EP1806504A1 - Leerlaufbetriebssystem für tandempumpe - Google Patents

Leerlaufbetriebssystem für tandempumpe Download PDF

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Publication number
EP1806504A1
EP1806504A1 EP05770828A EP05770828A EP1806504A1 EP 1806504 A1 EP1806504 A1 EP 1806504A1 EP 05770828 A EP05770828 A EP 05770828A EP 05770828 A EP05770828 A EP 05770828A EP 1806504 A1 EP1806504 A1 EP 1806504A1
Authority
EP
European Patent Office
Prior art keywords
spool
supply channel
fluid supply
channel
oil
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.)
Pending
Application number
EP05770828A
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English (en)
French (fr)
Inventor
Takeshi c/o TBK Co. Ltd. HOUJI
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.)
TBK Co Ltd
Original Assignee
TBK Co Ltd
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 TBK Co Ltd filed Critical TBK Co Ltd
Publication of EP1806504A1 publication Critical patent/EP1806504A1/de
Pending legal-status Critical Current

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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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F04C14/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • 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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/56—Number of pump/machine units in operation

Definitions

  • the present invention relates to a tandem pump which comprises two fluid pumps that are driven simultaneously by a single drive source, and in which the pressurized oil output from both fluid pumps is merged and supplied to the fluid supply destination.
  • the present invention relates to a tandem pump no-load operation device in which when the fluid supply flow rate increases and the pressure within the fluid supply channel reaches the no-load operation start pressure, one of the fluid pumps is operated under no load to reduce the power from the drive source.
  • a tandem pump includes two fluid pumps that are driven simultaneously by a single drive source, and the pressurized oil output from the respective outlets of the two fluid pumps can be at the same or different pressures.
  • Two separate actuators can be connected to the two outlets of this type of tandem pump and the actuators can be separately operated, but by merging the pressurized oil output from the two pumps and supplying a fluid supply destination, it is possible to obtain a flow rate corresponding to two fluid pumps.
  • An example of the use of the latter tandem pump is an oil pump provided in an automobile engine, for example, that supplies oil (engine oil) to an oil gallery provided in the engine block to lubricate and cool each part of the engine. This is configured so that the drive shaft of the tandem pump is driven by a gear installed on the engine crankshaft.
  • Fig. 7 shows an example of a conventional tandem pump no-load operation device.
  • a main oil pump P1 and a secondary oil pump P2 are driven simultaneously by a single drive source (an engine M).
  • a main oil supply channel L1 is connected to an oil supply destination (for example, an oil gallery provided within the engine block) OB from the outlet of the main oil pump P1 via a line filter that is not shown in the drawings.
  • a secondary oil supply channel L2 that extends from the outlet of the secondary oil pump P2 is connected to the middle portion of the main oil supply channel L1.
  • a check valve CV is installed in the secondary oil supply channel L2 to prevent the inflow of hydraulic oil from the main oil supply channel L1 towards the secondary oil pump P2 side, and an unload valve AV is installed on the secondary oil supply channel L2 between the check valve CV and the secondary oil pump P2.
  • the unload valve AV is closed, and the oil output from the secondary oil pump P2 passes through the check valve CV and flows into the main oil supply channel L1, so the oil output from both main and secondary oil pumps P1, P2 is merged and transmitted to the oil supply destination OB from the main oil supply channel L1.
  • the tandem pump no-load operation device comprises: a tandem pump comprising a main fluid pump (for example, the main oil pump 7 in the embodiments) and a secondary fluid pump (for example, the secondary oil pump 8 in the embodiments) that are driven simultaneously by a drive source; a main fluid supply channel (for example, the main oil supply channel 9 in the embodiments) that extends from an outlet of the main fluid pump to a fluid supply destination (for example, the oil supply destination OB in the embodiments); a secondary fluid supply channel (for example, the secondary oil supply channel 10 in the embodiments) that extends from an outlet of the secondary fluid pump and is connected to the middle of the main fluid supply channel; a valve bore that forms a part of the secondary fluid supply channel; a spool disposed by fitting and insertion within the valve bore so that the spool can freely move, having an internal flow channel that extends in an axial direction; an urging member (for example, the spring 30 in the embodiments) that urges the spool within the valve bore toward connection with the
