US3817033A - Hydraulic lifting apparatus with constant pull regulation - Google Patents

Hydraulic lifting apparatus with constant pull regulation Download PDF

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Publication number
US3817033A
US3817033A US00289236A US28923672A US3817033A US 3817033 A US3817033 A US 3817033A US 00289236 A US00289236 A US 00289236A US 28923672 A US28923672 A US 28923672A US 3817033 A US3817033 A US 3817033A
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United States
Prior art keywords
pressure
control
chamber
conduit
piston
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Expired - Lifetime
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US00289236A
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English (en)
Inventor
W Appel
R Kordak
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Bosch Rexroth AG
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GL Rexroth GmbH
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/48—Control devices automatic
    • B66D1/50—Control devices automatic for maintaining predetermined rope, cable, or chain tension, e.g. in ropes or cables for towing craft, in chains for anchors; Warping or mooring winch-cable tension control
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S254/00—Implements or apparatus for applying pushing or pulling force
    • Y10S254/90—Cable pulling drum having wave motion responsive actuator for operating drive or rotation retarding means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S60/00—Power plants
    • Y10S60/905—Winding and reeling

Definitions

  • the present invention relates to a hydrostatic drive transmission, particularly for winches on a boat, for example, winches for winding up fishing nets.
  • the hydrostatic drive transmission includes a main pump, whose displaced volume of fluid is adjustable, and a hydraulic main motor driven by the main pump.
  • the adjusting means of the main pump regulates the pump between reversed conditions, and in idling condition.
  • the regulation of such a drive for obtaining a constant pull of a rope wound up on a winch driven by the hydraulic motor is of great importance for winches operated on boats for winding up and letting off fishing nets.
  • the required constant pull regulation is sometimes referred to as mooring regulation.
  • the pull on the rope is maintained constant during the lifting of a fishing net, independent of the up and down motion of the boat due to high waves. If the pull on the rope rises above a predetermined force, it is necessary that the hydrostatic drive transmission yield, and the motor runs inreversed direction of rotation, permitting a paying-out of the rope, irrespective of the risingof the winch, but avoiding slackeningof the rope. If the load and pull on. the rope is reduced, for example when the boat moves froma wave crest to a valley, it is necessary that the hydrostatic. transmission is automatically adjusted to a liftingoperation so that continuous pulling of the ropes in the opposite direction takes place at a constant pull of the ropes.
  • This type of constant pull or mooring regulation requires due to the frequent change of the direction of rotation of the hydraulic drive motor, a pump adjustablethrough a zero or idlingcondition.
  • a hydraulic piston and cylinder motor is used for operating the adjusting means of the transmission pump.
  • the pullon the ropes during the lifting operation is determined in accordance with the pressure in the high pressure conduitof the hydrostatic transmission, and this pressure is measured by a manometer and transformed by the same into an electric signal controlling an electromagnet operating a valve which is associated with a hydraulic cylinder and piston motor forming the adjusting means of the pump.
  • the electric part of this constant pull regulation is very expensive if a comparatively reliable regulation is to-be obtained.
  • Another object of the invention is to provide a hydraulic circuit controlled by the pressure in the hydrostatic transmission to adjust the hydrostatic transmis-
  • An embodiment of the lifting apparatus of the invention comprises a hydrostatic drive transmission including a driven main pump having adjusting means for regulating the displaced volume, a hydraulic drive motor, and high pressure, and low pressure conduits; a hydraulic adjusting motor with adjusting; means and including a cylinder, and a piston forming first and second chambers in the cylinder; pump conduit means connecting a control pump with the first chamber; control conduit means between the control pump and the second chamber; control valve means in the control conduit means having a first control position for connecting the control pump with the second chamber, and the second control position connecting the second chamber with a low pressure discharge area.
  • the adjusting motor is operated in the first and second control positions, respectively, to adjust the adjusting means of the main pump to cause increase or reduction, respectively, of the volume displaced by the main pump, and rotation of the drive motor for lifting and lowering a load.
