KR20080105168A - Variable displacement sliding vane pump - Google Patents

Variable displacement sliding vane pump Download PDF

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Publication number
KR20080105168A
KR20080105168A KR1020087025425A KR20087025425A KR20080105168A KR 20080105168 A KR20080105168 A KR 20080105168A KR 1020087025425 A KR1020087025425 A KR 1020087025425A KR 20087025425 A KR20087025425 A KR 20087025425A KR 20080105168 A KR20080105168 A KR 20080105168A
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KR
South Korea
Prior art keywords
pump
chamber
slide
pressure
rotor
Prior art date
Application number
KR1020087025425A
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Korean (ko)
Inventor
폴 엠 모튼
로버트 에이치 무이
맨프레드 아놀드
Original Assignee
더 게이츠 코포레이션
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Priority to US11/389,687 priority Critical patent/US20070224067A1/en
Priority to US11/389,687 priority
Application filed by 더 게이츠 코포레이션 filed Critical 더 게이츠 코포레이션
Publication of KR20080105168A publication Critical patent/KR20080105168A/en

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22Control 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
    • F04C14/223Control 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
    • F04C14/226Control 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/30Rotary-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
    • F04C2/34Rotary-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
    • F04C2/344Rotary-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

Abstract

A variable displacement sliding vane pump comprising a pump body, inlet and outlet ports formed in said pump body, a drive shaft rotatably mounted in said pump body, a rotor driven by said drive shaft and co-axially aligned therewith, a plurality of radially extending vanes slidably disposed in said rotor, a pivot disposed in said pump body, a slide pivotally disposed on said pivot in said pump body and having a central axis eccentric to the axis of said rotor, a plurality of fluid chambers defined by said rotor, said vanes, and said slide that are successively connected to said inlet and outlet ports, a spring acting on said slide to urge said slide in one direction, a first chamber and a second chamber, each suitable for receiving a fluid pressure and each disposed between said pump body and an outer surface of said slide, the first chamber in fluid communication with a pump outlet discharge pressure, and a valve operable to selectively pressurize and depressurize the second chamber. ® KIPO & WIPO 2009

