EP1323926B1 - Pompe - Google Patents

Pompe Download PDF

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Publication number
EP1323926B1
EP1323926B1 EP03005717A EP03005717A EP1323926B1 EP 1323926 B1 EP1323926 B1 EP 1323926B1 EP 03005717 A EP03005717 A EP 03005717A EP 03005717 A EP03005717 A EP 03005717A EP 1323926 B1 EP1323926 B1 EP 1323926B1
Authority
EP
European Patent Office
Prior art keywords
fluid
housing
conveying device
pump
supply channel
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 - Lifetime
Application number
EP03005717A
Other languages
German (de)
English (en)
Other versions
EP1323926A2 (fr
EP1323926A3 (fr
Inventor
Willi Parsch
Dirk Webert
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.)
ixetic Bad Homburg GmbH
Original Assignee
ixetic Bad Homburg 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
Priority claimed from DE29823902U external-priority patent/DE29823902U1/de
Priority claimed from DE29823903U external-priority patent/DE29823903U1/de
Application filed by ixetic Bad Homburg GmbH filed Critical ixetic Bad Homburg GmbH
Publication of EP1323926A2 publication Critical patent/EP1323926A2/fr
Publication of EP1323926A3 publication Critical patent/EP1323926A3/fr
Application granted granted Critical
Publication of EP1323926B1 publication Critical patent/EP1323926B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C15/062—Arrangements for supercharging the working space

