US3912419A - Hydraulic pump control arrangement - Google Patents

Hydraulic pump control arrangement Download PDF

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Publication number
US3912419A
US3912419A US156737A US15673771A US3912419A US 3912419 A US3912419 A US 3912419A US 156737 A US156737 A US 156737A US 15673771 A US15673771 A US 15673771A US 3912419 A US3912419 A US 3912419A
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United States
Prior art keywords
conduit
valve
pressure
pump
piston
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Expired - Lifetime
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US156737A
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English (en)
Inventor
Gerhard Lutz
Karl Reiff
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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
    • 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
    • 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

Definitions

  • a piston is controlled by the pressure differential upstream and downstream of a throttle in the consumer conduit, to urge the pressure limiting valve to a closed position so that the pressure limiting valve opens when the filler pump supplies more fluid to the main pump than can be absorbed by the same, and the pressure differential does not increase.
  • the present invention is concerned with a hydraulic control arrangement for a displacement pump whose output volume is variable, and whose suction spaces are filled by a filler pump whose output volume is greater than the maximum volume transported bythe displacement pump so that the excess pumped by the filler pump must be discharged to a container at low pressure.
  • the German Auslegeschrift No. 1,255,010 discloses an arrangement of this type in which a pressure limiting valve permits discharge of the excess volume pumped by the filler pump.
  • the volume pumped by the filler pump In order to completely fill the suction spaces of the main pump even at very high rotary speeds, the volume pumped by the filler pump must be greater than the maximum pumped volume of the main pump.
  • the excess fluid pumped by the filler pump is discharged by means of a bypass or pressure limiting valve, which causes substantial losses in the efficiency of the apparatus.
  • Another object of the invention is to control the discharge of the excess fluid pumped by the filler pump by the pressure prevailing in the output consumer conduit of the main pump.
  • a throttle is provided in the output consumer conduit of the main pump, and the pressure differential produced by the throttle acts on a pressure limiting valve which is spring biassed and subjected to the pressure of the output conduits of the filler pump.
  • the pressure limiting valve is controlled by a control valve which is controlled by the pressure differential.
  • a control arrangement comprises a main pump having a consumer conduit and an inlet conduit; a throttle in the consumer conduit producing a pressure differential upon operation of the main pump; a filler pump having an outlet conduit connected with the inlet conduit for supplying at least as much fluid to the main pump the same can absorb; pressure limiting valve means connected with the outlet conduit and including spring means biassing the pressure limiting valve means to a closed position while the pressure of the fluid from the outlet conduit urges the pressure limiting valve to an open position for discharg ing the fluid to a low pressure space; piston and cylinder means connected to the consumer conduit upstream and downstream of the throttle, and including a movable member subjected to the pressure differential; and connecting means connecting the pressure limiting valve with the movable member.
  • the pressure limiting valve moves to the open position when the filler pump supplies more fluid to the main pump than the same can absorb and the pressure in the outlet conduit of the filler pump increases, while the pressure differential in the consumer conduit of the main pump does not increase.
  • the piston and cylinder means include a piston having a piston rod directly connected to a valve slide of the pressurelimiting valve.
  • a branch conduit communicating with the outlet conduit of the filler pump has another throttle
  • the connecting means include a control valve having an inlet connected with the branch conduit downstream of the throttle in the same, and a discharge outlet communicating with a low pressure space.
  • the valve member of the control valve is mechanically connected with the piston of the piston and cylinder means, and the pressure limiting valve is connected with the branch conduit downstream of the throttle in the output conduit for being urged to a closed position until the valve member of the control valve connects the branch conduit downstream of the throttle with the discharge outlet.
  • FIG. 1 is a fragmentary schematic view illustrating a pump control arrangement according to one embodiment of the invention.
  • FIG. 2 is a fragmentary schematic view illustrating a pump arrangement according to another embodiment of the invention.
  • a main pump I provided with means for varying the pumped volume, as indicated by an arrow, has an inlet connected with a filler pump 2 which is connected for rotation with the main pump 1, and is driven with the same.
  • the main pump 1 pumps a fluid or liquid into the consumer conduit 3 in which a throttle 4 is provided.
  • a first conduit 5 is connected with consumer conduit 3 upstream of throttle 4, and a second conduit 9 is connected with consumer conduit 3 downstream of the throttle 4.
  • conduits 5 and 9 communicate, respectively, with chambers 6 and 10 formed by a piston 8 in a cylinder of a cylinder and piston means 7.
