US3767327A - Power control device for two or more hydraulic pumps - Google Patents

Power control device for two or more hydraulic pumps Download PDF

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Publication number
US3767327A
US3767327A US00166389A US3767327DA US3767327A US 3767327 A US3767327 A US 3767327A US 00166389 A US00166389 A US 00166389A US 3767327D A US3767327D A US 3767327DA US 3767327 A US3767327 A US 3767327A
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United States
Prior art keywords
pump
pressure
delivery
power control
power
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Expired - Lifetime
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US00166389A
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English (en)
Inventor
L Wagenseil
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Hydromatik GmbH
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Hydromatik GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/02—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for several machines or pumps connected in series or in parallel
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • F04B49/007—Installations or systems with two or more pumps or pump cylinders, wherein the flow-path through the stages can be changed, e.g. from series to parallel
    • 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
    • F16H61/431—Pump capacity control by electro-hydraulic control means, e.g. using solenoid valves
    • 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
    • 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
    • F16H61/472—Automatic regulation in accordance with output requirements for achieving a target output torque
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01J—MEASUREMENT OF INTENSITY, VELOCITY, SPECTRAL CONTENT, POLARISATION, PHASE OR PULSE CHARACTERISTICS OF INFRARED, VISIBLE OR ULTRAVIOLET LIGHT; COLORIMETRY; RADIATION PYROMETRY
    • G01J3/00—Spectrometry; Spectrophotometry; Monochromators; Measuring colours
    • G01J3/28—Investigating the spectrum
    • G01J3/30—Measuring the intensity of spectral lines directly on the spectrum itself
    • G01J3/32—Investigating bands of a spectrum in sequence by a single detector