Description

Variable displacement sliding vane pumps {VARIABLE DISPLACEMENT SLIDING VANE PUMP}
The present invention relates to a variable displacement sliding vane pump having a slide whose position is controlled by a differential pressure between a constant pressure source and a variable pressure source, the differential pressure being a spring force applied to the slide to form the required flow rate and pressure. A variable displacement sliding vane pump is to be balanced.
The lubrication system for the engine pressurizes and distributes lubricating oil to the engine lubrication circuit. This lubrication system utilizes slides and rotors with a number of vanes and cavities that can vary the volume of fluid delivered to the oil circuit.
The slide is eccentrically offset from the rotor to create a fluid chamber defined by the vanes, the rotor and the inner surface of the slide. The compression springs position the slide to create a large fluid chamber by default. When the engine requires a small volume of fluid or low oil pressure by the pump, the pressure regulator directs the fluid from the pump output line to the regulation chamber in the pump. The pressure in the regulating chamber pivots the slide against spring force, aligning the center of the rotor and slide more closely, thereby reducing the size of the fluid chamber. This reduces the amount of fluid discharged from the fluid reservoir into the pump, the amount of fluid output by the pump, thereby reducing the oil pressure.
There are two ways to control the pump output. The first method is to direct the line pressure to the control chamber via a pressure regulator to reduce the pump output. The second method is to increase the pump output by removing the pressure from the control chamber via the pressure regulator by discharging the fluid.
A representative technique is Schuster, U.S. Pat.No. 4434545 (1982), which has a controllable variable variable eccentricity between the rotor and the ring, and a variable displacement beam that has a pivotally mounted ring member to control pump displacement. Start the doll pump. Since the ring is placed on the pivot, the center of the ring always pivots to maintain the pure ring repulsion due to the internal pressure being directed to one side of the pivot connection in response to the displacement control pressure being pressed on a portion of the outer surface of the ring. Located within one quarter of the axis through the point and center of the pump rotor, this improves control stability over the displacement range.
What is needed is a variable displacement sliding vane pump having a slide whose position is controlled by a differential pressure between a constant pressure source and a variable pressure source, the differential pressure being balanced with the spring force applied to the slide to create the required flow rate and pressure. Variable displacement sliding vane pump. The present invention satisfies this need.
A first aspect of the invention is a variable displacement sliding vane pump having a slide whose position is controlled by a differential pressure between a constant pressure source and a variable pressure source, the differential pressure being applied to the slide to form the required flow rate and pressure. Loss is a variable displacement sliding vane pump that is balanced with spring force.
Other aspects of the invention will be pointed out or made clear by the following detailed description of the invention and the accompanying drawings.
The present invention provides a pump body, an inlet and an outlet port formed in the pump body, a drive shaft rotatably mounted to the pump body, a rotor driven by the drive shaft and aligned coaxially with the drive shaft, and slidable to the rotor. A slide having a plurality of vanes extending radially and extending radially, a pivot disposed on the pump body, a pivotally disposed on the pivot in the pump body, the central axis being eccentric with the axis of the rotor, and the rotor, vanes and slides. A plurality of fluid chambers formed by and connected to the inlet and outlet ports, springs acting on the slide to urge the slide in one direction, each adapted to receive hydraulic pressure and between the pump body and the outer surface of the slide A first chamber and a second chamber disposed respectively in the first chamber, wherein the first chamber is in fluid communication with the pump outlet discharge pressure. And a variable displacement sliding vane pump comprising a burr and a second chamber and a valve operable to selectively pressurize and depressurize the second chamber.
BRIEF DESCRIPTION OF THE DRAWINGS The accompanying drawings, which are incorporated in and form a part of this specification, illustrate preferred embodiments of the invention in conjunction with the description, and illustrate the principles of the invention.
1 is a front view of the pump with the outer cover removed;
2 is an exploded view of the pump.
