, and the adapter ring 6.
- the pump cover as a side member and the side plate 20 are arranged in a state where both side surfaces of the rotor 2, the cam ring 5 and the adapter ring 6 are sandwiched.
- a pump chamber 7 partitioned by each vane 4 is defined between the rotor 2 and the cam ring 5.
- a through hole 21 (FIG. 3A) into which the shaft 1 is fitted, a suction port 22 that guides the working fluid into the pump chamber 7, A discharge port 23 is formed to take out the working fluid and lead it to the fluid pressure device.
- the suction port 22 and the discharge port 23 are each formed in an arc shape with the through hole 21 as the center.
- a through-hole, a suction port, and a discharge port are formed on the sliding contact surface in sliding contact with the rotor 2 at a position symmetrical to the side plate 20. That is, the suction port of the pump cover communicates with the suction port 22 of the side plate 20 via the pump chamber 7, and the discharge port of the pump cover communicates with the discharge port 23 of the side plate 20 via the pump chamber 7. Yes. Further, the through hole of the pump cover is arranged coaxially with the through hole 21 of the side plate 20. However, when the manufacturing accuracy of the pump cover is low, each port may be set smaller than each port 22, 23 of the side plate 20 so that the port switching timing is determined by the side plate 20.
- the cam ring 5 is an annular member, and has an inner circumferential cam surface 5a with which the front end portion 4a of the vane 4 which is an end portion in the direction in which the vane 4 protrudes from the slit 2a is in sliding contact.
- the cam ring 5 defines a suction region 31 where the volume of the pump chamber 7 expands according to the expansion and contraction of the vane 4 and a discharge region 32 where the volume of the pump chamber 7 contracts.
- the suction port 22 passes through the side plate 20 and communicates with a tank (not shown) through a suction passage (not shown) formed in the pump body 3, and the working fluid of the tank sucks the side plate 20 through the suction passage. It is supplied from the port 22 to the pump chamber 7.
- the discharge port 23 passes through the side plate 20 and communicates with a high-pressure chamber (not shown) formed in the pump body 3.
- the high-pressure chamber communicates with a fluid pressure device (not shown) outside the vane pump 100 through a discharge passage (not shown). That is, the working fluid discharged from the pump chamber 7 is supplied to the fluid pressure device through the discharge port 23, the high pressure chamber, and the discharge passage.
- the adapter ring 6 is housed in the pump housing recess 3 a of the pump body 3.
- a support pin 8 is interposed between the adapter ring 6 and the cam ring 5 and closer to the discharge port 23 than the rotor 2.
- a cam ring 5 is supported by the support pin 8, and the cam ring 5 swings around the support pin 8 inside the adapter ring 6 and is eccentric with respect to the center of the shaft 1.
- a seal groove 6 c is formed on the inner circumference of the adapter ring 6 and on the opposite side of the shaft 1 from the support pin 8.
- a seal material 9 is slidably contacted with the outer peripheral surface of the cam ring 5 when the cam ring 5 swings.
- a first fluid pressure chamber 11 and a second fluid pressure chamber 12 are partitioned by a support pin 8 and a seal material 9.
- the cam ring 5 swings about the support pin 8 as a fulcrum due to the pressure difference between the first fluid pressure chamber 11 and the second fluid pressure chamber 12.
- the amount of eccentricity of the cam ring 5 with respect to the rotor 2 changes, and the discharge capacity of the pump chamber 7 changes.
- the cam ring 5 swings counterclockwise with respect to the support pin 8 in FIG. 1, the eccentric amount of the cam ring 5 with respect to the rotor 2 decreases, and the discharge capacity of the pump chamber 7 decreases.
- the cam ring 5 swings in the clockwise direction of FIG. 1 with respect to the support pin 8, the eccentric amount of the cam ring 5 with respect to the rotor 2 increases, and the discharge capacity of the pump chamber 7 increases.
- the parts 6b are formed to bulge out. That is, the restricting portion 6 a defines the minimum eccentric amount of the cam ring 5 with respect to the rotor 2, and the restricting portion 6 b defines the maximum eccentric amount of the cam ring 5 with respect to the rotor 2.
