EP0043459B1 - Dispositif de réglage pour un ensemble de plusieurs pompes entraînées par une source d'énergie commune - Google Patents

Dispositif de réglage pour un ensemble de plusieurs pompes entraînées par une source d'énergie commune Download PDF

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Publication number
EP0043459B1
EP0043459B1 EP81104452A EP81104452A EP0043459B1 EP 0043459 B1 EP0043459 B1 EP 0043459B1 EP 81104452 A EP81104452 A EP 81104452A EP 81104452 A EP81104452 A EP 81104452A EP 0043459 B1 EP0043459 B1 EP 0043459B1
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EP
European Patent Office
Prior art keywords
pressure
control
line
valve
pump
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
Application number
EP81104452A
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German (de)
English (en)
Other versions
EP0043459A2 (fr
EP0043459A3 (en
Inventor
Dietrich Kuchenbecker
Erich Eckhardt
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.)
Linde GmbH
Original Assignee
Linde GmbH
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Filing date
Publication date
Application filed by Linde GmbH filed Critical Linde GmbH
Publication of EP0043459A2 publication Critical patent/EP0043459A2/fr
Publication of EP0043459A3 publication Critical patent/EP0043459A3/de
Application granted granted Critical
Publication of EP0043459B1 publication Critical patent/EP0043459B1/fr
Expired legal-status Critical Current

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    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery

