EP0059709B1 - Torque and high pressure limiting control for variable displacement pumps - Google Patents

Torque and high pressure limiting control for variable displacement pumps Download PDF

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Publication number
EP0059709B1
EP0059709B1 EP81901178A EP81901178A EP0059709B1 EP 0059709 B1 EP0059709 B1 EP 0059709B1 EP 81901178 A EP81901178 A EP 81901178A EP 81901178 A EP81901178 A EP 81901178A EP 0059709 B1 EP0059709 B1 EP 0059709B1
Authority
EP
European Patent Office
Prior art keywords
spool
valve
pressure signal
pump
modulating
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
Application number
EP81901178A
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German (de)
English (en)
French (fr)
Other versions
EP0059709A4 (en
EP0059709A1 (en
Inventor
Walter Z. Ruseff
James E. Schimpf
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Caterpillar Inc
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Caterpillar Inc
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Filing date
Publication date
Application filed by Caterpillar Inc filed Critical Caterpillar Inc
Publication of EP0059709A1 publication Critical patent/EP0059709A1/en
Publication of EP0059709A4 publication Critical patent/EP0059709A4/en
Application granted granted Critical
Publication of EP0059709B1 publication Critical patent/EP0059709B1/en
Expired legal-status Critical Current

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    • 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
    • F04B49/08—Regulating by delivery pressure
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate

