EP2253847A1 - Variable capacity lubricant vane pump - Google Patents

Variable capacity lubricant vane pump Download PDF

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Publication number
EP2253847A1
EP2253847A1 EP09160524A EP09160524A EP2253847A1 EP 2253847 A1 EP2253847 A1 EP 2253847A1 EP 09160524 A EP09160524 A EP 09160524A EP 09160524 A EP09160524 A EP 09160524A EP 2253847 A1 EP2253847 A1 EP 2253847A1
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EP
European Patent Office
Prior art keywords
control
pump
control chamber
variable capacity
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP09160524A
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German (de)
French (fr)
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EP2253847B1 (en
Inventor
Stefano Fiorini
Giacomo Armenio
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pierburg Pump Technology GmbH
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Pierburg Pump Technology GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Pierburg Pump Technology GmbH filed Critical Pierburg Pump Technology GmbH
Priority to EP09160524.6A priority Critical patent/EP2253847B1/en
Priority to CN201010209718.3A priority patent/CN101892981B/en
Publication of EP2253847A1 publication Critical patent/EP2253847A1/en
Application granted granted Critical
Publication of EP2253847B1 publication Critical patent/EP2253847B1/en
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Classifications

    • 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
    • F04C2/3441—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—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 the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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

Definitions

  • the present invention refers to a mechanically driven variable capacity lubricant vane pump for lubrication of an internal combustion engine, and in particular refers to a pressure controlled pump in which at least to different set pump delivery pressures can be controlled by the pump itself.
  • the pump chamber volume has to be variable in a similar range to provide a constant lubricant pressure.
  • Variable capacity lubricant vane pumps which can control two different set pump delivery pressures are known in the state of the art.
  • a vane pump with a pivotable capacity control ring is dislosed.
  • the control ring position is determined by two control chambers which directly act against the capacity control ring and both are arranged on one single side with respect to the pivot axis. Both control chambers act in the same direction against the spring power of a preload spring preloading the control ring into a high pump chamber volume direction.
  • the two pressure chambers are separated from each other by one single sliding sealing element.
  • the lubricant pump according to the invention is provided with a first and a second control chamber being arranged on different sides with respect to the pivot axis, and therefore act against each other.
  • the first control chamber is acting against the preload spring and the second control chamber is acting in parallel with the preload spring and, if activated, is supporting the preload spring.
  • the preload spring pushes the control ring in a high pump chamber volume direction. Since the two control chambers do not need to share one side of the control ring, the circumferential size of both control chambers can be increased significantly. This gives more freedom for the construction of the pump, and in particular for dimensioning and placing the two control chambers.
  • the pressure leakage via the control chambers can be reduced when the pump is driven in the higher pump volume constellation.
  • both control chambers are provided with the pump delivery pressure.
  • Both pumping chambers preferably are separated from each other by a pivot bearing in the pivot axis. When the pump is driven in the higher volume constellation, the pressure on both sides of the pivot bearing is equal so that no lubricant leakage can appear in the first control chamber, so that the pump pressure cannot exceed a maximum value.
  • the pivot bearing in the pivot axis constitutes a sealing between the two control chambers.
  • the two control chambers can be separated from each other by the pivot bearing. This is very simple and space effective solution.
  • the sealing between the control chambers needs not to be perfect because in the high pressure state of the pump, both control chambers are provided with the pump pressure at the pump outlet port.
  • the two control chambers have a different circumferential extend around the control ring.
  • the two set pressure levels of the pump are determined by the spring force of the preload spring, the effective surfaces of the two control chambers and the respective moment arms with the two pressure levels of the pump are in particular determined by the circumferential extend of the control chambers around the control ring.
  • the first control chamber is in fluidic connection with a pump outlet port and is pushing the control ring in a high pump chamber volume direction, preferably against the spring force of the preload spring.
  • the fluidic connection between the first control chamber and the outlet port can be realized by one or more bores in the control ring separating the pump outlet port and the first control chamber.
  • the term "fluidic connection with a pump outlet” does not necessarily mean a direct and short connection with the pump outlet itself. The term includes every fluidic connection with the pressurized part between the pump outlet port and the lubricant outlet of the internal combustion engine, as every port which gives information about the lubricant pressure before, in or after the engine.
  • the second control chamber is in fluidic connection with the pump outlet port as well, and a control valve controls the fluidic connection of the second control chamber to atmospheric pressure.
  • the control valve can either be a simple on/off valve closing and opening a fluidic line between the second control chamber and the atmospheric pressure, or can be realized as a 3-way valve connecting the second control chamber to either the pump outlet port or to atmospheric pressure.