Definitions

  • the invention relates to a pump for conveying a fluid, in particular vane pump, with a housed in a housing conveyor, a formed in the housing, extending into the intake of the conveyor supply channel for the fluid and a serving for conveying the fluid injector device, wherein the injector under high-pressure fluid injected into the outgoing from the feed channel in one of the conveyor blast chamber fluid and thereby entrains or accelerated, the feed channel opens on both sides of the conveyor, each with a sub-channel in a blasting chamber, the injector radiates on both sides, so that in each of the two jet chambers is directed at least one jet nozzle of the injector, and wherein the housing is closed on one side by a front-side housing cover and on the other side by a bearing flange.
  • Pumps of the generic type are used for example in power steering systems and promote a special oil to cause a support of applied to the steering wheel of a motor vehicle steering force.
  • these are vane pumps which suck in oil from a reservoir provided outside the pump, for example from an external tank.
  • Such pumps are usually equipped with a flow control valve, via which oil from the high pressure area - pressure side - in the suction - suction side - the pump can be passed. From a certain pump speed and at a fixed adjustable flow rate opens the flow control valve has a discharge hole through which high-pressure oil can escape. The oil enters the suction chamber of the conveyor.
  • a pump which has a very special promotion measure for conveying the tank oil to realize a possible cavitation-free operation, namely an injector device which operates similar to a water jet pump.
  • the injector device is acted upon by fluid under high pressure, which is supplied to the injector device from the high-pressure region.
  • This high-pressure fluid injects the injector into the fluid from the supply channel, in the region of a blasting chamber upstream of the conveyor.
  • the fluid coming from the tank is entrained or accelerated and passes from there via a further channel system into the intake region of the conveyor.
  • the pump comprises an injector device which injects high-pressure fluid into the fluid emerging from feed channels in a jet chamber upstream of the conveyor and thereby entrains the same.
  • the injector device radiates on two sides into a respective blasting chamber, wherein in each of the two blasting chambers at least one blasting nozzle of the injector device is directed.
  • the US 3,359,913 shows in itself a vane pump with injector, jet nozzles and a high-pressure injection channel, wherein the injector radiates into the bearing flange and in side plates formed, the same length distribution channels.
  • a comparable vane pump is from the US 4,213,744 known.
  • the present invention is therefore based on the object, a pump of the generic type to design and further develop that a uniform charging of the cells of the conveyor is ensured. Damage due to cavitation should be effectively avoided.
  • a pump of the type mentioned above is characterized in that the blasting chamber formed on both sides of the conveyor is at least largely incorporated in the housing cover and possibly in the bearing flange and that the jet nozzles inclined obliquely downward to the outlet of the feed channel opposite wall of the housing cover and / or the bearing flange are directed.
  • the same amount of fluid should be made available under the same conditions on both sides of the housing in the respective intake region of the conveyor, ie immediately before the suction kidneys of the conveyor. Furthermore, it has been recognized that such a provision of the fluid is only possible if the supply channel for supplying the fluid coming from the tank actually opens on both sides of the conveyor, each with a sub-channel, in a blasting chamber serving to accelerate the fluid.
  • a jet nozzle of the injector is directed into each of the two jet chambers, so that due to the irradiation of the fluid under high pressure, the fluid coming from the tank is accelerated or entrained.
  • the generic type pump may have on one side of the housing a frontal housing cover and on the other side of the housing a bearing flange, which is not mandatory.
  • the blasting chamber formed on both sides of the conveying device is at least largely incorporated in the housing cover or in the bearing flange. It is conceivable that the blasting chamber is assigned to the actual housing and limited by the inner wall on the one hand of the housing cover and on the other hand, the bearing flange.
  • the fluid coming from the tank is divided on both sides of the conveyor, with acceleration of the fluid by injection taking place on these two sides of the conveyor in the respective blasting chamber.
  • the jet nozzles are inclined downwards and can preferably be directed at an angle deviating from 90 °, in particular at an acute angle (not shown in the figures), to the wall of the housing and / or the bearing flange opposite the outlet of the feed channel, so that the accelerated fluid there bounces with high energy and evades according to the contour of the wall of the housing and / or the bearing flange on both sides. Consequently, here again a division of the fluid takes place, namely on both sides of the conveyor on again two separate flow paths, both sides of the housing provided in the central bore for the conveyor or for the conveyor forming the rotary pump.
  • the injector device or its inlet is arranged substantially centrally above the conveyor.
  • Such a central arrangement of the injector has the advantage that the paths extending on both sides of the conveyor on the one hand to accelerate the fluid coming from the tank and on the other hand of the fluid under high pressure and for injection are about the same length. Accordingly, the fluid reaching the two-sided intake regions of the delivery devices is under the same pressure, so that a uniform loading of the delivery device can take place on both sides.
  • the jet nozzles are oriented such that the injected via the jet nozzle under high pressure fluid hits the fluid to be accelerated in the flow direction or at an acute angle to its flow direction.
  • the acceleration of the fluid coming from the tank is favored again, wherein the high-pressure fluid is already divided within the injector on both jet nozzles, namely at high kinetic energy of the fluid for injection.
  • the jet nozzles it is advantageous if they have an approximately round nozzle shape, so that the fluid forms a kind of jet jacket or a cylindrical / conical jet jacket on exit. Compared to a thin fine beam, this results in a larger contact surface, which is double due to the radiation on both sides by means of the jet nozzles. Finally, the fluid passes through discharge bores on both sides to the jet nozzles of the injector device.
  • the coming from the tank fluid-conducting sub-channels of the divided on both sides of the conveyor supply channel are formed in about the same length, so that in this respect equally long distances are covered by the fluid coming from the tank.
  • the oil coming from the tank is acted upon and accelerated by the injected oil under high pressure and at high kinetic energy, which is similar to a water jet pump.
  • the sub-channels of the divided on both sides of the conveyor supply channel are advantageously formed not only in about the same length, but also preferably have the same course, this course is possibly designed mirror-inverted on both sides.
  • the wall of the housing and optionally of the bearing flange is designed such that it divides the accelerated fluid impinging there approximately equally by lateral outflow and at least largely in the sense of a guide in both sides trained suction channels, wherein the suction channels in the immediate intake lead the conveyor.
  • the suction channels lead directly to the suction kidneys of the conveyor, on both sides of the conveyor on two separate flow paths, so that the suction kidneys of the conveyor are supplied at four independent locations with fluid under equal pressure and with the same volume of fluid. A uniform loading of the conveyor is guaranteed.
