EP1922487B1 - Pompe volumétrique présentant un volume de transport variable - Google Patents

Pompe volumétrique présentant un volume de transport variable Download PDF

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Publication number
EP1922487B1
EP1922487B1 EP06764316.3A EP06764316A EP1922487B1 EP 1922487 B1 EP1922487 B1 EP 1922487B1 EP 06764316 A EP06764316 A EP 06764316A EP 1922487 B1 EP1922487 B1 EP 1922487B1
Authority
EP
European Patent Office
Prior art keywords
pressure
cam ring
positive displacement
fluid connections
housing
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.)
Expired - Fee Related
Application number
EP06764316.3A
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German (de)
English (en)
Other versions
EP1922487A1 (fr
Inventor
Günter DRASKOVITS
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
Robert Bosch Automotive Steering 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 Robert Bosch Automotive Steering GmbH filed Critical Robert Bosch Automotive Steering GmbH
Publication of EP1922487A1 publication Critical patent/EP1922487A1/fr
Application granted granted Critical
Publication of EP1922487B1 publication Critical patent/EP1922487B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F04C14/18—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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0046—Internal leakage control
    • 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

Definitions

  • the invention relates to a displacement pump with variable displacement according to the preamble of claim 1.
  • a generic positive displacement pump is from the DE 199 42 466 A1 known.
  • the geometric displacement pump In the generic positive displacement pump can be adjusted or adjusted by a displacement of the cam ring or the cam ring within the housing, the eccentricity between the rotor and the cam ring. Thus, the geometric displacement of the working chambers can be increased or decreased.
  • the term "geometric" delivery volume refers to the per revolution funded volume of the positive displacement pump. In an adjustable vane pump, the geometric displacement is determined by the difference between the smallest and largest cell. The volume of a single working chamber or cell is changed by the eccentricity between the rotor and the cam ring and / or by the rotation of the rotor.
  • cam ring To adjust the cam ring is according to the DE 199 42 466 A1 provided that two mutually delimited and substantially opposite pressure chambers are formed between the housing and the cam ring.
  • the pressure chambers can be acted upon with a fluid pressure.
  • the cam ring is displaced correspondingly in dependence on the pressure chamber acted on by the fluid pressure, so that the geometric delivery volume is reduced or increased. It is provided that the cam ring is shifted at high speeds such that the geometric delivery volume is reduced. Conversely, it is provided at low speeds that the cam ring is moved so that increases the geometric displacement.
  • the supply of the pressure chambers with fluid via fluid connections which are each formed at least from a bore in the housing and a corresponding bore in the outer ring.
  • the boundary between two components namely the housing and the outer ring overcome.
  • fluid escapes or creates a leakage / leakage oil.
  • the leakage oil causes in the radial gap between the housing and the outer ring undefined pressure conditions, which can lead to leaks in other areas of the pump.
  • the leakage oil exits at a seal between the housing and a housing or bearing cap. Due to the leakage oil, the seal between the housing and the housing cover must be a high pressure seal. In principle, however, low-pressure seals are to be preferred, since they are much less critical and less demanding.
  • a control piston which is connected in a known manner via holes and channels with a pressure channel and a suction channel of the pump.
  • the control piston is used to control the eccentricity of the cam ring to the rotor by the control piston via the fluid connections described the respective pressure chamber supplies fluid or allows an outflow of fluid from the other pressure chamber.
  • the JP 2001 263264 A shows an adjustable vane pump.
  • the outer ring has a plurality of openings to relieve a radial gap between the housing and outer ring of leakage fluid.
  • the present invention has for its object to provide a positive displacement pump, are avoided in the undefined pressure conditions in the radial gap between the outer ring and the housing due to leakage fluids leading to the pressure chambers fluid connections, the positive displacement pump have a cost-optimized design with the least possible sealing points should.
