US3716308A - Hydraulic system - Google Patents

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US3716308A
US3716308A US00109813A US3716308DA US3716308A US 3716308 A US3716308 A US 3716308A US 00109813 A US00109813 A US 00109813A US 3716308D A US3716308D A US 3716308DA US 3716308 A US3716308 A US 3716308A
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pressure
relief valve
pumps
pump
valve means
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US00109813A
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W Kobald
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F16H61/4148—Open loop circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F16H61/4008—Control of circuit pressure
    • F16H61/4017—Control of high pressure, e.g. avoiding excess pressure by a relief valve
    • 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
    • F16H61/4043—Control of a bypass valve
    • 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
    • F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation
    • F16H61/448—Control circuits for tandem pumps or motors
    • 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
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve

Definitions

  • the relief valve of this commonly used system does protect the user circuit from excessive pressure by opening. It can occur, however, where the pump or pumps are capable of a very large output, that the prime mover is overloaded.
  • prime mover is an internal combustion engine
  • the engine can stall. If it is an electric motor, the
  • An object of the invention is an hydraulic system that is very simple and inexpensive and yet dependably protects the prime mover from overloading.
  • Another object of the invention is an hydraulic system of the preceding object that is equally suitable for one pump or for several pumps.
  • the invention consists of pump means with constant volume delivery, driving means for operating the pump means, the maximum output of the driving means being less than the maximum output that can be delivered by the pump means, user circuit means connected to the delivery side of the pump means for accepting the hydraulic fluid delivered by the pump means, resiliently loaded relief valve means for the user circuit means, and pressure responsive means, acting on the relief valve means, connected to the delivery side of the pump means and responsive to the pressure thereat to reduce, with increasing pressure at the delivery side, the pressure on the relief valve means required to open the latter so that the relief valve means opens to reduce the pressure in the user circuit means before the driving means can stall.
  • FIGURE shows schematically one embodiment of the invention.
  • a further line 12 that leads to a relief valve 13, the cut-off pressure of which is determined by a spring 14.
  • a discharge line 15 connects the relief valve to a vessel 16.
  • a valve 17 is connected in the discharge line 15.
  • a spring 19 bears against the end face 18 of the differential piston 8 and acts on the relief valve 13 so as to counteract the pressure of the spring 14.
  • the cut-off pressure of the relief valve 13 is varied in dependence on the tension of the spring 19, which tension is dependent on the position of the differential piston 8.
  • a two position valve 21 connects to a vessel 22 that is at atmospheric pressure.
  • the valve 21 has a closed position and an opened position. This valve is controlled by the pressure in a line 23, which is connected to the line 15 at a position between the discharge end of the relief valve 13 and the valve 17. The pressure in the line 23 acts against a spring 24 of the valve 21.
  • the movement of the latter tensions the spring 19, which acts on the relief valve 13 with a force that opposes the force of the spring 14, which latter normally determines the cut-off pressure of the relief valve.
  • the cut-off pressure is consequently reduced, and the maximum pressure within the user circuit 4 and against which the pump 2 must operate is lowered.
  • the maximum output-such as the torque, in the case of a hydrostatic vehicle propulsion-demanded of the prime mover 1 is therefore reduced.
  • the sum of the outputs of the pumps 2 and 3 is consequently not greater than the maximum available output of the prime mover 3, which latter is therefore prevented from stalling.
  • valve 21 When a large amount of hydraulic fluid is shunted through the relief valve 13, the fluid undesirably can heat up. In order to prevent this, the valve 21 is provided. The valve 17 backs up the hydraulic fluid, raising the pressure in the line 23 and thereby opening the valve 21. Hydraulic fluid is now free to flow directly out of the overloaded user circuit 4, without heating up. After the pressure inthe user circuit 4 is reduced, the spring 24 again closes the valve 21.
  • the invention can also be used for hydraulic systems having only a single pump. lts use is advantageous, however, only if the maximum output that can be demanded of the pump exceeds the maximum available output of the prime mover.
  • a relief valve 13 and a two position valve 21 can be connected, in the described manner, in the second, or each additional, user circuit associated with the third or fourth pump. It is not necessary to use more than one differential piston. If, for example, the hydraulic system has three pumps, a differential piston of three steps is used, the piston acting on three springs, each spring cooperating with the relief valve 13 of a respective user circuit.
  • the kind of user determines which of the user circuits are provided with the arrangement of the invention.
  • a hydraulic circuit comprising, in combination, a first and a second pump with constant volume delivery; driving means for operating said first and said second pump, the maximum output of said driving means being less than the maximum output that can be delivered by said first and said second pump; a user circuit connected to the delivery side of each of said pumps for accepting the hydraulic fluid delivered by said first and said second pumps, respectively; relief valve means for the user circuit of at least one of said pumps and including resilient means for holding said relief valve means in closed position until the pressure in said user circuit of said at least one of said pumps exceeds a predetermined required pressure and pressure responsive means acting on said relief valve means in opposition to the resilient means of the latter and being connected to the delivery side of both said first and said second pumps and responsive to the pressure thereat to reduce, with increasing pressure at said delivery side, the said predetermined required pressure to open the relief valve means under the influence of the fluid pressure in said user circuit of said at least one of said pumps so that the relief valve means opens to thereby reduce the pressure in the last mentioned user circuit before said driving means can stall.