  • suction channels leading to the suction kidneys are at least largely of the same length, namely to avoid pressure losses in the fluid which are different in size.
  • Fig. 1 and 2 clearly show that extends into the intake, ie to the suction side 112, a supply channel 113 for the fluid. Furthermore, an injector device 114 serving to convey the fluid is provided, which operates in a manner similar to a water jet pump. This injector device 114 injects high-pressure fluid into a blasting chamber 115 upstream of the conveying devices 1, and there into the fluid emerging from the feed channel 113 and accelerates the fluid thereby or entrains the fluid with it.
  • the supply channel 113 opens on both sides of the conveyor 1, each with a sub-channel 116 in a - separate - blasting chamber 115, wherein the injector 114 emits two sides, so that in each of the two jet chambers 115 a jet nozzle 117 of the injector 114 is directed.
  • the Fig. 1 and 2 show together that the injector 114 is disposed centrally above the conveyor 1.
  • the jet nozzles 117 are aligned such that the fluid injected via the jet nozzle 117 under high pressure impinges on the fluid to be accelerated approximately in its flow direction, so that an acceleration of the fluid coming from the tank is favored again.
  • the fluid passes via the supply channel 113, the valve bore 125 and the outflow bores 126 to the two jet nozzles 117.
  • Fig. 1 and 2 show further that the sub-channels 116 of the divided on both sides of the conveyor 1 supply channel 113 are approximately equal in length, namely, namely, the supply channel 113 also equally approximately in the middle of the conveyor 1 evenly divided.
  • Fig. 1 shows that the blast chamber 115 formed on both sides of the conveyor 1 is largely incorporated in the housing cover 3 on one side and in the bearing flange 4 on the other side.
  • the jet nozzles 117 are directed orthogonally to the exit of the supply channel 113 opposite wall 118 of the housing cover 3 on one side and to the outlet of the feed channel 113 opposite wall 119 of the bearing flange 4.
  • the wall 119 of the bearing flange 4 is formed such that it divides the incident there accelerated fluid by lateral outflow approximately equally.
  • the flow path of the fluid is identified by the reference numeral 120.
  • the walls 119, 120 guide the fluid in the sense of a guide in both sides formed suction channels 121, so that a repeated division of the fluid takes place.
  • the suction channels 121 lead to suction cups, not shown in the figures, of the conveying device 1, these being arranged downstream of the direct suction region 122 of the conveying device 1.
  • Fig. 4 shows, moreover, that the suction channels 121 leading to the suction kidneys or to the suction region 122 are of approximately the same length, so that equal pressure conditions prevail on both sides in the suction region 122 and an equal volume of fluid is made available.
  • the above statements also apply to the situation on the side of the housing cover 3, wherein Fig. 3 only in a front view the Housing 2 relative to the housing cover shows, where the mouths of the feed channel 113 and the sub-channel 116 and the injector 114 and the jet nozzle 117 are shown.
  • the wall 118 of the housing cover 3 according to the representation of the bearing flange 4 in Fig. 8 is omitted for the sake of simplicity.
  • Fig. 3 shows further that the supply channel 113 with a in Fig. 3
  • a leakage oil passage 124 opens into the supply passage 113, so that recirculated pilot oil and leak oil within the supply passage 113 mix with the fluid coming from the tank.
  • the resulting total amount of fluid is then applied after exiting the supply channel 113 and the sub-channel 116 via the injector 114 or via the outflow holes 126 and the jet nozzles 117 with fluid under high pressure and thereby accelerated.
  • Fig. 5 shows in a simplified representation of a generic type pump in a sectional side view, which is here in concrete terms a vane pump with a rotation group 1 or conveyor not described here in detail.
  • a rotation group 1 is merely exemplary of the DE 39 28 029 A1 directed.
  • the pump shown here comprises - as essential components - a housing 2 and a housing 2 accommodated in the conveyor, which is the already mentioned rotation group 1.
  • the front side is on the one hand a housing 2 final housing cover 3 and on the other side - on the housing cover 3 opposite side - a subsequent to the housing 2 bearing flange 4 is provided.
  • an outwardly acting seal 5, 6 is arranged, wherein the force acting relative to the housing cover 3 seal 5 in a formed in the end face 7 of the housing 2 groove 8 is used.
  • the seal 6 is assigned to the bearing flange 4 or inserted into a groove 9 incorporated in the bearing flange 4.
  • the groove 9 could also be incorporated in the end face 10 of the housing 2.
  • the leakage path 13 is on the inside of the seal - media side - at least partially parallel to the seal 5, 6 is formed.
  • Fig. 6 shows particularly clearly that the formation of the leakage path 13, the groove 8 is formed wider than the seal 5, so that on the inside seal 14 parallel to the seal 5, the leakage path 13 is formed. Likewise, the leakage path 13 is formed by the groove 9 in the bearing flange 4, wherein in the representation of the bearing flange 4 according to Fig. 7 was dispensed with the separate representation of the seal 6.
  • FIGS. 5 to 8 show together that the grooves 8, 9 are formed as self-contained annular grooves. Accordingly, the seals 5, 6 are designed as sealing rings, wherein the leakage path 13 extends only over those areas of the grooves 8, 9 away, where leakage oil accumulates and accordingly wegzuANCn or be transported away. Only there is the leakage path 13 as an integral part of the groove 8, 9 executed, this being in view of the in Housing cover 3 formed groove 8 very particularly clearly in Fig. 6 is shown.
  • Fig. 6 Furthermore, it is hinted that the widened area of the groove 8 forming the leakage path 13 is flow-connected to the suction side 12 of the pump, namely via an integral leakage oil channel 15 Fig. 2 is further indicated, as the leakage oil 16 in the leakage path 13 - parallel to the seal 5 -, ie in the groove 8, and how the leak oil 16 is supplied from there via the leakage oil passage 15 of the suction side 12 and thus the tank oil ,
  • Fig. 5 indicated that the pressure side 11, that is, the high pressure, at least predominantly within the housing interior 17 or directly adjacent to this is sealed.
  • seals 18, 19, 20, 21 are provided, which is also here about sealing rings and / or combined seals. Consequently, the first-mentioned seals 5, 6 are substantially exposed to a lower pressure near the suction-side pressure or the tank pressure, which considerably favors the sealing effect of the pump as a whole.
  • Fig. 8 shows three specific embodiments of the groove, which may be both the groove 8 formed in the end face 7 of the housing 2 and the groove 9 formed in the bearing flange 4.
  • Fig. 8 shows in the upper diagram, that the groove 8 or 9 is formed to form the leakage path 13 substantially wider than that required to receive the seal 5 or 6.
  • the leakage path 13 is formed immediately adjacent to the seal 5 or 6, respectively on the inside of the pressure.
  • FIG. 8 shows a stepped configuration of the groove 8 or 9, wherein the seal 5 or 6 is disposed in the deeper groove area.
  • the leakage path 13 is at a slightly higher level than the groove 5 or 6 receiving groove bottom of the deeper groove area.
  • Fig. 8 shows a two-part groove 8 or 9, wherein in the context of this embodiment, the leakage path 13 is separated by a web 22 of the seal 5 or 6 receiving portion of the groove 8 or 9, wherein the web 22 is lower than the outer wall 23 of the groove 8 or 9 and the leakage path 13 is executed, so that with sufficient amount of leakage oil this can go directly to the seal 5 or 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (7)

