EP0525507A2 - Dispositif de réglage d'un actionneur pour régler la cylindrée d'un machine hydrostatique - Google Patents

Dispositif de réglage d'un actionneur pour régler la cylindrée d'un machine hydrostatique Download PDF

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Publication number
EP0525507A2
EP0525507A2 EP92112031A EP92112031A EP0525507A2 EP 0525507 A2 EP0525507 A2 EP 0525507A2 EP 92112031 A EP92112031 A EP 92112031A EP 92112031 A EP92112031 A EP 92112031A EP 0525507 A2 EP0525507 A2 EP 0525507A2
Authority
EP
European Patent Office
Prior art keywords
shaft
zero position
actuator
zero
contact surface
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
EP92112031A
Other languages
German (de)
English (en)
Other versions
EP0525507B1 (fr
EP0525507A3 (en
Inventor
Horst Stegmaier
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
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, Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0525507A2 publication Critical patent/EP0525507A2/fr
Publication of EP0525507A3 publication Critical patent/EP0525507A3/de
Application granted granted Critical
Publication of EP0525507B1 publication Critical patent/EP0525507B1/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
    • F04B49/12—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 by varying the length of stroke of the working members

Definitions

  • the invention relates to a device according to the preamble of claim 1, which is provided for adjusting the actuator for the displacement volume of a hydrostatic machine.
  • FIGS. 3 and 4 Such devices are known from practice and are shown in FIGS. 3 and 4 using an exemplary embodiment with hydraulic control of the actuator of a reversible hydrostatic machine, FIG. 4 being a section along the line 11-11 in FIG. 3.
  • the shaft 1 of this known device is in hydraulic connection with the actuator 4 via two hydraulic lines 2, 3 and is designed to control the hydraulic action thereof as a control shaft of a rotary valve with feedback.
  • the feedback consists of a shaft 6 surrounding the shaft 6, which is rotatably mounted in the housing 5, and a return element 7 which connects it to the actuator 4 and is pivotably mounted in the housing 7.
  • a hand lever 8 is used to rotate the shaft 1 in opposite directions until it is reached an end position which corresponds to an end position of the actuator 4 corresponding to the respective maximum displacement volume setting of the hydrostatic machine.
  • the reset arrangement of this known device comprises an approximately half inserted in the shaft 1 reset pin 9, the free end protruding from the shaft 1 engages between two axially displaceable reset bolts 10 within the housing 5, which are coaxial to one another and transverse to the shaft 1 and transverse to Reset pin 9 arranged and held by the pressure of a spring 11 in contact with the latter.
  • the shaft 1 is in a rotational position, referred to as zero position, relative to the housing 5, which corresponds to a zero position of the actuator 4 corresponding to the zero displacement volume setting of the hydrostatic machine.
  • Rotation of the shaft 1 in the direction of one of its end positions results in a corresponding pivoting movement of the reset pin 9 and thus in the same direction displacement of both reset pins 10 in the corresponding direction.
  • the resulting force imbalance between the springs 11 is available for returning the shaft 1 to its zero position.
  • the known device is disadvantageous in that, due to different fatigue behavior of the springs 11 on the zero position shaft 1, force imbalance may prevail, which causes the shaft 1 to rotate further into a rotational position in which the force balance is achieved, but the shaft does not assume the zero position; the repeatable exact setting of the hydrostatic machine to zero displacement is therefore not guaranteed.
  • This disadvantage is particularly critical in the case of zero overlap at the control edges of the rotary valve.
  • Another disadvantage is the undesirably large design effort.
  • the restoring element In the zero position, the restoring element according to the invention rests with its contact areas on the contact surface of the shaft as a result of its application of force by, for example, a spring and fixes the latter in its zero position due to the arrangement of its contact areas on both sides of the plane which approximately perpendicularly intersects the plane and contains the shaft rotation axis .
  • the shaft moves away from its zero position with its contact surface from one of the two contact areas, but remains in contact with the other and, via this, gives the restoring element a movement impulse in the manner of a cam against the restoring force of the spring.
  • the shaft and thus the restoring element are rotated or displaced into an end position or end position, which is preferably adjustable by means of a stop, which corresponds to a specific displacement volume setting of the hydrostatic machine.
  • the restoring force of the spring which is tensioned at the same time is available for displacing the restoring element back into the zero position and for fixing the shaft in the corresponding zero position. Since only one force-applying device, e.g. the aforesaid spring acts, no fatigue imbalance and thus no change in the zero position of the shaft can occur, even as it is tired, as is known in the prior art. In this way, the repeatable, exact setting of the shaft and thus the hydrostatic machine into the zero position or to the zero displacement volume setting is ensured.
