EP1118771B1 - Dispositif de régulation de puissance - Google Patents

Dispositif de régulation de puissance

Info

Publication number
EP1118771B1
EP1118771B1 EP20000127378 EP00127378A EP1118771B1 EP 1118771 B1 EP1118771 B1 EP 1118771B1 EP 20000127378 EP20000127378 EP 20000127378 EP 00127378 A EP00127378 A EP 00127378A EP 1118771 B1 EP1118771 B1 EP 1118771B1
Authority
EP
European Patent Office
Prior art keywords
piston
regulating device
control
power regulating
setting
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
EP20000127378
Other languages
German (de)
English (en)
Other versions
EP1118771A3 (fr
EP1118771A2 (fr
Inventor
Gerhard Beutler
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 Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1118771A2 publication Critical patent/EP1118771A2/fr
Publication of EP1118771A3 publication Critical patent/EP1118771A3/fr
Application granted granted Critical
Publication of EP1118771B1 publication Critical patent/EP1118771B1/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
    • 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
    • F04B49/002—Hydraulic systems to change the pump delivery

Definitions

  • the invention relates to a power control device for regulating the power of a piston engine according to the preamble of claim 1.
  • a control device for controlling an adjustable hydraulic pump according to the preamble of claim 1 is shown in EP 0 149 787 B2.
  • a disadvantage of the device known from EP 0 149 787 B2 is in particular the high construction costs, which is due to the attachment of the torque valve as a separate assembly to the hydraulic pump. Also, the possibility of readjusting the power during operation can be accomplished only with great effort.
  • Object of the present invention is therefore to provide a power control device, which manages with low construction costs and can be realized using an existing pump with adjustment.
  • the power controller according to the invention with the characterizing features of claim 1 has over the known from EP 0147987 B2 control device has the advantage that the controller can be set separately for different services by its design before installation. Likewise, the power setting during operation by a control device, which is easily accessible, be readjusted.
  • control device is a prefabricated overall component in a specific recess in the housing of the piston engine.
  • control device in this case already existing pumps with devices for adjusting the power without major construction costs retrofitted.
  • the performance curve of the pump can be moved as required by additional external hydraulic pressure.
  • the power control device according to the invention can therefore be used as a total power controller.
  • Another advantage is the low loss of control oil, since the power control device is controlled directly.
  • Fig. 1 shows an axial section through an axial piston machine 1 in swash plate design, in which a power control device 2 according to the invention is provided.
  • the basic structure of an axial piston machine 1 in swash plate design is known, so that the following description can be limited to the essential components.
  • a shaft 3 is rotatably mounted on a first bearing 4 and on a second bearing 5 in a housing 6 of the axial piston machine 1.
  • the housing 6 of the axial piston machine 1 is divided into a main body 6a and a lid body 6b screwed to the main body 6a.
  • a cylinder drum 7 is rotatably connected to the shaft 3.
  • the cylinder drum 7 are arranged on a pitch circle offset cylinder bores 8, in which piston 9 are axially displaceable.
  • the pistons 9 are connected via ball joint connections 10 with sliding shoes 11 and are supported on the sliding blocks 11 on a swash plate 12 designed as a pivoting cradle.
  • the swash plate 12 serves as an actuator for adjusting the delivery volume of the axial piston machine 1.
  • the compound of Cylinder bores 8 with a high-pressure line, not shown, and a low-pressure line, also not shown, via a control body 13 which has a kidney-shaped high-pressure opening 14 and a likewise kidney-shaped low-pressure opening 15.
  • the stroke of the piston 9 in the cylinder bores 8 is predetermined by the swivel angle ⁇ of the swash plate 12.
  • the swashplate 12 designed as a swivel cradle is shown twice in FIG. 1 both in its neutral position and in a position pivoted by the swivel angle ⁇ .
  • the cylinder drum 7 is held by a spring 22 on the control body 13 in abutment.
  • the spring 22 is supported on the cylinder drum 7 via a first ring 23 and on the shaft 3 via a second ring 24.