3 is a front view of the pump body without outer cover, slide, rotor and vanes.
4 is a top / top view of the pump rotor.
5 is a plan view of the pump slide.
6 is a schematic diagram of a pump fluid circuit.
7 is a graph showing pump performance including pump flow rate and pressure.
8 is a side view of the electric valve;
9 is a graph showing pump performance including pump flow rate and pressure.
1 is a front view of the pump with the outer cover removed; The pump 100 of the present invention includes a main body 10. The main body 10 forms a cavity 11 in which the slide 12 and the rotor 13 are disposed. A plurality of sliding vanes 14 are disposed radially around the rotor 13. Each vane 14 extends radially from the slot 15 in the rotor 13. Each vane 14 may move within each slot 15.
The pump shaft 16 is rotatably mounted to the main body 10. The spline end 160 of the pump shaft 16 engages the rotor 13. As the rotor 13 rotates, the vanes 14 are pushed outwardly by a pair of vane control rings 17 and centrifugal force to slidably engage the inner surface 120 of the slide 12.
The slide 12 pivotally engages the body at pivot member 18. The slide 12 pivots in the pivot member 18 in the cavity 11, drawing an arch that forms the operating range of the slide 12 operation.
The position of each vane 14 is a function of the slide 12 position relative to the ring 17. The ring 17 occupies a space determined by the end of the vane 14. The ring 17 is substantially concentric with the inner surface 120.
The position of the ring 17 relative to the rotor 13 determines the radial position of each vane 14 in each of the slots 15 and then compares the position of the axis of rotation of the rotor 13 to a given slide 12 ) Determine the location. This relationship determines the volume of each of the chambers 21 between the inlet port 19 and the outlet port 20 at a given engine speed and thus a given slide 12 position.
The body 12 forms a pair of child shaped ports 19, 20 that each include an inlet port and an outlet port for the pump 100. The plurality of chambers 21 are formed by vanes 14, rotors 13 and inner surfaces 120. As is well known for vane pumps, the chamber 21 rotates with the rotor 13 and expands and contracts during rotation.
Inlet port 19 receives fluid from a source or reservoir, such as an engine oil system, not shown, and then moves fluid into chamber 21 as rotor 13 rotates. The vanes 14 move the fluid in the chamber 21 from the inlet port 19 to the outlet port 20. If the pump rotor 13 rotates counterclockwise as can be seen in FIG. 1, the chamber 21 continuously expands to create a low pressure region that generates an inflow of fluid in the region of the inlet port 19, The hydraulic pressure is increased by contraction to cause the outflow of fluid in the region of the outlet port 20.
The position of the slide 12 is formed by the combined effect of the control pressures in the two chambers, ie chamber 22 and chamber 23, respectively, which work in balance with the spring force from the spring 31. The chamber 22 extends around a portion of the outer circumference of the slide 12 from the seal member 25 disposed in the groove 26 formed in the slide 12 to the seal member 25 disposed in the groove 27, respectively. . Each seal member 24 and 25 is urged against the surface 28 outwardly by each of the elastic backing members 29 and 30. The chamber 23 extends from the seal member 24 to the pivot member 18 around a portion of the outer periphery of the slide 12.
The spring 31 acts against the total sum of the hydraulic pressures in the chambers 22 and 23, so that the total pressure in the chambers 22 and 23 increases so that the torque of the slide about the pivot member increases and thus the pump slide 12 Moves clockwise about pivot member 18. The combined torque generated by the pressure in the chambers 22, 23 is balanced by the spring force of the spring 31.
The hydraulic pressure in the chamber 22 is supplied by the fluid in final communication with the outlet port 20 of the pump 11, thus passing through the engine gallery from the outlet pressure of the pump 100, or the feedback channel (see FIG. 5). ). The hydraulic pressure in the chamber 23 is supplied by fluid communication with a second pressure source that is also connected to the outlet port 20 of the pump 100. The hydraulic pressure in the chamber 22 is proportional to the outlet pressure of the pump 100. The hydraulic pressure in the chamber 23 depends on the speed of the pump 100, ie the pressure in the chamber 23 is automatically discharged to the surroundings, eg the oil reservoir, at some operating intervals below the predetermined pump speed. When exceeding the predetermined speed, the pressure in the chamber 23 is equal to the pressure in the chamber 22. This may be referred to as a "switching point" and may be set at any speed depending on the use. The pressure in the chambers 22 and 23, and therefore the sum of the torques, determines the position of the slide 12. The position of the slide 12 determines the flow rate and outlet pressure of the pump.