- the pressure difference between the first fluid pressure chamber 11 and the second fluid pressure chamber 12 is controlled by the control valve 10 that supplies the working fluid pressure to the first fluid pressure chamber 11 and the second fluid pressure chamber 12.
- the control valve 10 controls the working fluid pressure in the first fluid pressure chamber 11 and the second fluid pressure chamber 12 so that the eccentric amount of the cam ring 5 with respect to the rotor 2 decreases as the rotational speed of the rotor 2 increases.
- FIG. 2 is a front view in which the rotor 2 and the vanes 4 are arranged on the side plate 20.
- the side plate 20 is shown in a direction in which the support pins 8 are positioned in the 12 o'clock direction in the drawing.
- a two-dot broken line in FIG. 2 indicates the inner peripheral cam surface 5a of the cam ring 5 when the eccentric amount of the cam ring 5 is maximum.
- the rotor 2 in which the vanes 4 are accommodated is fitted to the shaft 1 fitted to the side plate 20.
- the vane 4 protruding in the radial direction from the rotor 2 is in sliding contact with the inner peripheral cam surface 5 a of the cam ring 5 at the tip end portion 4 a.
- the pump chamber 7 defined between the rotor 2 and the vane 4 adjacent to the cam ring 5 moves in the circumferential direction of the rotor 2 as the rotor 2 rotates, and the volume changes according to the expansion and contraction of the vane 4.
- the pump chamber 7 communicates with the suction port 22, and the working fluid is sucked from the suction port 22 into the pump chamber 7.
- the pump chamber 7 communicates with the discharge port 23 and the working fluid is discharged from the pump chamber 7 through the discharge port 23.
- a predetermined interval is provided between the suction port 22 and the discharge port 23.
- a first transition section 24 is provided between the end 22 a of the suction port 22 and the start end 23 b of the discharge port 23, and a second transition is provided between the end 23 a of the discharge port 23 and the start end 22 b of the suction port 22.
- a section 25 is provided.
- the opening area to the suction port 22 gradually decreases and over the first transition section 24.
- the lap area gradually increases.
- the pump chamber 7 does not communicate with any of the suction port 22 and the discharge port 23, or even if it communicates, the opening area is very small.
- the opening area to the discharge port 23 gradually decreases and over the second transition section 25.
- the lap area gradually increases.
- the pump chamber 7 starts to communicate with the start end 22 b of the suction port 22. That is, the vane 4 on the front side in the circumferential direction of the pump chamber 7 exceeds the start end 22 b of the suction port 22. At this time, since the working fluid in the pump chamber 7 flows out vigorously due to the negative pressure of the suction port 22, the pressure in the pump chamber 7 is reduced (hereinafter, this timing is referred to as “low pressure reduction timing”).
- FIG. 5 is a front view showing a state in which the rotor 2 and the vanes 4 are arranged on the side plate 120 in the comparative example.
- FIG. 5 shows the side plate 120 in the direction in which the support pin 8 is positioned in the 12 o'clock direction in the figure, similarly to FIG. Further, the two-dot broken line in FIG. 5 indicates the inner peripheral cam surface 5a of the cam ring 5 when the eccentric amount of the cam ring 5 is maximum.
- the pump chamber 7 overlaps the first transition section 124 over the entire circumferential direction, and at the same time, the other pump chambers 7 It overlaps with the 2nd transition area 125 over the circumferential direction whole region.
- the pump chamber 7 on the first transition section 124 side communicates with the start end 123b of the discharge port 123 and at the same time the pump chamber 7 on the second transition section 125 side. Communicates with the start end 122 b of the suction port 122. That is, the high pressure timing matches the low pressure timing.
- the pressure distribution is biased, so that the cam ring 5 vibrates at a predetermined cycle. Therefore, the working fluid pressure discharged from the discharge port 123 may fluctuate and noise may occur.
- the suction port 22 is formed so that the pressure increase timing is different from the pressure decrease timing.
- the suction port 22 has an arc shape, and its shape is defined by an angle ⁇ 1 from the start end 22b to the end 22a of the suction port 22 around the rotor 2 (hereinafter referred to as “the angle ⁇ 1 of the suction port 22”). .
