EP0445529B1 - Dispositif hydraulique - Google Patents

Dispositif hydraulique Download PDF

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Publication number
EP0445529B1
EP0445529B1 EP91101440A EP91101440A EP0445529B1 EP 0445529 B1 EP0445529 B1 EP 0445529B1 EP 91101440 A EP91101440 A EP 91101440A EP 91101440 A EP91101440 A EP 91101440A EP 0445529 B1 EP0445529 B1 EP 0445529B1
Authority
EP
European Patent Office
Prior art keywords
pressure
sealing plate
control
line
gear
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
EP91101440A
Other languages
German (de)
English (en)
Other versions
EP0445529A1 (fr
Inventor
Dieter Dipl.-Ing. Weigle
Gottfried Dipl.-Ing. Olbrich
Hayno Dipl.-Ing. Rustige
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 GmbH
Original Assignee
Robert Bosch 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 GmbH filed Critical Robert Bosch GmbH
Publication of EP0445529A1 publication Critical patent/EP0445529A1/fr
Application granted granted Critical
Publication of EP0445529B1 publication Critical patent/EP0445529B1/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
    • 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
    • F04C14/265—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 being obtained by displacing a lateral sealing face

Definitions

  • the invention relates to a hydraulic system with a gear pump regulating its flow.
  • the load pressure which prevails at a consumer directly acts on a pressure field which acts on the sealing plate.
  • Such control of the sealing plate is not particularly precise.
  • the hydraulic system with the characterizing feature of the main claim has the advantage that the delivery rate of the gear pump used in the hydraulic system can be controlled very precisely. Further advantages result from the subclaims.
  • FIG. 1 a hydraulic system in a schematic representation, in Figure 2 an application in a gear motor, in Figure 3 another variant, in Figure 4 a longitudinal section through a gear pump and in Figure 5 a section along II-II of Figure 4.
  • 10 denotes a gear pump, which sucks pressure medium out of a container 12 via a suction line 11 and displaces it into a delivery line 13.
  • Several directional control valves 14, 15 can be connected to the delivery line, of which consumer lines 16, 17 lead to consumers 18 and not shown.
  • Each directional valve has a metering orifice 19 or 20 on the control slide, which are connected to chambers (not shown) to which a control line 21 is connected.
  • a control line 23 is connected to the delivery line 13, which leads to the one end face 24 A of a pressure compensator 24.
  • a branch line 25 branches off from the control line 21 and penetrates into a control line 26, which opens on the one hand on the front side 24 B of the pressure compensator 24 opposite the front side 24 A, and on the other hand on a pressure limiting valve 27.
  • a control spring 28 also acts on the front side 24 B.
  • a line 29 branches off from the control line 23, which opens into a line 30 which leads from the pressure compensator 24 to the gear pump and opens there at a sealing plate 31, which is discussed in more detail further on.
  • a throttle 32 is arranged in line 29.
  • a return line 34 leads from the interior of the gear pump 10 to the container.
  • the outlet line 35 emanating from the pressure compensator 24 also opens into this return line, into which the outlet line 36 of the pressure limiting valve 27 in turn penetrates.
  • a throttle 37 is arranged in the control line 21 before the line branch 25.
  • the pressure compensator closes due to the signal pressure in line 21, which corresponds to that in line 13, so that no pressure medium can flow from the line 30 via the pressure compensator 24 into the return line 35.
  • the pressure prevailing in the lines 13, 23, 29 and 30 presses the sealing plate 31 against the gear side surfaces, that is to say no pressure medium can flow out from the inside of the high pressure side to the low pressure side of the gear pump.
  • the pressure in the delivery line 13 and the consumer line 16 now increases, and the load pressure at the consumer, that is to say that behind the throttle 19, is transmitted via the control line 21 to the end face 24 B of the pressure compensator.
