EP0149787B1 - Dispositif de régulation de débit pour une pompe hydraulique réglable - Google Patents

Dispositif de régulation de débit pour une pompe hydraulique réglable Download PDF

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Publication number
EP0149787B1
EP0149787B1 EP84115198A EP84115198A EP0149787B1 EP 0149787 B1 EP0149787 B1 EP 0149787B1 EP 84115198 A EP84115198 A EP 84115198A EP 84115198 A EP84115198 A EP 84115198A EP 0149787 B1 EP0149787 B1 EP 0149787B1
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EP
European Patent Office
Prior art keywords
valve
control
pressure
pump
torque
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
EP84115198A
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German (de)
English (en)
Other versions
EP0149787A2 (fr
EP0149787A3 (en
EP0149787B2 (fr
Inventor
Gerhard Beutler
Heinz Berthold
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.)
Brueninghaus Hydraulik GmbH
Original Assignee
Brueninghaus Hydraulik GmbH
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Filing date
Publication date
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Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0149787A2 publication Critical patent/EP0149787A2/fr
Publication of EP0149787A3 publication Critical patent/EP0149787A3/de
Publication of EP0149787B1 publication Critical patent/EP0149787B1/fr
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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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • 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 flow control device according to the preamble of claim 1.
  • a flow control device of this type is known for example from DE-A-15 28 550 and FR-A-22 11 054.
  • the delivery rate is set solely for the purpose of traversing a specific performance curve as a function of the pump delivery pressure or a control or operating pressure which is synchronous with it.
  • the stroke volume of the pump there is a direct functional relationship between the stroke volume of the pump and the control of the operating pressure which actuates the control valve, which results in low-loss torque control because the torque characteristic is not determined by a throttle system by lowering the operating pressure, but only by changing the Spring preload on the momentary valve, d. H. by designing the measuring spring or the measuring spring set.
  • the relationship applies that the product of the operating pressure and the stroke volume of the pump must be constant.
  • the measure of the stroke volume of a hydraulic pump is the position of the pump actuator which adjusts the pump delivery quantity and which, according to the invention, is connected to the torque valve by means of the spring / measuring spring set.
  • the torque valve is followed by the control valve, which acts as a pressure compensator and primarily serves to adjust the delivery rate.
  • the control valve acts as a pressure compensator and primarily serves to adjust the delivery rate.
  • DE-A-15 28 550 and from DE-A-20 38 968 per se to connect a torque valve to the pump actuator by means of a measuring spring set for the delivery rate control, but there are significant differences between these known configurations and the solution according to the invention .
  • DE-A-15 28 550 there is no torque control, but the pump pressure is set so that the max. Operating pressure does not exceed a certain value.
  • DE-A-20 38 968 discloses a power control device for two or more hydraulic pumps, and moreover the torque valve is not arranged so that it pressurizes the operating pressure control line depending on the pressure in the operating pressure control line and the preload of the measuring spring set Process connects.
  • a torque valve is known per se from FR-A-13 18 661, the spring of which is connected to the pump frame, but this known embodiment relates to a manually adjustable pump, and moreover the torque valve does not become dependent on the pressure in the operating pressure control line controlled.
  • the design and arrangement of the torque valve according to the invention in a flow rate control allows in a further embodiment of the invention that the torque valve can be attached to the hydraulic pump as a separate assembly and a driver pin of the pump actuator on the torque valve to change the bias of the measuring spring / measuring spring set depending on the flow rate setting attacks.
  • Such a torque valve can be used for pumps of different sizes and capacities, these pumps only having to match in the adjustment path for the pump actuator, that is to say, for example, in the swivel angle for adjustable inclined-axis pumps.
  • An expedient embodiment of such a torque valve is characterized in claims 4 and 5.
  • the torque characteristic is determined solely by designing the characteristic of the measuring spring or the measuring spring set
  • a particularly expedient embodiment of the invention results if the stop for the measuring spring measuring spring set can be adjusted from the outside by means of a handle in the torque valve. Due to the externally adjustable measuring spring or measuring spring set, any number of different torque characteristics can be preselected and also set or adjusted during operation, which is particularly advantageous when the pump torque is optimally adapted to the torque of the drive machine driving the pump. A quick adaptation to any application is possible.
  • the stop in the torque valve can expediently be arranged on the end of the valve housing and be detachable for the exchange of the measuring spring / measuring spring set.
  • the torque control device is also suitable as a total control for two or more hydraulic pumps mechanically coupled on the drive side if, according to the invention, the closing element of the torque valve of each pump is acted upon by the sum of the pressure in the operating pressure control line of the individual pump and the pressure in the operating pressure line of the other pump (s) and that each torque valve pressurizes the operating pressure control line of its pump as a function of the total operating pressure and the preload of its measuring spring Process connects.