  • pressure responsive valve means in the control conduit means have a normal position permitting flow through the control conduit means, and an actuated position connecting the second chamber with a low pressure discharge area.
  • the high pressure conduit of the hydrostatic trans- 1 mission is connected withthe pressure responsive valve means and shifts the same to the actuated position when a predetermined pressure is reached in the high pressure conduit.
  • the pressure in the first chamber operates the adjusting motor to adjust the adjusting means to reduce the volume displaced by the main pump and thereby the speed of the hydraulic: drive motor.
  • the predetermined pressure is exceeded while the main pump is adjusted by the adjusting motor to idle, the direction of rotation of the drive motor is reversed by the adjusting motor and adjusting means.
  • the first chamber in the cylinder of the adjusting motor is traversed by the piston rod, and consequently the piston on this side has a smaller effective pressure surface than on the side of the secondchamber.
  • the pressure responsive valve means include first and second pressure responsive'valves which have a normal position connected in series.
  • the pressure responsive valves are responsive to different predetermined high pressures in the high pressure conduit of the hydrostatic transmissionto move to actuated positions connecting the second chamber of the adjusting motor with the low pressure discharge area.
  • FIGURE of the drawing is a schematic, partially sectional view illustrating a hydraulic lifting apparatus in connection with a winch mounted on a floating boat.
  • a main pump 1 and a hydraulic drive motor 2 are connected by low pressure and high pressure conduits 5 and 6 to form a hydrostatic transmission.
  • the main pump 1 is adjustable so that the volume displaced by main pump 1 can be varied by adjusting means, schematically represented by arrow 9, resulting in different speeds of the drive motor 2 which drives a winch 3 on which a rope 4 is wound up or paid out.
  • the rope may be connected with a fishing net, and it is desired that the pull on rope 4 is maintained constant irrespective of the raising and lowering of a floating boat carrying the winch 3. It will be understood that the pull on rope 4 will increase when the level of the boat and winch 3 rises, and that the pull on rope 4 is decreased when the level of the boat and winch 3 goes down due to the movement of waves.
  • Adjusting means 9 of main pump 1 are operated by a hydraulic adjusting motor 7 which includes a piston 35 forming in the cylinder a first pressure chamber 10 .through which the piston rod 8 passes out of the cylinder, and a second chamber 15. Due to piston 8, the effective surface 35a is greater than the annular effective surface 35b of piston 35.
  • piston rod 8 The outer end of piston rod 8 is articulated to the schematically shown adjusting means 9, and a lever 36, pivotally mounted on a stationary point 36a, is articulated at 36b to piston rod 8.
  • An auxiliary control pump 13 pumps pressure fluid through a pump conduit 13a, 12 and 11 into the first chamber 10, urging piston 35 to the right to reduce the volume of the second chamber 15.
  • a pressure limiting valve 14 is provided in the pump conduit 13a to limit the pressure in the pump conduit and chamber 10.
  • the second chamber 15 in the cylinder of-the adjusting motor 7, is connected by a control conduit 16, 26, in which two pressure responsive valves 17 and 18 are located, with a port in a control valve means 19 which, in the illustrated position b of the respective valve slide piston 19a, is separated from the pump conduit 20, 12, 13a.
  • control conduit portion 26 is connected with the pump conduit portion 20 and with the control pump 13.
  • the control conduit portion 26 is connected with a discharge conduit 50 for discharging into a low pressure discharge area, schematically indicated by an open container T.
  • the high pressure conduit 6 of the hydrostatic transmission 1, 2, 5, 6 is connected by a high pressure conduit with two selector valves 23 and 24 each of which can be'operated by operator actuated electromagnetic means 23a and 24a to move from the illustrated closed position b to an open position a in which pressure fluid is supplied from conduit 6, 25 to selector conduits 21, 22 which supply pressure to the pressure responsive valves 17, 18 which are adjusted to different predetermined pressures to open when the pressure supplied through conduits 21, 22 exceeds the predetermined pressure to which the respective pressure responsive valves 17 or 18 was adjusted by adjustment of springs 17a and 18a.