  • a drain channel is provided that is connected to the valve bore, and when the spool is acted on by the pressure within the main fluid supply channel the spool can move against the force of the urging member; when the pressure within the main fluid supply channel is lower than a no-load operation start pressure, the spool is moved by the force of the urging member towards the connection with the main fluid supply channel, the link with the drain channel is closed, and the secondary fluid supply channel and the main fluid supply channel are linked by the internal flow channel; and furthermore when the pressure within the main fluid supply channel rises higher than the no-load operation start pressure, the spool moves against the force of the urging member, and the secondary fluid supply channel is connected to the drain flow channel, and the poppet is moved into a position to contact and close the end of the internal flow channel of the spool by the difference in pressure between the secondary fluid supply channel and the main fluid supply channel resulting from pressurized oil within the secondary fluid supply channel being drained.
  • a flow channel serving also as a drain opens to both the main fluid supply channel and the external peripheral surface of the poppet is provided within the poppet, and when the pressure within the main fluid supply channel exceeds the no-load operation start pressure and reaches a relief setting pressure that is still higher, the spool is acted on by the force of the relief setting pressure and is moved to a position where the flow channel serving also as a drain and the drain flow channel are connected, and the pressurized fluid within the main fluid supply channel is drained from the drain flow channel.
  • the pressurized fluid within the secondary fluid supply channel passes through the internal flow channel of the spool and flows into the main fluid supply channel. At this time the fluid output from the main and secondary fluid pumps is merged and transmitted to the fluid supply destination.
  • the spool moves in the direction opposite to the direction of the force of the urging member, the pressurized fluid within the secondary fluid supply channel is drained, the poppet contacts the spool, and the internal flow channel of the spool is closed.
  • the tandem pump no-load operation device has a configuration in which the necessary components, which are the spool, the urging member, and the poppet, are provided within a single valve bore, while maintaining the same function as the conventional art, namely when the pressure in the secondary fluid supply channel rises and reaches the no-load operation start pressure, the secondary fluid pump enters the no-load operation state which reduces the power from the drive source (and furthermore when the pressure within the main fluid supply channel reaches the relief setting pressure, the pressurized oil within the main fluid supply channel is relieved), therefore the degree of freedom during circuit design is increased, and it is possible to make the overall device more compact.
  • Fig, 1 shows a tandem pump no-load operation device according to an embodiment of the present invention.
  • the no-load operation device is provided in an automobile engine to transmit under pressure oil (engine oil) that lubricates and cools all parts of the engine to an oil supply destination (for example, an oil gallery provided within the engine block, that is not shown in the drawings) OB, and is assembled into a pump body 1 formed in a part of the crank case of the engine.
  • a pump chamber 2 is formed in the pump body 1, within which a tandem pump 3 is disposed.
  • the tandem pump 3 includes a drive gear 4, and two driven gears (a first driven gear 5 and a second driven gear 6) on either side of and meshing with the drive gear 4, the drive gear 4, the first driven gear 5, and the second driven gear 6 are rotatably supported by a drive shaft 4a, and driven shafts 5a, 6a respectively.
  • the drive shaft 4a of the drive gear 4 is driven by the crankshaft of an engine (not shown in the drawings) to rotate in the direction of the arrow shown in Fig. 1 (counterclockwise).
  • the first driven gear 5 and the second driven gear 6 rotate in the direction of the arrows shown in Fig. 1 (clockwise) in accordance with the rotation of the drive gear 4.
  • the drive gear 4 and the first driven gear 5, and the drive gear 4 and the second driven gear 6 constitute conventional gear pumps.
  • the first driven gear 5 or the second driven gear 6
  • hydraulic oil flows in from low pressure portion, and hydraulic oil is expelled from the high pressure portion created by the rotation.