Definitions

  • This invention relates generally to a torque and high pressure limiting control for variable displacement pumps and more particularly to modulating means for continuously modulating a fluid pressure signal originating in a fluid actuator to vary the displacement of a variable displacement pump to prevent the system from exceeding a desired horsepower range and pressure level.
  • the valve generally functions to maintain the discharge pressure of the pump above a minimum pressure level and also above a load pressure generated in a fluid actuator, such- as a double-acting hydraulic cylinder.
  • a valve of this type is fully disclosed in U.S. Patent No. 4,116,587, issued on September 26, 1978 to Kenneth P. Liesener and assigned to the assignee of this application.
  • the "load-plus” valve functions to sense a load pressure signal and to automatically actuate a swash plate of the pump in response to such signal to maintain a desired pump discharge pressure.
  • the present invention is directed to overcoming one or more of the problems as set forth above.
  • US ⁇ A ⁇ 4 034 564 teaches a fluid circuit having a fluid actuator, a variable displacement pump including a control member movable between first and second displacement positions, first biasing means for urging said control member toward its first displacement position, and second biasing means for urging said control member towards its second displacement position in opposition to said first biasing means and in response to a load pressure signal communicated thereto from said fluid actuator, wherein modulating means for modulating said load pressure signal in said second biasing means to vary the displacement of said pump in response to the magnitude of said load pressure signal.
  • modulating means for modulating said load pressure signal in said second biasing means to vary the displacement of said pump in response to the magnitude of said load pressure signal.
  • US ⁇ A ⁇ 3 999 892 teaches modulating means which vary the displacement of a pump also in response to the position of a control member of said pump.
  • a fluid circuit having the features set forth in the preamble of claim 1 is characterized by the features of the second part of claim 1.
  • Preferred embodiments of the invention are disclosed in the subclaims.
  • the improved fluid circuit incorporating the modulating means therein, will thus provide maximum performance efficiency from the prime mover, such as an internal combustion engine, utilized to drive the pump.
  • the control circuit is torque limiting since the modulated load pressure signal is a function of both pump discharge pressure and pump displacement, i.e., the load pressure signal thus becomes a function of pump torque. This relationship is graphically illustrated in Figure 4 wherein curve A plots pump flow versus the load pressure signal and wherein curve B represents a horsepower curve for a particular engine.
  • Figure 1 illustrates a fluid circuit 10 comprising a variable displacement pump 11 adapted to communicate pressurized fluid from a source 12 to a fluid actuator 13 under the control of a directional control valve 14.
  • a prime mover 15 such as an internal combustion engine, is adapted to drive pump 11 which may take the form of a hydraulic pump of the type shown in Figure 2.
  • actuator 13 constitutes a double-acting hydraulic cylinder adapted for use in construction vehicles and the like in a conventional manner.
  • servo-system 22 includes a so-called "load-plus” valve 23 ( Figure 2) for maintaining pump discharge pressure P o in line 18 at a specified level above load pressure signal P L in line 20 and a modulating means or horsepower limiting valve 24 for modulating load pressure signal P L ,
  • pump 11 comprises a barrel 25 adapted to be driven by an output shaft 26 of engine 15, a plurality of reciprocal pistons 27 connected to a control member or swash plate 28, and a housing 29 enclosing the pump assembly.
  • the displacement of pump 11 is determined by the rotational orientation of swash plate 28 which has opposite sides thereof connected to first and second biasing means 30 and 31 by rods 32 and 33, respectively.
  • swash plate 28 will effect maximum pump displacement, whereas horizontal orientation of the swash plate in Figure 2 will effect zero or minimum displacement of the pump.
  • Second biasing means 31 may be considered to include "load-plus" valve 23, which functions substantially identically to the corresponding valve disclosed in above-referenced U.S. Patent No. 4,116,587.
  • pump discharge pressure P D in a main discharge passage 35 will communicate with branch passages 36 and 37, connected to first and second biasing means 30 and 31, respectively.
  • Branch passage 36 communicates discharge pressure to an actuating chamber 38 of biasing means 30 via a port 39 formed in a tubular member 40 secured within housing 29.
  • the force generated by fluid pressure in chamber 38 will tend to urge swash plate 28 counterclockwise in Figure 2, towards its maximum displacement position shown, by acting on a piston 41 and rod 32.
  • Such force is additive to the force of a compression coil spring 42 which is mounted between member 40 and a retainer 43 mounted on a lower end of piston 41.
  • Second branch passage 37 communicates pump discharge pressure to an annulus 44 to communicate such pressure to valve 23, via ports 45 and 46.
  • Spool 34 of valve 23 has lands 47, 48, and 49 formed thereon to define annuluses 50 and 51 about the spool.
  • Spool 34 is slidably mounted in a bore 52 defined in a tubular member 53 secured within housing 29 with the bore being blocked at the lower end of the spool by a plug 54.
  • An actuating chamber 55 is thus between reciprocal spool 34 and plug 54 and another actuating chamber 56 is defined between the plug and a piston 57 attached to rod 33.
  • pump discharge pressure communicated to branch passage 37 is communicated to actuating chamber 55 via port 46 and a longitudinal passage 58 formed in spool 34 to shift the spool upwardly in Figure 2 under certain operating conditions, against the opposed biasing force of a compression coil spring 59 and the fluid pressure prevalent in an actuating chamber 60.
  • Chamber 60 is adapted to have load pressure signal P L communicated thereto via passage 20'.
  • modulating means 24 for modulating load pressure signal P L in line 20' to continuously vary and automatically reset the displacement of pump 11.
  • modulating means 24 includes a first spool 65 reciprocally mounted in a bore 66, defined in member 40, and a second spool 67 reciprocally mounted in a bore 68 defined in spool 65.
  • a stop shown in the form of a cross pin 69, is secured within spool 65 to limit downward movement of spool 67, as shown in Figure 3.
  • Spool 65 is urged downwardly in Figures 2 and 3 by a first compression coil spring 70 of a two-stage biasing means 71 which further includes a second compression coil spring 72.
  • a lower end of spring 70 seats on a retainer 73 which receives an upper end of spool 67 therein.
  • Load pressure signal P L communicated to modulating means 24 by line 20 will enter an annulus 74 and communicate to an actuating chamber 75 via a port 76 defined in member 40, an annulus 77 defined on spool 65, and a port 78 formed in the spool.
  • pressurized fluid communicated to chamber 75 will act on the lower end of piston 67 to urge it upwardly against the opposed biasing force of spring 70 to initiate modulation of load pressure signal P L , as depicted at point A 1 in Figure 4.
  • load pressure signal P L will be modulated through metering slots 79 defined on spool 67, which are in communication on their upstream side with chamber 75 via a passage 80 and ports 81 and on their downstream side with a drain passage 82 upon opening thereof.
  • This modulation of fluid will cause a fluid flow through orifice 21, creating a pressure drop thereacross to cause load pressure signal P L to become less in passage 20' than in line 20.
  • second spring 72 may be employed in cooperation with spring 70 to restage the modulation feature, as depicted at point A 2 in Figure 4.
  • Figure 5 illustrates a second horsepower limiting or modulating means embodiment 24a which functions similar to modulating means 24, described above.
  • Identical numerals depict corresponding constructions and arrangements of the respective modulating means, with numerals depicting modified constructions in Figure 5 being accompanied by an "a”.
  • load pressure signal P L communicated to modulating means 24a by line 20 will pass through fixed orifice 21 and communicate to passage 20'.