In the best operating condition, the axis of the slide 12, and thus the inner surface 120, moves between the position 32 in the engine low speed condition and the position 33 in the engine high speed condition. As the vanes 14 rotate from the inlet port 19 to the outlet port 20, a pressure change occurs in the chamber 21.
Since the inner surface 120 undergoes internal pressure generation in the chamber 21, the slide 12 is inherently unbalanced during operation. The resulting net repulsive force due to internal pressure generation passes through the central axis of the inner surface 120. Always repulsive force provides a counterclockwise moment about the axis 18 as opposed to the clockwise moment generated by the control pressure in the chambers 22 and 23.
Since the pressure in the chambers 22, 23 is balanced against the force of the spring 31, the displacement of the pump, and consequently the flow, can be adjusted by changing the chamber pressure. The pump of the present invention controls both displacement and oil flow for two or more outlet pressure levels based on pump outlet pressure or engine gallery pressure.
Typically, the pressure level required in the pump for each chamber is the pressure level required to produce the appropriate oil flow and pressure for all engine speeds and load conditions. In some cases, engines at low rpm do not require high oil pressure levels, so some low pressure can be accommodated, thus reducing flow. By pressurizing the chamber 23 a low operating pressure and flow is obtained.
The amount of low oil pressure required depends on different engine parameters including whether it is a gas or diesel engine, engine complexity, engine speed and load.
The pump of the present invention provides two levels of control. The first is pressure control over a given speed range by the variable vane pump function. The second is based on the pump's ability to vary between two (or more) pressure levels by the use of two (or more) pressure chambers 22, 23 to control the position of the slide 12.
The cover 70 is fixed to the housing 10 by a plurality of fasteners 37. Leakage radially outward from the chamber 21 beyond the cover 70 is prevented by surface to surface contact.
2 is an exploded view of the pump. The position of the ring 17 relative to the rotor 13 determines the radial position of each vane 14 in each slot 15, and then compares the position of the rotation axis of the rotor 13 with the slide ( 12) Determine the location. The inner edge 14a of each of the vanes 14 abuts the outer surface 17a of the ring 17. In addition, the outer edge 14b of each vane 14 slides against the inner surface 120 of the slide 12. The pump may use a single spring 31 or, for example, two springs 31a and 31b.
3 is a front view of the pump body without outer cover, slide, rotor and vanes. The inlet port 19 and the outlet port 20 are arranged in the body 10. Conduit 34 transfers pressure from main oil gallery 204 to chamber 22 (see FIG. 5). Conduit 35 transfers pressure from main oil gallery 204 to chamber 23 (see FIG. 5). Conduit 34 is exposed to pump outlet pressure or engine gallery oil pressure at all pump operating conditions. Hydraulic pressure in conduit 35 is determined by the position of valve 207 (see FIG. 1).
4 is a top view of the pump rotor. The rotor 13 comprises a slot 15 which is oriented radially about the outer periphery. The vanes 14 slidably engage respective slots 15. The drive shaft 16 meshes with the rotor 13 through the spline hole 36. The drive shaft 16 may fit in the hole 36. Each slot 15 includes a radial length sufficient to accommodate the full range of motion of each of the vanes 14. Each vane 14 moves radially by a predetermined distance depending on the position of the ring 17 relative to the rotor 13 during pump operation.
5 is a plan view of the pump slide. The slide 12 includes an inner surface 120. The outer edge of each of the vanes 14 is slidably engaged with the inner surface 120. The inner surface 120 is cylindrical, but the shape of the surface may be slightly distorted to accommodate the design shape, for example, elliptical or oval. Pivot 18 is engaged with detent 121. Each of the grooves 26 and 27 receives seal members 24 and 25, respectively, to seal the hydraulic pressure in each of the chambers 23 and 22, respectively. The spring 31 abuts the surface 122. Seal members 24 and 25 may comprise any material having suitable affinity with the pump fluid, such as synthetic and / or natural rubber.
6 is an exemplary schematic diagram of a pump fluid circuit 200. Fluid conduit 201 connects pump outlet port 20 to oil filter 202, oil cooler 203, and main oil gallery 204. The main oil gallery 204 is exposed to the outlet pressure of the pump 100 to experience the friction losses common in any fluid system. The main oil gallery 204 is also connected to the engine oil system 210. This system is proposed only as an example and does not describe various engine oil systems that can be applied to the pumps and systems of the present invention.