  • Piston 8 has a fixed piston rod 11 which is axially movable in bearings of the housing of the cylinder and piston means 7, and is fixedly secured to a piston portion of a valve slide 12, which has a casing 16 in which another piston portion of valve slide 12 forms a pressure chamber 16'.
  • Casing 16 has two annular channels 17 and 18 of which channel 17 communicates with the output conduit 20 of the filler pump 2, which is also connected by output conduit 21 with,.the inlet of the main pump 1.
  • Another conduit 22 connects the output conduit 20, 21 with pressure chamber 16'.
  • the other annular channel 18 is connected with a discharge opening from which fluid can be discharged into a reservoir 19 from which filler pump 2 sucks fluid through the inlet conduit 23.
  • Main pump 1 may also be provided with an inlet conduit communicating with the reservoir 19.
  • Valve slide 12 has between the two piston portions at the ends thereof, a reduced portion 14 so that communication between the annular channels 17 and 18 is possible when valve slide 12 is moved to the right as viewed in FIG. 1 out of the illustrated position.
  • Filler pump 2 sucks through inlet conduit 23 fluid from reservoir 19 and pumps it through outlet conduits 20 and 21 to the inlet of the main pump for filling the suction chambers of the same.
  • the fluid pumped by main pump 1 through consumer conduit 3 flows through throttle 4 so that a pressure differential prevails between conduits 5 and 9 and the chambers 6 and 10, thepressure in conduit 9 and chamber 10 being lower than the pressure in conduit 5 and chamber 6.
  • Piston 8 is urged to the left as viewed in FIG.
  • valve slide 12 of the pressure limiting valve means 13 displace valve slide 12 of the pressure limiting valve means 13, and a spring is provided surrounding piston rod 11 and abutting the end face of valve slide 12 to urge valve slide 12 in the same direction to reduce the volume of the pressure chamber 16' which is supplied with pressure fluid from the outlet conduit 20, 21 and 22 of the filler pump 2.
  • main pump 1 now pumps fluid into the consumer conduit 3 and through throttle 4, a pressure differential develops upstream and downstream of throttle 4 and in the chambers 6 and 10, by which piston 8 is urged to the left and acts on slide 12 in the same direction as spring 15.
  • valve slide 12 is moved to the right, as viewed in the drawing against the action of spring 15. While in the position shown in FIG. 1, the right piston portion of valve slide 12 closes the annular channel 18, movement of valve slide 12 to the right due to the action of the pressure fluid in pressure chamber 16' displaces the piston portion to open the annular channel 18 which communicates with the annular channel 17 so that pressure fluid from outlet conduit 20 flows around portion 14 of valve slide 12 into the annular channel 18 and from there through a discharge outlet into the reservoir 19.
  • valve slide 12 of pressure limiting valve 13 is placed in a balanced position of equilibrium of the forces in which only a minimal excess volume is discharged into reservoir 19 while the required pressure is produced in the outlet conduit 20, 21 of the filler pump 2, and rises as the rotary speed of the pumps increases. Due to the provision of an additional control force exerted by piston 8 under control of the pressure differential in the consumer conduit 3, the complete filling of the suction spaces of the main pump 1 is obtained.
  • FIG. 2 illustrates a modified embodiment, and corresponding parts are indicated in FIG. 2 by the same reference numerals as in FIG. 1.
  • the embodiment of FIG. 2 is provided with a control valve 26 by which a pressure limiting valve 25 is hydraulically controlled.
  • the outlet conduit 27 of the filler pump 2 is connected by branch conduit 28 with the inlet of the main pump 1.
  • the branch conduit 28 connects the outlet conduit 27 also with a first chamber 29 in a casing of control valve 26, which has a second, larger chamber 35 connected by valve seat 30 with chamber 29.
  • a frustoconical valve member 31 cooperates with valve seat 30 and is fixedly secured to the piston rod 32 of piston 33 which forms in cylinder 34 two chambers respectively communicating with conduits 5 and 9 so that the pressure differential prevailing ,upstream and downstream of throttle 4, is also present on opposite sides of piston 33.
  • a spring 33a is mounted in the chamber on the right of piston 33 and urges piston 33 to the left so that valve member 31 abuts valve seat 30.
  • the chamber or space 35 is connected with a discharge conduit 36 which opens into the reservoir 19.
  • the pressure limiting valve 25 is connected at one side by conduit 38 with the outlet conduit 27 of filler pump 2, and on the other side by a conduit 37 with space or chamber 29 and branch conduit 28 downstream of a throttle 39, while conduit 38 communicates with the outlet conduit 27 upstream of throttle 39.
  • a spring 40 acts on the pressure limiting valve 25 to urge the same to a normal closed position, while high pressure in conduit 38 acts on the pressure limiting valve 25 against the action of spring 40 to move the same to an open position for discharging fluid supplied from outlet conduit 27 and conduit 38, out of discharge conduit 36 into reservoir 19.
  • valve member 31 and piston 33 reach a condition of equilibrium so that the position of the pressure limiting valve 25 is controlled whereby the required pressure is produced in the outlet conduit 27 of the filler pump 2 while thedischarged excess volume is a minimumfs'o that the apparatus operates at high efficiency.
  • conduits are schematically shown in the drawing outside of any casing, it will be understood that all conduits can be provided in the form of ducts in a body or housing.