  • control valve means 19 includes a shiftable valve slide piston 19a which has a normal position of rest b, and two control positions a and c.
  • Two end chambers are formed in the cylinder of the control valve 19 at opposite ends of the valve slide piston 19a, and are connected with conduits 27 and 28, respectively, which end in pressure regulating valves 29 and 30 which are schematically shown, and indicate by arrows that the conduits 27 and 28 are connected in the position of the valves 29 and 30 as shown in the drawing with a discharge conduit 54 opening into a low pressure discharge container T. Consequently, no axial pressure is exerted on the valve slide piston 19a which remains in the illustrated position of rest b in which the connection between the control pump 13 and the control conduit means 26, 16 with pressure responsive valves 17 and 18 is interrupted.
  • the pressure regulating valves 29 and 30 cooperate with springs 29a and 30a whose force can be varied by operation of a manual lever 31 which is fixedly connected to plate 31a on which 29a and 30a abut.
  • the input pressure of the pressure regulating valves 29 and 30 corresponds to the pressure in the pump conduit 12, 32.
  • the conduits 27 and 28 are connected by the pressure regulating valves 29 and 30 with a low pressure region, for instance a low pressure discharge container T, while pump conduit 32 is closed so that there is no pressure in the end chambers of control valve 19 which could displace the control valve slide piston 19a out of the position of rest b.
  • control lever 31 If the control lever 31 is moved to the position 33 shown in broken lines, the spring 29a is tensioned to a certain degree, while the pressure regulating valve 29 is shifted upwardly to a position in which conduit 27 is no longer connected with the discharge conduit 54, but is connected with the pump conduit 12, 32 so that the pressure at the left end of control valve 19 increases, and control valve slide 19a is shifted to the control position a in which the pump conduit 12, 20 is connected with the control conduit portion 26.
  • control valve slide pis ton 19a depends on the pressure adjusted at the pressure regulating valve 29 and on the characteristics of the spring 38.
  • Spring 38 is selected to have a substantially constant spring characteristic, and, to offer the same resistance irrespective of the lengths of deformation. Due to the constant characteristics of spring 38, the distance which the control valve slide piston 19a moves, is directly influenced by the magnitude of the control pressure preselected by the operation of lever 31 in theposition 33.
  • the pump conduit 12, 20 is connected with the control conduits 26, 16 and pressure responsive valves 17, 18 as explained above. Consequently, the second chamber 15 of the cylinder of the adjusting motor 7 is supplied with pressure fluid having the same pressure as the pressure fluid in chamber supplied through pump conduit 13a, 12, 11.
  • the effective pressure surface 35a is greater than the effective pressure surface 35b in chamber 10, due to the presence of piston rod 8 in chamber 10, the equal pressure on opposite sides of the piston 35 results in a force acting on piston 35 to move the same to the left together with piston rod 8 so that the schematically shown adjusting means 9 are turned for adjusting the main pump 1 out of the idling condition to a condition in which main pump 1 displaces a greater volume of fluid so that hydraulic motor 2 is driven, and drives winch 3.
  • control conduit 26, 16 is separated from the pump conduit 20 so that the communication between the chamber and the pump conduit 13a, 12, is interrupted, and no pressure fluid is supplied to chamber 15, ending the movement of piston 35 and piston rod 8 to the left so-that the adjusting means 9 is no longer operated.
  • Piston 35 has moved a distance which corresponds to the distance of movement of control slide valve piston 19a determined by the control pressure.
  • the displacement of piston 35 of the'adjusting motor 7 is at the same time a measure of the adjustment of main pump 1 by the adjusting means 9, and consequently also a measure of the number of revolutions of the hydraulic drive motor 2.