  • the cylinder drum 7 is axially movable relative to the stationary shaft 3 via a wedge and groove connection.
  • the power control device 2 is integrated in a receiving bore 16 of the housing 6 and consists of a connected via a ball joint sliding connection 17 with the swash plate 12 actuating piston 18 which is axially guided in the receiving bore 16, an inserted into the receiving bore 16 control valve 19.
  • the control valve 19 and the actuating piston 18 are axially offset from one another in the receiving bore 16.
  • a control valve for a flow control in the same manner can be used in the receiving bore 16, as is known from DE 199 49 169 A1.
  • the control valves are therefore modular exchangeable depending on the application.
  • a spherical sliding block 22 slidably, which forms the ball joint sliding joint 17 together with a spherical recess 23 shown in Fig. 1 of the swash plate 12.
  • the sliding block 22 could rest on the swash plate 12 slidably and the spherical recess 23 may be formed in the actuating piston 18.
  • the first embodiment of the power control device 2 according to the invention is shown enlarged in Fig. 2.
  • matching elements with matching reference numerals are provided with Fig. 1 in order to facilitate the assignment.
  • the actuating piston 18 is cup-shaped and has a central Befest Trentsdocht 30, which has a thread. In the thread 31, a threaded portion 31 of an extension 32 can be screwed, which extends in the axial direction by the adjusting piston 18, the control piston 20, a second spring retainer 33 and return springs 50, 53.
  • the actuating piston 18 is adjoined by a valve sleeve 35 which has a first operating pressure connection 36, which is connected to the operating pressure of the piston engine 1, and a tank connection 37.
  • the control piston 20 is surrounded in the radial direction by the valve sleeve 35 and is penetrated by the extension 32, which is guided through a recess 41 of the control piston 20 therethrough.
  • the control piston 20 has a first groove 38, which is connected to the first operating pressure port 36 and on which a first engagement surface 39 is formed for the operating pressure of the piston engine 1. Over the first attack surface 39 exerts the operating pressure of the piston engine. 1 an axial force on the control piston 20 from.
  • a second groove 40 in the control piston 20 is connected to the tank port 37.
  • the control piston 18 has a control pressure chamber 42 which is formed as a recess in the control piston 18.
  • the adjusting pressure chamber 42 communicates via axial bores 59a and at least one radial bore 59b in the valve sleeve 35 with a first control edge 43 and a second control edge 44 of the control piston 20 in connection.
  • the radial bore 59b is connected to the first groove 38 via the first control edge 43 or to the second groove 40 via the second control edge 44.
  • the pressure in the control pressure chamber is either increased or decreased.
  • the control pressure chamber 42 is connected via an integrated in the valve sleeve 35 outlet throttle 45 to the tank port 37, so that the actuating piston 18 displaces the hydraulic fluid from the control pressure chamber at a pivoting to maximum displacement volume.
  • the control piston 20 abuts with a first end 46 in a central recess 47 of the valve sleeve 35 and is connected at a second end 48 with the second spring retainer 33, which has an outside step 49.
  • a first return spring 50 is supported, which is penetrated by the extension 32 in the axial direction.
  • the first return spring 50 is supported on the end side on an outer support sleeve 52a, which forms a first spring receptacle 51 with an inner support sleeve 52b.
  • a second return spring 53 is supported.
  • the first spring retainer 51 bears against a lock nut 54, which is screwed onto a thread 55 at the end of the extension bolt 32. After loosening the lock nut 54 is an adjustment of the spring tension of the return springs 50 and 53 by screwing the spring retainer 51 relative to the extension 32 allows.
  • the return springs 50 and 53 and the first Spring receptacle 51 are arranged in a spring receiving space 34 and are surrounded by a spring chamber sleeve 56. This is designed removable and with a sealing element 57, z. As an O-ring sealed.
  • Another sealing element 58 which may also be designed as an O-ring seals the power control device 2 against the piston engine 1 from.