  1. Pompe pour refoulement d'un fluide, en particulier pompe à palettes, comprenant un dispositif de refoulement (1) logé dans un carter (2), une conduite d'alimentation (113) de fluide formée dans le carter (2), s'étendant dans la zone d'aspiration (122) du dispositif de refoulement (1) et un dispositif d'injection (114) servant à refouler le fluide, le dispositif d'injection (114) injectant du fluide à haute pression dans le fluide sortant de la conduite d'alimentation (113) et entrant dans une chambre d'éjection (115) située en amont du dispositif de refoulement (1) et ledit dispositif d'injection entraînant, respectivement accélérant ainsi ce dernier fluide, la conduite d'alimentation (113) débouchant de chaque côté du dispositif de refoulement (1) par une conduite partielle (116) dans une chambre d'éjection (115) respective, le dispositif d'injection (114) injectant de deux côtés de telle manière qu'au moins une buse d'éjection (117) du dispositif d'injection (114) est orientée dans chacune des deux chambres d'éjection (115), et le carter étant fermé d'un côté par un couvercle de carter (3) frontal et de l'autre côté par une bride de palier (4), caractérisée en ce que la chambre d'éjection (115) formée de chaque côté du dispositif de refoulement (1) est insérée au moins dans une large mesure dans le couvercle de carter (3) et, le cas échéant, dans la bride de palier (4) et que les buses d'éjection (117), inclinées à l'oblique vers le bas, sont orientées vers la paroi (118) du couvercle de carter (3) et/ou de la bride de palier (4) opposée à la sortie de la conduite d'alimentation (113).
  2. Pompe selon la revendication 1, caractérisée en ce que le dispositif d'injection (114), respectivement son entrée, est disposé essentiellement au centre au-dessus du dispositif de refoulement (1).
  3. Pompe selon la revendication 1 ou 2, caractérisée en ce que les conduites partielles (116) de la conduite d'alimentation (113) divisée de chaque côté du dispositif de refoulement (1) sont à peu près de la même longueur.
  4. Pompe selon l'une des revendications 1 à 3, caractérisée en ce que les conduites partielles (116) de la conduite d'alimentation (113) divisée de chaque côté du dispositif de refoulement (1) ont à peu près le même parcours, de préférence de manière inversement symétrique.
  5. Pompe selon l'une des revendications 1 à 4, caractérisée en ce que la paroi (118) est arrondie.
  6. Pompe selon l'une des revendications 1 à 5, caractérisée en ce que la paroi (118, 119) du couvercle de carter (3) et, le cas échéant, de la bride de palier (4) est réalisée de telle manière qu'elle divise le fluide accéléré qui y arrive à peu près régulièrement par un écoulement latéral et le guide au sens d'un dispositif de guidage au moins dans une large mesure dans des conduites d'aspiration (121) formées de chaque côté.
  7. Pompe selon la revendication 6, caractérisée en ce que les conduites d'aspiration (121) conduisent à des noix d'aspiration du dispositif de refoulement (1) et que les conduites d'aspiration (121) conduisant aux noix d'aspiration peuvent être réalisées au moins dans une large mesure de la même longueur.
EP03005717A 1998-08-13 1999-08-13 Pompe Expired - Lifetime EP1323926B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE29823902U DE29823902U1 (de) 1998-08-13 1998-08-13 Pumpe
DE29823902U 1998-08-13
DE29823903U 1998-08-13
DE29823903U DE29823903U1 (de) 1998-08-13 1998-08-13 Pumpe
EP99952381A EP1108144A1 (fr) 1998-08-13 1999-08-13 Pompe

