EP2253847B1 - Variable capacity lubricant vane pump - Google Patents
Variable capacity lubricant vane pump Download PDFInfo
- Publication number
- EP2253847B1 EP2253847B1 EP09160524.6A EP09160524A EP2253847B1 EP 2253847 B1 EP2253847 B1 EP 2253847B1 EP 09160524 A EP09160524 A EP 09160524A EP 2253847 B1 EP2253847 B1 EP 2253847B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- pump
- control chamber
- chamber
- chambers
- 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.)
- Active
Links
- 239000000314 lubricant Substances 0.000 title claims description 27
- 230000036316 preload Effects 0.000 claims description 13
- 238000002485 combustion reaction Methods 0.000 claims description 8
- 238000007789 sealing Methods 0.000 claims description 4
- 238000005461 lubrication Methods 0.000 claims description 2
- 238000005086 pumping Methods 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
Images
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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Rotary Pumps (AREA)
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 disclosed. 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. -
US 2008/0107554 A1 discloses a variable capacity lubricant vane pump with counter-acting control chambers. The first control chamber is directly connected with the pump outlet port and the second control chamber is connected to the pump inlet pressure. -
WO 2005/026553 A1 discloses a variable capacity lubricant vane pump with a first control chamber being directly connected with the pump outlet pressure and a second counter acting control chamber connected to the pump outlet pressure via a throttle valve. The second control chamber is also conntected to atmospheric pressure via an on/off valve which is itself controlled by the pump outlet pressure.US 2002/0172610 A1 discloses a variable capacity lubricant vane pump with two counter acting control chambers, whereby both control chambers are connected and disconnected by one double-valve arrangement and whereby a throttle valve provided. -
DE 2913414 A1 discloses a variable capacity lubricant vane pump with two counter acting control chambers, which are both synchronically switched to different pressure levels by a complex valve arrangement. -
DE 10039347 A1 discloses a variable capacity vane pump with two counter acting control chambers whereby both control chambers are connected to different pressure levels by a complex valve mechanism. -
WO 2007/128106 A1 discloses a variable capacity vane pump with two or three control chambers. All control chambers are connected to the pump outlet pressure by a switchable valve arrangement. - 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.
- 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.
- 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, 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.
- In one alternative embodiment, 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.
- This control valve is a simple on/off valve closing and opening a fluidic line between the second control chamber and the atmospheric pressure.
- In another alternative embodiment, a control valve realized as a 3-way valve connects 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 valves. 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 and3 , twodifferent lubricant pumps 10; 10' are shown which provide aninternal combustion engine 12 with a lubricant, i.e. oil. The lubricant finally flows from thecombustion engine 12 into aoil sump 13 which is under atmospheric pressure. From theoil sump 13 the lubricant is sucked via theinlet port 40 into thepump unit 14. Thevane pumps 10; 10' provide the lubricant with a constant pumping pressure. Thelubricant pumps 10; 10' comprise a variable capacity lubricantvane pump unit 14 and acontrol valve 16; 16' controlling the pumping pressure of thevane pump unit 14 at a pump outlet port 18. - The
vane pump unit 14 is mechanically driven by thecombustion engine 12 so that thevane pump unit 14 is driven within a large rotation speed interval. Therefore, the pump chamber volume of thevane pump unit 14 can be varied in a wide range, as well. Thecontrol valve 16; 16' is for selecting one of two set pump delivery pressures at thepump outlet port 42. - The
pump unit 14 comprises arotor ring 20 withnumerous vane slits 22 wherein radiallyslidable vanes 24 are arranged. Thevanes 24 are surrounded by acapacity control ring 26 which is pivotable around apivot axis 28. Therotor ring 20, thevanes 24, thecontrol ring 26 and not shown sidewalls definenumerous pump chambers 30 therebetween. In one sidewall acircular inlet port 40 and acircular outlet port 42 are provided. The size of thepump chambers 30 can be varied by pivoting thecontrol ring 26 around thepivot axis 28. In the pivot axis 28 abearing pin 32 is arranged forming a pivot bearing 31. - The position of the