- the eccentric amount of the cam ring 5 is the maximum as shown in FIG. 2, but the angle ⁇ 1 of the suction port 22 is the same as the high pressure increasing timing even when the eccentric amount of the cam ring 5 is smaller. It is formed so as to always deviate from the low pressure timing.
- the suction region 31 defined by the cam ring 5 is formed over a range of 180 °, which is a half in the circumferential direction of the inner peripheral cam surface 5a, by setting the angle ⁇ 1 of the suction port 22 to about 180 °, Pump performance can be improved by increasing the suction area and improving the suction performance of the working fluid.
- the discharge port 23 has an arc shape, and the shape thereof is defined according to the angle ⁇ 1 of the suction port 22. Between the end 22a of the suction port 22 and the start end 23b of the discharge port 23 (first transition section 24), an interval substantially corresponding to one chamber of the pump chamber is provided. Similarly, an interval substantially corresponding to one chamber of the pump chamber is also provided between the end 23a of the discharge port 23 and the start end 22b of the suction port 22 (second transition section 25).
- the angle ⁇ 1 of the suction port 22 is set to about 180 °
- the angle ⁇ 2 from the start end 23b to the end 23a of the discharge port 23 (hereinafter referred to as “the angle ⁇ 2 of the discharge port 23”) is the first transition section 24.
- the suction port 22 is set to be smaller than the angle ⁇ 1 by the amount corresponding to the second transition section 25.
- the cam ring 5 swings clockwise about the support pin 8 in FIG. 2 and is eccentric with respect to the center of the rotor 2.
- the inner peripheral cam surface 5a in the second transition section 25 moves from the outer periphery of the discharge port 23 and the suction port 22 to the inner peripheral side, so that the angle range of the second transition section 25 is wide.
- the angle of the second transition section 25 around the rotor 2 is set to be equal to or smaller than the angle of the first transition section 24.
- the angle range of the suction port 22 varies depending on whether the number of vanes 4 accommodated in the rotor 2 is an odd number or an even number.
- FIG. 3A is a diagram showing the minimum angle ⁇ 1min of the suction port 22 when the number of vanes 4 is an odd number.
- FIG. 3B is a diagram illustrating the maximum angle ⁇ 1max of the suction port 22 when the number of vanes 4 is an odd number.
- 3A and 3B show a case where the number of vanes 4 is 11 as an example, but the number of the vanes 4 may be an odd number of 5 or more, such as 9 or 13.
- a position shifted from the vane 4 by 180 ° around the rotor 2 is an intermediate position between the vanes 4 arranged on both sides of the position, that is, an intermediate position of the pump chamber 7. It corresponds to.
- the minimum angle ⁇ 1min of the suction port 22 based on 180 ° is a value obtained by subtracting the angle corresponding to half of the pump chamber 7 and the angle corresponding to the thickness of the vane 4 from 180 °.
- the maximum angle ⁇ 1max of the suction port 22 is a value obtained by adding an angle corresponding to half of the pump chamber 7 and an angle corresponding to the thickness of the vane 4 to 180 °.
- the angle ⁇ 1 of the suction port 22 is 180 ° ⁇ (360 ° / (2 N)) -t ⁇ ⁇ 1 ⁇ 180 ° + (360 ° / (2 ⁇ n)) + t.
- FIG. 4A is a diagram showing the minimum angle ⁇ 1min of the suction port 22 when the number of vanes 4 is an even number.
- FIG. 4B is a diagram illustrating the maximum angle ⁇ 1max of the suction port 22 when the number of vanes 4 is an even number. 4A and 4B show a case where the number of vanes 4 is 10 as an example, but the number of vanes 4 may be an even number of 6 or more, such as 8 or 12.
- another vane 4 is located at a position shifted from the vane 4 by 180 ° about the rotor 2.
- the minimum angle ⁇ 1min of the suction port 22 based on 180 ° is a value obtained by subtracting the angle corresponding to the thickness of the vane 4 from 180 °.
- the maximum angle ⁇ 1max of the suction port 22 is a value obtained by adding an angle corresponding to the pump chamber 7 and an angle corresponding to the thickness of the vane 4 to 180 °.
- the angle ⁇ 1 of the suction port 22 is 180 ° ⁇ t ⁇ ⁇ 1 ⁇ 180 °. It is set within the range of + (360 ° / n) + t.