Abstract

The user circuit for a pump having an output greater than the maximum output that can be accepted by the prime mover for the pump has a relief valve for shunting hydraulic fluid from the user circuit when the pressure within the circuit demands an output from the pump that exceeds the output available from the prime mover. The delivery side of the pump is connected to a piston that acts on the relief valve to open the latter in response to pressure within the user circuit.

Description

United States Patent [191 Kobald Feb. 13, 1973 HYDRAULIC SYSTEM Walter Kobald, bach, Germany Inventor: Stuttgart-Feuer- [73] Assignee: Robert Bosch Gmbll, Stuttgart, Ger- 7 many. Filed: Jan. 26, 1971 Appl. No.: 109,813
I Foreign Application Priority Data Jan. 28, 1970 Germany ..P 20 03 740.5
U.S; Cl. ..417/286, 417/308, 417/428 Int.- Cl. ..F04b 49/02, F04b 49/08 Field of Search ..4l7/308, 286, 287, 288, 428
References Cited UNITED STATES PATENTS 3,601,506 8/1971 Griswold ..417/ 288 X 2,273,152 2/1942 S onntag ..417/308 X Primary ExaminerCarlton R. Croyle Assistant Examiner-Richard J. Sher Attorney-Michael S. Striker [5 7] ABSTRACT 7 Claims, 1 Drawing Figure PATENTEU FEB I 73 lNl/ENTC R. Waite/ KOBALD his A rrop/wsv HYDRAULIC SYSTEM BACKGROUND OF THE INVENTION by a prime mover, the maximum available power output of which latter is less than the maximum output of the pump. A user circuit is connected to the delivery side of the pump, a resiliently loaded relief valve being connected to protect the circuit or the pump.
The relief valve of this commonly used system does protect the user circuit from excessive pressure by opening. It can occur, however, where the pump or pumps are capable of a very large output, that the prime mover is overloaded.
1 If the prime mover is an internal combustion engine,
the engine can stall. If it is an electric motor, the
windings of the motor can be burned out, ruining the motor. Moreover, the discharging of the hydraulic fluid through the relief valve undesirably heats the fluid.
One solution to these problems is to use pumps with variable delivery, the delivery being dependent upon the pressure. When the pressure increases, the amount of fluid delivered by the pump decreases, so as not to exceed the maximum power output of the prime mover.
These systems, such as hydrostatic drives for vehicles, have, however, the disadvantage that they are expensive, because a variable delivery pump is appreciably more expensive than a constant volume delivery pump.
I SUMMARY OF THE INVENTION An object of the invention is an hydraulic system that is very simple and inexpensive and yet dependably protects the prime mover from overloading.
Another object of the invention is an hydraulic system of the preceding object that is equally suitable for one pump or for several pumps.
Briefly, the invention consists of pump means with constant volume delivery, driving means for operating the pump means, the maximum output of the driving means being less than the maximum output that can be delivered by the pump means, user circuit means connected to the delivery side of the pump means for accepting the hydraulic fluid delivered by the pump means, resiliently loaded relief valve means for the user circuit means, and pressure responsive means, acting on the relief valve means, connected to the delivery side of the pump means and responsive to the pressure thereat to reduce, with increasing pressure at the delivery side, the pressure on the relief valve means required to open the latter so that the relief valve means opens to reduce the pressure in the user circuit means before the driving means can stall.
The novel features which are considered as characteristic for the invention are set forth in particular in the appended claims. The invention itself, however, both as to its construction and its method of operation, together with additional objects and advantages thereof, will be best understood from the following description of specific embodiments when read in connection with the accompanying drawing.
BRIEF DESCRIPTION OF THE DRAWING The single FIGURE shows schematically one embodiment of the invention.
DESCRIPTION OF THE PREFERRED EMBODIMENT which the latter has a smaller diameter than the former.
The piston sections 9 and 10 are borne upon respectively by the hydraulic fluid conveyed through the branch lines 6 and 11, the latter line being connected to the user circuit 5. The resulting pressure acting on the differential piston 8 is the sum of the two pressures in the user circuits 4 and 5.
Connected -to the user circuit 4 is a further line 12 that leads to a relief valve 13, the cut-off pressure of which is determined by a spring 14. A discharge line 15 connects the relief valve to a vessel 16. A valve 17 is connected in the discharge line 15.
A spring 19 bears against the end face 18 of the differential piston 8 and acts on the relief valve 13 so as to counteract the pressure of the spring 14. The cut-off pressure of the relief valve 13 is varied in dependence on the tension of the spring 19, which tension is dependent on the position of the differential piston 8.
Connected to the user circuit 4 is a further line 20, which a two position valve 21 connects to a vessel 22 that is at atmospheric pressure. The valve 21 has a closed position and an opened position. This valve is controlled by the pressure in a line 23, which is connected to the line 15 at a position between the discharge end of the relief valve 13 and the valve 17. The pressure in the line 23 acts against a spring 24 of the valve 21.
