EP0075618A1 - Arrangement de contrôle d'un circuit de fluide sous pression - Google Patents

Arrangement de contrôle d'un circuit de fluide sous pression Download PDF

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Publication number
EP0075618A1
EP0075618A1 EP81304425A EP81304425A EP0075618A1 EP 0075618 A1 EP0075618 A1 EP 0075618A1 EP 81304425 A EP81304425 A EP 81304425A EP 81304425 A EP81304425 A EP 81304425A EP 0075618 A1 EP0075618 A1 EP 0075618A1
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EP
European Patent Office
Prior art keywords
fluid
pistons
fluid pressure
arrangement according
control arrangement
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.)
Withdrawn
Application number
EP81304425A
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German (de)
English (en)
Inventor
John Harbidge
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.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to EP81304425A priority Critical patent/EP0075618A1/fr
Publication of EP0075618A1 publication Critical patent/EP0075618A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L33/00—Rotary or oscillatory slide valve-gear or valve arrangements, specially adapted for machines or engines with variable fluid distribution
    • F01L33/02—Rotary or oscillatory slide valve-gear or valve arrangements, specially adapted for machines or engines with variable fluid distribution rotary
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1176—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
    • F04B9/1178—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor the movement in the other direction being obtained by a hydraulic connection between the liquid motor cylinders