Conduit 205, which is connected to chamber 22 via conduit 34, is connected to main oil gallery 204 (see FIG. 1). Conduit 209 is connected to conduit 205. Conduit 209 is connected to an electric valve 207 (see FIG. 7). Valve 207 selectively connects or disconnects conduit 209 through conduit 206 to conduit 35 and chamber 23 in FIG. 1 having hydraulic pressure within conduit 205. Preferably, the valve 207 is received in the body 10. The valve 207 is shown schematically in FIG. 5 as being separated from the pump 100 for ease of explanation. However, valve 207 may be separated from pump body 100 as schematically shown in FIG. 5 to accommodate various physical limitations as required by system space needs. The valve 207 may comprise a mechanical valve known in the art, such as a valve that regulates the downstream pressure based on the upstream pressure, commonly known as a pressure regulating valve.
The total force exerted by the slide 12 against the spring 31 is the sum of the torque generated by the sum of the hydraulic pressure in the chamber 22 and the hydraulic pressure in the chamber 23, both of which are pivot members ( 18) work around.
Below the first operating speed, the valve 207 opens to allow engine gallery pressure to enter the chamber 23. The pressure in the chamber 23 combined with the pressure in the chamber 22 is equal to the arch distance to a position where the torque generated by the combined pressure in the chambers 22, 23 is balanced by the spring force of the spring 31. The slide 12 is pivoted about the pivot member 18. The pump characteristic with the slide 12 in this position is shown by part “A” in FIG. 7. The pressure in the chambers 22 and 23 is proportional to the pump speed. As the engine speed, and thus the pump speed, increases, the pressure in the chambers 22, 23 also increases. Under these operating conditions the pump output is less flow and pressure than the flow and pressure of the pump with the valve 207 (reduced chamber 23) closed at the same engine speed. The position of the slide 12, thus the pump output flow and the pressure in part “A” is a function of the pressure in both chambers 22, 23.
At operating conditions greater than the first operating speed, the valve 207 is closed to discharge the chamber 23 to external pressure (about 1 bar). The pressure in the chamber 22 causes the slide 12 to be centered about the pivot member 18 by an arc distance in an equilibrium position where the torque generated by the pressure in the chamber 22 is balanced by the spring force of the spring 31. Make a turn. As the pump speed increases, the pressure in the chamber 22 also increases and the slide 12 pivots because the force acting against the spring 31 increases. The pump characteristic with the slide 12 in this position is shown in part B of FIG. 7. The operating section of part B may also be characterized in the manual mode because the chamber 23 is evacuated to atmospheric pressure and the overall pivot motion and position of the slide 12 is determined by the pressure level of the chamber 22.
In alternative embodiments, valve 207 may be opened to a partial position, causing slide 12 to move to a position intermediate between position A and position B and generating intermediate outlet pressure and flow. Placement of the valve 207 at any position between fully open and fully closed can vary the pressure in the chamber 23, thereby providing a range of slide positions for a given pump outlet pressure.
In the event of a valve 207 failure, the pump continues to operate in the manual mode (decompressed chamber 23) while meeting all the oil requirements of the engine. Manual operating mode is much more effective in fixed displacement pumps. In operation, the valve 207 provides an incremental horsepower reduction in the manual design.
7 is an exemplary graph showing pump performance including pump flow rate and pressure. The range of engine speed is shown on the x axis and the range of pump outlet pressure is shown on the y axis. The range of pump flow rates also appears on the second y-axis in liters per minute.
Engine speed ranges from 0 RPM to 8000 RPM. The outlet pressure range is from 0 bar to 6.00 bar. The pump flow rate ranges from 0 liters / minute to 90.00 liters / minute.
For purposes of explanation, the characteristics of the pump of the present invention are described by selecting an engine speed of ˜3,500 RPM. The transition between the operating conditions "A" and "B" is shown as a "switching point" at the center of the curve in the graph.
At engine speeds lower than ˜3,500 RPM, the maximum pump outlet pressure is about 2.6 bar. The maximum flow rate is about 20.0 liters / minute.
At engine speeds greater than ~ 3,500 RPM, the pump outlet pressure quickly switches to a minimum outlet pressure of about 4.9 bar at 7,500 RPM. The flow rate is switched to a maximum of about 28.0 liters / minute at 7,500 RPM.
