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WO1992002713A1 - Systeme de transmission alternatif - Google Patents

Systeme de transmission alternatif Download PDF

Info

Publication number
WO1992002713A1
WO1992002713A1 PCT/GB1991/001218 GB9101218W WO9202713A1 WO 1992002713 A1 WO1992002713 A1 WO 1992002713A1 GB 9101218 W GB9101218 W GB 9101218W WO 9202713 A1 WO9202713 A1 WO 9202713A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
drive apparatus
valve
spool
low pressure
Prior art date
Application number
PCT/GB1991/001218
Other languages
English (en)
Inventor
Andrew Clayson
Original Assignee
Pacson Ltd.
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 Pacson Ltd. filed Critical Pacson Ltd.
Priority to JP91512818A priority Critical patent/JPH05508898A/ja
Publication of WO1992002713A1 publication Critical patent/WO1992002713A1/fr

Links

Classifications

    • 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
    • F04B9/103—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 only one pumping chamber
    • F04B9/105—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 only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • 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
    • F01L21/00—Use of working pistons or pistons-rods as fluid-distributing valves or as valve-supporting elements, e.g. in free-piston machines
    • F01L21/04—Valves arranged in or on piston or piston-rod

Definitions

  • This invention relates to reciprocating drive apparatus.
  • the invention is concerned especially, but not exclusively, with hydraulic reciprocating drive apparatus in combination with a hydraulic pump.
  • pressure intensifier is used for the combination of a hydraulic reciprocating drive operable by means of hydraulic fluid from a relatively low pressure source with a hydraulic pump dimensioned and arranged to deliver relatively high pressure hydraulic fluid.
  • Hydraulic reciprocating drives comprising a piston-and-cylinder assembly for double-acting operation, and control valve means operable to direct hydraulic fluid from a source of fluid under pressure alternately to the opposite sides of the piston of the said assembly thereby to obtain a reciprocating drive.
  • the control valve means includes piston end-of-stroke detecting means deployed to effect automatic regular operation of the control valve means.
  • Such drives hitherto have the disadvantages that they involve relatively numerous components and complex assembly, costly to manufacture and maintain.
  • An object of the present invention is to provide a hydraulic reciprocating drive apparatus of improved design whereby the aforementioned disadvantages are obviated or mitigated.
  • a reciprocating drive apparatus comprising a piston-and-cylinder assembly for double-acting operation, and control valve means mounted in the body of the piston and operable to direct fluid from a source of fluid under pressure alternately to the opposite sides of the piston of said assembly; characterised in that the said valve means comprises mutually separate valves of which one is adapted to be operable by pressure fluid and is arranged for reversing the action of the piston and the other is a pilot valve arranged for controlling the action of the reversing valve.
  • Fig. 1 is a sectional elevation on two different planes showing a hydraulic reciprocating drive apparatus in accordance with the present invention, combined with a double-acting high pressure piston-and-cylinder assembly;
  • Fig. 2 is a sectional end elevation on the line II-II in Fig. 1;
  • Fig. 3 is a sectional end elevation on the line III-III in Fig. 1;
  • Fig. 4 is a cross-sectional partial plan view on the line IV-IV in Fig. 2.
  • a pressure intensifier consists of a relatively low pressure piston-and-cylinder assembly (drive apparatus) which is indicated generally by reference numeral 10 surrounding a relatively high pressure piston-and-cylinder assembly which is indicated generally by reference numeral 11.
  • the low pressure assembly 10 has a cylinder 12 with end caps 13 and 14, and a low pressure piston 15 reciprocable within the cylinder 12 between the end caps 13, 14.
  • the high pressure assembly 11 has a cylinder 16 and a high pressure piston 17 which is directly connected with the low pressure piston 15 by means of a piston rod 18 which extends through sets of seals 19 which serve to keep the low pressure and high pressure systems mutually separate.
  • the swept volume on the right hand side of the high pressure piston 17 is approximately twice that on the left hand side of that piston for the reason explained hereinafter.
  • the low pressure cylinder 12 is provided with an inlet port 20 and an associated hydraulic coupling socket 21 for connection to a source of hydraulic drive fluid at relatively low pressure.
  • the cylinder 12 is provided also with an exhaust port 22 and an associated hydraulic coupling socket 23 for connection with a return fluid reservoir (not shown) .
  • the low pressure piston 15 has three axially spaced lands 24, 25 and 26 each provided with an annular seal or piston ring. Between these lands 24, 25 and 26, the piston 15 outer wall surface defines two galleries 27 and 28, the arrangement being such that for all positions of the piston 15 the gallery 27 always communicates with the inlet port 20, and the gallery 28 always communicates with the exhaust port 22.
  • the low pressure piston 15 carries control valve means operable to direct hydraulic fluid entering the inlet port 20 alternately to the opposite sides of the piston 15.
  • the control valve means consists of a main directional control valve or "reversing" valve 29 and an end-of-stroke-detecting pilot valve 30.
  • the valves 29 and 30 are in communication with the galleries 27 and 28 by way of ports 31, 32, 33 and 34 in the low pressure piston 15.
  • the main directional control valve 29 consists of a ported sleeve 35 which is located in a bore 36 between fixed end caps 37, and a reciprocable spool 38.