  • a relief hole is provided to relieve the radial gap between the housing and the outer ring of leakage or leakage oil, resulting from the fluid connections to the pressure chambers.
  • undefined pressure ratios are avoided. Leakage at other points of the pump, resulting from the undefined pressure conditions in the radial gap between the housing and the outer ring, is thus avoided.
  • the seals adjacent to the radial gap or in connection with the radial gap for example the seal between the housing and a housing or bearing cover, can be designed as low-pressure seals which are less critical for the functioning of the pump than high-pressure seals.
  • the solution according to the invention thus makes it possible On the one hand to save costs in the field of sealing the pump, on the other hand problems due to the undefined pressure conditions are avoided.
  • the fluid under high pressure which is supplied via the corresponding fluid connection of the pressurizing pressure chamber, can continue to penetrate into the radial gap between the housing and the outer ring, but is discharged through the discharge hole again. Since the high-pressure fluid must overcome a boundary between two components, namely the housing and the outer ring, the penetration of a certain amount of fluid into the gap between the components is practically unavoidable. Due to the solution according to the invention, however, the resulting undefined pressure conditions can be avoided.
  • the relief bore leads from the radial gap into a region in which the pressure level of the pump suction side prevails.
  • the region in which the pressure level of the pump suction side prevails may be, for example, the suction channel or the suction hole or a region connected thereto.
  • a control piston which is connected to the pressure chambers via in each case one of the fluid connections in such a way that the pressure chambers can be mutually connected both to the operating pressure of the pump and to a container connection, wherein the control piston forms an area has, which is designed so that it ensures a connection to the container port in each position and the discharge hole connects the radial gap with this area.
  • the relief hole thus leads advantageously in a relieved area of the control piston.
  • the region of the control piston which is designed so that it ensures a connection to the container connection in each position, be formed as a waist of the control piston.
  • the region it is also possible for the region to be formed by a groove in the housing, which surrounds the control piston in such a way that this groove ensures a connection to the container connection in every position.
  • a radial gap associated with the opening of the relief hole between the fluid chambers leading to the pressure chambers is arranged.
  • a centric or central arrangement of the opening between the two fluid connections has been found to be particularly suitable.
  • An arrangement of the radial gap associated opening of the relief bore in a region adjacent to the fluid connections to the pressure chambers or associated with the respective openings of the bores of the fluid connections, has proven to be particularly Suitably exposed to discharge leaking, high-pressure fluid from the radial gap and thus to relieve this. Since the two fluid connections are mutually acted upon by the operating pressure of the pump, the arrangement of the relief bore has been found to be particularly suitable centrally or centrally between the fluid connections.
  • two or more relief holes can be provided, the spatial arrangement with respect to the opening into the radial gap openings of the bores of the fluid connections can be selected correspondingly advantageous.
  • the figures show an embodiment of a displacement pump 1 according to the invention with a variable delivery volume as a single-stroke vane pump.
  • Single-stroke vane pumps are well known in terms of their basic operation from the general state of the art, including only for example on the DE 199 42 466 A1 as well as the DE 102 40 499 A1 is referenced. Below, therefore, only the features essential to the invention are shown in more detail.
  • the illustrated vane pump 1 is designed to generate a pressure medium flow for a power steering device of a motor vehicle.
  • the vane pump 1 has a housing 2.
  • an outer ring 3 also referred to as intermediate ring
  • a rotor 4 is mounted via a shaft 5.
  • the rotor 4 is surrounded by a cam ring 6.
  • the cam ring 6 to roll on a flattening 7 and a thickening of the outer ring 3 and thus in an elliptical space 8, which is formed in the outer ring 3, move.