  • a simple on/off valve the most simple construction can be used, i . e . a valve which is biased into the closed position by a spring and is open when actuated by an actuator. These kinds of valves are the most simple and least expensive valve.
  • a simple on/off-control valve being biased into the closed position is failsafe as well, because, if opening of the valve is not possible, the pump automatically is running in the high pressure state.
  • control valve is a simple on/off-control valve connecting the second control chamber to atmospheric pressure
  • a throttle valve is arranged between the pump outlet port and the second control chamber.
  • FIGS 2 and 3 two different lubricant pumps 10; 10' are shown which provide an internal combustion engine 12 with a lubricant, i . e . oil.
  • the lubricant finally flows from the combustion engine 12 into a oil sump 13 which is under atmospheric pressure. From the oil sump 13 the lubricant is sucked via the inlet port 40 into the pump unit 14.
  • the vane pumps 10; 10' provide the lubricant with a constant pumping pressure.
  • the lubricant pumps 10; 10' comprise a variable capacity lubricant vane pump unit 14 and a control valve 16; 16' controlling the pumping pressure of the vane pump unit 14 at a pump outlet port 18.
  • the vane pump unit 14 is mechanically driven by the combustion engine 12 so that the vane pump unit 14 is driven within a large rotation speed interval. Therefore, the pump chamber volume of the vane pump unit 14 can be varied in a wide range, as well.
  • the control valve 16; 16' is for selecting one of two set pump delivery pressures at the pump outlet port 42.
  • the pump unit 14 comprises a rotor ring 20 with numerous vane slits 22 wherein radially slidable vanes 24 are arranged.
  • the vanes 24 are surrounded by a capacity control ring 26 which is pivotable around a pivot axis 28.
  • the rotor ring 20, the vanes 24, the control ring 26 and not shown sidewalls define numerous pump chambers 30 therebetween, In one sidewall a circular inlet port 40 and a circular outlet port 42 are provided.
  • the size of the pump chambers 30 can be varied by pivoting the control ring 26 around the pivot axis 28.
  • a bearing pin 32 is arranged forming a pivot bearing 31.
  • the position of the control ring 26 is determined by three elements, i . e . a preload spring 34, a first control chamber 36 and a second control chamber 38.
  • the first control chamber 36 and the second control chamber 38 are provided on different sides with respect to the pivot axis 28 and, therefore, act against each other.
  • the two control chambers 36, 38 are separated by the bearing pin 32 so that the two control chambers 36, 38 are directly adjacent to each other.
  • the bearing pin 32 in the pivot axis 28 forms a pivot bearing 31.
  • the control ring 26 is provided with two pressure equalization bores 44, 45 which directly provide the first control chamber 36 with the pump pressure at the outlet port 42.
  • the second control chamber 38 is connected with the pump pressure via a throttle valve 48, as shown in figure 2 .
  • the second control chamber 38 can be connected to the oil sump 13 being under atmospheric pressure.
  • control valve 16 which is a simple on/off valve.
  • the control valve 16 is closed in its non-actuated position by a preload spring, as shown in figure 2 .
  • the valve actuator 17 When the valve actuator 17 is not active, the second control chamber 38 is provided with the pump pressure, as well.
  • the circumferential extend of the first control chamber 36 is larger than the circumferential extend of the second control chamber 38 so that identical pressures in both control chambers 36, 38 lead to a higher torque caused by the first control chamber 36 compared to the torque caused by the second control chamber 38.
  • the second control chamber is provided with the pump delivery pressure.
  • the second control chamber 38 then supports the preload spring 34 so that a higher set pump pressure is adjusted.
  • the control chamber 38 is provided with atmospheric pressure. In this case, the first control chamber 36 acts only against the preload spring 34 so that the pump chambers 30 become smaller which leads to a reduced set pump pressure.
  • the vane pump 10 is failsafe with respect to the control valve 16 because, if the actuator 17 fails to work, the control valve 16 is in the closed position and the higher set pump pressure is selected.
  • control valve 16' is designed as a 3-way valve which alternatively connects the second control chamber 38 with the pump outlet port 42 or the oil sump 13 being under atmospheric pressure.
  • the throttle valve 48 of the first embodiment can be omitted.
  • the control valve 16' connects the second control chamber 38 with the pump pressure, when the control valve 16' is not actuated, and connects the second control chamber 38 with the atmospheric pressure of the oil sump 13, when the control valve 16' is actuated by the actuator 17.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)

Abstract

A variable capacity lubricant vane pump (10;10') for lubrication of an internal combustion engine (12) is provided with radially slidable vanes (24) arranged in vane slits (22) of a rotor ring (20), the vanes (24) defining pump chambers (30) therebetween, a capacity control ring (26) surrounding the vanes (24) and being pivotable around a pivot axis (28) thereby varying the volume of the pump chambers (30), a first and a second hydraulic control chamber (36,38), both control chambers being in part defined by the control ring (26) and thereby pivoting the control ring (26), and a preload spring (34) preloading the control ring (26) in one direction, wherein the first control chamber (36) and the second control chamber (38) are arranged on different sides with respect to the pivot axis (28) and act against each other. This vane pump is very failsafe because, if the control valve (16) cannot be actuated, a high pump pressure at the pump outlet is set.