  • control lever 31 When control lever 31 is turned from the position 33 to the position 40 shown in broken lines, the pressure regulating valve 29 returns to a position for causing idling of the main pump when lever 31 is in the position shown in full lines whereupon the pressure regulating valve 30 is placed in a position corresponding to the position 40 of the control lever, i.e., shifted upwardly so that conduit 28 is connected with the pump conduit portion 32, and control valve slide piston 19a is shifted to the control position 0.
  • the distance which control valve slide piston 19a moves depends again on the magnitude of the control pressure acting through conduit 28 on the right end of the control valve slide 19a, and determined by position 40 of lever 31, and the compression of spring a.
  • thechamber 15 is connected by control conduit portion 16, the control conduit portions in pressure responsive valves 17 and 18, and by control conduit portion 26 with the discharge conduit 50 discharging into a low pressure container T; Since chamber 10 is still under pressure from pump conduit 13a, 12, 11, and piston encounters no resistance in chamber 15, piston 35 moves with piston rod 8 to the right as viewed in the drawing, and operates the adjusting means 9 in the opposite direction than before so that main pump 1 is regulated to pump fluid in a reversed flow so that drive motor 2 is driven in the reversed direction of rotation, and winch 3 pays out the rope 4. In this manner, the pull on rope 4 is maintained constant,even if the winch 3 together with the boat on which it is supported is rapidly moved upward by a wave.
  • the pressure responsive valves 17 and 18 are preset to different predetermined pressures by adjustment of,
  • one or the other pressure responsive valve is connected with conduit 25 and high pressure conduit 6, and controls the regulation of the main pump 1 in accordance with the pressure preset of the respective pressure responsive valve 17 or 18. In accordance with the predetermined pressures to which the valves 17 and 18 are set, different pulling forces are maintained constant at the rope 4.
  • an apparatus according to the invention which is advantageously used on a boat for lifting fishing nets by means of ropes, mainly comprises the following elements:
  • the adjusting motor 7 is operated in the first and second control positions a, c of control valve means 19, respectively, to adjust the adjusting means 9 to cause increase and reduction, respectively, of the volume displaced by the main pump 1 and the rotation of the drive motor 2 for lifting and lowering the load.
  • Pressure responsive valve means 17, 18 are provided in the control conduit means 26, 16 and have a normal position permitting flow through the conduit means 26, 16 and an actuated position connecting the second chamber 15 with the low pressure discharge container T, while interrupting in the actuated position the flow in the control conduit 26, 16 from the control pump 13 to the second chamber 15.
  • the high pressure conduit 6 of the transmission 1, 2, 5, 6 is connected with the pressure responsive valve means l7, 18 through selector valves 23 and 24 for shifting the same to an actuated position when a predetermined pressure is reached in the high pressure conduit 6.
  • the pressure in the second chamber 15 is reduced and the pressure in the first chamber 10 operates the adjusting motor 7 to adjust the adjusting means 9 to reduce the volume displaced by the main pump 1, and thereby the speed of the hydraulic drive motor 2.
  • Hydraulic lifting apparatus with constant pull regulation comprising a hydrostatic drive transmission including a driven main pump having adjusting means for regulating the displaced volume, a hydraulic drive motor, and low pressure and high pressure conduits; a hydraulic adjusting motor connected with said adjusting means, and including a cylinder, and a piston in said cylinder forming first and second chambers; a source of pressure fluid; pump conduit means connecting said source with said first chamber; control conduit means between said source and said second chamber; control valve means in said control conduit means having a first control position for connecting said source with said second chamber, and a second control position connecting said second chamber with a low pressure discharge region so that said adjusting motor is operated in said first andsecond control positions, respectively, to adjust said adjusting means to cause increase and reduction, respectively, of the volume displaced by said main pump, and rotation of said drive motor for lifting and lowering a load; and pressure responsive valve means in said control conduit means having a normal position permitting flow through said control conduit means, and an actuated position connecting said second chamber with said low pressure discharge region, said
  • control valve means has a position of rest interrupting the flow in said control conduit means.