The step change in pressure at the turning point is about 1.6 bar. The step change of flow is about 5 l / min.
The performance change is caused by the slide 12 pivoting about the pivot 18 generated by the deactivation of the valve 207 which discharges the chamber 23 to external atmospheric conditions. The valve 207 is controlled by, for example, an electrical signal transmitted by the engine ECU. When a predetermined engine speed, in this case ˜3,500 RPM, is reached, the ECU 208 (see FIG. 6) sends a signal to close the valve 207 to the same hydraulic pressure as the hydraulic pressure in the main oil gallery 204. 23) Pressurize.
As described above, the pressure in the chambers 22, 23 produces a greater torque, and therefore a force, than the combination of the force of the spring 31 and the fluid force in the chamber 21, thereby compressing the spring 31. . This pivots the slide 12. By turning clockwise each of the flow rate and outlet pressure substantially decreases at a given engine speed, because the pump displacement is reduced.
For comparison purposes, the dashed line in part A of FIG. 7 at less than ˜3,500 RPM shows the behavior of the outlet pressure and flow rate of the pump when the position of the slide 12 is controlled only by a single pressure chamber. In the case of a single chamber, at a relatively low engine speed that is only slightly above idle (~ 1,500 RPM), the pump operates at the relatively high outlet pressure and flow rate required by the engine. This is inefficient. The pump of the present invention provides only the necessary amount of flow and pressure for efficient operation at low engine speeds. This equates to significant energy savings in the system. However, at high engine speeds the pump can be switched to the higher flow rates and outlet pressures required to meet engine demands quickly and accurately.
8 is a side view of the electric valve. The valve 207 engages with the body 10 of the pump. The valve 207 is connected to an electrical harness of the engine or the vehicle (not shown). Electrical connectors (not shown) engage valve 207 at socket 208. When the valve 207 is deactivated, pressure is released from the chamber 23, thereby causing the pump to operate in zone "A". When valve 207 is actuated, hydraulic pressure is applied from nozzle 211 to chamber 23 to cause the pump to operate in zone "B". To avoid engine failure caused by improper hydraulic pressure at high speeds, the valve must be electrically deactivated to relieve pressure from chamber 23. This creates a failure prevention situation at high speed, i.e., the chamber 23 is discharged in the event of an electrical failure of the valve 207.
9 is a graph showing pump performance including pump flow rate and pressure. The range of engine speed is shown on the x axis and the range of pump outlet pressure is shown on the y axis. The range of pump flow rates is also shown on the second y-axis.
Engine speed ranges from 0 RPM to 8000 RPM. The outlet pressure range is from 0 bar to 6.00 bar. The pump flow rate ranges from 0 liters / minute to 90 liters / minute.
For purposes of explanation, an engine speed of ˜2,000 RPM is selected to describe the characteristics of the pump of the present invention. The transition between operating conditions "A" and "B" is shown as a "switching point" at about 2,000 RPM.
In this embodiment, valve 207 is OFF at engine speeds lower than 2,000 RPM at start up, ie chamber 23 is depressurized and discharged to ambient. At engine speeds lower than about 2,000 RPM, the maximum pump outlet pressure (line pressure) is about 3.6 bar. The maximum flow rate (flow rate) is about 25.0 liters / minute.
At engine speeds greater than about 2,000 RPM, the pump outlet pressure (line pressure) quickly shifts down to a minimum outlet pressure of about 2.4 bar at 2,000 RPM and 3.2 bar at about 7,500 RPM. The flow rate (flow rate) is switched to a minimum of about 23.0 liters / minute at 7,500 RPM.
The step change in pressure at the turning point is about 1.4 bar. The step change of flow is about 5 l / min.
In this embodiment, the performance change is caused by the slide 12 pivoting about the pivot 18 generated by the actuation of the valve 207 and thereby pressurizing the chamber 23. The valve 207 is controlled by, for example, an electrical signal transmitted by the engine ECU. When a predetermined engine speed, in this case about 2,000 RPM, is reached, the ECU 208 (see FIG. 6) transmits a signal that closes the valve 207 so that the chamber (at a hydraulic pressure equal to the hydraulic pressure of the main oil gallery 204) is reached. 23) Pressurize. If valve 207 fails, chamber 23 is depressurized to place pump in high discharge pressure mode.
While forms of the invention have been described herein, it will be apparent to those skilled in the art that modifications may be made in the construction and relationship of components without departing from the spirit and scope of the invention described herein.