Description

  • The present invention refers to a mechanically driven variable capacity lubricant vane pump for lubrication of an internal combustion engine, and in particular refers to a pressure controlled pump in which at least to different set pump delivery pressures can be controlled by the pump itself.
  • Since the rotational speed of a internal combustion engine driving the lubricant pump can vary with a factor of ten or more, the pump chamber volume has to be variable in a similar range to provide a constant lubricant pressure.
  • Variable capacity lubricant vane pumps which can control two different set pump delivery pressures are known in the state of the art. In WO 2006/066405 , a vane pump with a pivotable capacity control ring is dislosed. The control ring position is determined by two control chambers which directly act against the capacity control ring and both are arranged on one single side with respect to the pivot axis. Both control chambers act in the same direction against the spring power of a preload spring preloading the control ring into a high pump chamber volume direction. The two pressure chambers are separated from each other by one single sliding sealing element.
  • It is an object of the invention to improve a variable capacity lubricant vane pump with two different set pump pressures.
  • This object is, according to the invention, solved with a lubricant pump with the features of claim 1.
  • The lubricant pump according to the invention is provided with a first and a second control chamber being arranged on different sides with respect to the pivot axis, and therefore act against each other. As a consequence, the first control chamber is acting against the preload spring and the second control chamber is acting in parallel with the preload spring and, if activated, is supporting the preload spring. The preload spring pushes the control ring in a high pump chamber volume direction. Since the two control chambers do not need to share one side of the control ring, the circumferential size of both control chambers can be increased significantly. This gives more freedom for the construction of the pump, and in particular for dimensioning and placing the two control chambers.
  • The pressure leakage via the control chambers can be reduced when the pump is driven in the higher pump volume constellation. During the high pump volume constellation of the pump, both control chambers are provided with the pump delivery pressure. Both pumping chambers preferably are separated from each other by a pivot bearing in the pivot axis. When the pump is driven in the higher volume constellation, the pressure on both sides of the pivot bearing is equal so that no lubricant leakage can appear in the first control chamber, so that the pump pressure cannot exceed a maximum value.
  • When the second chamber is not provided with the pump pressure, lubricant leakage via the pivot bearing can appear but is not dangerous because the pump is driven in the low pressure state anyway so that an undesired overpressure does not exceed the maximum allowable pump delivery pressure for the combustion engine.
  • In a preferred embodiment of the invention, the pivot bearing in the pivot axis constitutes a sealing between the two control chambers. As already explained, the two control chambers can be separated from each other by the pivot bearing. This is very simple and space effective solution. The sealing between the control chambers needs not to be perfect because in the high pressure state of the pump, both control chambers are provided with the pump pressure at the pump outlet port.
  • In a preferred embodiment of the invention, the two control chambers have a different circumferential extend around the control ring. The two set pressure levels of the pump are determined by the spring force of the preload spring, the effective surfaces of the two control chambers and the respective moment arms with the two pressure levels of the pump are in particular determined by the circumferential extend of the control chambers around the control ring.
  • According to a preferred embodiment of the invention, the first control chamber is in fluidic connection with a pump outlet port and is pushing the control ring in a high pump chamber volume direction, preferably against the spring force of the preload spring. The fluidic connection between the first control chamber and the outlet port can be realized by one or more bores in the control ring separating the pump outlet port and the first control chamber. The term "fluidic connection with a pump outlet" does not necessarily mean a direct and short connection with the pump outlet itself. The term includes every fluidic connection with the pressurized part between the pump outlet port and the lubricant outlet of the internal combustion engine, as every port which gives information about the lubricant pressure before, in or after the engine.
  • According to another preferred embodiment of the invention, the second control chamber is in fluidic connection with the pump outlet port as well, and a control valve controls the fluidic connection of the second control chamber to atmospheric pressure.
  • The control valve can either be a simple on/off valve closing and opening a fluidic line between the second control chamber and the atmospheric pressure, or can be realized as a 3-way valve connecting the second control chamber to either the pump outlet port or to atmospheric pressure.
