EP1318304A2 - Pompe à palettes - Google Patents

Pompe à palettes Download PDF

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Publication number
EP1318304A2
EP1318304A2 EP02026051A EP02026051A EP1318304A2 EP 1318304 A2 EP1318304 A2 EP 1318304A2 EP 02026051 A EP02026051 A EP 02026051A EP 02026051 A EP02026051 A EP 02026051A EP 1318304 A2 EP1318304 A2 EP 1318304A2
Authority
EP
European Patent Office
Prior art keywords
pressure
pump
pressure medium
medium flow
valve
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
EP02026051A
Other languages
German (de)
English (en)
Other versions
EP1318304A3 (fr
EP1318304B1 (fr
Inventor
Johann Merz
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.)
Robert Bosch Automotive Steering GmbH
Original Assignee
ZF Lenksysteme 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 ZF Lenksysteme GmbH filed Critical ZF Lenksysteme GmbH
Publication of EP1318304A2 publication Critical patent/EP1318304A2/fr
Publication of EP1318304A3 publication Critical patent/EP1318304A3/fr
Application granted granted Critical
Publication of EP1318304B1 publication Critical patent/EP1318304B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F04C2/3446—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 more than one line or surface

Definitions

  • the invention relates to a vane pump for generating of a pressure medium flow to a consumer according to the preamble of claim 1.
  • a generic vane pump is from DE 41 36 150 A1 known.
  • the generic vane pump has in one Pump housing a non-rotatably mounted cam ring on.
  • a rotor is arranged inside the cam ring, which has a plurality of slots which are essentially are directed radially outwards.
  • In the slots are wings movably guided their movement, at a rotation of the rotor, through the inner contour of the Curve ring is controlled.
  • the working chambers each have a suction and pressure zone on.
  • the pump known from DE 41 36 150 A1 is used, for example for power steering of a motor vehicle used.
  • To the very different Speeds of the drive motor to the pressure medium requirement To adapt the consumer, such vane pumps equipped with a flow control valve. This is to ensure that the liquid flow to the auxiliary system at a high pump speed the liquid flow at a low pump speed equivalent.
  • the generic document describes a vane pump where the pressure medium flows from the two outlet chambers connected in series at high speeds become.
  • the construction is disadvantageous the vane pump with the special flow control valve relatively complex.
  • a Actuation of the flow control valve only reached when there is a corresponding resistance at the throttle point. Disadvantageously, this must be a high one Volume flow are promoted, the corresponding output requires and an undesirable heat development caused.
  • Vane pumps From the further prior art are two-winged Vane pumps known, mostly not regulated are or have a bypass control. There are also known vane pumps, in which a vane side is short-circuited. The efficiency of this Vane pumps are however lower and the volume flow control to a consumer even less precise, than in the generic vane pump, the has already proposed improvements for this.
  • the known vane pumps mostly promote high volume against a throttle or against a Resistance is led and if necessary by a Flow control valve and a bypass line traceable is.
  • the losses go directly into temperature over and warm up the pressure medium circuit significantly. This makes the use of appropriate coolers necessary, their size proportional to the pressures increases. Because especially in the automotive sector always more hydraulic power is required to go up those from the vane pumps known so far resulting performance losses, which are directly in the Knock down fuel consumption, significantly.
  • the present invention is based on the object to create a vane pump that the aforementioned Solves disadvantages of the prior art, in particular the efficiency at higher speeds clearly improved and at a low cost, compact Design an independent power control and a allows precise volume flow control to a consumer.
  • the shut-off valve optimizes the efficiency of the vane pump and enables a compact and inexpensive Construction.
  • a piston of the shut-off valve can be controlled depending on the pump speed, the piston of the shut-off valve on a first Piston side on the pump pressure side and on the opposite side, second piston side on the rear wing oil passage connected.
  • the pressure-independent switching is simple by pressurizing the piston on both sides reached.
  • the speed dependency is thereby achieved that the second piston side on the rear wing oil passage connected.
  • the pressure medium In the rear wing oil channel does the pressure medium have both the operating pressure, i.e. the pressure on the pump pressure side as well, with increasing Pump speed, a superimposed back pressure.