  • Another advantage of the device according to the invention is that both a non-reversible and a reversible hydrostatic machine require only a single force-actuated restoring element, and thus the design effort is more than halved compared to the prior art.
  • the contact areas are preferably those in FIG Edge regions running in the longitudinal direction of a shaft of a flat contact surface formed on the restoring element, the surface portion of which located between the edge regions comprises the further contact regions.
  • the device according to the invention according to FIGS. 1 and 2 comprises a housing 5, a shaft 12, a hand lever 8, a reset arrangement which consists of a spring 11, a reset element 13 acted upon by it and a closure part 14, and an adjustment arrangement consisting of an adjustment lever 15 and an eccentric 16 which is in engagement with an actuator 4 for the displacement volume of a hydrostatic machine, not shown.
  • the shaft 12 is rotatably supported about its axis of rotation 17 coinciding with its longitudinal center axis in a bearing bore in the housing 5, from which it projects with one end to which the hand lever 8 is attached.
  • the shaft 12 In the area of its opposite end, which is flush with the housing 5, the shaft 12 has an axially accessible threaded bore that opens into a radial blind bore of the shaft 12.
  • the adjusting lever 15 passes through a recess 18 in the housing 5 and engages with one end in the radial blind bore, in which it is held firmly by a screw 19 screwed into the axial threaded bore and adjustable from the outside.
  • the recess 18 has the shape of a circular sector. to enable the pivoting movement of the adjusting lever 15 that takes place when the shaft 12 rotates.
  • the eccentric 16 is fastened from the housing 5 or the recess 18 protruding end of the adjusting lever 15.
  • the adjusting lever 15 By turning the adjusting lever 15 within the blind bore - for example by means of a screwdriver engaging in a slot 60 in the eccentric 16 - the exact zero position of the actuator 4 can be set and fixed by means of the screw 19.
  • a stepped bore 20 in the housing 5 is formed offset by 90 ° with respect to the latter. It extends transversely to the shaft 12 from a housing wall 21 to the bearing bore bearing the shaft 12.
  • the closure part 14 in the form of a screw consisting of a head section 22 and a bolt section 23 is screwed into the larger diameter section of the bore 20 and is formed with a central stitch bore 24 which passes through the bolt section 23 with a larger diameter and ends in the head section 22 with a smaller diameter .
  • the restoring element 13 in the form of a cylindrical bolt is displaceably guided with a certain stroke in the section of smaller diameter of the bore 20 and in the section of larger diameter of the tap hole 24 and has a central tap hole which forms a cavity 25.
  • the spring 11 is arranged in this cavity 25 and in the tap hole 24 with prestress. It is supported on the bottom 26 of the tap hole 24 and acts on the cavity floor 27 of the cavity 25.
  • the free end of the restoring element 13 facing the bearing bore for the shaft 12 is provided with a central projection 28 which engages in a groove 29 cut into the shaft 12 transversely to this with such little play that it fixes the shaft 12 in the axial direction.
  • the groove 29 is open on both sides and its depth corresponds to the shaft radius, so that it is transverse to the shaft longitudinal axis measured width of the groove base 30 is equal to the shaft diameter.
  • the height of the extension 28 corresponds to the depth of the groove 29, so that in the rotational position of the shaft 12 shown in FIG. 4 relative to the housing 5, the restoring element 13 as a result of the force applied by the spring 11 having the plane designated as the contact surface 31 (FIG. 7)
  • the top of its shoulder 28 bears against the flat groove base 30 of the shaft 12, which is referred to as the contact surface.
  • the second embodiment of the reset arrangement shown in FIGS. 5 to 7 differs from the first embodiment according to FIGS. 3 and 4 only in that its closure part 32 has the shape of a bolt provided with the tap hole 24 or a hollow cylinder which is closed on one side, by its closed one At the end, an externally adjustable stop 33, consisting of a threaded pin that can be locked by means of a screw, protrudes for a sleeve 34 that can be displaced in the tap hole 24.
  • the restoring element 13 is displaceably arranged in the remaining part of the tap hole 24 with the same stroke as in FIGS. 1 and 2 and is acted upon in the same way by the spring 11 passing through the sleeve 34.
  • FIGS. 2 and 5, 6 show the shaft 12 in a rotational position, referred to as zero position, relative to the housing 5, which corresponds to a zero position of the actuator 4 corresponding to the zero displacement volume setting of the hydrostatic machine.
  • the correspondence is established by adjusting the adjustment lever 15 and thus the eccentric 16 accordingly (see FIG. 2).
  • the reset element 13 is in its zero position, in which it rests completely against the contact surface 31 of the contact surface 30 of the shaft 12 under the force of the prestressed spring 11.
  • the arrangement of the contact surface 30 and the contact surface 31 on both sides of a plane E intersecting both surfaces 30, 31 perpendicularly and containing the shaft axis of rotation 17, together with the spring 11, causes the shaft 12 and the restoring element 13 to be mutually fixed in the zero position or Zero position.
  • the shaft 12 serves on the one hand as a stop for the restoring element 13 and thus prevents the spring 11 from displacing it beyond the zero position, and on the other hand is reset by the restoring element 13 fixed in this way with the biasing force of the spring 11 in its zero position.
