US3854847A - Apparatus for damping the pressure increase of hydrostatic drives - Google Patents

Apparatus for damping the pressure increase of hydrostatic drives Download PDF

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Publication number
US3854847A
US3854847A US00333652A US33365273A US3854847A US 3854847 A US3854847 A US 3854847A US 00333652 A US00333652 A US 00333652A US 33365273 A US33365273 A US 33365273A US 3854847 A US3854847 A US 3854847A
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United States
Prior art keywords
pump
adjustment
oil
check valve
adjustment cylinder
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
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US00333652A
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English (en)
Inventor
K Schlecht
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Putzmeister Interholding GmbH
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Putzmeister Interholding GmbH
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Publication date
Application filed by Putzmeister Interholding GmbH filed Critical Putzmeister Interholding GmbH
Priority to US05/494,172 priority Critical patent/US3947194A/en
Application granted granted Critical
Publication of US3854847A publication Critical patent/US3854847A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/433—Pump capacity control by fluid pressure control means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4183—Preventing or reducing vibrations or noise, e.g. avoiding cavitations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/46—Automatic regulation in accordance with output requirements
    • F16H61/465—Automatic regulation in accordance with output requirements for achieving a target input speed

Definitions

  • the present invention relates to a new and improved construction of apparatus for damping the pressure increase of hydrostatic drives wherein a controllable axial piston pump, preferably equipped with a swash or wobble plate, drives a motor or selectively the hydraulic cylinder of a concrete pump.
  • Another and more specific object of the present invention aims at limiting the speed of increase of the pressure whenever the pressure increase occurs and irrespective of its magnitude, and specifically particularly during constant rotational speed of the pump or the oil motor or during uniform speed of the conveying cylinder.
  • the invention proposes that with a hydraulic pump, preferably an axial piston pump having a swash or wobble plate control, and which pump is equipped with a hydraulic adjustment cylinder and at the pre-biased oil circulation system with a supply pump and the therewith associated conventional filling pressure limiting devices, flu-- shing' and reversing valves, the pressurized oil com partment of the adjustment cylinder is connected with the low pressure side oil circulation system of the pump via a check valve.
  • a hydraulic pump preferably an axial piston pump having a swash or wobble plate control
  • the servo-control advantageously embodies an external adjustment lever hinged with the outer adjustment cylinder, and the inner adjustment cylinder likewise possesses a connection with the low pressure line in which the check valve is arranged.
  • the outer adjustment cylinder advantageously possesses a spring, the restoring force of which corresponds to a pressure which is only slightly less than the pressure prevailing at the low pressure line of the pump.
  • An advantageous further embodiment of the apparatus consists in the features that the servo-valve is coupled via a check valve with the auxiliary pump.
  • the supply pump which is usually flanged to the pump can then be dispensed with for this type of modified equipment.
  • a further variant construction of the apparatus of this development contemplates that when dispensing with the use of an auxiliary pump and a throttle arranged after such auxiliary pump, the adjustment cylinder is connected'with a mechanical adjustment mechanism and the side at the floor or bottom of the adjustment cylinder is connected via a regulating throttle and I a check valve with the servo-control pressure side of the pump.
  • FIG. 1 illustrates an exemplary embodiment of apparatus possessing an internal servo-adjustment of the swash or wobble plate of an axial piston pump andan auxiliary pump;
  • FIG. 2 is a modified form of the apparatus depicted in FIG. 1 without an auxiliary pump.
  • the piston rod 8b thereof is connected via a rigid mechanical connection 9 with an adjustment element, schematically indicated at 9a, of a conventional and therefore not particularly illustrated swash plate of the pump 1.
  • a mechanical return device 20 Between the piston rod 8b of the adjustment cylinder 8 and the servo valve mechanism 10 there is provided a mechanical return device 20.
  • this pump by means of a servo-adjustment, is switched to the desired delivery capacity when the adjustment lever 12 of the servo-valve mechanism 10 is rocked out of its null position.
  • the required adjustment pressure is generated by an auxiliary pump 14 which, as a general rule, is driven by the same motor as the pump 1 and therefore has a rotational speed proportional to the pump 1 and conveys in the direction of a regulation throttle 15.
  • the control oil pressure which is effective in the adjustment cylinder 13 increases proportionally as a function of the rotational speed of the drive motor.
  • the piston 13a of the adjustment cylinder 13 is displaced within the compartment 13b of the adjustment cylinder 13, and therefore, the pump 1 is switched over into its delivery or conveying mode via the servo mechanism 10 which is acted upon by the adjustment lever 12.
  • the auxiliary pump 14 generates a maximum oil pressure which, limited by the throttle 15 and, if desired, a further overpressure valve, preferably is at a value slightly below the low pressure prevailing in the conduit or line 3.
  • the return spring 17 accordingly can displace the piston 13a through a greater or lesser extent into the adjustment: cylinder 13.
  • the conveyed quantity of the main pump 1 is temporarily reduced via the adjustment lever 12 anad the servomechanism 10 and specifically for such length of time as there exists the increased consumption of leakage oil due to the increase in pressure and which exceeds the delivery capacity of the supply pump 5 and the auxiliary pump 14.
  • The-speed of the pressure increase can be controlled in a simple manner in that the delivered capacities of the supply pump 5 and the auxiliary pump l4are coordinated to one another. For instance,
  • the supply pump 5 can possess a constant delivery capacity starting from a certain rotational speed; the main pump then operates at .high rotational speeds and higher pressure loads in an increasing softer manner with respect to the pressure increase.
  • the housing of the adjustment cylinder 13 is rigidly connected with a mechanical adjustment mechanism.
  • the adjustment cylinder 13 serves as an intermediate element in the mechanicaladjustment.
  • the floor or bottom side of the adjustment cylinder 13 is continuously connected via a regulation or control throttle 52 and a check valve 1 l with the servo-control pressure side of the supply pump 5.
  • the piston 13a of the adjustment cylinder 13 can temporan ily discharage fluid via the check valve 16 into the low pressure conduit or line 3.
  • the compartment 13b of the adjustment cylinder 13 is less rapidly charged by the supply pump 5.
  • there is a temporary pivoting back of the adjustment lever 12 that is to say, a decrease in the delivery or conveying capacity of the pump 1 with subsequent repositioning of the adjustment lever after the pressure increase in the main conduit or line 2 has slowly been completed.
  • the speed of the pressure increase is limited in known manner for all servo-controlled pumps by an inflow throttle arranged forwardly of the servo-slide valve mechanism 10, which can also be designed to be controllable.
  • An apparatus of the described type can also be separately installed in a very simple manner as a supplementary unit at drives of this type which are already in operation.
  • An apparatus for damping the pressure increase of hydrostatic drives, especially axial piston pumps with swash plate control and pre-biased oil circulation system comprising an adjustment cylinder having a pressurized oil compartment, a pump, an oil infeed means including an oil infeed line for the pump, a check valve, the pressurized oil compartment 2.
  • the restoring force of which corresponds to a pressure which is only slightly less than the pressure prevailing at the low pressure infeed line of the pump.
US00333652A 1972-02-22 1973-02-20 Apparatus for damping the pressure increase of hydrostatic drives Expired - Lifetime US3854847A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US05/494,172 US3947194A (en) 1972-02-22 1974-08-02 Apparatus for damping the pressure increase of hydrostatic drives