  • the operating pressure of the rear wing oil duct results in a known manner from the connection of the rear wing oil duct through bores and grooves with the pump pressure side.
  • the occurring with increasing speed Back pressure results from the movement of the wings the slots of the rotor.
  • the rear wing pump arises from the fact that the wings in the area of the inlet chambers from the perspective of the rear wing oil duct migrate outwards and thus pressure medium Aspirate from the pressure collection chamber or the pump pressure side. This pressure medium is in the area of the outlet chambers pushed out of the slots again.
  • the delivery rate is defined as the wing front area times Stroke and is speed-proportional. These are around a small amount of oil.
  • the inventor recognized that the speed dependence of the dynamic pressure in the rear wing area used to control the shut-off valve can be and therefore a particularly advantageous Power control and precise volume flow control to a consumer is possible.
  • start valve is a spring has, which counteracts the pressure of the rear wing oil channel.
  • the spring is advantageously a first Switch position of the shut-off valve guaranteed in which is the pressure medium flow from the first outlet chamber Can be fed to the pressure collection chamber via a check valve is.
  • the first switch position of the shut-off valve is present at low pump speeds.
  • the spring is designed as a compression spring and on the first one connected to the pump pressure side Piston side arranged.
  • the shut-off valve thus has essentially two switching positions.
  • the first switch position in which the Is stretched spring, the pressure medium flow from the first outlet chamber to the pump pressure side or in the Pressure collection room promoted.
  • the second piston side opposite the spring which is connected to the rear wing oil duct, due to the proportionally increasing speed-dependent increase Pressure applied.
  • This pressure moves the piston with increasing speed in the spring direction and opens thus a drain control edge that allows a pressure-free drain of the pressure medium of the first outlet chamber for Pump suction side enables.
  • the pressure medium flow is thus the shortest way to Pump suction side returned.
  • the energy that the shorted or returned Brings pressure medium flow with it, can Charging the pressure medium flow coming from the suction connection be used.
  • the one from the suction port and the intersection formed injector thus causes that the returned pressure medium flow optimally Pump suction side is supplied without the pressure medium inflow is hindered from the outside. Resulting from it there are other energetic advantages for the vane pump.
  • shut-off valve in a pump cover is integrated.
  • the vane pump has a pump suction side 1 a suction port 2 and a pump pressure side 3, the leads to a consumer, not shown, on.
  • the vane pump is particularly suitable to supply a power steering system Motor vehicle.
  • a drive shaft is in a pump housing 4 5 stored with a located on it Rotor 6 is connected.
  • the rotor 6 points radially arranged slots 7 in which wings 8 slidably are led.
  • ten wings 8 may be provided.
  • the blades 8 and the rotor 6 are formed by a cam ring 9, which is connected to the pump housing 4 such that it cannot rotate is enclosed. Between the cylindrical Surrounding surface of the rotor 6 and the elliptical Bore of the cam ring 9 are the two Working chambers 10. The working chambers 10 are in the generally crescent-shaped. The funding volume results from the largest possible sickle segment between two blades 8 and the width of the rotor 6 or the wing 8.
  • FIG. 2 A schematic representation of the working chambers 10 is shown in Fig. 2. It follows that each Working chamber 10 each have a suction zone with an inlet chamber 11 or 12 and a pressure zone with an outlet chamber 13 or 14 have. The pressure medium flows out the outlet chambers 13, 14 are in a pressure collection space 15 feasible.
  • the vane pump has a rear wing oil channel 16, which does not have bores and grooves shown in more detail, with the pump pressure side 3 or the pressure collection chamber 15 connected is.
  • the rear wing oil channel 16 is also with a so-called cold start groove 17 connected.
  • the pressure medium flow from the first outlet chamber 13 by means of a shut-off valve 18, which is integrated in the pump cover 19, controllable.
  • the pressure medium flow is low Pump speeds the pressure collection chamber 15 and at higher pump speeds short-circuited or directly the pump suction side 1 supplied.
  • the shut-off valve 18 a piston 20 which is dependent the pump speed is controllable.
  • the piston 20 of the shut-off valve 18 is on a first piston side 21 to the pump pressure side 3 or the pressure collection space 15 connected.
  • the rear wing oil duct is on a second piston side 22 16 connected.