  • the shaft 12 is rotated from its zero position by a corresponding angular amount in the corresponding direction by means of the hand lever 8 and thus causes a pivoting movement of the adjusting lever 15 by a corresponding swivel angle.
  • This pivoting movement is transmitted from the eccentric 16 to the actuator 4, which in turn causes the hydrostatic machine to pivot out to a corresponding displacement.
  • the shaft 12 remains out of its zero position with only one of the two edges 35 and 36 of its contact surface 30 running in the longitudinal direction of the shaft (the left edge 36 in FIG. 7 in contact with the contact surface 31 of the restoring element 13 and displaces it the latter in the manner of a cam against the restoring force of the spring 11 in the direction of or up to the end position defined by the stop 33 and the sleeve 34.
  • a radial sliding movement of the relevant edge 35 or 36 takes place along the contact surface 31, of the respective other edge 36 or 35 moves away, namely in their respectively assigned edge region 37 or 38 along a distance which corresponds to the angle of rotation of the shaft 12.
  • FIG. 7 shows the end position of the shaft 12 that can be reached by turning counterclockwise, in which the return element 13 and the actuator 4, not shown, assume their end positions, which correspond to the maximum displacement volume setting of the hydrostatic machine.
  • the device shown in Figures 8 to 12 according to the second embodiment of the invention differs from the first embodiment according to FIGS. 1 and 2 by the adjustable stop 33 according to Figures 5 to 7 and by training as a hydraulic control device for the actuator 4 with a Shaft 1, which is designed as a control shaft of a rotary valve with feedback. Otherwise, both devices are of the same construction.
  • the shaft 1 is rotatably mounted in a bushing 6 which is rotatably arranged in the bearing bore of the housing 5 and is provided in the region facing the hand lever 8 to the side of the groove 29 at diametrically opposite points, each with a recess forming a control chamber 41, 42.
  • the socket 6 has four through openings 43 to 46, each offset by 90 °, to which four connection channels 47 to 50 in the housing 5 are assigned.
  • the diametrically opposite connection channels 47, 49 lead to the tank, not shown, or to a hydraulic pressure medium source, also not shown.
  • the remaining connection channels 48, 50 are connected via hydraulic lines 2 and 3 to pressure chambers of the actuator 4, not shown.
  • the shaft 1 with the control chambers 41, 42, the socket 6 with the through openings 43 to 46 and the connecting channels 47 to 50 represent the rotary valve.
  • the return comprises the socket 6 and a return element 7 of the shape shown in FIGS. 3 and 4 Adjusting lever 15, which passes through the same circular sector-shaped recess 18 shown in FIGS. 3 and 4, engages with one end in an incision 51 in the actuator 4 and with the other end via a ball 52 in a recess in the bush 6. A part of the ball 52 protruding into the area of the shaft is accommodated in the shaft 1 with sufficient play in an annular, transverse groove 53. In this way, the rotary movements of the shaft 1 and the bushing 6 which are otherwise blocked by the ball are made possible.
  • the return element 7 is pivotally mounted within the recess 18 about a cranked part 54 of a pin 55.
  • the pin 55 is rotatably arranged in corresponding bores running parallel to the shaft 1 in the housing 5, from which it projects with a threaded end. By rotating the pin 55 within the bores, the exact zero position of the actuator 4 can be set and fixed by means of a nut 56.
  • the bushing 6 also has an annular recess 57 in the region of the groove 29, which enables the bushing 6 to rotate undisturbed by the restoring element 13.
  • the shaft 1 is rotated out of its zero position in the corresponding direction, counterclockwise in FIG. 11 and into its end position, so that its control chambers 41, 42 are the pressure chambers of the Connect the actuator 4 to the pressure medium source and the tank, the socket 6 still remaining in its zero position.
  • the left pressure chamber 42 of the actuator 4 is connected to the pressure medium source via the line 2, the connecting channel 50, the through openings 46, 45 and the connecting channel 49, while the right pressure chamber of the actuator 4 is connected via the left control chamber 42 the line 3, the connecting duct 48, the through opening 44, the right control chamber 41, the through opening 43 and the connecting duct 47 to the tank is relieved.
  • the actuator 4 is displaced in the direction of its end position - to the right in FIG. 12 - and the hydrostatic machine is pivoted out accordingly.
  • the return element 7 transmits this displacement of the actuator 4 to the bushing 6, which is thereby rotated - counterclockwise in FIG. 12 - until, when the actuator 4 has reached its end position shown in FIG. 12, the same rotational position relative to the shaft 1 as in Figure 10 occupies.
  • the connections of the pressure chambers of the actuator 4 to the pressure medium source and the tank are interrupted and in this way the actuator 4 is hydraulically locked in its end position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Mechanically-Actuated Valves (AREA)
EP92112031A 1991-08-02 1992-07-15 Dispositif de réglage d'un actionneur pour régler la cylindrée d'une machine hydrostatique Expired - Lifetime EP0525507B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4125706A DE4125706C1 (fr) 1991-08-02 1991-08-02
DE4125706 1991-08-02