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2208172A DE2208172C3 (de) 1972-02-22 1972-02-22 Vorrichtung zur Dämpfung des belastungsbedingten Druckanstiegs bei hydrostatischen Antrieben

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US05/494,172 Division US3947194A (en) 1972-02-22 1974-08-02 Apparatus for damping the pressure increase of hydrostatic drives

Publications (1)

Publication Number Publication Date
US3854847A true US3854847A (en) 1974-12-17

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ID=5836660

Family Applications (1)

Application Number Title Priority Date Filing Date
US00333652A Expired - Lifetime US3854847A (en) 1972-02-22 1973-02-20 Apparatus for damping the pressure increase of hydrostatic drives

Country Status (15)

Country Link
US (1) US3854847A (xx)
JP (1) JPS589301B2 (xx)
AR (1) AR198072A1 (xx)
AU (1) AU5230473A (xx)
BR (1) BR7301293D0 (xx)
CA (1) CA983815A (xx)
CH (1) CH561869A5 (xx)
CS (1) CS170452B2 (xx)
DE (1) DE2208172C3 (xx)
ES (1) ES411597A1 (xx)
FR (1) FR2173565A5 (xx)
GB (1) GB1401374A (xx)
IT (1) IT977429B (xx)
SU (1) SU466678A3 (xx)
ZA (1) ZA731047B (xx)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4373865A (en) * 1981-02-10 1983-02-15 Tadeusz Budzich Reciprocating controls of a hydraulically driven piston gas compressor
EP0078415A2 (en) * 1981-10-23 1983-05-11 Fmc Corporation A system for controlling the speed of an hydraulic motor
US4483663A (en) * 1982-08-23 1984-11-20 Sundstrand Corporation Output speed droop compensating pump control
EP0144788A1 (de) * 1983-11-08 1985-06-19 Hydromatik GmbH Leistungs-Regelvorrichtung für einen hydrostatischen Antrieb mit Fördermengeneinstellung
US4527393A (en) * 1981-09-02 1985-07-09 General Signal Corporation Control device for a hydrostatic transmission
US4543787A (en) * 1981-11-03 1985-10-01 Linde Aktiengesellschaft Controls for continuously adjustable drive
US5205201A (en) * 1991-08-19 1993-04-27 Sauer, Inc. Displacement control valve
WO2003093702A1 (de) * 2002-05-03 2003-11-13 Brueninghaus Hydromatik Gmbh Hydromotoreinheit
CN104728094A (zh) * 2013-12-19 2015-06-24 北汽福田汽车股份有限公司 一种功率转移系统及带有所述系统的混凝土输送机械
CN106640576A (zh) * 2016-12-09 2017-05-10 柳州职业技术学院 一种卸载式自变量径向柱塞泵
CN109899333A (zh) * 2019-03-29 2019-06-18 潍柴动力股份有限公司 阀块、液压控制系统及车辆