control ring 26 is determined by three elements, i.e. apreload spring 34, afirst control chamber 36 and asecond control chamber 38. - The
first control chamber 36 and thesecond control chamber 38 are provided on different sides with respect to thepivot axis 28 and, therefore, act against each other. The twocontrol chambers pin 32 so that the twocontrol chambers - The bearing
pin 32 in thepivot axis 28 forms apivot bearing 31. - The
control ring 26 is provided with two pressure equalization bores 44, 45 which directly provide thefirst control chamber 36 with the pump pressure at theoutlet port 42. - In the first embodiment of the invention, the
second control chamber 38 is connected with the pump pressure via athrottle valve 48, as shown infigure 2 . In addition, thesecond control chamber 38 can be connected to theoil sump 13 being under atmospheric pressure. - The fluidic connection between the
second control chamber 38 and the atmospheric pressure of theoil sump 13 is opened and closed by thecontrol valve 16 which is a simple on/off valve. Thecontrol valve 16 is closed in its non-actuated position by a preload spring, as shown infigure 2 . When thevalve actuator 17 is not active, thesecond 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 thesecond control chamber 38 so that identical pressures in bothcontrol chambers first control chamber 36 compared to the torque caused by thesecond control chamber 38. When thecontrol valve 16 is not activated the second control chamber is provided with the pump delivery pressure. Thesecond control chamber 38 then supports thepreload spring 34 so that a higher set pump pressure is adjusted. When thecontrol valve 16 is activated in its open position, thecontrol chamber 38 is provided with atmospheric pressure. In this case, thefirst control chamber 36 acts only against thepreload spring 34 so that thepump chambers 30 become smaller which leads to a reduced set pump pressure. - The
vane pump 10 is failsafe with respect to thecontrol valve 16 because, if theactuator 17 fails to work, thecontrol 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 thesecond control chamber 38 with thepump outlet port 42 or theoil sump 13 being under atmospheric pressure. In this embodiment, thethrottle 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 thesecond control chamber 38 with the atmospheric pressure of theoil sump 13, when the control valve 16' is actuated by theactuator 17.
Claims (1)
- Variable capacity lubricant vane pump (10') for lubrication of an internal combustion engine (12), with
radially slidable vanes (24) being 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,
the first control chamber (36) and the second control chamber (38) being arranged on different sides with respect to the pivot axis (28) and acting against each other,
the preload spring (34) pushing the control ring (26) in a high pump chamber volume direction,
characterised by
the first control chamber (36) being in fluidic connection with a pump outlet port (42) and pushing the control ring (26) in a low pump chamber volume direction, and either
the second control chamber (38) being in fluidic connection with the pump outlel port (42) and a control valve (16) controlling the fluidic connection of the second control chamber (38) to atmospheric pressure, and the control valve (16) being an on/off valve opening or closing the connection between the second control chamber (38) and atmospheric pressure,
or
a control valve (16') being a 3-way switching valve connecting the second control chamber (38) either with the pump outlet port (42) or with the atmospheric pressure,
wherein a pivot bearing (31) in the pivot axis (28) constitutes a sealing between the two control chambers (36,38), and
wherein the two control chambers (36,38) have different circumferential extents around the control ring (26), and, the circumferential extent of the second control chamber (38) is shorter than that of the first control chamber (36), 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).
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 EP2253847A1 (en) | 2010-11-24 |
EP2253847B1 true EP2253847B1 (en) | 2019-07-03 |
Family
ID=41171288
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09160524.6A Active EP2253847B1 (en) | 2009-05-18 | 2009-05-18 | Variable capacity lubricant vane pump |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP2253847B1 (en) |
CN (1) | CN101892981B (en) |