Definitions

  • ABSTRACT [30] Fore1gn Appllcatlon Prlority Data Aug. 5 1970 Germany P 20 38 968.8
  • a pressure-responsive device on each pump is responsive to the delivery pressure of the companion [56] References Cited pump for adjusting its own power according to the UNITED STATES PATENTS Raymond 417/214 said delivery pressure.
  • the invention relates to a power control device for two or more adjustable hydraulic pumps, operated by a common driving means and is particularly though not exclusively concerned with positive displacement pumps having means for adjusting their delivery flow, each pump being fitted with its own power control device, which is continuously adjustable to the desired power value of each pump by means of an adjustment device.
  • Such devices are intended on the one hand to protect the common driving apparatus operating thehydraulic pumps against overload, and on the other hand they make it possible to utilize as far as possible without loss the power capacity of thedriving apparatus even when the load on the individual hydraulic pumps is different.
  • Power control devices are known for individual hydraulic pumps which keep constant the product p Q determining the power of a hydraulic pump, where p is the working pressure and Q the output of the pump.
  • p is the working pressure
  • Q the output of the pump.
  • the arrangement is designed in such a way that each pump takes half the power of the driving apparatus, and in addition the power control for each individual pump is carried out in normal manner.
  • An object of the invention is to provide a control device which keeps constant the sum of all the individual powers, arrived at for each pump individually from the product of the working pressure and the output flow, Le.
  • a power control apparatus for two or more adjustable hydraulic pumps driven by a common driving means and each having its own power regulator, includes a power control device for each pump for continuously adjusting the regulator to maintain a desired power value of the associated pump, and a pressure responsive device responsive to the delivery pressure of the companion pump and arranged to adjust the power of its own pump to the said delivery pressure.
  • the apparatus is provided with a device limiting the maximum delivery pressure of each pump, in which the power control device for each pump also has a delivery flow responsive device responsive to the delivery flow of the companion pump and arranged to adjust the power of its own pump according to the said delivery flow.
  • the power control device of each pump comprises a pilot valve acted on by a spring
  • the pressure responsive device comprises a throttle valve adjustable in accordance with thedelivery'pressure of the companion pump and connected in parallel with one of the restricted orifices.
  • the delivery flow measuring device rnay comprise a throttle valve adjustable in accordance with the delivery flow of the companion pump and also connected in parallel with the restricted orifice and the pressure responsive throttle valve.
  • the pressure responsive throttle valve may constitute the restricted orifice.
  • FIG. 1 is a diagram of a control device according to the invention for two hydraulic pumps
  • FIG. 2 is a similar diagram of a further arrangement
  • FIG. 3 shows performance curves to illustrate the modus operandi of the invention.
  • Two hydraulic pumps 1 and 2 adjustable with the aid of servo-motors 5 or 6, and driven by a driving apparatus not illustrated, deliver pressurized fluid in two working circuits 3 and 4 independent of each other.
  • a power control device 7 or 8 consisting in a measuring spring assembly 9 and 10 and control slide valve 11 or 12, the force of which may be adjusted by means of an adjustment device comprising a stationary throttle valve 15, 16 and an adjustable regulating throttle valve 17, 18.
  • the maximum pressure in the working circuits 3, 4 is limited by an over-pressure valve 21, 22 (FIG. 1) or a pressure regulating device 27, 28 (FIG; 2).
  • such a device operates as follows: When the pressure, in the working circuit 3, for example, increases, the pressure that builds up between the stationary throttle and the regulating throttle valve 17 acts on the measuring or piston surface 13 of the control slide valve 11 against the force of the measuring spring assembly 9 of the power control device. When the control slide valve 11 opens it admits pressure fluid from the working circuit 3 to the adjusting piston of the servo-motor 5 to adjust the hydraulic pump 1 to prevent further rise of pressure. At the same time, the crosshead 19 raises the initial force of the measuring spring assembly 9 until the control slide valve 11 again closes.
  • the power control device 7 When the pressure has reached, for example, the point B 1 (see FIG. 3) which is determined by the design of the power control device 7 and the power adjustment through the regulating throttle valve 17, the power control device 7 begins to operate in accordance with the curve N1, the characteristic of which is determined by the measuring spring assembly 9.
  • the regulated power is kept constant, as the delivery flow is continuously suited to the working pressure prevailing at any time.
  • the performance curve N1 will run from B 1 to C 1, while the output Q 1 will be decreased corresponding to the characteristic.
  • A1 and A2 denote the points of maximum output of the pumps at zero pressure, and D 1 and D 2 the points where the output is nil at maximum output pressure in the working circuit.
  • the respective power control devices 7 and 8 operate only in the applicable range B1 C1 or B2 C2 of the associated performance curve N1 or N2, so that in this range optimum matching of the sum of the powers of the two pumps to the power of the driving apparatus is possible.
  • each hydraulic pump 1 and 2 is provided with a pressure gauging member in the form of a pressureresponsive adjustable throttle valve 24 and 23 connected in parallel with the adjusting throttle valve 17 or 18 associated with the other pump.
  • both the adjustable throttles l7 and 24 or 18 and 23 jointly influence the pressure acting on the measuring surface 13 or 14 of the control slide valve 1 1 or 12, depending upon the working pressure of both pumps 2 and 1 and thereby the power adjustment of the power control device 7 or 8.
  • the pressure-dependent adjustable throttle valve 24 or 23 has for the purpose an adjusting piston 26 or 25 connected with the working circuit 4 or 3 of the other pump.
  • the throttle valves 23, 24 are open.
  • the power control device 7, 8 or of the other is so adjusted that the latter pumps 1 or 2 could take up the entire output of the driving apparatus and could operate in accordance with the performance curve N1 or N2 of FIG. 3. If in the working circuit 3 the output pressure begins to rise from the point Al to the point B1 in FIG. 3, then the pressure acts also upon the adjusting piston 25 which progressively closes the adjustable throttle valve 23,
  • the pump 1 can accept the entire driving power, and therefore work according to the curve N1.