  • the part above the portion where the drive gear 4 meshes with the first driven gear 5 is an inlet 7a, and the part below the meshing portion is an outlet 7b.
  • the part below the portion where the drive gear 4 meshes with the second driven gear 6 is an inlet 8a, and the part above the meshing portion is an outlet 8b.
  • the oil pump that includes the drive gear 4 and the first driven gear 5 is referred to as the main oil pump 7
  • the oil pump that includes the drive gear 4 and the second driven gear 6 is referred to as the secondary oil pump 8
  • the inlet 7a is referred to as the main oil pump 7 inlet
  • the outlet 7b is referred to as the main oil pump 7 outlet
  • the inlet 8a is referred to as the secondary oil pump 8 inlet
  • the outlet 8b is referred to as the secondary oil pump 8 outlet.
  • the tandem pump 3 includes the main oil pump 7 and the secondary oil pump 8 that are driven simultaneously by a single drive source (the engine). Also, a main oil supply channel 9 extends from the outlet 7b of the main oil pump 7 to which the main oil supply channel 9 is connected, and a secondary oil supply channel 10 (10a, 10b, 10c) extends from the outlet 8b of the secondary oil pump 8 to which the secondary oil supply channel 10 is connected.
  • the main oil supply channel 9 is connected to an oil supply destination OB which is not shown in the drawings, and as shown in Fig. 1, the secondary oil supply channel 10 (10a, 10b, 10c) is connected to the middle of the main oil supply channel 9.
  • a first oil inlet channel 11 that is connected to the inlet 7a of the main oil pump 7 is connected to an oil pan T
  • a second oil inlet channel 12 that is connected to the inlet 8a of the secondary oil pump 8 is connected to the middle of the first oil inlet channel 11.
  • a valve bore 13 is extended in the secondary oil supply channel 10 forming a part of the secondary oil supply channel 10, and a spool 20 whose overall shape is cylindrical is inserted into the valve bore 13 (see also Figs. 2 and 3).
  • the spool 20 includes an intermediate portion 22 having an internal flow channel 21 that extends in the axial direction, and a spring housing portion 23 provided to the left side of the intermediate portion 22 (the left side in Fig. 1), that has a cylindrical shape with a bottom and that is open to the left side, and that is disposed within the valve bore 13 so that the spool 20 can move freely in the direction of extension of the secondary oil supply channel 10.
  • the right end of a spring 30 disposed within a spring housing space 14 formed in the pump body 1 is housed within the spring housing portion 23, and the spool 20 is always forced by the spring 30 to the right (towards the main oil supply channel 9 side).
  • a hollow cylindrical shaped spool stopper 51 and a disk shaped force adjustment fitting 52 are housed within the spring housing space 14, and the spring housing space 14 is closed by an end plate 53 installed in a plate installation groove 15 provided within the pump body 1.
  • the force of the spring 30 can be adjusted as appropriate by changing and using force adjustment fittings 52 of different thicknesses.
  • spool contact surface 13a is formed in a step shape, and to the right of the spool contact surface 13a a poppet housing bore 13d is formed.
  • the poppet housing bore 13d and an aperture 13e on the right end thereof form part of the secondary oil supply channel 10.
  • the spool 20 is acted on by the force of the spring 30 and moves to the right within the valve bore 13, and can move until an end 28 (see Fig. 2) of the spool 20 on the main oil supply channel 9 side (in Fig. 1 the right side of the plane of the paper) contacts the spool contact surface 13a (see Fig. 2) formed in the valve bore 13, the position of the spool 20 at this time is referred to below as the "initial position". Also, the spool 20 is positioned in the leftmost position within the valve bore 13 when an end portion 23a of the spring housing portion 23 contacts an end portion 51a of the spool stopper 51 (see Fig. 1 and Fig. 2) from the right side, and this is referred to as the "leftmost position".
  • the poppet 40 has a large diameter trunk portion 41 and a seat portion 42 whose outer diameter is smaller than the outer diameter of the trunk portion 41 and that is located to the left side (the spool 20 side) of the trunk portion 41, and a plurality of linking holes 43b are formed in the seat portion 42 in the diametral direction.
  • the seat portion 42 can enter a right side open portion 21a of the spool 20 from the right (from the side of the main oil supply channel 9).
  • the seat portion 42 of the poppet 40 When the seat portion 42 of the poppet 40 is inside the right side open portion 21a but separated from a valve seat portion 24 formed within the internal flow channel 21 of the spool 20, the internal flow channel 21 of the spool 20 is linked to an internal space 43a of the poppet 40 via the linking holes 43b, and furthermore links with the main oil supply channel 9 through the secondary oil supply channel 10c (in this state, the poppet 40 is said to be in the open position).