Definitions

  • the invention relates to a control device for a unit comprising a plurality of pumps driven by a common primary energy source, of which at least one can be adjusted in terms of its stroke volume per revolution, the actuator of which is connected to an actuating piston which, in an actuating cylinder, increases the control pressure of the pump to a smaller stroke volume is adjustable, the control device also being provided with a control pressure auxiliary pump which is constant with respect to the delivery volume per revolution and driven by the same primary energy source and in the delivery capacity of which a throttle point is arranged, the pressure gradient upstream and downstream of this throttle point acting on the control pressure spaces of a hydraulically controlled drain valve, that is connected to a discharge line connected to the delivery line of the auxiliary control pump, an adjustable pressure valve also being provided, the setting of which depends on the sum of the delivery pressures d it is dependent on the pumps driven by the primary energy source, the flow of which is fed to the actual utility application.
  • the delivery line of the auxiliary control pressure pump branches behind the throttle point into the discharge line, which leads to the discharge valve, and a second line, which leads to the pressure valve, which is closed when the total delivery pressure of the pumps is below a limit value and throttling opens with increasing pressure, the throttling effect being reduced with increasing pressure in the delivery lines of the pumps.
  • Both the line emanating from the drain valve and the line emanating from the pressure valve are each connected to an input side of a pressure-dependent changeover valve, the output line of which is connected to the setting elements of the adjustable pump such that the higher of the two pressures, on the one hand, in the Drain line of the drain valve prevail and on the other hand prevail in the drain line of the pressure valve, which acts on the setting elements of the pump (US-A-3 841 795).
  • This device has the disadvantage that there is an unfavorable control characteristic, in particular pressure surges act on the setting members at the time of switching of the switching valve.
  • the discharge line leading to the discharge valve is connected to the delivery line of the control pressure auxiliary pump upstream of the throttle point and the control pressure line is connected, which leads to a cylinder in which a piston is displaceable, which is against a spring is supported, which is supported on the other hand against a mechanical link, act on the control piston parallel to said spring, each of which control piston is acted upon by the delivery pressure of a pump and is supported against a spring, this link being connected to the setting members of the individual adjustable pumps ist (DE-A-26 03 563 and Hydraulic, Pneumatic, Mechanical Power Band 23, No. 271, July 1977, pages 257-261, AT Clements “Power economy with hydrostatic transmission” see page 261, Fig. 6)
  • Known device is the "total power control" known per se by a speed reduction control overlaid. The mechanical part of the total power control is relatively complex here.
  • the invention has for its object to improve the control function of such a device and in particular to avoid discontinuities and vibrations.
  • the pressure valve is a pressure relief valve, which increases the pressure in the line leading to the pressure relief valve to a greater pressure as the sum of the pressures in the delivery lines of the pumps increases, this pressure relief valve in that of the Drain valve outgoing drain line is arranged and thus connected in series therewith, the drain line is further connected in the flow direction upstream of the throttle point to the control pump main line of the auxiliary control pressure pump and the control pressure line to which the setting elements of the adjustable pumps are connected is connected upstream of the drain valve.
  • the pressure in the control pressure line can act directly on the pistons connected to the actuator of a pump or can act indirectly on the actuators by the pressure acting on a control piston which controls the pressurization of the piston connected to an actuator of a pump.
  • control pistons which act on the pressure relief valve and which are displaceable in a control cylinder acted upon by the delivery pressure of the associated pump are supported against a control plate which is supported against a high pressure spring and which acts on the adjusting member of the pressure relief valve.
  • the discharge valve and the pressure relief valve are expediently arranged in a common block with the control pistons that control its setting.
  • the primary energy source is the diesel engine 1, which drives the adjustable pumps 6 and 7 and the pump 8, which is not adjustable in terms of its displacement volume per revolution, via the shaft 2 and the gear train 3, 4, 5.
  • the pump 6 delivers into the delivery line 9 and the pump 7 delivers into the delivery line 10. Both pumps 6 and 7 draw in from the pressureless container 11.
  • the pump 8 is connected in a closed circuit to the hydraulic motor 14 via the lines 12 and 13. Parts 2 to 14 are part of the main drive unit.
  • the diesel engine 1 also drives the auxiliary auxiliary pressure pump 16 via a secondary shaft 15, which also draws in from the container 11 and whose flow rate per revolution cannot be changed.
  • the auxiliary control pressure pump 16 feeds into the main control pump line 17, which is secured by a pressure relief valve 18 against impermissibly high pressure.
  • a throttle point 20 is arranged, which has the task of building up a pressure in the main control pressure pump line 17 dependent on the flow rate of the auxiliary control pressure pump 16 upstream of this throttle point 20.
  • this throttle point 20 has the task of causing a pressure gradient which is dependent on the drive speed of the control pressure auxiliary pump 16 and thus on the speed of the primary energy source 1 to be generated.
  • a discharge line 27 is connected to the control pump main line 17 at a point in the flow direction upstream of the throttle point 20 at a connection point 26, in which a constant throttle point 28 is arranged and which leads to the drain valve 24. From this drain line 27 branches off the control pressure line 29 which leads to the actuating cylinders 30 and 31 of the pumps 6 and 7, wherein an actuating piston can be displaced in each of the actuating cylinders 30 and 31 and is connected to the actuator of the respectively assigned pump 6 and 7 is.
  • the line 51 emanating from the drain valve 24 leads to the pressure limiting valve 37, the setting value of which is determined by the pretension of the low-pressure spring 38, which in turn is supported against a spring plate 41, which is rigidly connected via a plunger 42 to the control plate 43, against which support the control pressure pistons 44 and 45 and which is supported on the other hand against the high pressure spring 48.
  • the control pressure piston 44 is acted upon via line 46 by the pressure prevailing in the delivery line 9 of the pump 6 and the control pressure piston 45 is acted upon by the pressure prevailing in this delivery line 10 via line 47, which is connected to the delivery line 10 of the pump 7 .
  • the throttle point 20, the relief valve 24 and the pressure relief valve 37 with the associated control members, control pistons 44 and 45 and springs 48 and 38 are arranged in a common block 52.
  • the mode of operation is as follows: If the pressure drop at the throttle point 20, i.e. between the connection points 21 and 22, is large enough to overcome the actuating force at the drain valve 24, this remains open, so that the one acting in the main control pressure line 17 upstream of the throttle point 20 Pressure also acts before the throttle point 28. The current flowing through this flows through the discharge line 27 and the opened discharge valve 24 into the line 51 and from there to the pressure relief valve 37.
  • the pressure relief valve 37 When a pressure acts on the control pistons 44 and 45, the sum of which is less than the sum of the pressures, that are required to compress the high pressure spring 48, the pressure relief valve 37 remains open and the pressure medium flows from the line 51 to the container 11 without pressure, so that the line 51 and thus also the drain line 27 and thus also the control pressure line 29 are depressurized.
  • the pressure limiting valve 37 is set to a higher pressure as a result of an increase in the sum of the pressures in the delivery lines 9 and 10 and thus in the lines 46 and 47, the pressure in the line 51 thus increases, which increases through the discharge valve 24 the drain line 27 and thus affects the control pressure line 29, so that this higher pressure also acts on the actuating cylinders 30 and 31.
  • the discharge valve 24 closes as a result of this lower pressure gradient and first determines the congestion in front of the discharge valve 24 and thus in the discharge line 27 and thus in the control pressure line 29 also through its throttling and finally through its closed position with the result that the increasing pressure in the control pressure line 29 acts on the actuating cylinders 30 and 31 and thus sets the pumps 6 and 7 to a smaller delivery volume per revolution.
  • the discharge valve 24 opens again, so that pressure medium can flow out of the discharge line 27 and since the afterflow from the main control pressure line 17 is hindered by the throttle point 28 , the pressure in the discharge line 27 and thus in the control pressure line 29 drops again.
  • the throttling effect in the discharge valve 24 determines the pressure drop between the discharge line 27 and the line 51. If, at the beginning of the closing of the discharge valve 24, there was already an increased pressure in the line 51 as a result of the setting of the pressure relief valve 37, the pressure drop in the discharge valve 24 also causes the pressure in the discharge line 27 and thus the control pressure line 29 is influenced and increased accordingly, so that a superimposition effect occurs which, however, proceeds completely continuously without vibrations. Conversely, the same applies mutatis mutandis: if the drain valve 24 is in a throttling position and the pressure limiting valve 37 then begins to throttle, the pressure rising in the line 51 also has an effect on the drain line 27 upstream of the drain valve 24.
  • the control pump main line 17 is connected via a connection part 61 in such a way that it leads to a space 62 in the part 73 of the overall housing 52.
  • a component 60 is arranged in this space 62, which contains a baffle plate, which prevents the flow flowing axially through the line 17 from exerting a dynamic effect on the control piston 56.
  • a secondary bore 63 is connected to the space 62, in which a part 54 is arranged, which has a bore, which represents the throttle point 20, behind which the drain line 55 branches off, to the other consumers of low pressure, not shown and not dealt with further leads.
  • a component 58 is screwed into the control piston 56 and contains a narrower bore, which forms the throttle point 28.
  • the control piston 56 is supported against a spring 57 which holds the control piston 56 in its closed position when the pressure drop between the pressure in the space 62 and the pressure in the line 25 is too small. If the pressure drop is sufficient, the control piston 56 in FIG. 3 is displaced upwards so far that the control cone part 65 lies in front of the mouth of the line 27. In its most upwardly displaced position, the control piston 56 bears against the support screw 66, so that the transverse bores 67 in the control piston 56 lie in front of the mouths of the line 27. This is the normal operating situation.
  • the control piston 53 of the pressure relief valve is supported against the low pressure spring 38, which is supported on the other hand against the intermediate plate 43, against which the control pistons 44 and 45 are supported and which is connected to a pot-like part 68, on the flange on the left in the drawing, the high pressure spring 48 is supported.
  • the components in FIG. 3 with an upright axis thus form the drain valve 24, while the pressure relief valve 37 is shown with an axis lying horizontally.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Claims (3)