  • the closing elements of the torque valves have a plurality of measuring surfaces which act in parallel and are each acted upon by the operating pressure of one of the pumps.
  • the hydraulic pump 1 is driven via the shaft 2 by a drive, not shown.
  • the pump actuator consists of a swivel element 3, the swivel angle a of which is proportional to the stroke volume of the hydraulic pump 1.
  • the servo-setting device (not shown in detail) for adjusting the swivel angle ⁇ comprises a spring 4 and a steep piston 5 which can be pressurized, the spring 4 adjusting the hydraulic pump 1 in the direction of the maximum swivel angle ⁇ , that is to say the maximum delivery volume.
  • An actuating piston 6 of the actuating device which can also be functionally combined with the piston 5, takes over the resetting function in the direction of a smaller pivot angle a.
  • the control pressure acting on the piston 6 in the line 7 is removed via a control valve 8 and the line 9 from the delivery pressure line 10 of the hydraulic pump 1.
  • a common pressure relief valve 11 is in series with the control valve 8.
  • the control valve 8 is designed as a pressure compensator and is acted upon on the one hand by the delivery pressure and on the other hand by a control pressure in the operating pressure control line 12, which controls the operating pressure of the hydraulic pump 1 behind a throttle 13 which limits the control flow the operating pressure line 14 decreases after an optionally adjustable flow restrictor 15.
  • a moment valve 16 is acted upon on the one hand by the pressure in the control line 12 and on the other hand by a measuring spring or measuring spring set 17, the pretension of which is determined by the position of the piston 6 or the pump actuator 3.
  • the torque valve 16 can connect the control line 12 to the unpressurized outlet 18.
  • the operating pressure in the control line 12 reaches the value set on the torque valve 16 so that it begins to open, a pressure drop occurs at the control slide of the control valve 8 via the throttle 13.
  • the control slide is moved into the switching position 11 and supplies the piston 6 with Control pressure, so that it strives to adjust the actuator 3 of the hydraulic pump 1 in the direction of smaller flow rates.
  • the measuring spring 17 or the measuring spring set of the torque valve 16 is biased.
  • the spring characteristics of the measuring springs or the measuring spring set are designed such that, depending on the preload, an envelope curve is created in the theoretically desired power hyperbola.
  • a defined swivel angle a corresponds to a defined operating pressure in line 10.
  • the delivery rate setting of the hydraulic pump 1 in the area in which the torque control, that is to say the torque valve 16 has not yet responded is carried out in the usual way via the delivery rate throttle 15 and requires no special explanation.
  • FIG. 2 shows an embodiment of a torque valve 16 in its assignment to the pivotable pump actuator of an inclined-axis axial piston pump.
  • the pivotable actuator has a driver pin 20 projecting into the torque valve 16.
  • the torque valve 16 is designed as a seat valve arranged in a valve housing 21 with a valve cone 22 as a closing element which is acted upon by a measuring spring set 17 formed from the springs 23 and 24.
  • the valve seat for the valve cone 22 is formed on a valve body 25 which is displaceably arranged in the valve housing 21 and on which the driver pin 20 of the pump actuator acts.
  • the valve body is acted upon by a spring 26 which is supported in the valve housing 21 and holds the valve body 25 in positive engagement with the driver pin 20.
  • the spring 23 of the measuring spring set 17 is supported on a stop 27 and the spring 24 on an adjusting screw 28 in the stop 27.
  • the stop 27 is screwed into the end of the valve housing 21. Due to the rotational position of the stop 27, the preload of the measuring spring set 17 and thus the position of the desired torque characteristics and the response point of the torque valve 16 can be adjusted.
  • the stop 27 has a handle 29. The course of the torque characteristics or the spring characteristic can be done by changing the bias of the spring 24 with the help of the adjusting screw 28.
  • the pressure in the operating pressure control line 12 acts through the channel 30 in the valve body 25 on the closing member 22 against the force of the measuring spring set 17.
  • the width of the The valve seat determines the effective measuring surface on the closing element 22 for the pressure in the line 12. If the force exerted on the measuring surface by the pressure in the line 12 exceeds the prestressing force of the measuring spring set 17, the valve cone of the closing element 22 lifts off the valve seat in the valve body 25 and opens the control line 12 to the pressureless outlet, formed by the interior 31 of the valve housing 21 which is fixedly connected to the hydraulic pump, the interior 31 being connected to the depressurized interior 32 of the hydraulic pump.
  • the driving pin 20 moves the valve body 25 in FIG. 2 to the right against the closing member 22 and thus increases the preload of the spring set 17 in accordance with the desired course of the torque characteristic.
  • FIG. 3 shows the control device according to the invention as a total torque control for two hydraulic pumps 33, 34, the drive shafts of which are driven directly or via a corresponding transfer gear 35 (only schematically indicated by a dash) by a common drive machine, not shown.
  • the control devices for the individual pumps correspond to the control device shown in FIG. The same parts are provided with the same reference numerals and are not explained again.
  • Only the torque valves denoted by 16 in FIG. 1 are designed here as total torque valves 36 and differ from the torque valve 16 in that the closing member 22 according to FIG. 4 has an additional measuring surface 37. The operating pressure of the other pump acts on this measuring surface 37 in each case via a control line 38, 39.