  • the shutoff valve 18 also has a spring 23 on the pressure of the pressure medium from the rear wing oil duct 16 counteracts.
  • the spring 23 is on the first piston side 21 and arranged in the illustrated Embodiment designed as a compression spring.
  • the vane pump has a check valve 24 on the the pressure medium flow from the first outlet chamber 13 in can reach the pressure collection chamber 15.
  • the check valve 24 can advantageously be used as a diaphragm valve be trained.
  • the first outlet chamber 13 is then based of the schematic diagram in Fig. 2 described in more detail.
  • the intersection is designed as an injector 25.
  • the vane pump has a flow control piston 26, the Function for the device according to the invention in Fig. 2 is shown in more detail.
  • FIG. 2 shows a cam ring 9 already described which limits the rotor 6 with the wings 8.
  • the rotor 6 rotates in the direction of the arrow, making it more usual Way two working chambers 10, each with one Inlet chamber 11 or 12 and an outlet chamber 13 or 14 are formed.
  • this pressure medium from the inlet chambers 11 and 12 conveyed to the outlet chambers 13 and 14, respectively.
  • the pressure medium flow is controlled from the first outlet chamber 13 in a Exhaust line 30 drained, which is in Direction to the shut-off valve 18 and the check valve 24 branches. At low pump speeds the shut-off valve 18 is closed (as in FIG. 2 shown), so that the pressure medium flow from the controlled Outlet line 30 through the check valve 24 flows into the main pressure line 29.
  • the piston 20 of the shut-off valve 18 in the direction of the spring 23 moves such that a shutdown control edge 31 opens, an outflow of the pressure medium flow from the first outlet chamber 13 or the controlled one Outlet line 30 to the pump suction side 1 allows.
  • the check valve 24 prevents this Case a discharge of the pressure medium flow from the second outlet chamber 14 or from the main pressure channel 29 via the cut-off control edge 31 back to the pump suction side 1.
  • the pressure medium flow becomes the first Outlet chamber 13 into a pressure medium flow from a Oil container line 33 of an oil container 34 injected.
  • the piston 20 is actuated through the rear wing oil channel 16 the one with the second piston side 22 is connected by a rear wing oil line 35.
  • the speed-dependent actuation of the piston 20 takes place thereby by the already mentioned "rear wing pump", which is proportional to the radial movement of the wings 8 with the speed increasing, superimposed Back pressure generated.
  • the rear wing oil passage 16 has to increase the pressure with increasing speed also Throttling points 36. In that shown in Fig. 2 Embodiment are four throttling points 36 provided. Of course, there are also configurations feasible that a non-proportional Allow rise of the dynamic pressure.
  • the Main pressure channel 29 is through a branch channel 37 connected to the first piston side 21.
  • a control panel 38 In the main pressure line leading to the consumer 29 is a control panel 38, which, for control a bypass line 39, with the flow control piston 26 corresponds.
  • the bypass line 39 should one Excess pressure medium flow back to the pump suction side 1 lead. This ensures that a constant regulated pressure medium flow to the consumer arrives. It is particularly advantageous if by the shut-off valve 18 or the flow control piston 26 a straight or when the pump speed increases falling course of the pressure medium flow to the consumer is feasible.
  • the pressure medium flow to the consumer makes sense, because at a higher pump speed, the driving speed is correspondingly higher, so that a higher Steering resistance, driving dynamics and driving experience improved.
  • the flow control piston 26 is designed such that the flow control piston 26 from the bypass line 39 a certain, predetermined pressure opens.
  • the pressure who keeps the flow control piston 26 closed, will by a flow control piston spring 40 and a Current control line 41 built.
  • the power control line 41 is with the pressure of the pressure medium to the consumer applied.
  • the pressure on the flow control piston 26 opens, is applied through the main pressure line 29 or it becomes a differential pressure when flowing through the control panel 38 generated, the reduced Pressure on the side with the current control spring acts. at increasing volume flow, the differential pressure and opens the bypass 39.
  • the bypass line 39 forms with a suction line 42, into which the pressure medium may have been previously was injected from the return line 32, one Bypass injector 43.
  • the bypass line 39 can, for example as a intersection in the suction line 42 be introduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP20020026051 2001-12-07 2002-11-22 Pompe à palettes Expired - Fee Related EP1318304B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10160286 2001-12-07
DE2001160286 DE10160286A1 (de) 2001-12-07 2001-12-07 Flügelzellenpumpen