  • the operation of the power control device 2 is based on the background that the capacity of the reciprocating engine 1 is dependent on the swivel angle ⁇ of the swash plate 12 and the working pressure. If the swash plate 12 is at a right angle ( ⁇ 0 °) relative to the axis 3, the piston engine 1 is idling. As soon as the angle ⁇ becomes larger, the piston engine 1 starts to deliver hydraulic fluid. In order to regulate or limit the delivery rate, the control valve 19 can adjust the adjusting piston 18 so that the swashplate 12 is tilted at an angle ⁇ which extends from 0 ° to a certain maximum angle. The maximum angle is defined by the basic position of the actuating piston 18. The piston engine 1 always starts at this maximum angle to build up sufficient pressure.
  • the operating pressure is applied to the operating pressure connection 36 of the valve sleeve 35.
  • the hydraulic fluid filling the first groove 38 under operating pressure exerts a force on the first engagement surface 39, which moves the control piston 20 slowly against the force of the first return spring 50 which bears against the second spring mount 33 in the direction of the spring chamber sleeve 56.
  • the movement is due to the fact that the final surfaces of the first groove 38 have a slight paragraph, so that the pressures on the final surfaces of the first groove 38 are different in size and a resultant force in the direction of the spring chamber sleeve 56 is applied.
  • control piston 20 leads to a larger opposite movement of the actuating piston 18, which presses against the swash plate 12 and thereby reduces the pivot angle ⁇ .
  • the pressure in the control pressure chamber 42 is controlled by the control valve 19 to a lying between tank pressure and operating pressure setting. As long as the control pressure chamber 42 is in communication with the first groove 38, hydraulic fluid is pressed under operating pressure in the control pressure chamber 42, whereby the control piston 18 moves the swash plate 12 in the direction of smaller pivot angle ⁇ .
  • control pressure chamber 42 Since the control pressure chamber 42 is connected to the tank port 37 via the flow restrictor 45 integrated in the valve sleeve 35, the hydraulic fluid under control pressure can be returned to the tank port 37 in the event of a declining movement of the control piston 18.
  • the power control device 2 leads to an approximately constant maximum output of the piston engine 1.
  • the assumed values of pressure and displacement are in a pressure-displacement diagram (pV diagram) on a straight line, the slope in this area in about the slope of the theoretical butterhyperbel in pV diagram corresponds.
  • pV diagram pressure-displacement diagram
  • the second return spring 53 which is supported on an inner support sleeve 52 and only for the first time Wear occurs when the first return spring 50 is biased to a certain value, again a stable operating condition can be achieved, which corresponds to a second straight line in the pV diagram, wherein the second straight line has a higher slope than the first straight line and thus the slope of the linenhyperbel in the range of high pressures p or small delivery volumes V adapted.
  • a second embodiment of the power control device 2 according to the invention is shown, which differs from the first embodiment by a second operating pressure port 60, which is connected to the operating pressure of a further, not shown piston engine.
  • the control piston 20 has a third groove 61 which is connected to the second operating pressure port 60 and on which a second engagement surface 62 is formed for the operating pressure of the further piston engine. Via the second engagement surface 62, the operating pressure of the further piston engine exerts a further axial force on the control piston 20.
  • a corresponding choice of the individual operating pressures or the individual delivery volumes of the piston engine 1 and the other piston engine, not shown, means that the power control device 2 according to the invention can also be designed as a total power controller, the sum of the outputs of the piston engine 1 and the other piston engine, not shown a predetermined maximum is limited.
  • the actuating piston 18 moves as long as in the direction of smaller pivot angle ⁇ of the swash plate 12 until a balance between the sum of the operating pressures and the spring forces is restored.
  • the invention is not limited to the illustrated embodiments, but can also be used in a power control device 2 in a different construction or in axial piston machines 1 in a different construction. It should be emphasized that the travel of the actuating piston 18 is independent of the travel of the control piston 20 and despite a very small adjustment of the control piston 20 can achieve a much larger travel of the actuating piston 18.