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP99952381A Division EP1108144A1 (fr) 1998-08-13 1999-08-13 Pompe

Publications (3)

Publication Number Publication Date
EP1323926A2 EP1323926A2 (fr) 2003-07-02
EP1323926A3 EP1323926A3 (fr) 2003-09-10
EP1323926B1 true EP1323926B1 (fr) 2008-09-24

Family

ID=26062134

Family Applications (2)

Application Number Title Priority Date Filing Date
EP03005717A Expired - Lifetime EP1323926B1 (fr) 1998-08-13 1999-08-13 Pompe
EP99952381A Withdrawn EP1108144A1 (fr) 1998-08-13 1999-08-13 Pompe

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP99952381A Withdrawn EP1108144A1 (fr) 1998-08-13 1999-08-13 Pompe

Country Status (5)

Country Link
US (2) US6413064B1 (fr)
EP (2) EP1323926B1 (fr)
JP (2) JP2002522707A (fr)
DE (1) DE19981557B4 (fr)
WO (1) WO2000009888A2 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1303701B1 (fr) * 2000-07-27 2005-08-31 LuK Fahrzeug-Hydraulik GmbH & Co. KG Pompe
US6857859B2 (en) * 2003-02-19 2005-02-22 Siemens Vdo Automotive Corporation Gasket for jet pump assembly of a fuel supply unit
JP4728231B2 (ja) * 2003-06-30 2011-07-20 ルーク ファールツォイク・ヒドラウリク ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト ポンプ
DE102011084405B4 (de) * 2011-10-13 2021-05-27 Zf Friedrichshafen Ag Saugaufgeladene Pumpe zum Fördern einer Flüssigkeit
DE102016204099B3 (de) * 2016-03-11 2017-03-16 Magna Powertrain Bad Homburg GmbH Dichtungsanordnung für schaltbare Flügelzellenpumpe in Cartridge-Bauweise

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Also Published As

Publication number Publication date
JP5140059B2 (ja) 2013-02-06
EP1323926A2 (fr) 2003-07-02
JP2010101322A (ja) 2010-05-06
US20020110459A1 (en) 2002-08-15
US6413064B1 (en) 2002-07-02
EP1108144A1 (fr) 2001-06-20
EP1323926A3 (fr) 2003-09-10
DE19981557D2 (de) 2001-07-12
WO2000009888A3 (fr) 2001-01-11
DE19981557B4 (de) 2015-10-29
JP2002522707A (ja) 2002-07-23
WO2000009888A2 (fr) 2000-02-24

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