Definitions

  • This invention relates to the control of one or more fluid pressure (e.g. hydraulic) circuits especially a high pressure circuit or circuits where the latter is or are operated by at least one low pressure circuit (or vice versa) via a pump such as a fluid pressure transformer, e.g. of the differential piston kind.
  • a fluid pressure transformer e.g. of the differential piston kind.
  • the object of the invention is to provide an improved circuit control arrangement whereby control of fluid at high pressure and/or of a difficult nature t p handle can be readily effected. Practical advantages of the invention in this and other respects will be apparent from the following disclosure.
  • a fluid pressure circuit control arrangement comprises an input control circuit operable for controlling the supply of fluid under pressure to distributor valve means for distributing said fluid to cylinders containing operating pistons of a piston pump (such as a fluid pressure transformer of the differential piston kind) whereby one or more fluid output circuits supplied by the pump or transformer can be controlled by said input control circuit.
  • a piston pump such as a fluid pressure transformer of the differential piston kind
  • the general circuit arrangement comprises a low pressure input control circuit 4 for supplying fluid at low pressure to the differential piston and cylinder units 22 of a pump or fluid pressure transformer 1 via a distributor valve 5 controlling the supply of fluid to the cylinders 2 of the units 22 so as to act upon the large diameter operating pistons 3 of the latter in an appropriate sequence of operation.
  • Each piston 3 is shown connected in a compound manner by a piston rod 11 to a corresponding small diameter operated piston 13 in a cylinder 12 of each unit 22.
  • the distributor valve 5 is shown having a rotary action in which a rotatable valve member 50 operates in relation to ports 52 in the valve chamber 51, each port 52 being communicated with a corresponding cylinder 2. That part of the valve chamber 51 about the valve member 50 is supplied at 53 with fluid from the low pressure output of the control circuit 4, the hollow interior 500 of the valve member 50 being in constant exhaust communication with a reservoir 45 via the outlet port 54.
  • the direction of rotation of the valve member 50 is indicated for the sequence of piston operation shown but rotation in the opposite direction is possible with a corresponding sequence of operation (see FIGURE 4).
  • each unit 22 containing a small diameter operated piston 13 is communicated through non-return valve means 7 with a high pressure output circuit 8 for circulation of fluid at high pressure for any required purpose.
  • Each unit 22 is shown connected in a common high pressure circuit 8 but they may be connected to individual output circuits or in any desired grouped arrangement.
  • the low pressure input circuit 4 includes a pump 44 which may be of variable speed and/or variable capacity for supplying fluid to the distributor valve 5, the circuit 4 also including the reservoir 45.
  • control valve means 40 shown consisting of a shut-off valve 41 and a variable flow or relief valve 42 connected across the output and return flow lines of the low pressure circuit 4.
  • valves 41,42 are shown by way of typical example only and one or more valves may be employed according to requirements.
  • the shut-off and variable relief valves 41, 42 may be incorporated in one valve unit or provided by a single valve.
  • control of low pressure fluid flow by the control valve means 40 to the transformer 1 via the distributor valve 5 in turn effects fluid flow in the high pressure circuit 8 (or circuits).
  • the shut-off valve 41 is opened then the distributor valve 5 is by-passed and so becomes inoperative so that no fluid flow occurs in the high pressure circuit 8.
  • setting of the variable relief valve 42 results in corresponding operation of the transformer 1 and likewise corresponding fluid flow in the high pressure circuit 8.
  • control valves of simple and inexpensive construction at 40 in the low pressure circuit 4 for effecting control of fluid flow in the separate high pressure circuit 8 (or circuits) where otherwise valves of specialised and expensive construction would be necessary in the latter.
  • the remote control afforded in this way also has advantage where fluid in the circuit 8 (or circuits) is of a difficult nature to handle, (e.g. an acid or other corrosive or dangerous liquid or gas) which again would otherwise entail highly specialised control valve means.
  • Return or suction stroke movement of the inter-connected pistons 3, 13 may be assisted by return springs 21 and/or by fluid pressure operation which is also shown in FIGURE 1.
  • the volumetric space 23 in the cylinder bores 2, 12 between the large and small diameter pistons 3, 13 and about the piston rod 11 is communicated at 26 with a corresponding space 23 of a next or second cylinder unit 22 and which in turn is communicated in a similar manner with the space 23 of the third cylinder unit 22.
  • the space 23 of one of the cylinder units 22 such as the third unit shown in FIGURE 1, is arranged to be supplied via a non-return inlet valve 24 with hydraulic fluid whereby all three spaces 23 are filled with a required quantity of fluid for the purpose and at a suitable pressure determined by a relief valve 25 also shown communicated with the space 23 of the third cylinder unit 22.
  • the volumes 23 are varied with displacement of fluid from one to the other and for effecting appropriate piston return movement.
  • the volume of the associated space or spaces 23 of whatever pistons 3, 13 are performing a power stroke movement must equal the space volume at 23 of whatever pistons 3, 13 are performing a return stroke. In this way the volumes of the spaces 23 corresponds to piston movement and maintains a substantially constant total volume.
  • Such fluid pressure operated return of the pistons 3, 13 may obviate the need for return springs 21 although such springs can be provided as auxiliary means of piston return.
  • a suitable volumetric space 230 entrapped between the flanges 63, 613 receives hydraulic or other suitable fluid and these spaces 230 which are variable in volume are communicated with one another at 26 in the manner already described so as to effect piston return also as described.
  • FIGURE 3 a similar arrangement is shown but where the large diameter piston 3 is operated by the small diameter piston 13 of each cylinder unit 22 from a distributor valve. In such case it is desirable to provide a large diameter area for effecting return movement of the small diameter piston 13 by displacement of fluid from another similar or identical cylinder unit 22 via the communicating passage 26.
  • a tubular member 70 about the connecting rod 11 is provided having outwardly directed flanges 73, 713 provided with sealing rings 74 co-operating with corresponding bores 27, 217 therefor of the cylinder unit 22 whereby a volumetric space 237 is entrapped between the flanges 73, 713.
  • Displacement of fluid into the volumetric space 237 acts between the shoulder 227 between the bores 27 and 217 and the flange 713 to effect return movement of the small diameter piston 13 (and the large diameter piston 3 therewith) and vice versa.
  • Passageways 80, 81 vent variable air spaces 280, 281 to atmosphere.
  • each inter-connected pair of pistons 3, 13 is connected by a further connecting or piston rod 33 to a corresponding pair of inter-connected pistons 3', 13' in a complementary or opposed manner so as to provide a balanced double acting arrangement.
  • each opposed pair of larger pistons 3, 3' are connected by the central piston rod 33.
  • the cylinders 2, 2' containing the large diameter operating pistons 3, 3' are supplied by fluid under pressure from the distributor valve 5 of which each port 52 is communicated with a corresponding cylinder 2 or 2' of the units 22, 22'.
  • piston return movement is positively obtained without the need for return springs or other provision such as special fluid pressure operation for return purposes. Furthermore the operating capacity of the pump or transformer is increased,(e.g. doubled) yet can still remain a compact arrangement.
  • the cylinders 12' are shown communicated via non-return valves 7' with a high pressure output circuit 8'.
  • the circuits 8, 8' may be separate or communicated with a common output or again the cylinders 12, 12' may be communicated with individual output or circuits l in any desired grouped arrangement.
  • the double acting arrangement shown in FIGURE 4 is controlled by the low pressure circuit 4 via the distributor valve 5 in the same manner as that already described with reference to FIGURE 1 and with the same practical advantages.
  • the relative diameter of the pistons 3,13 or 3', 13' may be varied according to fluid pressure transformation requirements or, in some cases, with the advantages referred to above, may be of the same diameter.
  • FIGURE 5 a modified form of transformer 1 is shown in which a differential piston action is obtained due to the difference in effective surface area bf opposite sides of a piston 30, 30' in each cylinder 20, 20'.
  • the pistons 30, 30' are connected by a connecting or piston rod 33 so that as one piston performs a power stroke the other performs a return or suction stroke or vice versa and low pressure fluid is admitted at the appropriate time into each cylinder 20, 20' from the distributor valve 5 which in turn is supplied by the control circuit 4 in the manner already described.
  • the low pressure fluid acts on the unrestricted face or head 303 of a piston 30 or 30' so that the other face 313 of reduced effective area (i.e. less the cross-sectional area of the piston rod 33) expels fluid at increased pressure from the cylinder 20 or 20' to the output circuits8 or 8' via the appropriate non-return valve 7 or 7'.
  • control circuit 4 in which the control valve means 40, viz: the shut-off valve 41 and variable relief valve 42 (or a single valve providing such functions) act directly in line with the distributor valve inlet 53 and the pump 44 for controlling the operation of the distributor valve 5 and hence the output from the circuit 8 or circuits 8, 8'.
  • the control valve means 40 viz: the shut-off valve 41 and variable relief valve 42 (or a single valve providing such functions) act directly in line with the distributor valve inlet 53 and the pump 44 for controlling the operation of the distributor valve 5 and hence the output from the circuit 8 or circuits 8, 8'.
  • the control valve means 40 viz: the shut-off valve 41 and variable relief valve 42 (or a single valve providing such functions) act directly in line with the distributor valve inlet 53 and the pump 44 for controlling the operation of the distributor valve 5 and hence the output from the circuit 8 or circuits 8, 8'.
  • variable speed and/or variable capacity pump 44 can be utilised to control the supply of fluid to the distributor valve 5, i.e. alternatively or additionally to the control valve means 40.
  • the distributor valve 5 operates in an independent manner in that it is not controlled by movement or position of any of the pistons 3, 13; 3',13'; or 30, 30' of the transformer 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP81304425A 1981-09-25 1981-09-25 Arrangement de contrôle d'un circuit de fluide sous pression Withdrawn EP0075618A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP81304425A EP0075618A1 (fr) 1981-09-25 1981-09-25 Arrangement de contrôle d'un circuit de fluide sous pression