  • control valve means includes a control valve slide piston, and hydraulic shifting means for shifting said control valve slide between said control positions.
  • Apparatus as claimed in claim 5 comprising resetting means connecting said adjusting means with said control valve slide piston.
  • said piston of said adjusting motor includes a piston rod projecting through said first chamber out of said cylinder and being connected with said adjusting means so that the effective pressure surface of said piston is smaller in said first chamber than in said second chamber.
  • Apparatus as claimed in claim 7 comprising resetting means including a pivotally mounted lever connected with said piston rod and with said adjusting means, and resilient means having constant resiliency characteristics and connecting said control valve means with said lever; and wherein said control valve means includes a valve slide piston movable between said control positions, and a link connecting said valve slide piston with said resilient means.
  • said pressure responsive valve means include first and second pressure responsive valves forming conduit portions in said control conduit means connected in series in said normal position; comprising selector valve means for individually connecting said pressure responsive valves with said high pressure conduit; and wherein said pressure responsive valves are responsive to different predetermined high pressures in said high pressure conduit ing an open position and a closed position, and an electromagnetic means for shifting the respective selector valve between said positions thereof.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
US00289236A 1971-09-17 1972-09-15 Hydraulic lifting apparatus with constant pull regulation Expired - Lifetime US3817033A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2146586A DE2146586C3 (de) 1971-09-17 1971-09-17 Mit einer Konstantzug-Regelung versehener hydrostatischer Antrieb

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Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3967394A (en) * 1974-09-23 1976-07-06 Kelley Charles S Automatic grab crane
US3995831A (en) * 1974-12-17 1976-12-07 The United States Of America As Represented By The Secretary Of The Army Force feedback controlled winch
US4074891A (en) * 1974-12-20 1978-02-21 Kopat Gesellschaft Fur Konstruktion, Entwicklung Und Patentverwertung M.B.H. & Co. Kg Winding mechanism-drive, particularly for construction cranes or like hoisting devices
US4180362A (en) * 1978-05-05 1979-12-25 The Boeing Company System to transfer cargo or passengers between platforms while undergoing relative motion
US4223871A (en) * 1978-04-04 1980-09-23 Vickers Shipbuilding Group Limited Winch mechanism
US4400939A (en) * 1979-11-23 1983-08-30 Linde Aktiengesellschaft Drive units
US4448398A (en) * 1982-03-01 1984-05-15 Garlock Equipment Company Winch control system
WO1984003084A1 (en) * 1983-02-03 1984-08-16 Continental Emsco Co Emergency control hydraulic system for a crane
US4508281A (en) * 1983-08-15 1985-04-02 Tse International Hydraulic drive system for cable stringing apparatus
US4537364A (en) * 1982-12-15 1985-08-27 Sundstrand Corporation Constant tension cable reel drive
US4559778A (en) * 1978-05-30 1985-12-24 Linde Aktiengesellschaft Control device for a hydrostatic transmission