  • Load pressure signal P L ' will also communicate with an actuating chamber 75a, via annulus 74, port 76, an annulus 77a formed on a sleeve-like spool 65a, and ports 78a formed in the spool proper and a plug 65a' thereof.
  • Spool 65a is reciprocally mounted in a tubular member 40a, having rod 83 of the follow-up linkage reciprocally mounted therein in a manner similar to that shown in Figure 2.
  • a poppet 67a is biased downwardly against a seat formed on plug 65a' and defining a variable orifice 84a thereat by a compresssion coil spring 70a of a biasing means 71a.
  • Poppet 67a will thus control venting of load pressure signal P L from chamber 75a to drain passage 82 to thus control the operation of "load-plus” valve 23 ( Figure 2) via passage 20'.
  • the maximum desired pressure for a given displacement setting of pump 11, which is communicated to chamber 75a will tend to open poppet valve 67a to vent the load pressure signal to reduce the displacement of the pump.
  • a subsequent follow-up action will be effected by rod 83 moving upwardly to close poppet valve 67a at a position which has increased the force imposed on the poppet by spring 70a.
  • poppet 67a and its seat on plug 65a', defining variable orifice 84a will function substantially in the manner described in respect to modulating means 24 whereby the feedback from the pivoting of swash plate 28 will vary the force of spring 70a to infinitely adjust the load pressure setting in proportion to the position of the swash plate, so that a pump displacement reduces, system pressure will become proportionately higher and still not overcome maximum available horsepower.
  • Figure 6 illustrates a third horsepower limiting or modulating means embodiment 24b which functions similar to modulating means 24 and 24a with one of the differences being that modulation of load pressure signal P L is accomplished by a pair of variable orifices 21b and 84b in series rather than by a series of one fixed orifice 21 and a variable orifice 84 or 84a.
  • Identical numerals appearing in Figure 6 also depict corresponding constructions with numerals depicting modified constructions being accompanied by a "b" in Figure 6.
  • Load pressure signal P L communicated to modulating means 24b via line 20, is adapted to communicate with passage 20' leading to "load-plus” valve 23 ( Figure 2) after undergoing a pressure drop across variable orifice 21 b.
  • the size of orifice 21 b will vary depending on the reciprocal position of a spool 65b.
  • load pressure signal P L is communicated to passage 20' via passages 85 defined by a plurality of flat surfaces formed on the periphery of spool 65b, an annulus 66b, ports 76, and annulus 74. Simultaneously therewith, reduced load pressure signal P L will communicate from annulus 66b to an actuating chamber 75b, defined in spool 65b, via one or more ports 78b formed in spool 65b.
  • a slug 67b has its upper end disposed in engagement with housing 29 and has its lower end seated on the exit end of chamber 75b to define a second variable orifice 84b thereat.
  • a compression coil spring 70b of a biasing means 71 b has its lower end engaged on a retainer 87 which engages a rod 83b of a follow-up linkage.
  • the follow-up linkage further includes a compression coil spring 42b disposed between a retainer 88 secured to a lower end of rod 83b and a piston 41 b, engaged with rod 32.
  • branch passage 36 communicating with the pump discharge, further communicates with an actuating chamber 38b within the follow-up linkage via passages 39b.
  • spool 65b is normally urged upwardly in Figure 6 by spring 70b to provide substantial open communication from line 20 to line 20'.
  • Load pressure signal P L prevalent in actuating chamber 75b acts againstthe tower end of slug 67b to exert a downward force on spool 65b in opposition to spring 70b.
  • spool 65b will move downwardly to create a variable orifice at 84b to vent load pressure signal P L to drain via drain passages 82b' and 82b, the periphery of retainer 73b being slotted for this purpose.
  • Figure 7 illustrates a fourth horsepower limiting or modulating means embodiment 24c wherein identical numerals depict corresponding constructions, but wherein numerals depicting modified constructions are accompanied by a "c".
  • Modulating means 24c functions similar to above-described modulating means 24, 24a, and 24b and is further associated with a hereinafter described override means 89 for selectively overriding the automatic function of modulating means 24c. It should become obvious to those skilled in the arts relating hereto that override means 89 could be also associated with modulating means 24, 24a, and 24b with minor modification to these systems.
  • Load pressure signal P L communicates to modulating means 24c through line 20 and fixed orifice 21 in passage 20', connected to chamber 60 of "load-plus” valve 23 ( Figure 2).
  • Load pressure signal P L communicates to an actuating chamber 75c, via annulus 74, port 76, an annulus 77c, and radial ports 78c formed in a rod 83c which is attached to a piston (not shown), similar to piston 41 in Figure 2.
  • a piston or spool 67c is reciprocally mounted in rod 83c to selectively communicate chamber 74c with a drain passage 82c, through variable orifices 84c formed in the rod.
  • Piston 67c is biased downwardly to cover orifices 84c by a compression coil spring 70c, having its lower end seated on a cup-shaped retainer 73c. It should be further noted that an upper end of piston 67c engages retainer 73c to act against spring 70c to provide the type of follow-up and resetting function described above.
  • Override means 89 includes a piston 90 adapted to apply a counteracting and overriding force to rod 83c, additive to the force of spring 70c, upon the selective pressurization of an actuating chamber 91.
  • Chamber 91 is connected to a control 92, such as the steering valve of a construction vehicle, whereby orifices 84c, when opened by upward movement of piston 67c, can be closed upon pressurization of the chamber which forces piston 90 downwardly.
  • load-plus valve 23 will function as a conventional pressure compensated flow control valve operating in a normal manner throughout the working range of pump 11 to provide a load-sensitive control of pump discharge pressure P D in line 18, relative to load pressure signal P L by continuously providing a margin between these pressures, as described in above-referenced U.S. Patent No. 4,116,587.
  • load pressure signal P L reaches the desired maximum for a given displacement setting of pump 11, representative of the usable horsepower available from the engine, the load pressure signal P L in actuating chamber 75 ( Figure 3) will initiate upward movement of spool 67 against the opposed biasing force of spring 70 until metering slots 79 open to form a variable orifice at 84.
  • modulating means 24 This interaction within modulating means 24 will permit pump 11 to continue to operate at such a higher pressure setting without exceeding the horsepower limitations of the engine. Should the load carried by cylinder 13 demand an even greater pressure, the cycle will be repeated. It should be noted in Figure 4 that engagement of spring retainer 73 with second spring 72 of biasing means 71 will permit a restaging of the load pressure and pump displacement, as reflected at point A 2 on curve A. This cyclic action of modulating means 24 and interassociated biasing means 30 and 31 will continue throughout the working pressure range of pump 11 until spool 65 contacts shoulder 65' ( Figure 3), as reflected at point A3 on curve A in Figure 4. This establishes the maximum pressure obtained and further decreasing pump displacement will not increase maximum pressure obtained.
  • control system thus provides an infinitely variable horsepower limiting mechanism which will closely follow horsepower curve B of the engine to provide maximum work efficiency with minimum energy consumption or specified hydraulic circuit condition of operation.
  • Fixed orifice 21 will ensure that actuating chamber 60 of "load-plus” valve 23 can be bled-off at a sufficiently high rate to provide quick response of "load - plus” valve 23.
  • modified modulating means 24a, 24b, and 24c will function similar to modulating means 24.
  • override means 89 ( Figure 7) can be readily adapted for use with any one of the modulating means to selectively override the automatic functions thereof.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Fluid Gearings (AREA)
EP81901178A 1980-09-12 1980-09-12 Torque and high pressure limiting control for variable displacement pumps Expired EP0059709B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1980/001195 WO1982001047A1 (en) 1980-09-12 1980-09-12 Torque and high pressure limiting control for variable displacement pumps