  • the bore 36 extends through the low pressure piston 15 parallel with the central axis of the piston.
  • the spool 38 defines annular galleries A, B, C, D and E of which galleries B and D are in communication with a blind-end core 39 which opens to the left hand side only of the low pressure piston 15.
  • the galleries A and E are in communication with the pilot valve 30 by way of passages 40 and 41 which extend through the body of the low pressure piston 15.
  • the passages 40, 41 are represented by broken lines.
  • the valves 29 and 30 are side by side as shown in Fig. 2, and the passages 40 and 41 are straight drillings or may be a feature of a casting mould for the low pressure piston.
  • the spool 38 is guided and located co-axially with respect to the sleeve 35 by means of the end caps 37; and an annular clearance of the order of 0.025 mm is provided between the lands on the spool 38 and the bore of the sleeve 35 to obviate or mitigate seizure.
  • the pilot valve 30 consists of a ported sleeve 42 which is located in a bore 43 between circlips 44, and a reciprocable spool 45 located and guided by fixed end-caps 45A.
  • the spool 45 is provided with galleries F, G, H and I of which galleries F, G and I communicate with a central passage 46 which is closed at each end of the spool 45 by means of plunger heads 47 for contacting the end caps 13 and 14 to effect reversing action of the pilot valve 30 as explained later in this description.
  • the bore 43 extends through the body of the low pressure piston 15 parallel with the central axis.
  • the pilot spool 45 similarly to the main spool 38, is clear of its sleeve 42 by an annular clearance of the order of 0.025 mm to obviate or mitigate seizure.
  • the high pressure cylinder 16 is located in the end cap 14 by a flange-and-recess configuration, and is associated with a valve block 48 which is secured to the end cap 14 by means of screws one of which is shown at 49.
  • the body of the high pressure cylinder 16, as seen in Fig. 4, is provided with passages which communicate with passages in the valve block 48.
  • passage 50 in the valve block 48 conveys hydraulic fluid to and from the right hand end of the high pressure cylinder; passage 51 in the body of the high pressure cylinder 16 conveys hydraulic fluid to and from the left hand side of the high pressure cylinder and connects with passage 52 in the cylinder block 48; and passage 53 in the body of the high pressure cylinder 16 provides drainage for hydraulic fluid leakage between seals 19 and connects with passage 54 in the valve block 48.
  • valve block 48 there is provided an assembly of three check valves 55, 56 and 57.
  • the check valve 55 is arranged to pass low pressure hydraulic fluid from an inlet to the valve block 48 to the passage 50 for supplying hydraulic fluid to the right hand side of the high pressure piston 17.
  • the check valve 56 is arranged to pass high pressure hydraulic Uiid from the passage 50 both to the passage 52 and to the intake side of the check valve 57 which passes fluid to a high pressure fluid outlet of the valve block 48.
  • the main directional control valve 29 is bistable and therefore low pressure hydraulic fluid introduced through the inlet port 20 will gain access either to gallery B or gallery C and so quickly establish a preferred initial direction of the low pressure piston 15.
  • Fluid in gallery B gains access to the left hand side of piston 15 by way of open core 39; and hydraulic fluid in gallery C gains access to the right hand side of low pressure piston 15 by way of a port Cl and a central recessed portion 58 of the low pressure piston 15.
  • the recessed portion 58 is clear of the high pressure piston-and-cylinder assembly 11 permitting fluid flow between the recess 58 and the right hand side of the piston 15.
  • the low pressure piston-and-cylinder assembly 10 will continue to operate as a hydraulic reciprocating drive so long as low pressure fluid is supplied through the inlet port 20.
  • the low pressure piston-and-cylinder assembly 10 may be used to drive other than a high pressure hydraulic pump.
  • a reciprocating drive apparatus in accordance with the present invention can use compressed gas e.g. compressed air as the driving medium with appropriately reduced annular clearances in the reversing and pilot valves.
  • the pilot spool plunger heads may contact stops or adjustable stops other than the end caps of the cylinder 12.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Dans un dispositif d'intensification de pression hydraulique, une pompe hydraulique à haute pression (16, 17) est actionnée par un système alternatif de transmission hydraulique (10) dans lequel un piston de commande alternatif à basse pression (15) comporte un moyen de soupapes de commande (29, 30) servant à diriger un fluide depuis une source de fluide sous pression, alternativement vers les côtes opposés du piston à basse pression. Le moyen de soupapes de commande (29, 30) comprend des soupapes séparées réciproquement, parmi lesquelles une (29) est conçue pour s'actionner sous la pression du fluide ainsi que pour inverser l'action du piston (15). L'autre soupape (30) est une vanne pilote conçue pour commander l'action de la soupape d'inversion (29). L'action de celle-ci est bistable et s'effectue sur une période relativement courte tandis que l'action de la vanne pilote (30) s'effectue à la vitesse du déplacement du piston à basse pression (15). Une caractéristique du système de transmission à basse pression (10) est l'absence de joints dynamiques dans la soupape d'inversion (29) et la vanne pilote (30).
PCT/GB1991/001218 1990-08-02 1991-07-22 Systeme de transmission alternatif WO1992002713A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP91512818A JPH05508898A (ja) 1990-08-02 1991-07-22 往復動駆動装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB909016965A GB9016965D0 (en) 1990-08-02 1990-08-02 Hydraulic reciprocating drive apparatus
GB9016965.7 1990-08-02