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP81304425A EP0075618A1 (fr) 1981-09-25 1981-09-25 Arrangement de contrôle d'un circuit de fluide sous pression

Publications (1)

Publication Number Publication Date
EP0075618A1 true EP0075618A1 (fr) 1983-04-06

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP81304425A Withdrawn EP0075618A1 (fr) 1981-09-25 1981-09-25 Arrangement de contrôle d'un circuit de fluide sous pression

Country Status (1)

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EP (1) EP0075618A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1986003560A1 (fr) * 1984-12-12 1986-06-19 Birdwell J C Pompe a boue
WO1986004383A2 (fr) * 1985-01-16 1986-07-31 Birdwell J C Moyen fluide de transmission de donnees
US4676724A (en) * 1981-10-08 1987-06-30 Birdwell J C Mud pump
US4784579A (en) * 1986-12-19 1988-11-15 Allied-Signal Inc. Hydraulic-pneumatic power transfer unit
EP0365805A2 (fr) * 1988-10-22 1990-05-02 Karl Eickmann Dispositif pour le réglage du courant et pompe à haute pression
WO2004111452A1 (fr) * 2003-06-13 2004-12-23 Dietmar Kaiser Ag Pompe haute pression
EP1985866A1 (fr) * 2007-04-26 2008-10-29 Services Pétroliers Schlumberger Distributeur rotatif pour multiplicateur de pression