  • the internal flow channel 21 of the spool 20 is closed at this part by the poppet 40 (in this state the poppet 40 is said to be in the closed position).
  • the channel formed by the internal space 43a of the poppet 40 and the plurality of linking holes 43b provided in the outer peripheral surface of the seat portion 42 of the poppet 40 is referred to as a drain multi-use linking channel 43. Therefore, when the seat portion 42 of the poppet 40 is separated from the valve seat 24 of the spool 20, as shown in Fig. 1, the internal flow channel 21 of the spool 20 is linked to the main oil supply channel 9 via the drain multi-use linking channel 43 of the poppet 40 and the secondary oil supply channel 10c.
  • a spool rod 25 whose outer diameter is smaller than the outer diameter on both sides is provided in the central portion of the intermediate portion 22 of the spool 20.
  • a left and right spool land 26a, 26b is formed, and the left and right spool lands 26a, 26b are inserted into and mate with the valve bore 13 (13b, 13c).
  • a plurality of linking holes 27 is provided along the outer peripheral surface of the left spool land 26a, and the linking holes 27 connect to the internal flow channel 21.
  • a plurality of drain apertures 29 that penetrates in the diametral direction is formed in the right spool land 26b to the right of the spool rod 25, and the drain apertures 29 are also connected to the internal flow channel 21.
  • the secondary oil supply channel 10 is explained as being divided into the part within the valve bore 13 (the channel 10b), the part from the outlet 8b of the secondary oil pump 8 to the valve bore 13 (the flow channel 10a), and the part from the valve bore 13 to the main oil supply channel 9 (the flow channel 10c), but the linking holes 27 are positioned so that they are always connected to the flow channel 10a even if the spool 20 moves from the "initial position" to the "leftmost position".
  • a hydraulic oil channel 16 is formed between the outer peripheral surface of the spool rod 25 and a seat bore 13b of the valve bore 13 and the hydraulic oil channel 16 is connected to a drain channel 17 that that leads to the oil pan T via the second oil inlet channel 12,
  • the passage between the flow channel 10a and the hydraulic oil channel 16 is obstructed by the spool land 26a mating with the seat bore 13b, but when the spool 20 moves further to the left, the flow channel 10a and the hydraulic oil channel 16 are linked.
  • the poppet 40, the spool 20, the spring 30, the spool stopper 51, and the force adjustment fitting 52 are inserted into the valve bore 13 (including the poppet bore 13d) of the pump body 1, then the force adjustment fitting 52 is pressed with a finger to compress the spring 30, and then the end plate 53 is inserted into the plate installation groove 15 of the pump body 1.
  • the tandem pump 3 no-load operation device configured in this way, when the drive gear 4 is driven to rotate, the first driven gear 5 and the second driven gear 6 that are meshed with the drive gear 4 also rotate, and the main oil pump 7 and the secondary oil pump 8 operate as pumps. Specifically, the main oil pump 7 draws in oil in the oil pan T through the inlet 7a, and expels the oil from the outlet 7b. Also, the secondary oil pump 8 draws in oil in the oil pan T through the inlet 8a, and expels the oil from the outlet 8b.
  • the oil supply destination OB for the expelled oil is the oil gallery within the engine block, and as the flow rate of the supplied oil increases the supply pressure increases. Therefore, when the rotation speed of the engine is low, the flow rate of the oil output by both the main and secondary oil pumps 7, 8 is also small, so the pressure within the oil supply channels 9, 10 is also low.
  • the output pressure from the secondary oil pump 8 acts on the internal flow channel 21, and acts to force the spool 20 to the left. Therefore, the spool 20 moves to the left from the initial position resisted by the force of the spring 30, but the output pressure is low so the amount of movement is small, and as shown in Fig.
  • the oil output from the secondary oil pump 8 that has flowed into the internal flow channel 21 pushes the poppet 40 towards the main oil supply channel 9 side (the seat portion 42 of the poppet 40 is separated from the valve seat 24 of the spool 20) and flows into the main oil supply channel 9 (see the flow of oil indicated by the arrows in Fig. 4). Therefore, the oil output from the main oil pump 7 and the oil output from the secondary oil pump 8 is merged, and transmitted to the oil supply destination OB by the main oil supply channel 9. At this time, the flow rate of oil output from both the main and secondary oil pumps 7, 8 is small, but the two flows are combined and transmitted to the oil supply destination OB, so overall a sufficient supply flow rate of lubricating oil can be ensured.