  • the pressure compensator opens, whereupon the pressure in the line 30 drops, that is to say a control pressure for the sealing plate 31 is formed in this line, but which is designed so that it is substantially lower than the pressure in line 23. If, for example, a pressure of 153 bar prevails in the delivery line, a pressure of 150 bar in control line 21 - the pressure difference arises at throttle 19 - thus forms the pressure compensator in line 30, for example, a pressure of 120 bar. In this way, a pressure drop in line 30 is obtained, which contributes to improving the control sensitivity.
  • the pressure relief valve 27 is a maximum pressure valve. If, for example, the maximum pressure in the hydraulic system is reached and the pressure relief valve 27 opens, the pressure compensator 24 immediately goes into the open position and thus relieves the pressure on the sealing plate 31 completely, so that all pressure medium conveyed by the gear pump 10 immediately flows from the high pressure to the low pressure side . So you get an internal pressure limitation.
  • the throttle 37 is used to generate the differential pressure for the pressure compensator control.
  • the embodiment according to FIG. 2 is to a certain extent the reverse of the example mentioned above, that is to say here a flow control of a gear motor with a sealing plate and pressure compensator takes place.
  • the pressure difference required for the control is generated by an adjustable throttle 40, which is in the return line 41 is arranged from the gear motor 42 to the container.
  • the pressure drop across the throttle 40 acts on the pressure compensator 24.
  • the control pressure is generated in a line 45 which is connected to a line 29 which starts from the pressure line, specifically at a point upstream of the throttle 32
  • the pressure compensator is controlled via the throttle 40 so that there is a low control pressure in the control line 45 when the pressure compensator is open, so that the sealing plate 31 has lifted off the gear side surfaces.
  • the exemplary embodiment according to FIG. 3 differs from the previous one in that two gear pumps 10, 50 are provided which are driven by a common shaft.
  • the sealing plate 31 is arranged on the gear pump 50, which is connected via its delivery line 51 to the delivery line 13 of the pump 10.
  • the directional control valves 14, 15 are again designed as in the exemplary embodiment according to FIG. 1, where the load pressure-carrying control line 52 is brought to a pressure compensator 53, the other side of which is acted upon via a line 54 connected to the delivery line 13.
  • a control line 55 leads from the pressure compensator 53 to the sealing plate 31.
  • FIGS. 4 and 5 show the gear pump 10 used in the hydraulic system. However, this is not shown in all its constructive details. It has a housing 60 which is closed on both sides by covers 61, 62. In the interior of the housing, two gearwheels 63, 64 mesh with one another in external engagement, the shafts 65, 66 of which are arranged in bearing bodies 67, 68. Between the bearing body 68 and the gear wheels, the sealing plate 31 is arranged, which has the contour of the interior and covers the gear wheels. The bearing body 67, 68 and the sealing plate 31 and also the gears are mounted in the housing 60 with little axial play.
  • two pressure fields A and B are formed, of which the pressure field A is continuously acted upon by high pressure, which prevails in a housing bore 70, which penetrates from the outside into a recess 71 at the level of the gearwheels, which extends along of the housing interior extends.
  • the high-pressure side HD to which the delivery line 13 is connected is located at the bore 70.
  • a bore 72 is formed in the housing, which opens into a recess 73, which likewise runs along the interior.
  • the bore 72 is the low-pressure side ND, from which the line 11 leads to the container 12, from which the gear pump sucks in pressure medium.
  • the pressure field B is the controlled pressure field to which the line 30 according to FIG. 1 is connected. It is identified in FIG. 5 as a short, dot-dash hole.
  • the sealing plate can be pressed onto the gearwheels 63 by appropriately acting on the pressure field B, or when the pressure field B is relieved, the sealing plate 31 is lifted off the gearwheels, since the high pressure of the machine prevails below it. As stated above, the sealing plate is somewhat movable in the axial direction. When it has lifted off the gearwheel side surfaces, the pressure medium delivered flows directly from the high pressure side HD along the gearwheels and below the sealing plate to the tank side. The gear pump then delivers in neutral circulation.