- the angle ⁇ 1 of the suction port 22 is set so that the pump chamber 7 starts to communicate with the start end 23b of the discharge port 23 from the first transition section 24, and the other pump chamber 7 starts from the second transition section 25 to the start end of the suction port 22. It is set so as to deviate from the low pressure start timing at which communication with 22b starts. Therefore, it is possible to suppress a sudden change in the distribution of pressure acting on the inner periphery of the cam ring 5, and to prevent the working fluid pressure discharged from the discharge port 23 from fluctuating due to vibration of the cam ring 5 to generate noise. can do.
- the angle ⁇ 1 of the suction port 22 is set larger than the angle ⁇ 2 of the discharge port 23, the suction performance of the working fluid can be improved and the pump performance can be improved.
- the angle ⁇ 2 of the discharge port 23 is relatively small, the area where the discharge port 23 receives pressure from the high-pressure working fluid is small, so that the force generated in the pump is reduced and the cam ring 5 is operated by vibration. The fluctuation of the fluid pressure can be prevented more reliably.
- the angle ⁇ 1 of the suction port 22 is 180 ° ⁇ (360 ° / (2.n)) ⁇ t ⁇ ⁇ 1 ⁇ 180 ° + (360 ° / ( 2 ⁇ n)) + t.
- the suction port 22 is maintained at an angle ⁇ 1 of about 180 ° to improve the suction performance, and the high pressure timing and the low pressure timing coincide with each other. Can be avoided.
- the angle ⁇ 1 of the suction port 22 is defined by the equation 180 ° ⁇ t ⁇ ⁇ 1 ⁇ 180 ° + (360 ° / n) + t.
- the suction port 22 is maintained at an angle ⁇ 1 of approximately 180 ° to improve the suction performance, and the high pressure timing and the low pressure timing coincide with each other. Can be avoided.
- the angle of the second transition section 25 around the rotor 2 is set to be smaller than the angle of the first transition section 24, the eccentric amount of the cam ring 5 increases and the inner peripheral cam surface 5a becomes the discharge port. 23 and the suction port 22 move from the outer periphery to the inner periphery, the angle range of the second transition section 25 increases, and the difference in the angle range between the first transition section 24 and the second transition section 25 increases. This can be prevented.
- the angle ⁇ 1 of the suction port 22 is set so that the high pressure timing and the low pressure timing are always shifted regardless of the eccentric amount of the cam ring 5, so that the vibration of the cam ring 5 is always controlled regardless of the rotational speed of the vane pump 100. The fluctuation of the working fluid pressure due to can be prevented.
- the vane pump 100 includes a first fluid pressure chamber 11 and a second fluid pressure chamber 12 that decenter the cam ring 5 with respect to the rotor 2 by a pressure difference between the first fluid pressure chamber 11 and the second fluid pressure chamber 12.
- the control valve 10 for controlling the pressure of the working fluid. Therefore, the fluctuation of the working fluid pressure discharged from the discharge port 23 is suppressed, so that the first fluid pressure chamber 11 and the second fluid pressure are discharged from the discharge port 23. The fluctuation of the working fluid pressure guided to the chamber 12 is also suppressed, and the control valve 10 can function properly.
- angles ⁇ 1 and ⁇ 2 of the suction port 22 and the discharge port 23 provided in the side plate 20 are defined, but the angles of the suction port and the discharge port provided in the pump cover may be defined similarly. .
- the angle ⁇ 1 of the suction port 22 is larger than the angle ⁇ 2 of the discharge port 23 has been described.
- the angle ⁇ 2 of the discharge port 23 is within the range where the high pressure timing and the low pressure timing do not match. You may set so that it may become large.
- the angle range of the suction port 22 is defined on the basis of 180 °, but it may be defined on the basis of an angle smaller than 180 ° within a range in which the suction property is not deteriorated.
- the angle of the second transition section 25 is set to be equal to or smaller than the angle of the first transition section 24, but the angle of the second transition section 25 is larger than the angle of the first transition section 24. May be set.
- the angle ⁇ 1 of the suction port 22 is set so that the high pressure timing and the low pressure timing are always shifted regardless of the eccentric amount of the cam ring 5, but the high pressure timing is set only for a predetermined eccentric amount. May be set so that the timing of pressure reduction is shifted.