  • the secondary oil pump 8 enters the no-load operation state, and the power from the drive source (the engine) to drive the tandem pump 3 is reduced.
  • the oil output from the main oil pump 7 is transmitted to the oil supply destination OB through the main oil supply channel 9, but the flow rate of the oil output from the main oil pump 7 has already reached a sufficient magnitude, so it is possible to ensure the necessary supply flow rate of lubricating oil to the oil supply destination OB.
  • the drain apertures 29 provided on the right spool land 26b of the spool 20 open into the drain channel 17, and a part of the pressurized oil within the main oil supply channel 9 flows into the drain multi-use flow channel 43 of the poppet 40 from the flow channel 10c and into the drain flow channel 17 through the drain apertures 29 provided on the spool 20, and is returned to the oil pan T (see Fig. 6).
  • the pressure within the main oil supply channel 9 is equal to or greater than the relief setting pressure, the drain multi-use flow channel 43 is connected to the drain flow channel 17 via the drain apertures 29, and the pressurized oil within the main oil supply channel 9 is drained.
  • This type of drain operation (relief operation) of the pressurized oil within the main oil supply channel 9 by the spool 20 and the poppet 40 is an operation as a relief valve (pressure regulator valve), and the pressure within the main oil supply channel 9 is prevented from exceeding a predetermined maximum pressure (relief setting pressure) by this type of relief operation, so safety of the circuit is ensured.
  • the "no-load operation start pressure" at which the no-load operation of the secondary oil pump 8 starts and the “relief setting pressure” at which pressurized oil within the main oil supply channel 9 is relieved as described above can be arbitrarily set by the spring characteristics of the spring 30 and the initial displacement (the displacement of the spring 30 when the spool 20 is in the initial position). Therefore, to change the no-load operation start pressure or the relief setting pressure the spring 30 may be changed for a spring with different spring characteristics, or the force adjustment fitting 52 may be changed for a fitting with a different thickness.
  • tandem pump no-load operation device when the pressure in the secondary oil supply channel 10 reaches the no-load operation start pressure, the secondary oil pump 8 enters the no-load operation state and the drive power from the drive source is reduces, furthermore, when the pressure in the main oil supply channel 9 reaches the relief setting pressure, the pressurized oil within the main oil supply channel 9 is relieved, so the same function as the conventional art is maintained, and the necessary components which are the spool 20, the spring 30, and the poppet 40 are provided within a single valve bore 13, so the degree of freedom of layout during circuit design is high, and it is possible to make the overall device more compact.
  • the drain multi-use flow channel 43 that is open to both the main oil supply channel 9 and the outer peripheral surface of the poppet 40 is provided within the poppet 40, and the drain apertures 29 are provided in the valve spool 20, and when the pressure within the main oil supply channel 9 reaches the relief setting pressure, the drain multi-use flow channel 43 is connected to the drain apertures 29, and the pressurized oil within the main oil supply channel 9 is drained, and the spool 20, the poppet 40, and the spring 30 have been configured to function as a relief valve, but the drain multi-use flow channel 43 and the drain apertures 29 may be omitted, and a separate relief valve provided in the main oil supply channel 9,
  • the components that perform the function of the check valve and the unload valve in the conventional configuration, namely the spool, the poppet, and the spring are housed within a single valve bore, so the effect that the configuration can be simplified compared with conventional art can be sufficiently obtained.
  • the oil supply destination of the present invention may be a fluid actuator, and the device may be used to control the operation speed of the actuator in accordance with the load.
  • the fluid output from and supplied by the tandem pump was oil, but the fluid is not limited to oil, and water or air may be used.
  • the two fluid pumps comprising the tandem pump were gear pumps, but provided two fluid pumps are driven simultaneously by a single drive source, other forms of pump may be used (for example, vane pumps, piston pumps, and so on).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
EP05770828A 2004-09-22 2005-08-03 Leerlaufbetriebssystem für tandempumpe Pending EP1806504A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2004274855 2004-09-22
PCT/JP2005/014610 WO2006033207A1 (ja) 2004-09-22 2005-08-03 タンデムポンプの無負荷運転装置