Publications (3)

Publication Number Publication Date
EP1318304A2 true EP1318304A2 (fr) 2003-06-11
EP1318304A3 EP1318304A3 (fr) 2003-09-10
EP1318304B1 EP1318304B1 (fr) 2009-02-18

Family

ID=7708468

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020026051 Expired - Fee Related EP1318304B1 (fr) 2001-12-07 2002-11-22 Pompe à palettes

Country Status (2)

Country Link
EP (1) EP1318304B1 (fr)
DE (2) DE10160286A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1378665A1 (fr) * 2002-07-03 2004-01-07 ZF Lenksysteme GmbH Pompe à palettes
EP2476905A3 (fr) * 2011-01-13 2015-01-21 Hamilton Sundstrand Corporation Compresseur de vanne sans soupape

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10354577A1 (de) * 2003-11-21 2005-06-16 Zf Friedrichshafen Ag Pumpeneinrichtung, insbesondere zur Förderung von Getriebeöl
DE102020105173A1 (de) 2020-02-27 2021-09-02 Fte Automotive Gmbh Pumpenaggregat für einen Antriebsstrang eines Kraftfahrzeugs

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4136150A1 (de) 1991-11-02 1993-05-06 Zf Friedrichshafen Ag, 7990 Friedrichshafen, De Fluegelzellenpumpe

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB559108A (en) * 1940-11-15 1944-02-04 Cyril Alphonso Pugh Improvements in or relating to fuel supply systems for internal-combustion engines
JPS61119472A (ja) * 1984-11-15 1986-06-06 Toyoda Mach Works Ltd ベ−ンポンプの容量切替装置
EP0522505A3 (en) * 1991-07-09 1993-07-14 Toyoda Koki Kabushiki Kaisha Variable-displacement vane pump
DE4136151C2 (de) * 1991-11-02 2000-03-30 Zahnradfabrik Friedrichshafen Flügelzellenpumpe
JPH0655946U (ja) * 1993-01-12 1994-08-02 株式会社ユニシアジェックス ベーンポンプの流量制御機構

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4136150A1 (de) 1991-11-02 1993-05-06 Zf Friedrichshafen Ag, 7990 Friedrichshafen, De Fluegelzellenpumpe

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1378665A1 (fr) * 2002-07-03 2004-01-07 ZF Lenksysteme GmbH Pompe à palettes
EP2476905A3 (fr) * 2011-01-13 2015-01-21 Hamilton Sundstrand Corporation Compresseur de vanne sans soupape

Also Published As

Publication number Publication date
DE10160286A1 (de) 2003-06-18
EP1318304A3 (fr) 2003-09-10
EP1318304B1 (fr) 2009-02-18
DE50213284D1 (de) 2009-04-02

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