The sum of the pressures in the user circuits 4 and 5 act on the differential piston 8. The movement of the latter tensions the spring 19, which acts on the relief valve 13 with a force that opposes the force of the spring 14, which latter normally determines the cut-off pressure of the relief valve. The cut-off pressure is consequently reduced, and the maximum pressure within the user circuit 4 and against which the pump 2 must operate is lowered. The maximum output-such as the torque, in the case of a hydrostatic vehicle propulsion-demanded of the prime mover 1 is therefore reduced. The sum of the outputs of the pumps 2 and 3 is consequently not greater than the maximum available output of the prime mover 3, which latter is therefore prevented from stalling.
When a large amount of hydraulic fluid is shunted through the relief valve 13, the fluid undesirably can heat up. In order to prevent this, the valve 21 is provided. The valve 17 backs up the hydraulic fluid, raising the pressure in the line 23 and thereby opening the valve 21. Hydraulic fluid is now free to flow directly out of the overloaded user circuit 4, without heating up. After the pressure inthe user circuit 4 is reduced, the spring 24 again closes the valve 21.
The invention can also be used for hydraulic systems having only a single pump. lts use is advantageous, however, only if the maximum output that can be demanded of the pump exceeds the maximum available output of the prime mover.
in accordance with the invention, a relief valve 13 and a two position valve 21 can be connected, in the described manner, in the second, or each additional, user circuit associated with the third or fourth pump. It is not necessary to use more than one differential piston. If, for example, the hydraulic system has three pumps, a differential piston of three steps is used, the piston acting on three springs, each spring cooperating with the relief valve 13 of a respective user circuit.
The kind of user determines which of the user circuits are provided with the arrangement of the invention.
It will be understood that each of the elements described above, or two or more together, may also find a useful application in other types of constructions differing from the types described above.
While the invention has been illustrated and described as embodied in an hydraulic system, it is not intended to be limited to the details shown, since various modifications and structural changes may be made without departing in any way from the spirit of the present invention.
Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can by applying current knowledge readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic or specific aspects of this invention and, therefore, such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the following claims.
What is claimed as new and desired to be protected by Letters Patent is set forth in the appended claims.
1. A hydraulic circuit comprising, in combination, a first and a second pump with constant volume delivery; driving means for operating said first and said second pump, the maximum output of said driving means being less than the maximum output that can be delivered by said first and said second pump; a user circuit connected to the delivery side of each of said pumps for accepting the hydraulic fluid delivered by said first and said second pumps, respectively; relief valve means for the user circuit of at least one of said pumps and including resilient means for holding said relief valve means in closed position until the pressure in said user circuit of said at least one of said pumps exceeds a predetermined required pressure and pressure responsive means acting on said relief valve means in opposition to the resilient means of the latter and being connected to the delivery side of both said first and said second pumps and responsive to the pressure thereat to reduce, with increasing pressure at said delivery side, the said predetermined required pressure to open the relief valve means under the influence of the fluid pressure in said user circuit of said at least one of said pumps so that the relief valve means opens to thereby reduce the pressure in the last mentioned user circuit before said driving means can stall.
2. An hydraulic system as defined in claim 12, wherein said pressure responsive means is a piston acting on said relief valve means to open the latter with increasing pressure at said delivery side of said one pump.
3. An hydraulic system as defined in claim 2, including resilient means acting on said relief valve means to open the latter, said piston acting on said resilient means to increase the pressure of the latter on said relief valve with increasing pressure at said delivery side of said one pump.
4. An hydraulic system as defined in claim 1, including pressure regulating valve means connected to the delivery side of said relief valve means; hydraulic fluid line means connected between said pressure regulating valve means and said relief valve means; vessel means at atmospheric pressure; and pressure responsive valve means connected to said hydraulic fluid line means and connecting said user circuit of said one pump to said vessel means, said pressure responsive valve means opening in response to increasing pressure in said hydraulic fluid line means to permit discharge from said user circuit means into said vessel means.
5. An hydraulic system as defined in claim 1, said pressure responsive means having a discrete pressure bearing surface for each of said first and second pumps, each said surface bearing only the pressure at said delivery side of the associated pump.
6. An hydraulic system as defined in claim 5, wherein said pressure responsive means is a differential piston.
7. An hydraulic system as defined in claim 6, including resilient means acting on said relief valve means to open the latter, said differential piston acting on said first resilient means to increase the pressure of the latter on said relief valve means with increasing pressure at each said delivery side.