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

Claims (9)

1. Dispositif de régulation de débit pour pompe hydraulique réglable, muni d'un appareil de servo-réglage hydraulique pour le réglage continu du débit de la pompe, dans lequel le réglage du débit est déterminé par la pression de sortie de la pompe et la pression qui règne dans un conduit de pilotage à la pression de fonctionnement, et dans lequel l'appareil de réglage contient un ressort (4) qui agit sur l'organe de réglage de la pompe dans le sens du débit maximum, et au moins un piston qui agit sur l'organe de réglage de la pompe dans le sens d'une réduction de débit, la surface du piston pouvant être placée sous la pression de sortie grâce à une valve de pilotage actionnée hydrauliquement, ou est en communication avec un circuit de décharge. l'actionnement de la valve de pilotage intervenant par la pression qui règne dans le conduit de pilotage de la pression de fonctionnement. caractérisé par le fait qu'on prévoit une valve de couple (16. 36) dont la force de fermeture est déterminée par un ressort étalonné 17, ou un jeu de ressorts étalonné, qui sont reliés fonctionnellement à l'organe de réglage (3) de pompe et qui sont prétendus en fonction du réglage de débit et en ce que la valve de couple (16, 36) fait communiquer le conduit de pilotage (12) de la pression de fonctionnement, avec le circuit de décharge (18) sans pression, en fonction de la pression qui règne dans le circuit de pilotage (12), et de la tension préalable du ressort étalonné (17).
2. Dispositif de régulation selon la revendication 1, caractérisé par le fait que la pression régnant dans le conduit de pilotage (12) de la pression de fonctionnement, qui agit sur la valve de pilotage (8) et la valve de couple (16-36), c'est-à-dire sur leurs organes de fermeture, est prélevée à travers une valve d'étranglement (13) dans le conduit de pilotage qui dérive du conduit de pression de fonctionnement (14) de la pompe (1) et en ce qu'en amont de la dérivation du conduit de pilotage (12), on prévoit une valve d'étranglement de débit le cas échéant réglable dans le conduit de pression de fonctionnement.
3. Dispositif de régulation selon l'une des revendications 1 ou 2, caractérisé par le fait que la valve de couple (16, 36) est fixée en tant que sous-ensemble séparé sur la pompe hydraulique (1) et qu'une tige d'entraînement (20) de l'organe de réglage de la pompe est en prise sur la valve de couple (16, 36) pour changer la tension préalable du ressort étalonné (17), ou du jeu de ressorts étalonné, en fonction du réglage du débit.
4. Dispositif de régulation selon la revendication 3, caractérisé par le fait que la valve de couple (16) est formée d'une soupape à siège dans laquelle l'organe de fermeture (22) en forme de cône de soupape, est sous l'action du ressort étalonné (17), ou du jeu de ressorts étalonné, qui s'appuie d'un côté sur une butée (27) réglable dans le corps de valve (21), et dans laquelle le siège de soupape est disposé dans un corps de soupape (25) qui peut coulisser, sur lequel la tige d'entraînement (20) est en prise.