  • If a simple on/off valve is used, the most simple construction can be used, i.e. a valve which is biased into the closed position by a spring and is open when actuated by an actuator. These kinds of valves are the most simple and least expensive valve. In addition, a simple on/off-control valve being biased into the closed position is failsafe as well, because, if opening of the valve is not possible, the pump automatically is running in the high pressure state.
  • In case the control valve is a simple on/off-control valve connecting the second control chamber to atmospheric pressure, a throttle valve is arranged between the pump outlet port and the second control chamber.
  • Two preferred embodiments of the present invention are described with reference to the figures, wherein
    • figure 1 is a cross-sectional view on the variable capacity lubricant vane pump,
    • figure 2 is showing first embodiment of the variable capacity lubricant vane pump including an on/off-control valve controlling the second control chamber, and
    • figure 3 is showing a second embodiment of the variable capacity lubricant vane pump including a 3-way control valve.
  • In figures 2 and 3, two different lubricant pumps 10; 10' are shown which provide an internal combustion engine 12 with a lubricant, i.e. oil. The lubricant finally flows from the combustion engine 12 into a oil sump 13 which is under atmospheric pressure. From the oil sump 13 the lubricant is sucked via the inlet port 40 into the pump unit 14. The vane pumps 10; 10' provide the lubricant with a constant pumping pressure. The lubricant pumps 10; 10' comprise a variable capacity lubricant vane pump unit 14 and a control valve 16; 16' controlling the pumping pressure of the vane pump unit 14 at a pump outlet port 18.
  • The vane pump unit 14 is mechanically driven by the combustion engine 12 so that the vane pump unit 14 is driven within a large rotation speed interval. Therefore, the pump chamber volume of the vane pump unit 14 can be varied in a wide range, as well. The control valve 16; 16' is for selecting one of two set pump delivery pressures at the pump outlet port 42.
  • The pump unit 14 comprises a rotor ring 20 with numerous vane slits 22 wherein radially slidable vanes 24 are arranged. The vanes 24 are surrounded by a capacity control ring 26 which is pivotable around a pivot axis 28. The rotor ring 20, the vanes 24, the control ring 26 and not shown sidewalls define numerous pump chambers 30 therebetween, In one sidewall a circular inlet port 40 and a circular outlet port 42 are provided. The size of the pump chambers 30 can be varied by pivoting the control ring 26 around the pivot axis 28. In the pivot axis 28 a bearing pin 32 is arranged forming a pivot bearing 31.
  • The position of the control ring 26 is determined by three elements, i.e. a preload spring 34, a first control chamber 36 and a second control chamber 38.
  • The first control chamber 36 and the second control chamber 38 are provided on different sides with respect to the pivot axis 28 and, therefore, act against each other. The two control chambers 36, 38 are separated by the bearing pin 32 so that the two control chambers 36, 38 are directly adjacent to each other.
  • The bearing pin 32 in the pivot axis 28 forms a pivot bearing 31.
  • The control ring 26 is provided with two pressure equalization bores 44, 45 which directly provide the first control chamber 36 with the pump pressure at the outlet port 42.
  • In the first embodiment of the invention, the second control chamber 38 is connected with the pump pressure via a throttle valve 48, as shown in figure 2. In addition, the second control chamber 38 can be connected to the oil sump 13 being under atmospheric pressure.
  • The fluidic connection between the second control chamber 38 and the atmospheric pressure of the oil sump 13 is opened and closed by the control valve 16 which is a simple on/off valve. The control valve 16 is closed in its non-actuated position by a preload spring, as shown in figure 2. When the valve actuator 17 is not active, the second control chamber 38 is provided with the pump pressure, as well.
  • The circumferential extend of the first control chamber 36 is larger than the circumferential extend of the second control chamber 38 so that identical pressures in both control chambers 36, 38 lead to a higher torque caused by the first control chamber 36 compared to the torque caused by the second control chamber 38. When the control valve 16 is not activated the second control chamber is provided with the pump delivery pressure. The second control chamber 38 then supports the preload spring 34 so that a higher set pump pressure is adjusted. When the control valve 16 is activated in its open position, the control chamber 38 is provided with atmospheric pressure. In this case, the first control chamber 36 acts only against the preload spring 34 so that the pump chambers 30 become smaller which leads to a reduced set pump pressure.
  • The vane pump 10 is failsafe with respect to the control valve 16 because, if the actuator 17 fails to work, the control valve 16 is in the closed position and the higher set pump pressure is selected.
  • In the second embodiment shown in figure 3, the control valve 16' is designed as a 3-way valve which alternatively connects the second control chamber 38 with the pump outlet port 42 or the oil sump 13 being under atmospheric pressure. In this embodiment, the throttle valve 48 of the first embodiment can be omitted.
  • The control valve 16' connects the second control chamber 38 with the pump pressure, when the control valve 16' is not actuated, and connects the second control chamber 38 with the atmospheric pressure of the oil sump 13, when the control valve 16' is actuated by the actuator 17.