  • the cam ring 6 is adjustable or displaceable within the elliptical space 8. Between the rotor 4 and the cam ring 6 9 delimited working chambers 10 are formed via rotor elements or wings. By a displacement of the cam ring 6 changes the eccentricity between the rotor 4 and the cam ring 6, whereby the volume of the working chambers 10 and thus the geometric displacement of the vane pump 1 is determined.
  • the fluid supply of the rear wing area is ensured by bores and slots 11a, 11b in a control plate 12 and a housing or bearing cap 14.
  • the control plate 12 also has kidney-shaped slots 13a, 13b, which control the fluid inlet and outlet to the working chambers 10.
  • the bearing cap 14 is provided with a rotor surface (rotor 4, wing 9 and cam ring 6) facing flat surface 15, which ensures the frontal sealing of the rotor set.
  • the bearing cap 14 has 12 corresponding kidney-shaped slots 16 a, 16 b to the control plate.
  • the bearing cap 14 contains in a preferred embodiment, the main bearing of the pump consisting of two plain bearing bushes. Optionally, a bearing of ball and plain bearings can be used. Alternatively, the main storage can be accommodated in the housing 2.
  • Fig. 1 results, the cam ring 6 pressed by a compression spring 17 in the direction of maximum deflection.
  • the compression spring 17 is mounted laterally and the necessary housing bore preferably closed with a screw 18.
  • the pressure chambers 19, 20 are separated in the lower region by the flattening 7 and in the upper region by a suitable sealing element 21 from each other. This can be caused by pressurization of the two pressure chambers 19, 20, a displacement of the cam ring 6.
  • a spring-loaded control piston 22 is provided, which is connected via fluid connections 23, 24 with the pressure chambers 19, 20.
  • the pressure chambers 19, 20 are pressurized via the fluid connections 23, 24 or can flow out of the pressure-relieved pressure chamber 19, 20 via the fluid connections 23, 24.
  • the fluid connections 23, 24 are each formed in the embodiment of a bore 23 a, 24 a in the housing 2 and a bore 23 b, 24 b in the outer ring 3.
  • the pressure chambers 19, 20 can be mutually connected by the control piston 22 both with the operating pressure of the pump and with a container port 32 and a suction channel 25. Due to the resulting pressure difference in the pressure chambers 19, 20, the displacement of the cam ring 6 is achieved.
  • a relief bore 26 is provided, to relieve a radial gap 27 between the housing 2 and the outer ring 3 of leakage.
  • the leakage liquid is formed by the fluid connections 23, 24, which must overcome the boundary between two components, namely the housing 2 and the outer ring 3.
  • the bores 23a and 23b, which form the fluid connection 23, or the bores 24a and 24b, which form the fluid connection 24, correspond or align with each other, so that a fluid flow is impeded as little as possible, but can be an injection of fluid in the radial gap 27 between the housing 2 and the outer ring 3 does not completely prevent.
  • the relief bore 26 leads from the radial gap 27 into a relieved area of the vane pump 1 in which the pressure level of the pump suction side prevails.
  • This area can be, for example, the container connection 32, the suction channel 25 or an area connected to the suction channel 25.
  • the control piston 22 has a region 28 which is designed such that it ensures a connection 29 to the container port 32 in each position and the relief bore 26 connects the radial gap 27 with this region 28.
  • the region 28 is formed as a sidecut of the control piston 22.
  • an opening 26a of the relief bore 26 assigned to the radial gap 27 is centered between the two fluid connections 23, 24 leading to the pressure chambers 19, 20 and the openings of the bores 23a and 24a or 23b and 24b leading into the radial gap 27 arranged.
  • the relief bore 26 extends obliquely from a bearing cover 14 facing portion of the outer ring 3 to the control piston 22nd
  • a arranged between the bearing cap 14 and the housing 2 seal 30 may be formed as a low pressure seal.
  • Fig. 3 shows, the vane pump 1, a pressure relief valve 31, which in response to the control piston 22 moves so that the cam ring 6 is moved in the direction of reduced promotion.
  • the pressure relief valve 31 is integrated in the control piston 22, so that the pressure-remote side of the pressure relief valve 31 is connected to the sidecut 28 of the control piston 22.
  • Fig. 3 also shows a pressure channel 33, which communicates with the spring-loaded end of the control piston 22. Since the basic operation of the control piston 22 is well known from the prior art, will not be discussed in detail.
  • connection 29 can be produced via a bore or, as provided in the exemplary embodiment, in that the connection 29 is formed by the casting core through which the suction channel 25 is formed.