  • Hydraulic pump control arrangement comprising main pump means having a consumer conduit and an inlct conduit; a throttle in said consumer conduit producing a pressure differential upon operation of said main pump means; a filler pump having an outlet conduit connected with said inlet conduit for supplying at least much fluid to said main pump means as the same can absorb; pressure limiting valve means including a casing having a discharge outlet, an inlet having a connecting conduit connected with said outlet conduit, a valve slide in said casing, and spring means biasing said valve slide in one direction to move to a closed position disconnecting said inlet from said discharge outlet while the pressure of the fluid from said outlet conduit urges said pressure limiting valve means to an open position for discharging the fluid to a low pressure space; said fluid from said connecting conduit urging said valve means in the opposite direction to said open position against the action of said spring means; piston and cylinder means forming a high pressure chamber and a low pressure chamber connected to said consumer conduit upstream and downstream of said throttle, respectively, and including a movable member subjected to said pressure.
  • connecting means mechanically connecting said movable member of said piston and ,eylinder'means with said valve slide so that the'pressure differential biases said valve slide to move in said'one direction whereby said pressure limiting valve means movesto said open position when said flllerpump supplies morefluid to saidmain pump meansthan the same can absorb and the pressure in said outlet conduit increases while said pressure differential does not increase.
  • piston and cylinder means include a stationary cylinder, and a piston in the same having a pis-' ton rod projecting out of said cylinder-into said casing and being directly connected with. said valve slide;
  • said spring means surrounds the portion of said piston rod located in said casing-and abuts said valve slide.
  • Hydraulic pump control arrangement comprising main pump means having a consumer conduit and an inlet conduit; a throttle in said consumer conduit producing a pressure differential upon operation of said main pump means; a filler pump having an outlet conduit connected with said inlet conduit for supplying at least as much fluid to said main pump means as the same can absorb; pressure limiting valve means including a spring means biasing said pressure limiting valve means to a closed position; a connecting conduit connecting said outlet conduit with said pressure limiting valve means so that the pressure of said fluid from said outlet conduit urges said pressure limiting valve means to an open position for discharging the fluid to a low pressure space; piston and cylinder means forming a high pressure chamber and a low pressure chamber connected to said consumer conduit upstream and downstream of said throttle, respectively, and including a movable member subjected to said pressure differential; and connecting means connecting said pressure limiting valve means with said movable member so that said pressure limiting valve means moves to said open position when said filler pump supplies more fluid to said main pump means than the same can absorb and g the pressure in said
  • Pump control arrangement as claimed in claim 3 wherein said main pump means include regulating means for adjusting the pumped volume of fluid.
  • Pump control arrangement as claimed in claim 3 and including means connecting said main pump means and filler pump for rotation.
  • said piston and cylinder means include a stationary cylinder, and a piston defining said two chambers in said cylinder respectively communicating with said consumer conduit on opposite sides of said throttle; and wherein said connecting means include a piston outlet conduit; and a throttle means in said branch conduit; wherein said connecting means include a control valve having an inlet connected with said branch conduit downstream of said throttle means and a discharge outlet communicating with a low pressure space, and a -valve member mechanically connected with said movable member of said piston and cylinder means; and
  • said pressure limiting valve means is connected on one side withsaid outlet conduit of said filler pump upstream of said throttle means to be urged in one direction to the open position against the action of said spring means, and is connected on the other side thereof with said branch conduit downstream of said throttle means for being urged in the opposite direction to the closed position until said valve member of said control valve connects said branch conduit downstream of said throttle means with said discharge outlet.
  • piston and cylinder means include a stationary cylinder and a piston in the same having a piston rod projecting out of said cylinder and being directly connected with said valve member of said control valve.
  • control valve includes a casing having said inlet and said discharge outlet, and forming a first space communicating through said inlet with said branch conduit, a second space communicating with said discharge outlet, and a valve seat between said first and Second spaces; wherein said valve member is secured to said piston rod and cooperates with said valve seat; said control valve comprising another conduit connecting said first space with said other side of said pressure limiting valve means.
  • valve member is a frustoconical head fixedly secured to the end of said piston rod; and wherein said second space is larger than said first space.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)
US156737A 1970-07-03 1971-06-25 Hydraulic pump control arrangement Expired - Lifetime US3912419A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19702033053 DE2033053A1 (de) 1970-07-03 1970-07-03 Steuereinrichtung für Verdrängerpumpe

