EP0211980A1 - Installation de réglage pour le couple moteur - Google Patents

Installation de réglage pour le couple moteur Download PDF

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Publication number
EP0211980A1
EP0211980A1 EP85110318A EP85110318A EP0211980A1 EP 0211980 A1 EP0211980 A1 EP 0211980A1 EP 85110318 A EP85110318 A EP 85110318A EP 85110318 A EP85110318 A EP 85110318A EP 0211980 A1 EP0211980 A1 EP 0211980A1
Authority
EP
European Patent Office
Prior art keywords
control device
valve
piston
control
pressure
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
EP85110318A
Other languages
German (de)
English (en)
Other versions
EP0211980B1 (fr
Inventor
Gerald Warren
Raffaele Sandroni
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.)
Vickers Systems GmbH
Original Assignee
Vickers Systems 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 Vickers Systems GmbH filed Critical Vickers Systems GmbH
Priority to EP85110318A priority Critical patent/EP0211980B1/fr
Priority to DE8585110318T priority patent/DE3581539D1/de
Priority to US06/786,791 priority patent/US4631005A/en
Publication of EP0211980A1 publication Critical patent/EP0211980A1/fr
Application granted granted Critical
Publication of EP0211980B1 publication Critical patent/EP0211980B1/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
    • 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
    • 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
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a control device for adjusting the drive torque of a hydraulic pump with a variable displacement volume according to the preamble of claim 1.
  • the object is achieved to provide a control device for adjusting the drive torque of a hydraulic pump with a variable displacement volume, which can be conveniently set or remotely adjusted by the operator, for example from an operating cabin.
  • a remote control device is designed to deliver a remote control pressure signal which the control piston device counteracts the action of Return device can be fed.
  • the remote control device can be constructed hydromechanically or hydroelectrically.
  • further status signals of the engine and the working machine can be processed and taken into account in order to meet the numerous special requirements for the respective user. Two use cases are discussed below:
  • Preselecting the drive torque of the pump should be one of the simplest arrangements for adapting to the power requirement.
  • the remote control device can be designed as an electro-hydraulic servo valve. Such can be controlled arbitrarily by hand or automatically by means of electronics, whereby further parameters can be taken into account.
  • the remote control device can also be designed as a pressure reducing valve.
  • the control valve can be a conventional compensator construction in which an additional auxiliary piston is installed to act on the compensator slide, so that an adapted control piston device is provided tion is created according to the cross-sectional relationships of the compensator slide and the auxiliary piston.
  • a hydraulic pump 10 with a variable displacement volume and with a flow direction is connected to a suction line 12 and a pressure line 14, which delivers a delivery flow Q at a pressure P.
  • the hydraulic pump 10 has a displacement adjustment device 16 and a hydraulic servomotor 18, which is pretensioned by a return spring or hydraulically reset.
  • the hydraulic pump 10 is driven via a drive shaft 20 by a motor, not shown, which develops the necessary torque M within certain limits.
  • the pump pressure line 14 has a branch 22 for supplying a control pressure circuit 25.
  • the control pressure circuit 25 includes a torque scanner 28, which consists of two changeable laminar throttles 29a, 29b, which are arranged in series with a drain line 26, 30.
  • a pressure sensing line 32 is connected at the connection point of the two laminar throttles 29a, 29b. These are formed by a thin flow space between a long cylinder 34 and a piston 36.
  • the piston 36 is mechanically connected to the displacement adjustment device 16, as indicated by an action line 38. If the displacement volume of the pump 10 is reduced, the mechanical Connection 38 displaces the piston 36 in such a way that the resistance of the laminar throttle 29a is reduced and the resistance of the laminar throttle 29b is increased.
  • the control pressure circuit 25 also has a control valve 42, often referred to as a compensator, which can be designed as a throttling three-way valve, so that three connection openings are provided, one of which is connected to the branch line 22 via a branch line 44, while the second connection opening is connected via a control line 40 is connected to the hydraulic servomotor 18 and the third connection opening leads to the tank via a drain line 46.
  • the control valve 42 has a slide piston 43 which is on the one hand under the action of a return device 50 and on the other hand a control piston device 51.
  • the return device 50 consists of an adjustable valve spring.
  • the control piston device 51 contains a first piston 48, which is connected to the torque scanner 28 via the line 32 and acts against the force of the return device 50.
  • the pump 10 in operation supplies the fluid through the pump pressure line 14 against variable pressure and with variable swallowing capacity (requirement on the flow rate) of the consumer.
  • the line 32 is connected to the pump pressure line 14 via the drain line 22, 26, 30, the sensed pressure P f in the line 32 depends on the level of the pump pressure in the line 14 and on the ratio a / b of the resistances of the laminar chokes 29a and 29b to each other. Since the piston 36 is connected to the displacement setting device 16, the ratio a / b of the resistance values changes with the displacement setting of the pump 10.