Claims (9)

  1. Variable capacity lubricant vane pump (10;10') for lubrication of an interval combustion engine (12), with
    radially slidable vanes (24) arranged in vane slits (22) of a rotor ring (20), the vanes (24) defining pump chambers (30) therebetween,
    a capacity control ring (26) surrounding the vanes (24) and being pivotable around a pivot axis (28) thereby varying the volume of the pump chambers (30),
    a first and a second hydraulic control chamber (36,38), both control chambers (36, 38) being in part defined by the control ring (26) and thereby pivoting the control ring (26), and
    a preload spring (34) preloading the control ring (26) in one direction,
    characterized in that
    the first control chamber (36) and the second control chamber (28) are arranged on different sides with respect to the pivot axis (28) and act against each other.
  2. The variable capacity lubricant vane pump (10;10') of claim 1, wherein a pivot bearing (31) in the pivot axis (28) constitutes a sealing between the two control chambers (36,38).
  3. The variable capacity lubricant vane pump (10; 10') of claim 1 or 2, wherein the two control chambers (36,38) have different circumferential extents around the control ring (26), and, preferably, the circumferential extent of the second control chamber (38) is shorter than that of the first control chamber (36).
  4. The variable capacity lubricant vane pump (10; 10') of one of the preceding claims, wherein the preload spring (34) pushes the control ring (26) in a high pump chamber volume direction.
  5. The variable capacity lubricant vane pump (10; 10') of one of the preceding claims, wherein the first control chamber (36) is in fluidic connection with a pump outlet port (42) and is pushing the control ring (26) in a low pump chamber volume direction.
  6. The variable capacity lubricant vane pump (10,10') of one of the preceding claim, wherein the second control chamber (38) is in fluidic connection with the pump outlet port (42) and a control valve (16,16') controls the fluidic connection of the second control chamber (38) to atmospheric pressure.
  7. The variable capacity lubricant vane pump (10) of one of the preceding claims, wherein the second control chamber (38) is in fluidic connection with the pump outlet port (42) via a throttle valve (48).
  8. The variable capacity lubricant vane pump (10) of one of the preceding claims, wherein the control valve (16) is an on/off-vaive opening or closing the connection between the second control chamber (38) and atmospheric pressure.
  9. The variable capacity lubricant vane pump (10') of one of claims 1 - 7, wherein the control valve (16') is a 3-way switching valve connecting the second control chamber (38) either with the pump outlet port (42) or with the atmospheric pressure.
EP09160524.6A 2009-05-18 2009-05-18 Variable capacity lubricant vane pump Active EP2253847B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP09160524.6A EP2253847B1 (en) 2009-05-18 2009-05-18 Variable capacity lubricant vane pump
CN201010209718.3A CN101892981B (en) 2009-05-18 2010-05-18 variable capacity lubricant vane pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09160524.6A EP2253847B1 (en) 2009-05-18 2009-05-18 Variable capacity lubricant vane pump

Publications (2)

Publication Number Publication Date
EP2253847A1 true EP2253847A1 (en) 2010-11-24
EP2253847B1 EP2253847B1 (en) 2019-07-03

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WO2013038221A1 (en) * 2011-09-16 2013-03-21 Melling Do Brasil Componentes Automotivos Ltda. Single chamber variable displacement vane pump
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US9109597B2 (en) 2013-01-15 2015-08-18 Stackpole International Engineered Products Ltd Variable displacement pump with multiple pressure chambers where a circumferential extent of a first portion of a first chamber is greater than a second portion
US9181803B2 (en) 2004-12-22 2015-11-10 Magna Powertrain Inc. Vane pump with multiple control chambers
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US9494153B2 (en) 2012-11-27 2016-11-15 Hitachi Automotive Systems, Ltd. Variable displacement oil pump
US9494152B2 (en) 2012-11-27 2016-11-15 Hitachi Automotive Systems, Ltd. Variable vane displacement pump utilizing a control valve and a switching valve
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US9903367B2 (en) 2014-12-18 2018-02-27 Hitachi Automotive Systems, Ltd. Variable displacement oil pump
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