Publications (1)

Publication Number Publication Date
WO1992002713A1 true WO1992002713A1 (fr) 1992-02-20

Family

ID=10680054

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1991/001218 WO1992002713A1 (fr) 1990-08-02 1991-07-22 Systeme de transmission alternatif

Country Status (4)

Country Link
EP (1) EP0541644A1 (fr)
JP (1) JPH05508898A (fr)
GB (1) GB9016965D0 (fr)
WO (1) WO1992002713A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020167108A1 (fr) 2019-02-14 2020-08-20 DE LA PAZ AGUIRRE, Jaime Système d'augmentation de l'efficacité énergétique pour des dispositifs hydrauliques
WO2023080771A1 (fr) 2021-11-03 2023-05-11 Olvera Alvarez Bernadette Système amplificateur de puissance hydraulique

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4348161A (en) * 1980-03-15 1982-09-07 Tsugio Shibata Pressure converting apparatus
FR2588316A1 (fr) * 1985-10-09 1987-04-10 Hydroem Verin hydraulique alternatif

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4348161A (en) * 1980-03-15 1982-09-07 Tsugio Shibata Pressure converting apparatus
FR2588316A1 (fr) * 1985-10-09 1987-04-10 Hydroem Verin hydraulique alternatif

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020167108A1 (fr) 2019-02-14 2020-08-20 DE LA PAZ AGUIRRE, Jaime Système d'augmentation de l'efficacité énergétique pour des dispositifs hydrauliques
WO2023080771A1 (fr) 2021-11-03 2023-05-11 Olvera Alvarez Bernadette Système amplificateur de puissance hydraulique

Also Published As

Publication number Publication date
GB9016965D0 (en) 1990-09-19
EP0541644A1 (fr) 1993-05-19
JPH05508898A (ja) 1993-12-09

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