  • the pressure P f in the line 32 is therefore proportional to the product of the displacement volume and the pump pressure.
  • each set displacement of the pump 10 corresponds to a specific pump Flow rate Q in line 14.
  • the pressure P f in line 32 is then also proportional to the pump output, which results from the product of the pump pressure P and the flow rate Q.
  • the switching pressure (cracking pressure) of the control valve 42 can be adjusted at which fluid begins to flow into the control line 40.
  • Each setting of the valve spring therefore corresponds to a certain graded maximum pump output.
  • graduated maximum pump outputs can be represented by hyperbola in a pressure-flow diagram, i.e. Operating points of a power-controlled pump can be found in the respective field between the coordinate axes and the respective hyperbola.
  • the power limitation also means a limitation of the drive torque, since the drive power can also be calculated from the drive torque multiplied by the speed.
  • Each hyperbola in FIG. 4 is accordingly assigned a specific drive torque in FIG. 5.
  • the control device differs from the known one in the design of the control piston device 51 and in that a remote control device 60 is provided.
  • the remote control device 60 consists of a directional control valve 61 and a pressure reducing valve 62, which are arranged one behind the other in a remote control line 63 connected to pump pressure, which leads to the control piston device 51.
  • the output pressure P c of the pressure reducing valve 62 can be adjusted by adjusting the valve spring 64 accordingly. If you can quickly wants to preselect a plurality of drive torques on the shaft 20, then a plurality of pressure reducing valves 62 with different outlet pressures P c1 ...
  • P cn are arranged in parallel next to each other and can be activated individually by a corresponding multi-way valve 61.
  • a corresponding multi-way valve 61 instead of the directional control valve 61 shown with two connections and two specific positions and with manual operation, it is of course also possible to use electrically or hydraulically switching devices in connection with pressure control valves.
  • control piston device 51 also has a second piston 52 which is acted upon by the outlet pressure P c and acts in the same sense as the first piston 48 against the force of the return device 50.
  • the output pressure P c thus represents a heel control signal, via which the switching state of the control valve 42 is more likely to be reached and the torque on the shaft 20 is reduced accordingly.
  • the remote control signal P c can also (see FIG. 2) be formed by a pilot pump 65 with the aid of at least one pressure limiting valve 66. If you want to change the torque M quickly, you can provide several pressure relief valves 66 side by side and connect one each to the remote control line 63 via a selector switch (corresponding to the directional control valve 61 in Fig. 1), so that this pressure relief valve determines the desired remote control signal P c .
  • the pressure relief valve 66 can be actuated hydromechanically or electrohydraulically.
  • two pistons 48, 52 are arranged side by side, only a range of, for example, 80 to 10% of the maximum torque can be set remotely.
  • FIG 3 shows an exemplary embodiment without this limitation and with a pilot-controlled control valve 42 and a proportional throttle 70 as a remote control device 60.
  • the control valve 42 has a main valve 45 as the first stage and a pilot valve 47 as the second stage.
  • the adjustable return device 50 also has a throttle 56, via which the pump pressure is fed to the pilot valve 47, which opens according to an adjustable valve spring 57 at a specific, adjustable response pressure, after which the pressure in the spring pressure chamber 55a of the main valve 45 drops and the valve spool 43 for connecting the lines 14 and 40 is moved.
  • the pilot valve 47 returns to its initial position, and the spool 43 shuts off the line 40 after the displacement setting device 16 has assumed a new position. This known mode of action does not need to be examined in greater detail here.
  • the control piston device 51 has an auxiliary piston 58, to which the pressure P f of the line 32 is present and which acts on the slide piston 43.
  • the slide piston 43 has a piston surface 59 which is acted upon by the pressure P c in the line 63.
  • the remote control device 60 contains an electro-hydraulic servo valve 70, which is designed as a throttling three-way valve.
  • a connection 74 is connected to a pressure supply, a second connection 75 to the tank and the third connection 73 to the line 63.
  • the throttle slide 72 can be adjusted so that a desired pressure P c is fed via line 63 to the control valve 42 in order to set a desired power specification or a desired maximum torque.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP85110318A 1985-08-17 1985-08-17 Installation de réglage pour le couple moteur Expired - Lifetime EP0211980B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP85110318A EP0211980B1 (fr) 1985-08-17 1985-08-17 Installation de réglage pour le couple moteur
DE8585110318T DE3581539D1 (de) 1985-08-17 1985-08-17 Antriebsdrehmoment-regeleinrichtung.
US06/786,791 US4631005A (en) 1985-08-17 1985-10-11 Input torque control device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP85110318A EP0211980B1 (fr) 1985-08-17 1985-08-17 Installation de réglage pour le couple moteur