Claims (7)

1. A hydraulic circuit comprising, in combination, a first and a second pump with constant volume delivery; driving means for operating said first and said second pump, the maximum output of said driving means being less than the maximum output that can be delivered by said first and said second pump; a user circuit connected to the delivery side of each of said pumps for accepting the hydraulic fluid delivered by said first and said second pumps, respectively; relief valve means for the user circuit of at least one of said pumps and including resilient means for holding said relief valve means in closed position until the pressure in said user circuit of said at least one of said pumps exceeds a predetermined required pressure and pressure responsive means acting on said relief valve means in opposition to the resilient means of the latter and being connected to the delivery side of both said first and said second pumps and responsive to the pressure thereat to reduce, with increasing pressure at said delivery side, the said predetermined required pressure to open the relief valve means under the influence of the fluid pressure in said user circuit of said at least one of said pumps so that the relief valve means opens to thereby reduce the pressure in the last mentioned user circuit before said driving means can stall.
1. A hydraulic circuit comprising, in combination, a first and a second pump with constant volume delivery; driving means for operating said first and said second pump, the maximum output of said driving means being less than the maximum output that can be delivered by said first and said second pump; a user circuit connected to the delivery side of each of said pumps for accepting the hydraulic fluid delivered by said first and said second pumps, respectively; relief valve means for the user circuit of at least one of said pumps and including resilient means for holding said relief valve means in closed position until the pressure in said user circuit of said at least one of said pumps exceeds a predetermined required pressure and pressure responsive means acting on said relief valve means in opposition to the resilient means of the latter and being connected to the delivery side of both said first and said second pumps and responsive to the pressure thereat to reduce, with increasing pressure at said delivery side, the said predetermined required pressure to open the relief valve means under the influence of the fluid pressure in said user circuit of said at least one of said pumps so that the relief valve means opens to thereby reduce the pressure in the last mentioned user circuit before said driving means can stall.
2. An hydraulic system as defined in claim 12, wherein said pressure responsive means is a piston acting on said relief valve means to open the latter with increasing pressure at said delivery side of said one pump.
3. An hydraulic system as defined in claim 2, including resilient means acting on said relief valve means to open the latter, said piston acting on said resilient means to increase the pressure of the latter on said relief valve with increasing pressure at said delivery side of said one pump.
4. An hydraulic system as defined in claim 1, including pressure regulating valve means connected to the delivery side of said relief valve means; hydraulic fluid line means connected between said pressure regulating valve means and said relief valve means; vessel means at atmospheric pressure; and pressure responsive valve means connected to said hydraulic fluid line means and connecting said user circuit of said one pump to said vessel means, said pressure responsive valve means opening in response to increasing pressure in said hydraulic fluid line means to permit discharge from said user circuit means into said vessel means.
5. An hydraulic system as defined in claim 1, said pressure responsive means having a discrete pressure bearing surface for each of said first and second pumps, each said surface bearing only the pressure at said delivery side of the associated pump.
6. An hydraulic system as defined in claim 5, wherein said pressure responsive means is a differential piston.
US00109813A 1970-01-28 1971-01-26 Hydraulic system Expired - Lifetime US3716308A (en)