1. Dispositif de régulation d'un groupe de plusieurs pompes (6, 7, 8) entraînées par une source commune d'énergie primaire (1) et dont au moins une est réglable en ce qui concerne sa cylindrée par tour, son organe de réglage étant relié à un piston de réglage qui est mobile dans un cylindre de réglage (30, 31 ) lors d'une augmentation de la pression de commande pour régler la pompe à une cylindrée plus petite, le dispositif de régulation étant en outre pourvu d'une pompe auxiliaire de pression de commande (16) dont la cylindrée par tour est constante, qui est entraînée par la même source d'énergie primaire (1 ) et dans le tuyau de refoulement (17) de laquelle est disposée une zone d'étranglement (20), la baisse de pression entre l'amont et l'aval de cette zone d'étranglement (20) sollicitant les chambres de réglage d'une soupape de décharge (24) hydraulique- ment et qui est reliée à un tuyau de décharge (27) raccordé au tuyau de refoulement (17) de la pompe auxiliaire de pression de commande (16), et dans lequel, en outre, il est prévu une soupape de pression réglable (37) dont la position de réglage est fonction de la somme de la pression de refoulement des pompes (6, 7, 8) entraînées par la source d'énergie primaire (1), caractérisé en ce que la soupape de pression est une soupape de limitation de pression (37) qui, lors d'une augmentation de la somme des pression régnant dans les tuyaux de refoulement (9, 10) des pompes (6, 7) fait passer la pression régnant dans le tuyau (51 ) aboutissant à la soupape de limitation de pression (37) à une pression supérieure, en ce que cette soupape de limitation de pression est disposée sur le tuyau de décharge (51 ) partant de la soupape de décharge (24) et est ainsi branchée en série avec celle-ci, en ce que le tuyau de décharge (27) est relié, dans la direction d'écoulement, en amont de la zone d'étranglement (20) au tuyau principal de pompe de commande (17) de la pompe auxiliaire de pression de commande (16) et en ce que du tuyau de décharge (27) et en amont de la soupape de décharge (24) est dérivé un tuyau de pression de commande (29) auquel sont reliés tous les organes de réglage (30, 31 ), des pompes réglables (6 et 7).
2. Dispositif de régulation selon la revendication 1, caractérisé en ce que les pistons de commande (44,45) agissant sur la soupape de limitation de pression (37) et pouvant chacun coulisser dans un cylindre de commande sollicité par la pression de refoulement de la pompe associée (6 ou 7) sont en appui contre une plaque de commande elle-même en appui contre un ressort haute pression (48) et qui agit sur l'organe de réglage de la soupape de limitation (37).
3. Dispositif de régulation selon la revendication 1 ou la revendication 2, caractérisé en ce que la soupape de décharge (24) et la soupape de limitation de pression (37) sont disposées dans un bloc commun (52) avec les cylindres de commande dans lesquels peuvent coulisser les pistons de commande (44 et 45) commandant le réglage de la soupape de limitation de pression (37).
EP81104452A 1980-06-28 1981-06-10 Dispositif de réglage pour un ensemble de plusieurs pompes entraînées par une source d'énergie commune Expired EP0043459B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19803024399 DE3024399A1 (de) 1980-06-28 1980-06-28 Regeleinrichtung fuer ein aggregat aus mehreren, von einer gemeinsamen primaerenergiequelle angetriebenen pumpe
DE3024399 1980-06-28