Publications (2)

Publication Number Publication Date
EP0211980A1 true EP0211980A1 (fr) 1987-03-04
EP0211980B1 EP0211980B1 (fr) 1991-01-23

Family

ID=8193686

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85110318A Expired - Lifetime EP0211980B1 (fr) 1985-08-17 1985-08-17 Installation de réglage pour le couple moteur

Country Status (3)

Country Link
US (1) US4631005A (fr)
EP (1) EP0211980B1 (fr)
DE (1) DE3581539D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0797009A2 (fr) * 1996-03-22 1997-09-24 Trinova Limited Circuit de commande de fluide

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0270190B1 (fr) * 1986-12-01 1992-09-02 Hitachi Construction Machinery Co., Ltd. Transmission hydraulique
US4892465A (en) * 1988-09-14 1990-01-09 Hagglunds Denison Corporation Automatic control for variable displacement pump
ZA923131B (en) * 1992-04-29 1993-10-29 Ingersoll Rand Co On-off valve for hydraulic rockdrill
US5486097A (en) * 1995-01-26 1996-01-23 Denison Hydraulics Inc. Control for a variable displacement axial piston pump
US9803637B2 (en) * 2011-07-14 2017-10-31 Ford Global Technologies, Llc Variable displacement hydraulic pump control

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1536041A (fr) * 1967-09-06 1968-08-09 Abex Corp Dispositif pour modifier le débit d'une pompe hydraulique à centre croisé
FR2153889A5 (fr) * 1971-09-22 1973-05-04 Sperry Rand Corp
FR2153892A5 (fr) * 1971-09-22 1973-05-04 Sperry Rand Corp
DE2719029A1 (de) * 1976-07-02 1978-01-12 Eaton Corp Hydraulische regeleinrichtung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NO124443B (fr) * 1970-04-22 1972-04-17 Ingebret Soeyland
US3784327A (en) * 1972-06-13 1974-01-08 Sperry Rand Corp Power transmission
JPS5347810A (en) * 1976-10-12 1978-04-28 Mitsubishi Electric Corp Magnetic head
DE2813486C2 (de) * 1977-03-31 1986-06-26 Kabushiki Kaisha Komatsu Seisakusho, Tokio/Tokyo Steuervorrichtung für Hydraulikpumpen
JPS5648105A (en) * 1979-09-27 1981-05-01 Kogyosha Tsuushinkiki Seisakusho:Kk Solenoid

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1536041A (fr) * 1967-09-06 1968-08-09 Abex Corp Dispositif pour modifier le débit d'une pompe hydraulique à centre croisé
FR2153889A5 (fr) * 1971-09-22 1973-05-04 Sperry Rand Corp
FR2153892A5 (fr) * 1971-09-22 1973-05-04 Sperry Rand Corp
DE2719029A1 (de) * 1976-07-02 1978-01-12 Eaton Corp Hydraulische regeleinrichtung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0797009A2 (fr) * 1996-03-22 1997-09-24 Trinova Limited Circuit de commande de fluide
EP0797009A3 (fr) * 1996-03-22 1999-06-23 Trinova Limited Circuit de commande de fluide

Also Published As

Publication number Publication date
EP0211980B1 (fr) 1991-01-23
US4631005A (en) 1986-12-23
DE3581539D1 (de) 1991-02-28

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