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DE2003740A DE2003740C3 (en) 1970-01-28 1970-01-28 Hydraulic system with at least two pumps

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US3716308A true US3716308A (en) 1973-02-13

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DE (1) DE2003740C3 (en)
FR (1) FR2077386B1 (en)
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US3910044A (en) * 1973-08-24 1975-10-07 Case Co J I Hydraulic summating system
US3924971A (en) * 1974-01-30 1975-12-09 Poclain Sa Device for regulating the supply of pressurized fluid of two circuit systems having at least two pumps of constant cubic capacity
US3962954A (en) * 1974-02-04 1976-06-15 Poclain Supply apparatus for two receiving means having a pressure summation device
US4545202A (en) * 1983-10-24 1985-10-08 Sundstrand Corporation Pressure-regulating system
US4957283A (en) * 1988-10-07 1990-09-18 Combined Fluid Products Co. Vacuum system for feeding sheets
US5136846A (en) * 1989-04-18 1992-08-11 Kubota, Ltd. Hydraulic circuit with a switchover valve for switching between a high and a low-pressure relief
US5918573A (en) * 1997-05-02 1999-07-06 Killion; David L. Energy efficient fluid pump
US7086366B1 (en) 1999-04-20 2006-08-08 Metaldyne Machining And Assembly Company, Inc. Energy efficient fluid pump
US20070039782A1 (en) * 2005-07-28 2007-02-22 J.C. Bamford Excavators Limited Providing lubricant to an engine
US20150184680A1 (en) * 2014-01-02 2015-07-02 Caterpillar Paving Products, Inc. Torque Limit Control

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JP2000045728A (en) 1998-08-03 2000-02-15 Unisia Jecs Corp Hydraulic circuit of internal combustion engine
JP7256449B2 (en) 2019-04-12 2023-04-12 トヨタ自動車株式会社 cylinder head

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US2273152A (en) * 1938-03-21 1942-02-17 American Machine & Metals Hydraulic pressure control for testing machines
US3601506A (en) * 1969-11-28 1971-08-24 Chandler Evans Inc Wear equalized fuel delivery system

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US3601506A (en) * 1969-11-28 1971-08-24 Chandler Evans Inc Wear equalized fuel delivery system

Cited By (14)

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US3910044A (en) * 1973-08-24 1975-10-07 Case Co J I Hydraulic summating system
US3924971A (en) * 1974-01-30 1975-12-09 Poclain Sa Device for regulating the supply of pressurized fluid of two circuit systems having at least two pumps of constant cubic capacity
US3962954A (en) * 1974-02-04 1976-06-15 Poclain Supply apparatus for two receiving means having a pressure summation device
US4545202A (en) * 1983-10-24 1985-10-08 Sundstrand Corporation Pressure-regulating system
US4957283A (en) * 1988-10-07 1990-09-18 Combined Fluid Products Co. Vacuum system for feeding sheets
US5136846A (en) * 1989-04-18 1992-08-11 Kubota, Ltd. Hydraulic circuit with a switchover valve for switching between a high and a low-pressure relief
US5918573A (en) * 1997-05-02 1999-07-06 Killion; David L. Energy efficient fluid pump
US7086366B1 (en) 1999-04-20 2006-08-08 Metaldyne Machining And Assembly Company, Inc. Energy efficient fluid pump
US20070039782A1 (en) * 2005-07-28 2007-02-22 J.C. Bamford Excavators Limited Providing lubricant to an engine
US7516729B2 (en) * 2005-07-28 2009-04-14 J.C. Bamford Excavation Limited Providing lubricant to an engine
US20150184680A1 (en) * 2014-01-02 2015-07-02 Caterpillar Paving Products, Inc. Torque Limit Control
CN104763693A (en) * 2014-01-02 2015-07-08 卡特彼勒路面机械公司 Torque limit control
US9464580B2 (en) * 2014-01-02 2016-10-11 Caterpillar Paving Products Inc. Torque limit control
CN104763693B (en) * 2014-01-02 2018-09-18 卡特彼勒路面机械公司 Torque limit controls

Also Published As

Publication number Publication date
CH510203A (en) 1971-07-15
FR2077386B1 (en) 1976-03-19
DE2003740C3 (en) 1981-05-07
DE2003740B2 (en) 1980-08-07
DE2003740A1 (en) 1971-08-12
GB1325022A (en) 1973-08-01
FR2077386A1 (en) 1971-10-22

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