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH224724A (de) * 1941-11-19 1942-12-15 Sulzer Ag Pumpanlage zur Förderung von Flüssigkeiten auf hohen Druck.
US2442916A (en) * 1945-11-05 1948-06-08 J D Buchanan Hydraulic booster
US3022738A (en) * 1959-04-20 1962-02-27 Krute Everett Archie Pump systems
CH364395A (de) * 1957-10-19 1962-09-15 Inst Werkzeugmaschinen Verfahren und Vorrichtung zur Steuerung der Bewegung eines durch ein Druckmedium bewegten Kolbens
US3295451A (en) * 1965-11-10 1967-01-03 James E Smith Hydraulic power converter
US3312172A (en) * 1964-12-02 1967-04-04 Albert W Vaudt Switching valve
GB1068865A (en) * 1964-04-14 1967-05-17 Royal Industries Improvements in or relating to pumps
FR1488575A (fr) * 1965-09-14 1967-07-13 Sulzer Ag Dispositif pour l'injection du carburant dans un moteur à combustion interne à pistons
US3662652A (en) * 1971-01-21 1972-05-16 Halliburton Co Hydraulically powered power unit
GB1406861A (en) * 1971-09-25 1975-09-17 Walter Gmbh Hellmuth Metering pumps
US3976401A (en) * 1975-01-02 1976-08-24 Mountain Donald C Pump for abrasive slurries and the like
GB1599411A (en) * 1978-03-10 1981-09-30 Harbidge J Fluid pressure circuit control arrangement
GB1599524A (en) * 1978-03-10 1981-10-07 Harbridge J Fluid pressure transformer

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH224724A (de) * 1941-11-19 1942-12-15 Sulzer Ag Pumpanlage zur Förderung von Flüssigkeiten auf hohen Druck.
US2442916A (en) * 1945-11-05 1948-06-08 J D Buchanan Hydraulic booster
CH364395A (de) * 1957-10-19 1962-09-15 Inst Werkzeugmaschinen Verfahren und Vorrichtung zur Steuerung der Bewegung eines durch ein Druckmedium bewegten Kolbens
US3022738A (en) * 1959-04-20 1962-02-27 Krute Everett Archie Pump systems
GB1068865A (en) * 1964-04-14 1967-05-17 Royal Industries Improvements in or relating to pumps
US3312172A (en) * 1964-12-02 1967-04-04 Albert W Vaudt Switching valve
FR1488575A (fr) * 1965-09-14 1967-07-13 Sulzer Ag Dispositif pour l'injection du carburant dans un moteur à combustion interne à pistons
US3295451A (en) * 1965-11-10 1967-01-03 James E Smith Hydraulic power converter
US3662652A (en) * 1971-01-21 1972-05-16 Halliburton Co Hydraulically powered power unit
GB1406861A (en) * 1971-09-25 1975-09-17 Walter Gmbh Hellmuth Metering pumps
US3976401A (en) * 1975-01-02 1976-08-24 Mountain Donald C Pump for abrasive slurries and the like
GB1599411A (en) * 1978-03-10 1981-09-30 Harbidge J Fluid pressure circuit control arrangement
GB1599524A (en) * 1978-03-10 1981-10-07 Harbridge J Fluid pressure transformer

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4676724A (en) * 1981-10-08 1987-06-30 Birdwell J C Mud pump
WO1986003560A1 (fr) * 1984-12-12 1986-06-19 Birdwell J C Pompe a boue
WO1986004383A2 (fr) * 1985-01-16 1986-07-31 Birdwell J C Moyen fluide de transmission de donnees
WO1986004383A3 (fr) * 1985-01-16 1986-09-12 J C Birdwell Moyen fluide de transmission de donnees
AU590251B2 (en) * 1985-01-16 1989-11-02 J.C. Birdwell Fluid means for data transmission
US4784579A (en) * 1986-12-19 1988-11-15 Allied-Signal Inc. Hydraulic-pneumatic power transfer unit
EP0365805A2 (fr) * 1988-10-22 1990-05-02 Karl Eickmann Dispositif pour le réglage du courant et pompe à haute pression
EP0365805A3 (fr) * 1988-10-22 1990-12-05 Karl Eickmann Dispositif pour le réglage du courant et pompe à haute pression
WO2004111452A1 (fr) * 2003-06-13 2004-12-23 Dietmar Kaiser Ag Pompe haute pression
EP1985866A1 (fr) * 2007-04-26 2008-10-29 Services Pétroliers Schlumberger Distributeur rotatif pour multiplicateur de pression

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