  • the pump 2 As soon as the pump 2 is loaded and the pressure increases in the working circuit 4, its pressure acts upon the pressure gauging piston 26, which progressively closes the adjustable throttle valve 24.
  • the working circuit 3 As the working circuit 3 is under pressure, a pressure accumulates between the fixed throttle valve 15 and the adjusting throttle valve 24, which acts additionally upon the measuring surface 13 of the control slide valve 11, thereby altering the power adjustment of the hydraulic pump 1, so that the performance curve N1, (on which the pump 1 operates while the pump 2 operates between the points A2 and B2) is shifted in the direction of the performance curve N1.
  • Each power adjustment of the hydraulic pump 2 is given a matching power adjustment of the hydraulic pump 1, which permits of the utilization of the total driving power, before the adjustment ranges originally allotted to the pumps (performance curves N1 and N2) are reached.
  • the performance curve N l is reached when the throttle valve 24 is closed, i.e. the pump 2 has reached the point B2 through adjustment and loading.
  • the pressure in the working circuit can at a maximum reach the point B2, as with the closure of the throttle valve 23 the performance curve of the pump 2 would be shifted from N2 to N2.
  • FIG. 2 shows a modified arrangement in which the output that would be lost through this release from one pump is made available to the other pump.
  • each of the hydraulic pumps 1 and 2 is provided with a further output-dependent adjustable throttle valve 30 or 29, which is connected with the servomotor 6 or 5 of the other pump 2 or 1, via a lever 32 or 31 connected to the crosshead 20 or 1.9, so as to depend on the position of adjustment of the pump.
  • the adjustable throttle valves 29, 30 are connected in parallel with the adjustable throttle valves 23, 24 and,- like them, affect the output adjustment of the hydraulic pump, as described already for the pressure-responsive adjustable throttle valves 23, 24.
  • the two hydraulic pumps 1, 2 operate in their adjustment ranges B1 C1 or B2 C2 along the performance curve NI or N2, the throttle valves 29, 30, variable according to the output delivery, are closed.
  • the pressure regulating valve 28 (replacing the overpressure valve 22) will respond, and will connect the working circuit 4 with the adjusting piston of the servo-motor 6, whereupon the hydraulic pump 2 adjusted to reduce its delivery.
  • This causes the crosshead and the throttle valve link 32, to open the adjustable throttle valve 30.
  • the effect of this on the output adjustment of the pump 1, as described with reference to FIG. 1, is that the performance curve is shifted from the curve N1 towards the curve N1, so that the pump 1 can now operate at a higher output in such a way that the entire drive output is again utilized by the two pumps.
  • the throttle valves 23 or 24 may be so designed that their closure by the adjusting pistons 25 and 26 is adjustably limited; thus, they may be closed up to only a preset degree, when points B2 or B1 are reached.
  • the concept of the invention may also be applied to more than two hydraulic pumps, when the pumps are, as regards power control, suitably considered pairwise, to carry out in connection with other pumps or pairs of pumps a control according to the invention.
  • a power control apparatus for two or more adjustable hydraulic pumps driven by a common driving means and each having its own power regulator, including a power control device for each pump for continuously adjusting the regulator to maintain a desired power value of the associated pump, and a pressure responsive device in fluid communication with and responsive to the delivery pressure of the companion pump and arranged to adjust the power of its own associated pump according to the said delivery pressure of the companion pump, and wherein the power control device of each pump comprises a pilot valve acted on by a spring, the force of which depends on the delivery flow adjustment of its associated pump, said pilot valve having a piston surface in fluid communication with and acted on by a control pressure depending upon the delivery pressure of its associated pump, the power control device of each pump also comprises two re stricted orifices connected in series and in fluid communication with the output of its associated pump, and wherein said control pressure is derived from a point between the two restricted orifices connected in series whilst the pressure responsive device comprises a throttle valve adjustable in accordance with the delivery pressure of the companion pump and connected in parallel with one
  • a power control apparatus for two or more adjustable hydraulic pumps driven by a common driving means and each having its own power regulator including a power control device for each pump for continuously adjusting the regulator to maintain a desired power value of the associated pump, and a pressure responsive device in fluid communication with and responsive to the delivery pressure of the companion pump and arranged to adjust the power of its own associated pump according to the said delivery pressure of the companion pump, a device limiting the maximum delivery pressure of each pump, and wherein-the power control device for each pump also has a delivery flow responsive device responsive to the delivery flow of the companion pump and arranged to adjust the power or its own pump according to the said delivery flow, and wherein the power control device of each pump comprises a pilot valve acted on by a spring, the force of which depends on the delivery flow adjustment of its associated pump, said pilot valve having a piston surface in fluid communication with and acted on by a control pressure depending upon the delivery pressure of its associated pump, the power control device of each pump also comprises two restricted orifices connected in series and in fluid communication with the output of its associated pump,
  • Control apparatus in which an adjustable throttle valve constitutes said one of the restricted orifices.
  • Control apparatus as claimed in claim 2, in which the pressure-responsive throttle valve closes as the delivery pressure of the companion pump increases, and the flow-responsive throttle valve opens as the flow of the companion pump decreases, and the arrangement is such that in the regulation range of the power control device the two throttle valves are closed, or offer a maximum restriction.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Structural Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Spectroscopy & Molecular Physics (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Operation Control Of Excavators (AREA)
  • Control Of Fluid Gearings (AREA)
US00166389A 1970-08-05 1971-07-27 Power control device for two or more hydraulic pumps Expired - Lifetime US3767327A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2038968A DE2038968C3 (de) 1970-08-05 1970-08-05 Leistungs-Regelvorrichtung für zwei oder mehrere Hydropumpen