US4727718A (en) * 1981-07-21 1988-03-01 Koopmans Luitzen B Winch system having hydraulic transmission including a safety circuit
US5205201A (en) * 1991-08-19 1993-04-27 Sauer, Inc. Displacement control valve
EP0850871A2 (de) * 1996-12-27 1998-07-01 Kässbohrer Geländefahrzeug GmbH Verfahren zum Betreiben einer Winde und zugehörige Vorrichtung
US5794920A (en) * 1994-09-01 1998-08-18 Kronberger; Gale A. Hydraulic winch assembly using a vehicle steering pump
US5970906A (en) * 1997-10-13 1999-10-26 Pullmaster Winch Corporation Motion compensation winch
US6012707A (en) * 1995-05-19 2000-01-11 Tamrock Oy Arrangement for controlling tension in a winch cable connected to rock drilling equipment
WO2003095831A1 (de) * 2002-05-10 2003-11-20 Brueninghaus Hydromatik Gmbh Verstellvorrichtung für hydrostatische kolbenmaschinen
CN102424330A (zh) * 2011-08-19 2012-04-25 三一汽车起重机械有限公司 一种起重机及其收钩系统、方法
CN108178082A (zh) * 2017-11-14 2018-06-19 武汉船用机械有限责任公司 用于主动波浪补偿的马达控制阀组

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2903940C2 (de) * 1979-02-02 1983-11-10 Hermann Sürken GmbH & Co KG, 2990 Papenburg Steuerung des Antriebs einer Konstantzugwinde
EP0033239B1 (en) * 1980-01-25 1985-10-02 Aquila Steel Company Limited Crane hydraulic control system
JPS58185324A (ja) * 1982-04-26 1983-10-29 Suzuki Motor Co Ltd オ−トバイのラジエタ−装着装置
ZA842416B (en) * 1983-04-18 1984-11-28 Combustion Eng Submerged scraper conveyor load-speed integration monitor and control
DE102008027351A1 (de) * 2008-06-07 2009-12-10 Howaldtswerke-Deutsche Werft Gmbh Unterseeboot
DE102014109918A1 (de) * 2014-07-15 2016-01-21 Bauer Maschinen Gmbh Baumaschine und Verfahren zum Steuern einer Baumaschine
CN114212714B (zh) * 2021-11-09 2024-04-05 中船华南船舶机械有限公司 一种吊机的液压系统

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2402789A (en) * 1937-08-14 1946-06-25 Waterbury Tool Co Power transmission
US2554381A (en) * 1948-01-14 1951-05-22 Jr Joseph C Patterson Ship roll energy device
US3679180A (en) * 1969-10-17 1972-07-25 Nat Defence Canada Cable control system

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD29993A (ja) *
GB958334A (en) * 1961-08-28 1964-05-21 New Yrok Air Brake Company Fluid pressure servomotor control for hydrostatic transmissions
DE1523567A1 (de) * 1966-04-04 1969-08-21 Molly Dipl Ing Hans Hyperbelwertgebender Mechanismus und seine Einschaltung in die Verstellglieder von zu regelnden hydrostatischen Maschinen
DE1653385C3 (de) * 1967-08-25 1980-07-24 Volvo Hydraulikfabrik Gmbh, 1000 Berlin Vorrichtung zum Konstanthalten des Produktes aus Druck und Hubvolumen bei einer Verdrängerpumpe
FR1560435A (ja) * 1968-01-12 1969-03-21
DE2017656A1 (de) * 1969-04-23 1970-11-05 Pensa, Carlo, Esino Lario, Como (Italien) Hydraulische FördermengeneinsteHvorrichtung für eine oder mehrere Pumpen
DE1922145A1 (de) * 1969-04-25 1970-10-29 Bellows Valvair Kaemper Gmbh Kombinationsregler
DE1929645C3 (de) * 1969-06-09 1975-03-13 Mannesmann-Meer Ag, 4050 Moenchengladbach Regelvorrichtung zum Konstanthalten des Verdrängungsvolumens von Flüssigkeitspumpen oder -motoren
DE1929757A1 (de) * 1969-06-12 1970-12-23 Daimler Benz Ag Steuereinrichtung einer hydrostatischen Bremsanlage eines Fahrzeuges
DE2003774A1 (de) * 1970-01-23 1971-07-29 Bellows Valvair Deutschland Ni Vorrichtung zum Konstanthalten des Produktes aus Druck und Hubvolumen bei Verdraengerpumpen

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2402789A (en) * 1937-08-14 1946-06-25 Waterbury Tool Co Power transmission