Publications (3)

Publication Number Publication Date
EP0525507A2 true EP0525507A2 (fr) 1993-02-03
EP0525507A3 EP0525507A3 (en) 1994-05-18
EP0525507B1 EP0525507B1 (fr) 1996-09-04

Family

ID=6437603

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92112031A Expired - Lifetime EP0525507B1 (fr) 1991-08-02 1992-07-15 Dispositif de réglage d'un actionneur pour régler la cylindrée d'une machine hydrostatique

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EP (1) EP0525507B1 (fr)
DE (2) DE4125706C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1219831A2 (fr) * 2000-12-20 2002-07-03 Brueninghaus Hydromatik Gmbh Dispositif de réglage de la course pour une machine hydrostatique à débit variable

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19540654C1 (de) * 1995-10-31 1996-12-19 Brueninghaus Hydromatik Gmbh Verstellvorrichtung mit hydraulischer Zentriereinrichtung
DE10006405B4 (de) * 2000-02-14 2005-04-14 Brueninghaus Hydromatik Gmbh Verstellvorrichtung
EP2138720A3 (fr) * 2008-06-24 2010-01-20 MALI Holding AG Dispositif de réglage pour le réglage de machines à pistons axiaux.
DE102012200217B4 (de) * 2012-01-09 2015-01-08 Danfoss Power Solutions Gmbh & Co. Ohg Neutraleinstellungsvorrichtung einer verstellbaren Hydraulikmaschine
DE102016226039B3 (de) * 2016-12-22 2018-02-08 Danfoss Power Solutions Gmbh & Co. Ohg Verdrängungssteueranordnung für eine axialkolbenpumpe
DE102016015779A1 (de) 2016-12-22 2018-06-28 Danfoss Power Solutions Gmbh & Co. Ohg Verdrängungssteueranordnung für eine Axialkolbenpumpe
DE102021205359A1 (de) 2021-05-26 2022-12-01 Danfoss Power Solutions Gmbh & Co. Ohg Neutraleinstellvorrichtung für eine einstellbare Hydraulikeinheit

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1082374A (en) * 1965-08-19 1967-09-06 Murray Mfg Corp Improvements in or relating to mechanical biassing arrangements
US3392526A (en) * 1966-10-11 1968-07-16 Int Harvester Co Control mechanism
FR1535116A (fr) * 1967-08-18 1968-08-02 Bosch Gmbh Robert Mécanisme de transmission hydraulique
GB2037916A (en) * 1978-12-07 1980-07-16 Saab Scania Ab Device in a gear selection mechanism for a manual vehicle transmission

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE605386C (de) * 1931-04-16 1934-11-09 Hans Thoma Dr Ing Reglungseinrichtung fuer Fahrzeuge mit Antrieb durch einen Verbrennungsmotor und hydraulischer Kraftuebertragung auf die Fahrzeugachsen
GB994692A (en) * 1961-06-12 1965-06-10 Dowty Hydraulic Units Ltd Improved positive displacement pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1082374A (en) * 1965-08-19 1967-09-06 Murray Mfg Corp Improvements in or relating to mechanical biassing arrangements
US3392526A (en) * 1966-10-11 1968-07-16 Int Harvester Co Control mechanism
FR1535116A (fr) * 1967-08-18 1968-08-02 Bosch Gmbh Robert Mécanisme de transmission hydraulique
GB2037916A (en) * 1978-12-07 1980-07-16 Saab Scania Ab Device in a gear selection mechanism for a manual vehicle transmission

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1219831A2 (fr) * 2000-12-20 2002-07-03 Brueninghaus Hydromatik Gmbh Dispositif de réglage de la course pour une machine hydrostatique à débit variable
EP1219831A3 (fr) * 2000-12-20 2003-12-03 Brueninghaus Hydromatik Gmbh Dispositif de réglage de la course pour une machine hydrostatique à débit variable

Also Published As

Publication number Publication date
EP0525507B1 (fr) 1996-09-04
DE59207036D1 (de) 1996-10-10
DE4125706C1 (fr) 1993-01-14
EP0525507A3 (en) 1994-05-18

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