Publications (1)

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US3767327A true US3767327A (en) 1973-10-23

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US00166389A Expired - Lifetime US3767327A (en) 1970-08-05 1971-07-27 Power control device for two or more hydraulic pumps

Country Status (7)

Country Link
US (1) US3767327A (enrdf_load_stackoverflow)
CH (1) CH541723A (enrdf_load_stackoverflow)
DE (1) DE2038968C3 (enrdf_load_stackoverflow)
FR (1) FR2103965A5 (enrdf_load_stackoverflow)
GB (1) GB1347056A (enrdf_load_stackoverflow)
NL (1) NL7110730A (enrdf_load_stackoverflow)
SE (1) SE372064B (enrdf_load_stackoverflow)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3897174A (en) * 1973-05-28 1975-07-29 Poclain Sa Devices for feeding fluid under pressure to at least two load circuits
US3910044A (en) * 1973-08-24 1975-10-07 Case Co J I Hydraulic summating system
US3999892A (en) * 1976-02-09 1976-12-28 Caterpillar Tractor Co. Interconnected pump control means of a plurality of pumps
US4212596A (en) * 1978-02-23 1980-07-15 Caterpillar Tractor Co. Pressurized fluid supply system
US4498847A (en) * 1982-06-29 1985-02-12 Kabushiki Kaisha Komatsu Seisakusho Control system for variable displacement hydraulic pumps
US4545202A (en) * 1983-10-24 1985-10-08 Sundstrand Corporation Pressure-regulating system
US4613286A (en) * 1984-12-31 1986-09-23 Kabushiki Kaisha Komatsu Seisakusho Constant torque control system for a variable displacement pump or pumps
US6109030A (en) * 1998-02-13 2000-08-29 Sauer Inc. Apparatus and method for ganging multiple open circuit pumps
US20050226738A1 (en) * 2004-04-08 2005-10-13 Ulf Bergquist Tree feller power management
US20050278556A1 (en) * 2004-06-15 2005-12-15 Smith David E Power controller
US20080103609A1 (en) * 2006-10-12 2008-05-01 Smith David E Determining power
US8571753B2 (en) 2010-04-14 2013-10-29 Caterpillar Forest Products Inc. Power management system for a forestry machine to automatically adjust engine load

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2505780C2 (de) * 1975-02-12 1986-03-06 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zum Regeln wenigstens einer verstellbaren Pumpe
DE2505779C2 (de) * 1975-02-12 1983-01-13 Robert Bosch Gmbh, 7000 Stuttgart Grenzlastregeleinrichtung für verstellbare Pumpen
DE3232695C2 (de) * 1982-09-02 1984-08-16 Hydromatik GmbH, 7915 Elchingen Leistungsregel-Vorrichtung für eine Hydropumpe
DE3340332C2 (de) * 1983-11-08 1988-11-10 Hydromatik GmbH, 7915 Elchingen Leistungs-Regelvorrichtung für einen hydrostatischen Antrieb mit Fördermengeneinstellung
DE3638889A1 (de) * 1986-11-14 1988-05-26 Hydromatik Gmbh Summen-leistungsregelvorrichtung fuer wenigstens zwei hydrostatische getriebe
CA1278978C (en) * 1987-02-19 1991-01-15 Lary Lynn Williams Hydraulic system for an industrial machine
DE3728207A1 (de) * 1987-08-24 1989-03-09 Rexroth Mannesmann Gmbh Ventilanordnung fuer zwei von einem gemeinsamen antrieb angetriebene leistungsgeregelte pumpen
DE4118869C2 (de) * 1991-06-07 1995-06-29 Hydromatik Gmbh Regelvorrichtung zur Regelung des Verdrängungsvolumens mehrerer hydrostatischer Maschinen