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4017219A (en) * 1975-12-22 1977-04-12 Abex Corporation Control system for variable displacement pumps
JPS5387401U (xx) * 1976-12-20 1978-07-18
JPS605821B2 (ja) * 1980-10-17 1985-02-14 日立建機株式会社 油圧駆動装置の制御方法
DE3436960A1 (de) * 1984-10-09 1986-04-17 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8000 München Betriebsbremse fuer einen lkw oder omnibus
CN103557197B (zh) * 2013-11-21 2015-11-11 无锡市蓝力机床有限公司 液压机油缸退回快速排油回路
DE102014206460B3 (de) * 2014-04-03 2015-07-23 Danfoss Power Solutions Gmbh & Co. Ohg Umschaltbare hydrostatische Verstelleinrichtung und zugehöriger Steuerkolben
CN112901339B (zh) * 2021-01-15 2022-04-26 河北工业大学 基于氨热解装置的直喷天然气发动机系统及其控制方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3543508A (en) * 1968-10-16 1970-12-01 Hyster Co Hydrostatic transmission with pressure control
US3650108A (en) * 1968-09-20 1972-03-21 Sigma Hydrostatic transmission control
US3660975A (en) * 1970-09-17 1972-05-09 Lucas Industries Ltd Hydrostatic transmission systems

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3650108A (en) * 1968-09-20 1972-03-21 Sigma Hydrostatic transmission control
US3543508A (en) * 1968-10-16 1970-12-01 Hyster Co Hydrostatic transmission with pressure control
US3660975A (en) * 1970-09-17 1972-05-09 Lucas Industries Ltd Hydrostatic transmission systems

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4373865A (en) * 1981-02-10 1983-02-15 Tadeusz Budzich Reciprocating controls of a hydraulically driven piston gas compressor
US4527393A (en) * 1981-09-02 1985-07-09 General Signal Corporation Control device for a hydrostatic transmission
EP0078415A2 (en) * 1981-10-23 1983-05-11 Fmc Corporation A system for controlling the speed of an hydraulic motor
EP0078415A3 (en) * 1981-10-23 1985-01-09 Fmc Corporation A system for controlling the speed of a rotatable load
US4543787A (en) * 1981-11-03 1985-10-01 Linde Aktiengesellschaft Controls for continuously adjustable drive
US4483663A (en) * 1982-08-23 1984-11-20 Sundstrand Corporation Output speed droop compensating pump control
EP0144788A1 (de) * 1983-11-08 1985-06-19 Hydromatik GmbH Leistungs-Regelvorrichtung für einen hydrostatischen Antrieb mit Fördermengeneinstellung
US5205201A (en) * 1991-08-19 1993-04-27 Sauer, Inc. Displacement control valve
WO2003093702A1 (de) * 2002-05-03 2003-11-13 Brueninghaus Hydromatik Gmbh Hydromotoreinheit
US7415821B2 (en) 2002-05-03 2008-08-26 Brueninghaus Hydromatik Gmbh Hydraulic motor unit
CN104728094A (zh) * 2013-12-19 2015-06-24 北汽福田汽车股份有限公司 一种功率转移系统及带有所述系统的混凝土输送机械
CN106640576A (zh) * 2016-12-09 2017-05-10 柳州职业技术学院 一种卸载式自变量径向柱塞泵
CN109899333A (zh) * 2019-03-29 2019-06-18 潍柴动力股份有限公司 阀块、液压控制系统及车辆

Also Published As

Publication number Publication date
CS170452B2 (xx) 1976-08-27
DE2208172A1 (de) 1973-09-06
CH561869A5 (xx) 1975-05-15
JPS48103961A (xx) 1973-12-26
GB1401374A (en) 1975-07-16
FR2173565A5 (xx) 1973-10-05
DE2208172B2 (de) 1973-12-13
JPS589301B2 (ja) 1983-02-19
SU466678A3 (ru) 1975-04-05
AR198072A1 (es) 1974-05-31
ZA731047B (en) 1973-11-28
ES411597A1 (es) 1976-01-01
CA983815A (en) 1976-02-17
BR7301293D0 (pt) 1974-05-16
DE2208172C3 (de) 1974-07-11
AU5230473A (en) 1974-08-22
IT977429B (it) 1974-09-10

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