Claims (16)

  1. Dispositif de régulation de puissance (2) pour réguler la puissance d'un appareil à pistons (1), comprenant :
    un piston de positionnement (18) qui agit sur l'organe de réglage (12) de l'appareil à pistons (1), et
    une valve de commande (19) avec un piston de commande (20), sur lequel agissent une pression de service du moteur à pistons (1) et au moins un ressort de rappel (50) dont la précontrainte dépend de la position de l'organe de réglage (12),
    caractérisé en ce que
    le piston de positionnement (18) et la valve de commande (19) sont agencés en décalage axial l'un par rapport à l'autre,
    un prolongement (32) du piston de positionnement (18) s'étend à travers la valve de commande (19) ; et
    le ressort de rappel (50) est tendu (50) entre un premier logement à ressort (51) du prolongement (32) du piston de positionnement (18), et un second logement à ressort (33), opposé au piston de positionnement (18), du piston de commande (20).
  2. Dispositif de régulation de puissance selon la revendication 1, caractérisé en ce que le piston de positionnement (18) et la valve de commande (19) sont agencés dans un évidement commun (16) d'un boîtier (6) de l'appareil à pistons (1).
  3. Dispositif de régulation de puissance selon la revendication 1 ou 2, caractérisé en ce que la valve de commande (19) comprend une douille de valve (35), dans laquelle sont ménagés un premier raccord de pression de service (36), qui est relié à la pression de service du moteur à pistons (1), et un raccord de réservoir (37).
  4. Dispositif de régulation de puissance selon la revendication 3, caractérisé en ce que le piston de commande (20) présente une première gorge (38) qui est reliée au premier raccord de pression de service (36) et sur laquelle est réalisée une première surface d'attaque (39) pour la pression de service du moteur à pistons (1), via laquelle la pression de service du moteur à pistons (1) exerce une force axiale sur le piston de commande (20).
  5. Dispositif de régulation de puissance selon la revendication 4, caractérisé en ce que le piston de commande (20) présente une seconde gorge (40) qui est reliée au raccord de réservoir (37).
  6. Dispositif de régulation de puissance selon la revendication 5, caractérisé en ce qu'une chambre de pression de positionnement (42) est adjacente au piston de positionnement (18), ladite chambre pouvant être reliée, en fonction de la position du piston de commande (20), à la première gorge (38) via une première arête de commande (43), et à la seconde gorge (40) du piston de commande (20) via une seconde arête de commande (44).
  7. Dispositif de régulation de puissance selon la revendication 6, caractérisé en ce que la chambre de pression de positionnement (42) est reliée au raccord de réservoir (37) via un étranglement de sortie (45) intégré dans la douille de valve (35).
  8. Dispositif de régulation de puissance selon l'une des revendications 3 à 7, caractérisé en ce que la douille de valve (35) comporte un second raccord de pression de service (60), qui peut être relié à la pression de service d'un autre moteur à pistons.
  9. Dispositif de régulation de puissance selon la revendication 8, caractérisé en ce que le piston de commande (20) comporte une troisième gorge (61), qui peut être reliée au second raccord de pression de service (60), et sur laquelle est réalisée une seconde surface d'attaque (62) pour la pression de service de l'autre moteur à pistons, via laquelle la pression de service de l'autre moteur à pistons exerce une force axiale sur le piston de commande (20).
  10. Dispositif de régulation de puissance selon l'une des revendications 1 à 9, caractérisé en ce qu'ils est prévu plusieurs ressorts de rappel (50, 53) qui sont précontraints les uns après les autres, au fur et à mesure du rappel de l'organe de positionnement (12), en direction d'un volume de refoulement minimum.
  11. Dispositif de régulation de puissance selon la revendication 10, caractérisé en ce que les ressorts de rappel (50, 53) sont agencés dans une chambre de réception de ressort (34), qui se trouve sur le côté de la valve de commande (19) opposé au piston de positionnement (18), et en ce que le prolongement du piston de positionnement (18) s'étend jusque dans la chambre de réception du ressort (34).
  12. Dispositif de régulation de puissance selon la revendication 11, caractérisé en ce que le prolongement (32) est réalisé à la manière d'un goujon, qui est relié au piston de commande (18) et au premier logement à ressort (51) par coopération de forces et de manière à pouvoir être réglé axialement.
  13. Dispositif de régulation de puissance selon la revendication 12, caractérisé en ce que le goujon (32) s'étend à travers un évidement (41) du piston de commande (20).
  14. Dispositif de régulation de puissance selon la revendication 11 ou 12, caractérisé en ce que le piston de positionnement (18) est réalisé en forme de pot avec une mèche de fixation centrale (30), dans laquelle peut être vissé un tronçon fileté (31) du goujon (32).
  15. Dispositif de régulation de puissance selon l'une des revendications 11 à 14, caractérisé en ce que la chambre de réception de ressort (34) est entourée par une douille amovible (56) formant logement de ressort.
  16. Dispositif de régulation de puissance selon la revendication 2, caractérisé en ce que, en variante à la valve de commande (19) pour la régulation de puissance, on peut utiliser une valve de commande pour une régulation d'alimentation et/ou pour un écrêtage de pression.
EP20000127378 2000-01-18 2000-12-13 Dispositif de régulation de puissance Expired - Lifetime EP1118771B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000101826 DE10001826C1 (de) 2000-01-18 2000-01-18 Vorrichtung zum Regeln der Leistung einer verstellbaren Kolbenmaschine
DE10001826 2000-01-18

Publications (3)

Publication Number Publication Date
EP1118771A2 EP1118771A2 (fr) 2001-07-25
EP1118771A3 EP1118771A3 (fr) 2005-10-19
EP1118771B1 true EP1118771B1 (fr) 2006-08-16