Claims (10)

  1. Pump body;
    An inlet port and an outlet port in the pump body;
    A drive shaft rotatably mounted to the pump body;
    A rotor driven by the drive shaft;
    A plurality of vanes slidably disposed in the rotor and extending radially;
    A pivot disposed within the pump body;
    A slide pivotally disposed on the pivot and having a central axis eccentric with the axis of the rotor;
    A plurality of fluid chambers formed by the rotor, vanes and slides and continuously connected to the inlet and outlet ports;
    A spring acting on the slide to urge the slide in one direction;
    A first chamber and a second chamber, each receiving hydraulic pressure and disposed between the pump body and the outer surface of the slide, respectively, wherein the first chamber is connected to a pump outlet discharge pressure. ; And
    A valve operable to selectively pressurize the second chamber to a hydraulic pressure higher than ambient atmospheric pressure conditions
    Variable displacement sliding vane pump comprising a.
  2. The variable displacement sliding vane pump of claim 1, further comprising a second spring operating in parallel with the spring.
  3. The variable displacement sliding vane pump of claim 1, wherein the valve is electric and controlled by an engine ECU.
  4. The variable displacement sliding vane pump of claim 1, wherein the pump outlet discharge flow rate decreases upon decompression of the second chamber.
  5. 2. The variable displacement bow of claim 1 wherein the second chamber is pressurized to a pressure greater than ambient atmospheric pressure for engine speeds lower than a predetermined engine speed, and decompressed to ambient atmospheric pressure for engine speeds greater than the predetermined engine speed. Stock vane pump.
  6. The variable displacement sliding vane pump of claim 1, wherein the first chamber and the second chamber are both in fluid communication with a pump output discharge pressure.
  7. Pump body;
    An inlet port and an outlet port in the pump body;
    A drive shaft rotatably mounted to the pump body;
    A rotor driven by the drive shaft and aligned coaxially with the drive shaft;
    A plurality of vanes slidably disposed in the rotor and extending radially;
    A pivot disposed within the pump body;
    A slide pivotally disposed on the pivot in the pump body and having a central axis eccentric with the axis of the rotor;
    A plurality of fluid chambers formed by the rotor, vanes and slides and continuously connected to the inlet and outlet ports;
    A spring acting on the slide to urge the slide in one direction;
    First and second chambers, respectively, in fluid communication with the pump discharge oil pressure, disposed between the pump body and the outer surface of the slide; And
    Valves that can operate at the desired pump speed
    Wherein the second chamber is selectively switched between ambient atmospheric pressure and pump discharge oil pressure.
  8. Pump body;
    An inlet port and an outlet port in the pump body;
    A drive shaft rotatably mounted in the pump body;
    A rotor driven by the drive shaft and aligned coaxially with the drive shaft;
    A plurality of vanes slidably disposed in the rotor and extending radially;
    A pivot disposed within the pump body;
    A slide pivotally disposed on the pivot in the pump body and having a central axis eccentric with the axis of the rotor;
    A plurality of fluid chambers formed by the rotor, vanes and slides and continuously connected to the inlet and outlet ports;
    A spring acting on the slide to urge the slide in one direction;
    A first chamber and a second chamber, each adapted to receive hydraulic pressure and each disposed between the pump body and the outer surface of the slide, the first chamber in fluid communication with a pump outlet discharge pressure. And a second chamber; And
    A valve operable to selectively pressurize and depressurize the second chamber
    Variable displacement sliding vane pump comprising a.
  9. 9. The variable of claim 8, wherein the second chamber is pressurized to a pressure greater than ambient atmospheric pressure for engine speeds lower than a predetermined engine speed, and reduced to ambient atmospheric pressure for engine speeds greater than the predetermined engine speed. Displacement sliding vane pump.
  10. The variable displacement sliding vane pump of claim 8, wherein the second chamber can be pressurized to near pump outlet discharge pressure.
KR1020087025425A 2006-03-27 2007-03-12 Variable displacement sliding vane pump KR20080105168A (en)

Priority Applications (2)

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US11/389,687 US20070224067A1 (en) 2006-03-27 2006-03-27 Variable displacement sliding vane pump
US11/389,687 2006-03-27

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US (1) US20070224067A1 (en)
EP (1) EP1999373A1 (en)
JP (1) JP2009531598A (en)
KR (1) KR20080105168A (en)
CN (1) CN101443557A (en)
AU (1) AU2007241171A1 (en)
BR (1) BRPI0709186B1 (en)
CA (1) CA2647376A1 (en)
MX (1) MX2008012455A (en)
RU (1) RU2396462C2 (en)
WO (1) WO2007123607A1 (en)

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WO2007123607A1 (en) 2007-11-01
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US20070224067A1 (en) 2007-09-27
AU2007241171A1 (en) 2007-11-01

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