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

Claims (5)

  1. Dispositif hydraulique comportant une pompe à engrenage (10) réglant le débit, avec une plaque d'étanchéité (31) appliquée contre les flancs des engrenages, cette plaque étant légèrement mobile dans la direction axiale et elle est sollicitée par la pression de commande d'une installation de soupape 24, et suivant son éloignement des flancs des roues dentées, la plaque d'étanchéité laisse passer une fraction plus ou moins importante du débit créé par la pompe, directement du côté haute pression (HD) vers le côté basse pression (ND), dispositif caractérisé en ce que le dispositif à soupape est une balance de pression (24) branchée en parallèle sur la conduite de transfert (13) de la pompe à engrenage, cette balance étant d'une part sollicitée par la pression de refoulement de la pompe à engrenage et d'autre part par la pression de charge des utilisateurs reliés à la conduite de transfert, la pression de charge étant prise de manière connue sur une arête de commande (19, 20) du distributeur à tiroir (14, 15) en amont de l'utilisateur concerné.
  2. Dispositif selon la revendication 1, caractérisé en ce que la balance de pression (24) comporte en parallèle dans sa conduite d'alimentation (21, 25) sollicitée par la pression de charge, une soupape de limitation de pression (27) pour régler la pression maximale.
  3. Dispositif selon la revendication 1 et/ou 2, caractérisé en ce que la balance de pression (24) commande par une conduite de commande (30) un champ de pression (B) dans la pompe à engrenage et ce champ de pression crée la force d'application de la plaque d'étanchéité (31).
  4. Dispositif selon la revendication 1, caractérisé par deux pompes à engrenage (10, 50) dont l'une est régulée en débit par la plaque d'étanchéité (31) et fournit en fonction de la pression de charge au niveau des utilisateurs, une quantité de fluide sous pression au circuit hydraulique, la balance de pression (53) étant intégrée au bloc du distributeur à tiroir.
  5. Dispositif hydraulique comportant un moteur à engrenage dont le débit se règle par une installation à soupape (24), la vitesse de rotation du moteur à engrenage (42) étant réglable par une plaque d'étanchéité (31) dont le champ de pression est commandé à partir d'une balance de pression (24) par la conduite de commande (45), dispositif caractérisé en ce que l'installation de soupape est une balance de pression (24) commandée par la différence de pression d'un organe d'étranglement réglable (40) qui se trouve dans la conduite de retour (41) du moteur à engrenage.
EP91101440A 1990-03-07 1991-02-04 Dispositif hydraulique Expired - Lifetime EP0445529B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4007073 1990-03-07
DE4007073A DE4007073A1 (de) 1990-03-07 1990-03-07 Hydraulikanlage

Publications (2)

Publication Number Publication Date
EP0445529A1 EP0445529A1 (fr) 1991-09-11
EP0445529B1 true EP0445529B1 (fr) 1994-10-19

Family

ID=6401559

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91101440A Expired - Lifetime EP0445529B1 (fr) 1990-03-07 1991-02-04 Dispositif hydraulique

Country Status (2)

Country Link
EP (1) EP0445529B1 (fr)
DE (2) DE4007073A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1046819A2 (fr) 1999-04-19 2000-10-25 Hydraulik-Ring GmbH Machine hydraulique volumétrique
EP1048879A2 (fr) 1999-04-30 2000-11-02 Hydraulik-Ring GmbH Alimentation en fluide sous pression d' une transmission de type CVT
DE19924855A1 (de) * 1999-04-30 2000-11-02 Hydraulik Ring Gmbh Druckmittelversorgung eines CVT-Getriebes
DE102014216038A1 (de) 2014-08-13 2016-02-18 Robert Bosch Gmbh Zahnradmaschine mit schaltbarem internem Umlauf

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2706541B1 (fr) * 1993-06-11 1995-09-08 Renault Vehicules Ind Procédé de régulation de la pression et du débit de refoulement d'une pompe volumétrique et pompe volumétrique pour la mise en Óoeuvre du procédé.
DE112006003469B4 (de) * 2005-12-17 2015-07-02 Schaeffler Technologies AG & Co. KG Drehdurchführung und Drehmomentübertragungseinrichtung mit einer Drehdurchführung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1040904B (de) * 1952-05-21 1958-10-09 Borg Warner Hydraulische Pumpenanlage
FR1080123A (fr) * 1952-05-24 1954-12-07 Borg Warner Perfectionnements relatifs aux systèmes de transmission hydraulique
US3175468A (en) * 1962-04-05 1965-03-30 Cessna Aircraft Co Fluid motor with delayed pressure loading
DE2335054A1 (de) * 1972-07-10 1974-01-31 Komatsu Mfg Co Ltd Zahnradpumpe bzw. zahnradmotor

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1046819A2 (fr) 1999-04-19 2000-10-25 Hydraulik-Ring GmbH Machine hydraulique volumétrique
DE19917593C2 (de) * 1999-04-19 2002-05-02 Hydraulik Ring Gmbh Hydraulische Verdrängermaschine
EP1048879A2 (fr) 1999-04-30 2000-11-02 Hydraulik-Ring GmbH Alimentation en fluide sous pression d' une transmission de type CVT
DE19924855A1 (de) * 1999-04-30 2000-11-02 Hydraulik Ring Gmbh Druckmittelversorgung eines CVT-Getriebes
US6387000B1 (en) 1999-04-30 2002-05-14 Hydraulik-Ring Gmbh Pressure medium supply arrangement for a continuous variable transmission
DE102014216038A1 (de) 2014-08-13 2016-02-18 Robert Bosch Gmbh Zahnradmaschine mit schaltbarem internem Umlauf

Also Published As

Publication number Publication date
DE59103251D1 (de) 1994-11-24
DE4007073A1 (de) 1991-09-12
EP0445529A1 (fr) 1991-09-11

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