Family

ID=7627827

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20000127378 Expired - Lifetime EP1118771B1 (fr) 2000-01-18 2000-12-13 Dispositif de régulation de puissance

Country Status (2)

Country Link
EP (1) EP1118771B1 (fr)
DE (2) DE10001826C1 (fr)

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10341331B3 (de) * 2003-09-08 2005-05-25 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung
DE102007022569A1 (de) 2007-05-14 2008-11-20 Robert Bosch Gmbh Axialkolbenmaschine mit Rückführvorrichtung
DE102009006909B4 (de) 2009-01-30 2019-09-12 Robert Bosch Gmbh Axialkolbenmaschine mit reduzierter Stelldruckpulsation
DE102013214861A1 (de) 2012-08-16 2014-05-22 Robert Bosch Gmbh Verstellvorrichtung für eine hydrostatische Pumpe und hydrostatische Pumpe
DE102012022997A1 (de) 2012-11-24 2014-05-28 Robert Bosch Gmbh Verstelleinrichtung für eine Hydromaschine und hydraulische Axialkolbenmaschine
DE102013206161A1 (de) * 2013-04-08 2014-10-30 Robert Bosch Gmbh Axialkolbenmaschine
DE102014202411A1 (de) 2014-02-11 2015-08-13 Robert Bosch Gmbh Elektrisch angesteuertes Druckregelventil für eine verstellbare hydrostatische Pumpe und eine verstellbare hydrostatische Pumpe mit einem Druckregelventil
DE102014202412A1 (de) 2014-02-11 2015-08-13 Robert Bosch Gmbh Elektrisch angesteuertes Druckregelventil für eine verstellbare hydrostatische Pumpe und verstellbare hydrostatische Pumpe mit einem Druckregelventil
DE102014202413A1 (de) 2014-02-11 2015-08-13 Robert Bosch Gmbh Elektrisch angesteuertes Regelventil für eine verstellbare hydrostatische Pumpe und verstellbare hydrostatische Pumpe
DE102014226378A1 (de) 2014-02-18 2015-08-20 Robert Bosch Gmbh Elektrisch angesteuertes Druckregelventil für eine verstellbare hydrostatische Pumpe
DE102014206755A1 (de) 2014-02-18 2015-08-20 Robert Bosch Gmbh Verstelleinrichtung einer Axialkolbenmaschine
DE102015207260A1 (de) 2014-05-22 2015-11-26 Robert Bosch Gmbh Verstelleinrichtung für eine hydrostatische Kolbenmaschine und hydrostatische Axialkolbenmaschine
DE102015207259A1 (de) 2014-05-22 2015-11-26 Robert Bosch Gmbh Verstelleinrichtung für eine hydrostatische Kolbenmaschine und hydrostatische Axialkolbenmaschine
DE102014211202A1 (de) * 2014-06-12 2015-12-17 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise und Lüfter mit einer hydro-statischen Axialkolbenmaschine
CH714321A1 (de) 2017-11-11 2019-05-15 Liebherr Machines Bulle Sa Verstellvorrichtung für eine Axialkolbenmaschine.

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WO1982001046A1 (fr) * 1980-09-12 1982-04-01 Liesener K Commande d'utilisation de puissance pour pompes a deplacement variable
DE3200885A1 (de) * 1982-01-14 1983-07-21 Robert Bosch Gmbh, 7000 Stuttgart Leistungsregler fuer eine hydrostatische pumpe
DE3232903A1 (de) * 1982-09-04 1984-03-08 Alfred Teves Gmbh, 6000 Frankfurt Hydrostatischer antrieb
DE8335902U1 (fr) * 1983-12-14 1987-06-04 Brueninghaus Hydraulik Gmbh, 7240 Horb, De
DE3935800C2 (de) * 1989-10-27 1997-03-27 Linde Ag Einstellbare Axialkolbenmaschine in Schrägscheibenbauweise
DE4141722A1 (de) * 1991-12-18 1993-06-24 Bayer Ag Isocyanat-trimerisierungskatalysator
DE19949169C2 (de) 1999-10-12 2001-10-11 Brueninghaus Hydromatik Gmbh Verstellvorrichtung

Also Published As

Publication number Publication date
EP1118771A3 (fr) 2005-10-19
DE10001826C1 (de) 2001-09-20
DE50013332D1 (de) 2006-09-28
EP1118771A2 (fr) 2001-07-25

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