Publications (3)

Publication Number Publication Date
EP0059709A1 EP0059709A1 (en) 1982-09-15
EP0059709A4 EP0059709A4 (en) 1984-04-27
EP0059709B1 true EP0059709B1 (en) 1987-07-29

Family

ID=22154543

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81901178A Expired EP0059709B1 (en) 1980-09-12 1980-09-12 Torque and high pressure limiting control for variable displacement pumps

Country Status (5)

Country Link
EP (1) EP0059709B1 (OSRAM)
JP (1) JPS57501393A (OSRAM)
BE (1) BE888823A (OSRAM)
DE (1) DE3071999D1 (OSRAM)
WO (1) WO1982001047A1 (OSRAM)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4854125A (en) * 1987-02-20 1989-08-08 Honda Giken Kogyo Kabushiki Kaisha Hydrostatically operated continuously variable transmission
US4999020A (en) * 1989-11-30 1991-03-12 Lucas Aerospace Power Transmission Corp. Variable displacement high pressure pump with internal power limiting arrangement
US5655463A (en) * 1995-06-19 1997-08-12 Douglas Nagel Apparatus and method for burning waste material
GB2502824A (en) * 2012-06-08 2013-12-11 Water Hydraulics Company Ltd Axial piston variable stroke hydraulic machine
WO2015048635A1 (en) 2013-09-27 2015-04-02 Duke University Mper-liposome conjugates and uses thereof

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4034564A (en) * 1976-01-23 1977-07-12 Caterpillar Tractor Co. Piston pump assembly having load responsive controls
US3999892A (en) * 1976-02-09 1976-12-28 Caterpillar Tractor Co. Interconnected pump control means of a plurality of pumps

Also Published As

Publication number Publication date
EP0059709A4 (en) 1984-04-27
WO1982001047A1 (en) 1982-04-01
JPS57501393A (OSRAM) 1982-08-05
DE3071999D1 (en) 1987-09-03
BE888823A (fr) 1981-11-16
EP0059709A1 (en) 1982-09-15

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