5. Dispositif de régulation selon la revendication 4, caractérisé par le fait que le corps de soupape (25) est sous l'action d'un ressort qui le maintient en contact mécanique avec la tige d'entraînement (20).
6. Dispositif de régulation selon la revendication 4, caractérisé par le fait que la butée (27) du ressort étalonné, ou du jeu de ressort étalonné, peut être réglée de l'extérieur au moyen d'une manette (29).
7. Dispositif de régulation selon la revendication 4 ou 6, caractérisé par le fait que la butée (27) est disposée au bout du corps de valve (21) et peut être démontée pour le remplacement du ressort étalonné (17), ou du jeu de ressort étalonné.
8. Dispositif de régulation selon l'une des revendications précédentes, réalisant une régulation cumulative pour deux ou plusieurs pompes hydrauliques accouplées en ce qui concerne leur entraînement, caractérisé par le fait que l'organe de fermeture (22) de la valve de couple de chaque pompe (33, 34) est sous la somme de la pression qui règne dans le conduit de pilotage (12) de la pression de fonctionnement des pompes individuelles et de la pression de fonctionnement (14)c>"!: de l'autre pompe, ou des autres pompes et que chaque valve de couple (36) fait communiquer le conduit de pilotage (12) de la pression de fonctionnement de sa pompe avec le circuit de décharge (18) sans pression, en fonction de la pression de fonctionnement cumulée et de la tension préalable de son ressort étalonné (17).
9. Dispositif de régulation selon la revendication 8, caractérisé par le fait que les organes de fermeture des valves de couple présentent plusieurs surfaces de mesure qui agissent en parallèle et sont dans chaque cas sous la pression de fonctionnement de l'une des pompes.
EP84115198A 1983-12-14 1984-12-12 Dispositif de régulation de débit pour une pompe hydraulique réglable Expired - Lifetime EP0149787B2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE3345264 1983-12-14
DE8335902U DE8335902U1 (de) 1983-12-14 1983-12-14 Drehmomenten-Regeleinrichtung für eine verstellbare Hydropumpe
DE19833345264 DE3345264A1 (de) 1983-12-14 1983-12-14 Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe

Publications (4)

Publication Number Publication Date
EP0149787A2 EP0149787A2 (fr) 1985-07-31
EP0149787A3 EP0149787A3 (en) 1985-08-21
EP0149787B1 true EP0149787B1 (fr) 1987-05-06
EP0149787B2 EP0149787B2 (fr) 1991-10-02

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ID=25816438

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EP84115198A Expired - Lifetime EP0149787B2 (fr) 1983-12-14 1984-12-12 Dispositif de régulation de débit pour une pompe hydraulique réglable

Country Status (4)

Country Link
US (1) US4668171A (fr)
EP (1) EP0149787B2 (fr)
JP (1) JPS60147588A (fr)
DE (2) DE8335902U1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102017213458A1 (de) 2017-08-03 2019-02-07 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit Leistungsbegrenzung

Also Published As

Publication number Publication date
DE8335902U1 (de) 1987-06-04
DE3345264A1 (de) 1985-06-27
EP0149787A2 (fr) 1985-07-31
JPS60147588A (ja) 1985-08-03
EP0149787A3 (en) 1985-08-21
US4668171A (en) 1987-05-26
EP0149787B2 (fr) 1991-10-02
JPH0526955B2 (fr) 1993-04-19

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