Publications (1)

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US3912419A true US3912419A (en) 1975-10-14

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US156737A Expired - Lifetime US3912419A (en) 1970-07-03 1971-06-25 Hydraulic pump control arrangement

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US (1) US3912419A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
JP (1) JPS493401B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
CH (1) CH525395A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
DE (1) DE2033053A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
FR (1) FR2097177B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
GB (1) GB1315064A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2641362A1 (de) * 1976-06-22 1977-12-29 Lucas Industries Ltd Vorrichtung zum vorwaermen der verbrennungsluft von durch druck selbstzuendenden brennkraftmaschinen
US4169448A (en) * 1976-06-22 1979-10-02 Lucas Industries Limited Air heater system
US4531359A (en) * 1983-11-04 1985-07-30 General Motors Corporation Gas turbine engine fuel system
US4662181A (en) * 1984-12-24 1987-05-05 Zwich Energy Research Organization, Inc. Method and apparatus for extending the duration of operation of a cryogenic pumping system
US5020324A (en) * 1990-03-13 1991-06-04 Deere & Company Charge flow priority circuit
US5186612A (en) * 1992-01-16 1993-02-16 Caterpillar Inc. Variable pressure inlet system for hydraulic pumps
US6772794B2 (en) 2002-01-24 2004-08-10 Seguin Carl Variable volume reservoir
US20040219032A1 (en) * 2003-04-30 2004-11-04 Bishop Michael B. Radial piston pump

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3445516C1 (de) * 1984-12-13 1989-05-18 Mannesmann Rexroth GmbH, 8770 Lohr Steuervorrichtung fuer eine Regelpumpe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2604047A (en) * 1945-09-19 1952-07-22 Hulman Two-stage hydraulic pressure pump
US2709339A (en) * 1953-07-06 1955-05-31 Pacific Airmotive Corp Two-stage pumping system with automatic demand responsive control
US3002462A (en) * 1957-08-13 1961-10-03 Racine Hydraulics & Machinery Fluid translating apparatus
US3153508A (en) * 1961-08-04 1964-10-20 Gen Turbine Corp Vehicle mounted air compressor
US3515164A (en) * 1968-10-16 1970-06-02 Servoflo Corp Flow delivery system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2604047A (en) * 1945-09-19 1952-07-22 Hulman Two-stage hydraulic pressure pump
US2709339A (en) * 1953-07-06 1955-05-31 Pacific Airmotive Corp Two-stage pumping system with automatic demand responsive control
US3002462A (en) * 1957-08-13 1961-10-03 Racine Hydraulics & Machinery Fluid translating apparatus
US3153508A (en) * 1961-08-04 1964-10-20 Gen Turbine Corp Vehicle mounted air compressor
US3515164A (en) * 1968-10-16 1970-06-02 Servoflo Corp Flow delivery system

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2641362A1 (de) * 1976-06-22 1977-12-29 Lucas Industries Ltd Vorrichtung zum vorwaermen der verbrennungsluft von durch druck selbstzuendenden brennkraftmaschinen
US4169448A (en) * 1976-06-22 1979-10-02 Lucas Industries Limited Air heater system
US4531359A (en) * 1983-11-04 1985-07-30 General Motors Corporation Gas turbine engine fuel system
US4662181A (en) * 1984-12-24 1987-05-05 Zwich Energy Research Organization, Inc. Method and apparatus for extending the duration of operation of a cryogenic pumping system
US5020324A (en) * 1990-03-13 1991-06-04 Deere & Company Charge flow priority circuit
WO1993014317A1 (en) * 1992-01-16 1993-07-22 Caterpillar Inc. Variable pressure inlet system for hydraulic pumps
US5186612A (en) * 1992-01-16 1993-02-16 Caterpillar Inc. Variable pressure inlet system for hydraulic pumps
EP0577783B1 (en) * 1992-01-16 1997-04-02 Caterpillar Inc. Variable pressure inlet system for hydraulic pumps
US6772794B2 (en) 2002-01-24 2004-08-10 Seguin Carl Variable volume reservoir
US20050011565A1 (en) * 2002-01-24 2005-01-20 Carl Seguin Variable volume reservoir
US6981523B2 (en) * 2002-01-24 2006-01-03 Sobacor Variable volume reservoir
US20040219032A1 (en) * 2003-04-30 2004-11-04 Bishop Michael B. Radial piston pump
US6916158B2 (en) * 2003-04-30 2005-07-12 Actuant Corporation Radial piston pump

Also Published As

Publication number Publication date
DE2033053A1 (de) 1972-01-05
GB1315064A (en) 1973-04-26
CH525395A (de) 1972-07-15
FR2097177A1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1972-03-03
FR2097177B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1974-04-05
JPS493401B1 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1974-01-26

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