US3316846A - Regulating system - Google Patents

Regulating system Download PDF

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Publication number
US3316846A
US3316846A US542037A US54203766A US3316846A US 3316846 A US3316846 A US 3316846A US 542037 A US542037 A US 542037A US 54203766 A US54203766 A US 54203766A US 3316846 A US3316846 A US 3316846A
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US
United States
Prior art keywords
fluid
communicating
pump
dynamic system
conduit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US542037A
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English (en)
Inventor
Vagn S L Bender
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.)
Danfoss AS
Original Assignee
Danfoss AS
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Publication date
Application filed by Danfoss AS filed Critical Danfoss AS
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Publication of US3316846A publication Critical patent/US3316846A/en
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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
    • F04C14/10—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F04C14/14—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
    • 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
    • F04B1/14—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 having stationary cylinders
    • 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
    • F04B49/02—Stopping, starting, unloading or idling control
    • 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
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F04B49/035—Bypassing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86389—Programmer or timer
    • Y10T137/86405—Repeating cycle
    • Y10T137/86421—Variable

Definitions

  • This invention relates to a regulating system for regulating the volume rate of delivery of a fluid from the discharge side of a pump means to a fluid dynamic system without significantly effecting the fluid pressure in the fluid dynamic system.
  • fluid dynamic system refers to a system in which fluid flow occurs. Accordingly, the fluid dynamic system may be as simple as a single conduit or may be considerably more complex such as a plurality of interconnected conduits provided with valves. The invention will be. described herein with reference to a ffluid.
  • the fluid is aliquid.
  • the fluid dynamic system may be the lubricating passages or system of a machine, such as an engine, and the fluid, in this instance, would be a lubricating oil.
  • pump means used herein to denote that part of a pump which actually pumps, i.e., imparts energy to, a fluid, such as the gear and gear housing of a gear pump or the impeller and impeller housing of a centrifugal pump or the piston and cylinder of a piston pump, as distinguished from the other structure of the pump such as thatstructure defining an inlet conduit to and an outlet conduit from the gear or impeller housing or cylinder or the like.
  • first conduit means communicating between the suction side'of the pump means and a reservoir adapted to contairi a fluid
  • second conduit means communicating between the discharge side of the pump means and a fluid dynamic system.
  • the first and secondconduit means may sirhplybe the inlet and outlet, respectively, of the pump of which the pump means is the working portion or may be conduits external of the structure of the pump and communicating with the inlet and the outlet, respectively, of the pump.
  • This rate of delivery is, at any instant, determined by the level of the fluid pressure in the fluid dynamic system. Also, there is a substantial energy loss due to the pumping of that portion of the fluid which is returned to the suction side of the pump means.
  • the new regulating system of the invention makes possible the regulation as desired of the rate of delivery of the fluid from the discharge side of the pump means to the fluid dynamic system without significantly effecting the fluid pressure in the fluid dynamic system.
  • the expression without significantly effecting means that the fluid pressure in the fluid dynamic system remains substantially constant.
  • the regulating system of the invention essentially comprises an intermittently opening and closing fluid flow interruptor in communication with the discharge and suction sides of the pump means and a non-return valve means disposed downstream of the communication between the flow interruptor and the discharge side of the pump means and communicating between the discharge side of the pump means and the fluid dynamic system.
  • the fluid flow interruptor of the regulating system of the invention has a fluid inlet and a fluid outlet, and in the regulating system there is provided conduit means communicating between discharge conduit means, the discharge conduit means communicating with the discharge side of the pump means, and the inlet of the fluid flow interruptor and conduit means communicating between the outlet of the fluid flow interruptor and the reservoir adapted to contain the fluid.
  • the non-return valve means communicates between the discharge conduit means and the fluid dynamic system at a point downstream from the point of communication with the discharge conduit means of the conduit means to the inlet of the fluid flow interruptor. It is to be appreciated that all or any part of the regulating system of the invention may be mounted on or incorporated in the housing of the pump and, by virtue of such an arrangement, be considered to be part of the pump.
  • conduit means and even the tfluid flow interruptor of the regulating system may be provided in the form of structure within the housing of the pump. Accordingly, while for illustrative purposes the conduit means of the regulating system are shown as elongated conduits, these conduit means may in fact constitute any arrangement providing the required communication.
  • a pump 1 for example a gear pump, sucks a fluid (in this instance a liquid) from a reservoir 3 through a suction or inlet conduit 2a and discharges the fluid through a discharge or outlet conduit 2b to a fluid dynamic system 4, in this instance a simple conduit for transportation of the fluid.
  • a short-circuit or recycle conduit 5 communicates between the discharge or pressure side of the pump 1, by communicating with the discharge conduit 2b, and the suction side of the pump 1, by communicating with the reservoir 3.
  • the pump has a shaft 6 and is driven through the shaft 6 by conventional motor and linkage means which are not illustrated.
  • the shaft 6 is provided with a clutch 7 of conventional construction.
  • a non-return valve 8 of conventional construction is disposed to communicate between the discharge conduit 2b, at a point downstream from the short-circuit conduit 5, and the fluid dynamic system 4.
  • the non-return valve 8 includes a spring 9 which is arranged to urge the valve into its seat against the flow from the discharge conduit 2b.
  • the force With which the spring 9 urges the valve into its seat is pre-set so that the valve will not lift from its seat to permit passage of the fluid from the discharge conduit 2b to the fluid dynamic system 4 unless the pressure of the fluid in the discharge conduit 2b downstream from the short-circuit conduit exceeds a certain pre-determined value. It will be clear to those skilled in the art that this arrangement prevents return or reverse throw of the fluid from the fluid dynamic system or to the discharge conduit 2b.
  • a fluid flow interruptor 10 which is adapted to intermittently open and close to intermittently permit and prevent, respectively, flow of the fluid from the discharge side of the pump 1 to the suction side of the pump 1 through the short-circuit conduit 5.