Families Citing this family (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9181803B2 (en) | 2004-12-22 | 2015-11-10 | Magna Powertrain Inc. | Vane pump with multiple control chambers |
EP2476914B1 (en) * | 2011-01-13 | 2017-08-02 | Pierburg Pump Technology GmbH | Electric vehicle coolant pump |
DE112012001982A5 (en) * | 2011-05-05 | 2014-01-30 | Ixetic Bad Homburg Gmbh | variable |
WO2013038221A1 (en) * | 2011-09-16 | 2013-03-21 | Melling Do Brasil Componentes Automotivos Ltda. | Single chamber variable displacement vane pump |
DE102011086175B3 (en) * | 2011-11-11 | 2013-05-16 | Schwäbische Hüttenwerke Automotive GmbH | Rotary pump with improved sealing |
JP5688003B2 (en) * | 2011-12-21 | 2015-03-25 | 日立オートモティブシステムズ株式会社 | Variable displacement oil pump |
JP5679958B2 (en) * | 2011-12-21 | 2015-03-04 | 日立オートモティブシステムズ株式会社 | Variable displacement pump |
JP6154386B2 (en) * | 2012-09-07 | 2017-06-28 | 日立オートモティブシステムズ株式会社 | Variable displacement oil pump and oil supply system using the same |
JP6082548B2 (en) * | 2012-09-07 | 2017-02-15 | 日立オートモティブシステムズ株式会社 | Variable displacement pump |
JP6050640B2 (en) * | 2012-09-07 | 2016-12-21 | 日立オートモティブシステムズ株式会社 | Variable displacement oil pump |
JP6006098B2 (en) | 2012-11-27 | 2016-10-12 | 日立オートモティブシステムズ株式会社 | Variable displacement pump |
JP6004919B2 (en) | 2012-11-27 | 2016-10-12 | 日立オートモティブシステムズ株式会社 | Variable displacement oil pump |
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 |
JP5960616B2 (en) * | 2013-01-21 | 2016-08-02 | トヨタ自動車株式会社 | Variable displacement oil pump |
EP2770209B1 (en) * | 2013-02-21 | 2019-06-26 | Pierburg Pump Technology GmbH | Variable displacement lubricant pump |
EP2971779B1 (en) * | 2013-03-13 | 2020-08-05 | Magna Powertrain FPC Limited Partnership | Vane pump with multiple control chambers |
WO2014146675A1 (en) * | 2013-03-18 | 2014-09-25 | Pierburg Pump Technology Gmbh | Lubricant vane pump |
US10563652B2 (en) | 2014-07-18 | 2020-02-18 | Melling Tool Company | Variable displacement vane pump |
JP2016104967A (en) | 2014-12-01 | 2016-06-09 | 日立オートモティブシステムズ株式会社 | Variable capacity type oil pump |
JP6410591B2 (en) | 2014-12-18 | 2018-10-24 | 日立オートモティブシステムズ株式会社 | Variable displacement oil pump |
DE102015223414A1 (en) | 2015-11-26 | 2017-06-01 | Robert Bosch Gmbh | Variable displacement pump with an adjusting arm having adjusting ring for flow adjustment of the variable |
JP6039831B2 (en) * | 2016-01-13 | 2016-12-07 | 日立オートモティブシステムズ株式会社 | Variable displacement pump |
JP6917517B2 (en) * | 2017-08-03 | 2021-08-11 | ピエルブルグ ポンプ テクノロジー ゲーエムベーハーPierburg Pump Technology Gmbh | Variable Capacity Lubricating Oil Vane Pump |
US11635076B2 (en) * | 2021-01-22 | 2023-04-25 | Slw Automotive Inc. | Variable displacement vane pump with improved pressure control and range |
Family Cites Families (12)
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DE2913414A1 (en) | 1979-04-04 | 1980-10-16 | Gustav Beyer | Thermoelectric carburettor for IC engine - uses variable electric current to vaporise fuels of different boiling points prior to mixing with air |
DE3913414A1 (en) * | 1989-04-24 | 1990-10-25 | Walter Schopf | Variable-delivery rotary-vane pump - has compression zone in sections supplying separate hydraulic circuits |
US6352415B1 (en) | 1999-08-27 | 2002-03-05 | Bosch Braking Systems Co., Ltd. | variable capacity hydraulic pump |
US6688862B2 (en) | 2000-06-29 | 2004-02-10 | Tesma International Inc. | Constant flow vane pump |
ITBO20030528A1 (en) | 2003-09-12 | 2005-03-13 | Pierburg Spa | PUMPING SYSTEM USING A PALETTE PUMP |
EP1800007B1 (en) * | 2004-09-20 | 2013-12-25 | Magna Powertrain Inc. | Pump with selectable outlet pressure |
US7794217B2 (en) | 2004-12-22 | 2010-09-14 | Magna Powertrain Inc. | Variable capacity vane pump with dual control chambers |
JP2007239626A (en) * | 2006-03-09 | 2007-09-20 | Hitachi Ltd | Variable displacement vane pump and control method for variable displacement pump |
US20070224067A1 (en) * | 2006-03-27 | 2007-09-27 | Manfred Arnold | Variable displacement sliding vane pump |
DE112007001131B4 (en) | 2006-05-05 | 2015-02-05 | Adrian Constantin Cioc | Continuously adjustable rotary vane pump and corresponding system |
US8297943B2 (en) | 2006-11-06 | 2012-10-30 | Magna Powertrain, Inc. | Pump control using overpressure source |
US7862306B2 (en) * | 2007-02-06 | 2011-01-04 | Gm Global Technology Operations, Inc. | Pressure regulating variable displacement vane pump |
-
2009
- 2009-05-18 EP EP09160524.6A patent/EP2253847B1/en active Active
-
2010
- 2010-05-18 CN CN201010209718.3A patent/CN101892981B/en active Active
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
EP2253847A1 (en) | 2010-11-24 |
CN101892981B (en) | 2015-10-21 |
CN101892981A (en) | 2010-11-24 |
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