Publications (3)

Publication Number Publication Date
EP0043459A2 EP0043459A2 (fr) 1982-01-13
EP0043459A3 EP0043459A3 (en) 1982-01-20
EP0043459B1 true EP0043459B1 (fr) 1984-09-12

Family

ID=6105778

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81104452A Expired EP0043459B1 (fr) 1980-06-28 1981-06-10 Dispositif de réglage pour un ensemble de plusieurs pompes entraînées par une source d'énergie commune

Country Status (5)

Country Link
US (1) US4405287A (fr)
EP (1) EP0043459B1 (fr)
JP (1) JPS5746082A (fr)
BR (1) BR8104068A (fr)
DE (1) DE3024399A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3143539A1 (de) * 1981-11-03 1983-05-11 Linde Ag, 6200 Wiesbaden Steuereinrichtung fuer ein stufenlos einstellbares, vorzugsweise hydrostatisches getriebe
DE3323278C2 (de) * 1983-06-28 1986-05-22 Hydromatik GmbH, 7915 Elchingen Regelvorrichtung für mehrere aus hydrostatischen Getrieben bestehende Antriebsaggregate
US4739616A (en) * 1985-12-13 1988-04-26 Sundstrand Corporation Summing pressure compensation control
JPH01220706A (ja) * 1988-02-25 1989-09-04 Komatsu Ltd 油圧式掘削機の油圧制御装置
US4984427A (en) * 1989-09-01 1991-01-15 Kabushiki Kaisha Kobe Seiko Sho Control circuit for hydraulic actuator
US5600952A (en) * 1995-09-26 1997-02-11 Aurora Technology Corporation Auxilliary drive apparatus
JPH10141310A (ja) * 1996-11-13 1998-05-26 Komatsu Ltd 圧油供給装置
US8117837B1 (en) * 2003-12-17 2012-02-21 Sauer-Danfoss Inc. Hydrostatic transmission having integrated pressure compensated load sensing auxiliary pump
CN102305204A (zh) * 2011-08-22 2012-01-04 广西玉柴重工有限公司 转速感应式变量恒流泵
US11725647B2 (en) * 2021-05-18 2023-08-15 Hamilton Sundstrand Corporation On-demand dual variable displacement positive displacement pumping system

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3841795A (en) * 1972-07-17 1974-10-15 Caterpillar Tractor Co Combined engine speed and pressure responsive control for variable displacement pumps

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2505779C2 (de) * 1975-02-12 1983-01-13 Robert Bosch Gmbh, 7000 Stuttgart Grenzlastregeleinrichtung für verstellbare Pumpen
GB1496141A (en) * 1975-04-22 1977-12-30 Priestman Bros Ltd Hydraulic systems
DE2603563C2 (de) * 1976-01-30 1986-02-20 Linde Ag, 6200 Wiesbaden Steuereinrichtung für ein aus mindestens zwei Pumpen bestehendes Pumpen-Aggregat
JPS5364802A (en) * 1976-11-24 1978-06-09 Komatsu Ltd Input torque control equipment in hydraulic pump
US4080979A (en) * 1977-03-22 1978-03-28 Caterpillar Tractor Co. Combined summing and underspeed valve
DE2813486C2 (de) * 1977-03-31 1986-06-26 Kabushiki Kaisha Komatsu Seisakusho, Tokio/Tokyo Steuervorrichtung für Hydraulikpumpen
JPS5543246A (en) * 1978-09-22 1980-03-27 Komatsu Ltd Volume controller of variable hydraulic pump

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3841795A (en) * 1972-07-17 1974-10-15 Caterpillar Tractor Co Combined engine speed and pressure responsive control for variable displacement pumps

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
"Bauelemente der Ölhydraulik" *

Also Published As

Publication number Publication date
JPS5746082A (en) 1982-03-16
US4405287A (en) 1983-09-20
EP0043459A2 (fr) 1982-01-13
EP0043459A3 (en) 1982-01-20
BR8104068A (pt) 1982-03-16
DE3024399A1 (de) 1982-01-21

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