  • the fluid flow interruptor 10 comprises a housing 11 which is closed by a lid 12, a first hollow cylinder 13 having four openings or passages 14 communicating between its interior and its exterior and a second hollow cylinder 15 having four openings or passages 16 communicating between its interior and its exterior.
  • the hollow cylinder 13 is rotatably mounted in the casing 11 and can be engaged by the clutch 7 to be rotated by the shaft 6.
  • the hollow cylinder 13 is fixed to the lid 12, against axial displacement, by the packing 18 :and the retaining ring 19.
  • the hollow cylinder 15 is provided with a feather key 20 which is guided in a keyway 21 in the housing 11. Consequently, the hollow cylinder 15 is fixed against rotation relative to the housing 11 but can be displaced axially.
  • a threaded bore 23 is provided in the base 22 of the hollow cylinder 15 and a threaded spindle 24, having an adjusting lever 25, is provided to engage the threaded bore 23.
  • the threaded spindle 24 is rotatably mounted in the front 26 of the housing 11. By rotating the threaded spindle 24 by means of the lever the hollow cylinder 15 is axially displaced.
  • a fluid inlet passage 27 communicating with an annular chamber or header 28.
  • the hollow cylinder 13 is provided with four radial bores 29 communicating between the annular chamber 28 and an axial channel in the hollow cylinder 13.
  • the axial channel 30 is sealed upstream from the radial bores 29 by means of a stopper 31.
  • the axial channel 30 opens into the inner chamber 32 of the hollow cylinder 13.
  • the passages 14 and 16 are disposed on a common circle so that upon rotation of the hollow cylinder 13 the passages 14 and 16 will periodically come into alignment with each other, whereby a communicating relationship therebetween is established.
  • the passages 16 at all timescornrnunicate with the annular chamber 33 in the housing 11.
  • the fluid flow interruptor 10 is in its closed state or condition, in which closed state flow of the fluid through the conduit 5 from the discharge side of the pump 1 to the suction side of the pump 1 is prevented.
  • the passages 14 and 16 are of triangular cross-section and the triangular cross-section of each of the passages 14 is oriented differently from the triangular cross-section of each of the passages 16.
  • the triangular cross-section of each of the passages 14 is oriented in approximately 180 opposition to the triangular cross-section of each of the passages 16.
  • the triangular cross-sections are arranged symmetrically with respect to the common axis of the hollow cylinders 13 and 15. The purpose of such orientation and disposition of the cross-sections of the passages 14 and 16 is to permit particularly fine adjustment of the duration and magnitude of the open state of the fluid flow interruptor 10 by axial displacement of the hollow cylinder 15.
  • the extent to which the passages 16 align with the passages 14 may be adjusted or regulated.
  • the greater the circumferential distance over which the passages 14 and the passages 16 are in alignment the greater the duration of the open state of the fluid flow interruptor 10.
  • the greater the integral sum of the products of the overlapping areas 37 (shaded) of the cross-sections of the passages 14 and 16 and the differential time intervals during which said overlapping areas exist the greater is the magnitude of the open state of the fluid flow interruptor, i.e., the greater is the volume of flow of liquid through the fluid flow interruptor during its open state.
  • the openings 14 in the hollow cylinder 13 are four in number and are circumferentially spaced from each other by and, likewise, the openings 16 in the hollow cylinder 15 are four in number and are circumferentially spaced from. each other by 90. Accordingly, when the hollow cylinder 13 is interconnected to the shaft 6 by means of the clutch 7 and the hollow cylinder 13 is therefore rotated once for each rotation of the gear wheelof the pump 1, upon each rotation of the hollow cylinder 13 the fluid flow interruptor is in its open state four times because the openings 14 come into alignment with the openings 16 four times. When the openings 14 and the openings 16 are not in alignment, the fluid flow interruptor 10 is in its closed state.
  • the fluid in the discharge conduit 2b immediately upstream from the non-return valve 8 is at a suflicient pressure to lift the valve from its seat and to, accordingly, enter the fluid dynamic system 4.
  • the pressure of the fluid in the discharge conduit 2b immediately upstream from the non-return valve 8 is not of sufficient pressure to lift the valve from its seat and, accordingly, does not enter the fluid dynamic system 4.
  • the rate at which the fluid is delivered from the discharge conduit 2b to the fluid dynamic system 4 is regulated by adjusting the duration and magnitude of the open states of the fluid flow interruptor 10 by means of axially displacing the hollow cylinder 15 to the desired position.
  • the flow of the fluid through the short-circuit conduit 5 does not significantly influence the fluid pressure in the fluid dynamic system 4, because the non-return valve 8 is closed when the fluid is flowing through the short-circuit conduit 5.
  • the only eflect upon the fluid pressure in the fluid dynamic system 4 is a minor, insignificant oscillation.
  • the non-return valve 8 opens the fluid pressure in the fluid dynamic system 4 will momentarily and slightly increase and closes the fluid pressure in the fluid slightly and momentarily decreases.
  • the fluid dynamic system 4 could be considered to begin immediately downstream from the accumulator 38.
  • the accumulator 38 is or is not considered to be disposed in the fluid dynamic system 4; in either case, the accumulator 38 would be part of the regulating system of the invention. It only matters that the accumulator 38 be disposed downstream from and in communication with the non-return valve 8, in order that the accumulator 38 may cooperate with the non-return valve 8 in order to dampen fluid pressure oscillations.
  • a regulating system for regulating as desired the rate of delivery of said fluid from the discharge side of said pump means to said fluid dynamic system without significantly effecting the fluid pressure in said fluid dynamic system
  • said regulating system comprising an intermittently opening and closing fluid flow interruptor having a fluid inlet and a fluid outlet
  • said fluid flow interruptor comprising a first hollow member having at least one passage of triangular cross-section communicating between its interior and its exterior and a second hollow member having at least one passage of triangularcrbsssection communicating between its interior and its exterior, said second hollow member being disposed interiorly of said first hollow member with the triangular cross-section of said at least one passage of said first hollow member being oriented differently from the triangular cross-section of said at least one passage of said second hollow member, one of said hollow members being
  • a regulating system according to claim 1 further comprising an accumulator disposed downstream from and communicating with said non-return valve means.
  • a regulating system according to claim 1 in which the triangular cross-section of said at least one passage of said first hollow member is oriented in approximately opposition to the triangular cross-section of said at least one passage of said second hollow member.
  • a regulating system according to claim 3 further comprising an accumulator disposed downstream from and communicating with said non-return valve means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US542037A 1965-04-17 1966-04-12 Regulating system Expired - Lifetime US3316846A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DED0047071 1965-04-17