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3002462A (en) * 1957-08-13 1961-10-03 Racine Hydraulics & Machinery Fluid translating apparatus
US3188971A (en) * 1962-08-13 1965-06-15 Bendix Corp Control system for a pump
DE2017656A1 (de) * 1969-04-23 1970-11-05 Pensa, Carlo, Esino Lario, Como (Italien) Hydraulische FördermengeneinsteHvorrichtung für eine oder mehrere Pumpen
DE1922269A1 (de) * 1969-04-29 1970-11-12 Bellows Valvair Kaemper Gmbh Summenleistungsregler

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3002462A (en) * 1957-08-13 1961-10-03 Racine Hydraulics & Machinery Fluid translating apparatus
US3188971A (en) * 1962-08-13 1965-06-15 Bendix Corp Control system for a pump
DE2017656A1 (de) * 1969-04-23 1970-11-05 Pensa, Carlo, Esino Lario, Como (Italien) Hydraulische FördermengeneinsteHvorrichtung für eine oder mehrere Pumpen
DE1922269A1 (de) * 1969-04-29 1970-11-12 Bellows Valvair Kaemper Gmbh Summenleistungsregler

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3897174A (en) * 1973-05-28 1975-07-29 Poclain Sa Devices for feeding fluid under pressure to at least two load circuits
US3910044A (en) * 1973-08-24 1975-10-07 Case Co J I Hydraulic summating system
US3999892A (en) * 1976-02-09 1976-12-28 Caterpillar Tractor Co. Interconnected pump control means of a plurality of pumps
US4212596A (en) * 1978-02-23 1980-07-15 Caterpillar Tractor Co. Pressurized fluid supply system
US4498847A (en) * 1982-06-29 1985-02-12 Kabushiki Kaisha Komatsu Seisakusho Control system for variable displacement hydraulic pumps
US4545202A (en) * 1983-10-24 1985-10-08 Sundstrand Corporation Pressure-regulating system
US4613286A (en) * 1984-12-31 1986-09-23 Kabushiki Kaisha Komatsu Seisakusho Constant torque control system for a variable displacement pump or pumps
US6109030A (en) * 1998-02-13 2000-08-29 Sauer Inc. Apparatus and method for ganging multiple open circuit pumps
US20050226738A1 (en) * 2004-04-08 2005-10-13 Ulf Bergquist Tree feller power management
US7481051B2 (en) * 2004-04-08 2009-01-27 Timberjack Inc. Tree feller power management
US20050278556A1 (en) * 2004-06-15 2005-12-15 Smith David E Power controller
US7519837B2 (en) * 2004-06-15 2009-04-14 Hewlett-Packard Development Company, L.P. Power controller
US20080103609A1 (en) * 2006-10-12 2008-05-01 Smith David E Determining power
US7793117B2 (en) 2006-10-12 2010-09-07 Hewlett-Packard Development Company, L.P. Method, apparatus and system for determining power supply to a load
US8571753B2 (en) 2010-04-14 2013-10-29 Caterpillar Forest Products Inc. Power management system for a forestry machine to automatically adjust engine load

Also Published As

Publication number Publication date
GB1347056A (en) 1974-02-13
DE2038968C3 (de) 1978-09-07
FR2103965A5 (enrdf_load_stackoverflow) 1972-04-14
DE2038968B2 (de) 1974-02-21
CH541723A (de) 1973-09-15
SE372064B (enrdf_load_stackoverflow) 1974-12-09
NL7110730A (enrdf_load_stackoverflow) 1972-02-08
DE2038968A1 (de) 1972-02-10

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