- the eccentric amount of the cam ring 5 is controlled by supplying the working fluid discharged from the discharge port 23 to the first fluid pressure chamber 11 and the second fluid pressure chamber 12 on the outer periphery of the cam ring by the control valve 10.
- the present invention is also applicable when the eccentric amount of the cam ring 5 is controlled by a method other than the working fluid pressure.
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Description
Claims (7)
- 流体圧供給源として用いられる可変容量型ベーンポンプであって、
動力源の動力によって回転駆動されるロータと、
前記ロータの外周に開口部を有して放射状に複数形成されるスリットと、
前記スリットごとに摺動自在に収装されるベーンと、
前記ベーンの先端部が摺接する内周カム面を有し前記ロータの中心に対して偏心可能なカムリングと、
前記カムリングの側面に当接して設けられるサイド部材と、
前記ロータと前記カムリングと前記サイド部材と隣り合う前記ベーンとの間に画成されるポンプ室と、
前記ロータの回転に伴って前記ポンプ室の容積が拡張する領域側の前記サイド部材に円弧状に形成され、前記ポンプ室に吸い込まれる作動流体を導く吸込ポートと、
前記ロータの回転に伴って前記ポンプ室の容積が収縮する領域側の前記サイド部材に円弧状に形成され、前記ポンプ室から吐出される作動流体を導く吐出ポートと、
を備え、
前記サイド部材は、前記吸込ポートの終端から前記吐出ポートの始端までの区間である第1遷移区間と、前記吐出ポートの終端から前記吸込ポートの始端までの区間である第2遷移区間と、を有し、
前記ロータを中心とした前記吸込ポートの始端から終端までの角度は、前記ポンプ室が前記第1遷移区間から前記吐出ポートの始端に連通し始める高圧化タイミングと、他の前記ポンプ室が前記第2遷移区間から前記吸込ポートの始端に連通し始める低圧化タイミングと、がずれるように設定される、
可変容量型ベーンポンプ。 - 請求項1に記載の可変容量型ベーンポンプであって、
前記ロータを中心とした前記吸込ポートの始端から終端までの角度は、前記ロータを中心とした前記吐出ポートの始端から終端までの角度より大きい、
可変容量型ベーンポンプ - 請求項1に記載の可変容量型ベーンポンプであって、
前記ベーンの枚数nが5以上の奇数である場合、前記ロータを中心とした前記吸込ポートの始端から終端までの角度θは、ベーンの厚み分の角度をtとすると、180°-(360°/(2・n))-t≦θ≦180°+(360°/(2・n))+tを満たす、
可変容量型ベーンポンプ。 - 請求項1に記載の可変容量型ベーンポンプであって、
前記ベーンの枚数nが6以上の偶数である場合、前記ロータを中心とした前記吸込ポートの始端から終端までの角度θは、ベーンの厚み分の角度をtとすると、180°-t≦θ≦180°+(360°/n)+tを満たす、
可変容量型ベーンポンプ。 - 請求項1に記載の可変容量型ベーンポンプであって、
前記ロータを中心とした前記第2遷移区間の角度は、前記ロータを中心とした前記第1遷移区間の角度より小さい、
可変容量型ベーンポンプ。 - 請求項1に記載の可変容量型ベーンポンプであって、
前記ロータを中心とした前記吸込ポートの始端から終端までの角度は、前記カムリングの偏心量にかかわらず、常に前記高圧化タイミングと前記低圧化タイミングとがずれるように設定される、
可変容量型ベーンポンプ。 - 請求項1に記載の可変容量型ベーンポンプであって、
前記カムリング外周の収容空間内に区画され、互いの圧力差によって前記ロータに対して前記カムリングを偏心させる第1流体圧室及び第2流体圧室と、
前記吐出ポートから導かれる作動流体の圧力に応じて動作し、前記第1流体圧室及び前記第2流体圧室の作動流体の圧力を制御して前記ロータに対する前記カムリングの偏心量を変化させ、ポンプ吐出流量を制御する制御バルブと、
をさらに備える、
可変容量型ベーンポンプ。
Priority Applications (4)
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CN201480009478.9A CN105074216B (zh) | 2013-02-22 | 2014-02-05 | 可变容量式叶片泵 |
MX2015010886A MX2015010886A (es) | 2013-02-22 | 2014-02-05 | Bomba de paletas de desplazamiento variable. |
EP14754445.6A EP2960510A4 (en) | 2013-02-22 | 2014-02-05 | WING CELL PUMP WITH VARIABLE CAPACITY |
US14/766,525 US9879670B2 (en) | 2013-02-22 | 2014-02-05 | Variable displacement vane pump |
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JP2013033782A JP6200164B2 (ja) | 2013-02-22 | 2013-02-22 | 可変容量型ベーンポンプ |
JP2013-033782 | 2013-02-22 |