US2554381A (en) * 1948-01-14 1951-05-22 Jr Joseph C Patterson Ship roll energy device
US3679180A (en) * 1969-10-17 1972-07-25 Nat Defence Canada Cable control system

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3967394A (en) * 1974-09-23 1976-07-06 Kelley Charles S Automatic grab crane
US3995831A (en) * 1974-12-17 1976-12-07 The United States Of America As Represented By The Secretary Of The Army Force feedback controlled winch
US4074891A (en) * 1974-12-20 1978-02-21 Kopat Gesellschaft Fur Konstruktion, Entwicklung Und Patentverwertung M.B.H. & Co. Kg Winding mechanism-drive, particularly for construction cranes or like hoisting devices
US4223871A (en) * 1978-04-04 1980-09-23 Vickers Shipbuilding Group Limited Winch mechanism
US4240613A (en) * 1978-04-04 1980-12-23 Vickers Shipbuilding Group Ltd. Winch mechanism
US4180362A (en) * 1978-05-05 1979-12-25 The Boeing Company System to transfer cargo or passengers between platforms while undergoing relative motion
US4559778A (en) * 1978-05-30 1985-12-24 Linde Aktiengesellschaft Control device for a hydrostatic transmission
US4400939A (en) * 1979-11-23 1983-08-30 Linde Aktiengesellschaft Drive units
US4727718A (en) * 1981-07-21 1988-03-01 Koopmans Luitzen B Winch system having hydraulic transmission including a safety circuit
US4448398A (en) * 1982-03-01 1984-05-15 Garlock Equipment Company Winch control system
US4537364A (en) * 1982-12-15 1985-08-27 Sundstrand Corporation Constant tension cable reel drive
WO1984003084A1 (en) * 1983-02-03 1984-08-16 Continental Emsco Co Emergency control hydraulic system for a crane
US4508281A (en) * 1983-08-15 1985-04-02 Tse International Hydraulic drive system for cable stringing apparatus
US5205201A (en) * 1991-08-19 1993-04-27 Sauer, Inc. Displacement control valve
US5794920A (en) * 1994-09-01 1998-08-18 Kronberger; Gale A. Hydraulic winch assembly using a vehicle steering pump
US6012707A (en) * 1995-05-19 2000-01-11 Tamrock Oy Arrangement for controlling tension in a winch cable connected to rock drilling equipment
EP0850871A2 (de) * 1996-12-27 1998-07-01 Kässbohrer Geländefahrzeug GmbH Verfahren zum Betreiben einer Winde und zugehörige Vorrichtung
EP0850871A3 (de) * 1996-12-27 2000-04-12 Kässbohrer Geländefahrzeug AG Verfahren zum Betreiben einer Winde und zugehörige Vorrichtung
US5970906A (en) * 1997-10-13 1999-10-26 Pullmaster Winch Corporation Motion compensation winch
WO2003095831A1 (de) * 2002-05-10 2003-11-20 Brueninghaus Hydromatik Gmbh Verstellvorrichtung für hydrostatische kolbenmaschinen
US20050252369A1 (en) * 2002-05-10 2005-11-17 Winfried Lilla Regulating device for hydrostatic piston machines
US7171887B2 (en) 2002-05-10 2007-02-06 Brueninghaus Hydromatik Gmbh Regulating device for hydrostatic piston machines
CN102424330A (zh) * 2011-08-19 2012-04-25 三一汽车起重机械有限公司 一种起重机及其收钩系统、方法
CN102424330B (zh) * 2011-08-19 2013-12-18 三一汽车起重机械有限公司 一种起重机及其收钩系统、方法
CN108178082A (zh) * 2017-11-14 2018-06-19 武汉船用机械有限责任公司 用于主动波浪补偿的马达控制阀组
CN108178082B (zh) * 2017-11-14 2019-11-15 武汉船用机械有限责任公司 用于主动波浪补偿的马达控制阀组

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Publication number Publication date
DE2146586C3 (de) 1981-12-17
DE2146586B2 (de) 1977-04-28
JPS5752318B2 (ja) 1982-11-06
JPS4837852A (ja) 1973-06-04
DE2146586A1 (de) 1973-03-22

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