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

Claims (8)

  1. Pompe volumétrique présentant un volume de transport variable, en particulier pompe à palettes à course unique, pour la production d'un courant de fluide sous pression vers un consommateur, avec un corps dans lequel est monté un rotor, avec un anneau à courbes entourant le rotor et avec des chambres de travail délimitées par des éléments de rotor entre le rotor et l'anneau à courbes, dont le volume est réglable par changement de l'excentricité entre le rotor et l'anneau à courbes, dans laquelle l'anneau à courbes est entouré par un anneau extérieur disposé dans le corps, qui maintient l'anneau à courbes librement rotatif, dans laquelle deux chambres de refoulement sont formées entre l'anneau extérieur et l'anneau à courbes, qui peuvent être mises sous pression par des liaisons fluidiques pour le déplacement de l'anneau à courbes, dans laquelle les liaisons fluidiques sont respectivement formées par au moins un alésage dans le corps et un alésage correspondant dans l'anneau extérieur, dans laquelle il est prévu un alésage de délestage (26) destiné à délester une fente radiale (27) entre le corps (2) et l'anneau extérieur (3) de liquides de fuite des liaisons fluidiques (23, 24) conduisant aux chambres de refoulement (19, 20), caractérisée en ce que l'alésage de délestage (26) conduit de la fente radiale (27) à une région dans laquelle règne le niveau de pression du côté d'aspiration de la pompe.
  2. Pompe volumétrique selon la revendication 1, caractérisée en ce que l'alésage de délestage (26) débouche dans une région de la pompe (1) raccordée à un canal d'aspiration (25).
  3. Pompe volumétrique selon les revendications 1 et 2, caractérisée en ce que l'alésage de délestage (26) débouche dans le canal d'aspiration (25).
  4. Pompe volumétrique selon la revendication 1, caractérisée en ce qu'il est prévu un piston de commande (22), qui est raccordé aux chambres de refoulement (19, 20) respectivement par une des liaisons fluidiques (23, 24), de telle manière que les chambres de refoulement (19, 20) puissent être raccordées alternativement aussi bien à la pression de service de la pompe (1) qu'à un raccord de réservoir (32), dans laquelle le piston de commande (22) présente une région (28), qui est configurée de telle manière qu'elle garantisse dans chaque position du piston de commande (22) une liaison (29) vers un raccord de réservoir (32) et que l'alésage de délestage (26) relie la fente radiale (27) à cette région (28).
  5. Pompe volumétrique selon la revendication 4, caractérisée en ce que la région est réalisée sous la forme d'un taillage (28) du piston de commande (22).
  6. Pompe volumétrique selon l'une quelconque des revendications 1 à 5, caractérisée en ce qu'une ouverture (26a) de l'alésage de délestage (26) associée à la fente radiale (27) est disposée entre les deux liaisons fluidiques (23, 24) conduisant aux chambres de refoulement (19, 20).
  7. Pompe volumétrique selon la revendication 6, caractérisée en ce que l'ouverture (26a) de l'alésage de délestage (26) est disposée entre les alésages (23a et 24a ou 23b et 24b) des deux liaisons fluidiques (23, 24), qui conduisent dans la fente radiale (27).
  8. Pompe volumétrique selon la revendication 6 ou 7, caractérisée en ce que l'ouverture (26a) de l'alésage de délestage (26) est disposé au centre entre les alésages (23a et 24a ou 23b et 24b) des deux liaisons fluidiques (23, 24).
EP06764316.3A 2005-09-09 2006-08-08 Pompe volumétrique présentant un volume de transport variable Expired - Fee Related EP1922487B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005043252.2A DE102005043252B4 (de) 2005-09-09 2005-09-09 Verdrängerpumpe mit variablem Fördervolumen
PCT/EP2006/065127 WO2007028688A1 (fr) 2005-09-09 2006-08-08 Pompe volumetrique presentant un volume de transport variable

Publications (2)

Publication Number Publication Date
EP1922487A1 EP1922487A1 (fr) 2008-05-21
EP1922487B1 true EP1922487B1 (fr) 2016-10-19

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EP06764316.3A Expired - Fee Related EP1922487B1 (fr) 2005-09-09 2006-08-08 Pompe volumétrique présentant un volume de transport variable

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EP (1) EP1922487B1 (fr)
DE (1) DE102005043252B4 (fr)
WO (1) WO2007028688A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007033194A1 (de) 2007-07-17 2009-01-22 Zf Lenksysteme Gmbh Verdrängerpumpe mit variablem Fördervolumen
DE102007000970B4 (de) 2007-10-23 2015-11-05 Robert Bosch Automotive Steering Gmbh Verdrängerpumpe mit Druckkammerdichtung
DE102015112672A1 (de) 2015-08-03 2017-02-09 Robert Bosch Automotive Steering Gmbh Verdrängerpumpe zur förderung eines fluides für einen verbraucher eines kraftfahrzeuges

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000087877A (ja) * 1998-09-10 2000-03-28 Bosch Braking Systems Co Ltd 可変容量形ポンプ
JP2001263264A (ja) * 2000-03-15 2001-09-26 Showa Corp 可変容量型ポンプ
JP3933843B2 (ja) * 2000-04-27 2007-06-20 ユニシア ジェーケーシー ステアリングシステム株式会社 可変容量形ポンプ
JP3922878B2 (ja) * 2000-12-04 2007-05-30 株式会社ジェイテクト 可変容量形ポンプ
JP3861638B2 (ja) * 2001-08-31 2006-12-20 ユニシア ジェーケーシー ステアリングシステム株式会社 可変容量形ポンプ
DE10240499A1 (de) * 2002-09-03 2004-03-11 Zf Lenksysteme Gmbh Einhubige Flügelzellenpumpe

Also Published As

Publication number Publication date
WO2007028688A1 (fr) 2007-03-15
DE102005043252A1 (de) 2007-03-15
DE102005043252B4 (de) 2016-12-08
EP1922487A1 (fr) 2008-05-21

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