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US (1) | US9879670B2 (ja) |
EP (1) | EP2960510A4 (ja) |
JP (1) | JP6200164B2 (ja) |
CN (1) | CN105074216B (ja) |
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JP5787803B2 (ja) * | 2012-03-21 | 2015-09-30 | カヤバ工業株式会社 | 可変容量型ベーンポンプ |
JP6538542B2 (ja) * | 2015-12-22 | 2019-07-03 | 東芝三菱電機産業システム株式会社 | 自励式無効電力補償装置 |
JP2017160800A (ja) * | 2016-03-07 | 2017-09-14 | 日立オートモティブシステムズ株式会社 | 可変容量形ベーンポンプ |
EP3577342A1 (de) * | 2017-02-01 | 2019-12-11 | Pierburg Pump Technology GmbH | Flügelzellen-gaspumpe |
JP6711528B2 (ja) * | 2017-02-10 | 2020-06-17 | 日立オートモティブシステムズ株式会社 | 可変容量形ポンプ |
DE202019100917U1 (de) | 2019-02-19 | 2020-05-20 | Punch Powertrain N.V. | Drehschieberpumpe |
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JP4527597B2 (ja) * | 2005-05-18 | 2010-08-18 | 日立オートモティブシステムズ株式会社 | ベーンポンプ |
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JP4759474B2 (ja) * | 2006-08-30 | 2011-08-31 | 日立オートモティブシステムズ株式会社 | ベーンポンプ |
JP4927601B2 (ja) * | 2007-03-05 | 2012-05-09 | 日立オートモティブシステムズ株式会社 | 可変容量型ベーンポンプ |
JP5216470B2 (ja) * | 2008-08-08 | 2013-06-19 | カヤバ工業株式会社 | 可変容量型ベーンポンプ |
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JP5475701B2 (ja) * | 2011-02-07 | 2014-04-16 | 日立オートモティブシステムズ株式会社 | ベーンポンプ |
-
2013
- 2013-02-22 JP JP2013033782A patent/JP6200164B2/ja not_active Expired - Fee Related
-
2014
- 2014-02-05 WO PCT/JP2014/052682 patent/WO2014129311A1/ja active Application Filing
- 2014-02-05 US US14/766,525 patent/US9879670B2/en active Active
- 2014-02-05 CN CN201480009478.9A patent/CN105074216B/zh active Active
- 2014-02-05 EP EP14754445.6A patent/EP2960510A4/en not_active Withdrawn
- 2014-02-05 MX MX2015010886A patent/MX2015010886A/es active IP Right Grant
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JPS529043Y1 (ja) * | 1968-10-16 | 1977-02-25 | ||
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JPH0693978A (ja) * | 1992-09-16 | 1994-04-05 | Toyo A Tec Kk | 可変容量型ベーンポンプ |
JPH06241176A (ja) * | 1993-02-18 | 1994-08-30 | Jidosha Kiki Co Ltd | 可変容量形ポンプ |
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Also Published As
Publication number | Publication date |
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CN105074216A (zh) | 2015-11-18 |
JP2014163267A (ja) | 2014-09-08 |
EP2960510A1 (en) | 2015-12-30 |
CN105074216B (zh) | 2017-05-03 |
EP2960510A4 (en) | 2016-10-12 |
MX2015010886A (es) | 2016-04-04 |
JP6200164B2 (ja) | 2017-09-20 |
US20160010642A1 (en) | 2016-01-14 |
US9879670B2 (en) | 2018-01-30 |
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