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Publication Number Publication Date
US3316846A true US3316846A (en) 1967-05-02

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US542037A Expired - Lifetime US3316846A (en) 1965-04-17 1966-04-12 Regulating system

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US (1) US3316846A (de)
CH (1) CH445300A (de)
DE (1) DE1528401A1 (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3367269A (en) * 1966-09-23 1968-02-06 Walter V. Nelson Booster assembly for low pressure pump
US3650295A (en) * 1970-04-20 1972-03-21 Richard J Smith Rotary valve
FR2339758A1 (fr) * 1976-01-27 1977-08-26 Cyphelly Ivan J Dispositif pour faire varier avec peu de pertes le courant de refoulement d'une pompe a deplacement par interruption periodique de ce courant de refoulement
US4265267A (en) * 1977-08-25 1981-05-05 Cyphelly Ivan J Flow control device for use with positive displacement pump
US4781527A (en) * 1986-03-19 1988-11-01 Sundstand Corporation Cartridge pump
US5285536A (en) * 1991-08-26 1994-02-15 Arthur Long Wave generating system
DE19627438A1 (de) * 1996-07-08 1998-01-15 Danfoss As Anordnung zur Einstellung des Ausgangsdrucks einer durch einen rotierenden Motor angetriebenen Pumpe
US8220488B2 (en) * 2010-07-30 2012-07-17 Mccully Tim Flow control valve with internal isolation means
US10557556B2 (en) * 2011-02-15 2020-02-11 Origin Medical Devices Inc. Variable orifice rotary valves for controlling gas flow