Publications (1)

Publication Number Publication Date
EP1806504A1 true EP1806504A1 (de) 2007-07-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP05770828A Pending EP1806504A1 (de) 2004-09-22 2005-08-03 Leerlaufbetriebssystem für tandempumpe

Country Status (5)

Country Link
US (1) US20080107545A1 (de)
EP (1) EP1806504A1 (de)
JP (1) JPWO2006033207A1 (de)
CN (1) CN100419267C (de)
WO (1) WO2006033207A1 (de)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5007085B2 (ja) * 2006-08-15 2012-08-22 株式会社Ｔｂｋ タンデムポンプのバルブ構造
DE102006056844A1 (de) * 2006-12-01 2008-06-05 Robert Bosch Gmbh Innenzahnradpumpe
JP5232843B2 (ja) * 2010-09-16 2013-07-10 株式会社山田製作所 可変流量オイルポンプ
JP5232842B2 (ja) * 2010-09-16 2013-07-10 株式会社山田製作所 可変流量オイルポンプ
JP5923361B2 (ja) 2012-03-28 2016-05-24 株式会社山田製作所 可変流量オイルポンプを備えたエンジン
CN103277505B (zh) * 2013-05-30 2015-10-28 长城汽车股份有限公司 汽车、自动变速器及混合动力液压控制系统
CN105370567B (zh) * 2015-12-14 2017-08-29 贵州红林机械有限公司 自动分压式双联齿轮泵
US9464482B1 (en) 2016-01-06 2016-10-11 Isodrill, Llc Rotary steerable drilling tool
US9657561B1 (en) 2016-01-06 2017-05-23 Isodrill, Inc. Downhole power conversion and management using a dynamically variable displacement pump
CN106050763B (zh) * 2016-08-15 2018-01-05 阜新北鑫星液压有限公司 一种转控恒流液压油泵
CN116321561A (zh) * 2023-03-24 2023-06-23 西南石油大学 一种用于超临界二氧化碳压裂的co2加热装置

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2669256A (en) * 1951-10-26 1954-02-16 Bendix Aviat Corp Fluid-metering valve for hydraulic motor control systems
US2887060A (en) * 1953-06-22 1959-05-19 American Brake Shoe Co Variable volume pumping mechanism
US3692432A (en) * 1970-12-22 1972-09-19 Ford Motor Co Two-stage positive displacement pump
US3985472A (en) * 1975-04-23 1976-10-12 International Harvester Company Combined fixed and variable displacement pump system
US4204811A (en) * 1977-08-19 1980-05-27 The Garrett Corporation Fluid pumping system
US4245964A (en) * 1978-11-08 1981-01-20 United Technologies Corporation Efficiency fluid pumping system including sequential unloading of a plurality of pumps by a single pressure responsive control valve
US4478043A (en) * 1982-01-18 1984-10-23 The Garrett Corporation Method for controlling the operation of an hydraulic assist turbocharger
US4502845A (en) * 1983-03-24 1985-03-05 General Motors Corporation Multistage gear pump and control valve arrangement
US5087177A (en) * 1989-10-31 1992-02-11 Borg-Warner Automotive, Inc. Dual capacity fluid pump
US5338161A (en) * 1991-06-19 1994-08-16 Dana Corporation Gear pump having internal bypass valve
US5241826A (en) * 1992-07-21 1993-09-07 Stearns Charles F Fixed geometry variable displacement pump system
KR100243893B1 (ko) * 1993-09-30 2000-03-02 다나까 도미오 기어펌프
US5797732A (en) * 1993-12-28 1998-08-25 Unisia Jecs Corporation Variable capacity pump having a pressure responsive relief valve arrangement
JP3815805B2 (ja) * 1994-11-15 2006-08-30 富士重工業株式会社 自動変速機のポンプ吐出量制御装置
JPH09126157A (ja) * 1995-08-29 1997-05-13 Aisin Seiki Co Ltd タンデムポンプ装置
JPH10131751A (ja) * 1996-10-29 1998-05-19 Aisin Seiki Co Ltd タンデムポンプ装置
KR100221591B1 (ko) * 1997-03-22 1999-09-15 토니헬 보조 펌프 구조
US6186750B1 (en) * 1999-04-27 2001-02-13 Borgwarner, Inc. Oil pump control valve spool with pilot pressure relief valve
US6206044B1 (en) * 1999-12-09 2001-03-27 Eaton Corporation By-pass solenoid with integral check valve
JP2002070757A (ja) * 2000-08-31 2002-03-08 Tokico Ltd 可変容量ギヤポンプ
FR2826069B1 (fr) * 2001-06-15 2004-03-12 Renault Pompe volumetrique a double engrenage
JP3968266B2 (ja) * 2002-04-30 2007-08-29 株式会社東芝 液圧発生装置
JP4065721B2 (ja) * 2002-05-14 2008-03-26 社団法人日本航空宇宙工業会 直列並列切り替え用ダブルギアポンプおよび切り替え回路
US20040101420A1 (en) * 2002-11-18 2004-05-27 Breeden Robert H. Solenoid regulated pump assembly

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006033207A1 *

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US20080107545A1 (en) 2008-05-08
CN100419267C (zh) 2008-09-17
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JPWO2006033207A1 (ja) 2008-05-15
CN101027485A (zh) 2007-08-29

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