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4329955C2 (de) * 1993-09-04 1997-01-16 Danfoss As Pumpenanordnung für einen Ölbrenner und Verfahren zur Kapazitätsregelung dieses Ölbrenners

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US685510A (en) * 1900-09-06 1901-10-29 Westinghouse Machine Co Air and gas mixing ang governing device for gas-engines.
US2433954A (en) * 1944-01-20 1948-01-06 Clark Equipment Co Fluid pump and control therefor
US2714854A (en) * 1952-03-28 1955-08-09 Oilgear Co System for maintaining accumulator pressures within close limits
GB780191A (en) * 1954-03-26 1957-07-31 Power Jets Res & Dev Ltd Improvements in or relating to control devices for fluid supply systems
US2880760A (en) * 1956-08-24 1959-04-07 Bendix Aviat Corp Harmonic exciter valve
US3049141A (en) * 1959-05-18 1962-08-14 Chrysler Corp Accumulator charging mechanism
US3065699A (en) * 1959-09-10 1962-11-27 Carl F Gromme Low pressure fuel distribution system
US3068793A (en) * 1957-09-04 1962-12-18 S U Carburetter Co Ltd Fuel-injection pumps for compressionignition internal combustion engines
US3157173A (en) * 1961-06-29 1964-11-17 Mono Cam Ltd Fuel injection pumps
US3179053A (en) * 1962-06-15 1965-04-20 Alfonso G Jordan Fuel injector rack setting means

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US685510A (en) * 1900-09-06 1901-10-29 Westinghouse Machine Co Air and gas mixing ang governing device for gas-engines.
US2433954A (en) * 1944-01-20 1948-01-06 Clark Equipment Co Fluid pump and control therefor
US2714854A (en) * 1952-03-28 1955-08-09 Oilgear Co System for maintaining accumulator pressures within close limits
GB780191A (en) * 1954-03-26 1957-07-31 Power Jets Res & Dev Ltd Improvements in or relating to control devices for fluid supply systems
US2880760A (en) * 1956-08-24 1959-04-07 Bendix Aviat Corp Harmonic exciter valve
US3068793A (en) * 1957-09-04 1962-12-18 S U Carburetter Co Ltd Fuel-injection pumps for compressionignition internal combustion engines
US3049141A (en) * 1959-05-18 1962-08-14 Chrysler Corp Accumulator charging mechanism
US3065699A (en) * 1959-09-10 1962-11-27 Carl F Gromme Low pressure fuel distribution system
US3157173A (en) * 1961-06-29 1964-11-17 Mono Cam Ltd Fuel injection pumps
US3179053A (en) * 1962-06-15 1965-04-20 Alfonso G Jordan Fuel injector rack setting means

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3367269A (en) * 1966-09-23 1968-02-06 Walter V. Nelson Booster assembly for low pressure pump
US3650295A (en) * 1970-04-20 1972-03-21 Richard J Smith Rotary valve
FR2339758A1 (fr) * 1976-01-27 1977-08-26 Cyphelly Ivan J Dispositif pour faire varier avec peu de pertes le courant de refoulement d'une pompe a deplacement par interruption periodique de ce courant de refoulement
US4164240A (en) * 1976-01-27 1979-08-14 Cyphelly Ivan J Device for low-loss variation of flow from a positive displacement pump by periodic interruption of the flow
US4265267A (en) * 1977-08-25 1981-05-05 Cyphelly Ivan J Flow control device for use with positive displacement pump
US4781527A (en) * 1986-03-19 1988-11-01 Sundstand Corporation Cartridge pump
US5285536A (en) * 1991-08-26 1994-02-15 Arthur Long Wave generating system
DE19627438A1 (de) * 1996-07-08 1998-01-15 Danfoss As Anordnung zur Einstellung des Ausgangsdrucks einer durch einen rotierenden Motor angetriebenen Pumpe
DE19627438C2 (de) * 1996-07-08 1998-04-23 Danfoss As Anordnung zur Einstellung des Ausgangsdrucks einer durch einen rotierenden Motor angetriebenen Pumpe
US8220488B2 (en) * 2010-07-30 2012-07-17 Mccully Tim Flow control valve with internal isolation means
US10557556B2 (en) * 2011-02-15 2020-02-11 Origin Medical Devices Inc. Variable orifice rotary valves for controlling gas flow

Also Published As

Publication number Publication date
DE1528401A1 (de) 1969-07-10
CH445300A (de) 1967-10-15

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