EP0087794A2 - Hydraulische Versorgungseinheit - Google Patents

Hydraulische Versorgungseinheit Download PDF

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Publication number
EP0087794A2
EP0087794A2 EP83101948A EP83101948A EP0087794A2 EP 0087794 A2 EP0087794 A2 EP 0087794A2 EP 83101948 A EP83101948 A EP 83101948A EP 83101948 A EP83101948 A EP 83101948A EP 0087794 A2 EP0087794 A2 EP 0087794A2
Authority
EP
European Patent Office
Prior art keywords
pump
power unit
tank
hydraulic
mouth
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.)
Granted
Application number
EP83101948A
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English (en)
French (fr)
Other versions
EP0087794A3 (en
EP0087794B1 (de
Inventor
Gian Luigi Gamberini
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 AT83101948T priority Critical patent/ATE24027T1/de
Publication of EP0087794A2 publication Critical patent/EP0087794A2/de
Publication of EP0087794A3 publication Critical patent/EP0087794A3/en
Application granted granted Critical
Publication of EP0087794B1 publication Critical patent/EP0087794B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • This invention relates to a hydraulic power unit particularly adapted for hydraulic circuits for activating double-acting hydraulic actuators or reversible-movement users, and comprising a pump, a tank for the hydraulic liquid and valves for connecting the pump to the tank.
  • the invention aims to provide a hydraulic power unit of the specified type permitting to selectively activate in either direction reversible-movement users, for example double-acting hydraulic actuators, and to readily reverse the direction of operation even without a sliding valve, said power unit being of easy and economical construction while ensuring high reliability and long duration, as well as extremely reduced dimensions, whereby it can be advantageously used in all circumstances where space problems are to be solved.
  • the pump is of reversible type and may be selectively activated in either direction, for example by means of a reversible electric motor, while two mouths of the pump, each of which can operate alternately as a suction mouth and as a delivery mouth, are each connected or connectible at one side to the user and at the other side to the hydraulic liquid tank, either by means of an associated unidirectional valve which opens only in the direction of the flow from the tank to the respective mouth, or - in parallel with said unidirectional valve - by means of an associated automatic pressure relief valve.
  • the unidirectional and/or pressure relief valves are so constructed as to permit a limited seepage of hydraulic liquid towards the tank in the closure direction of the unidirectional valves and in the closure position of the pressure relief valves.
  • Hydraulic liquid is sent to the user from one of the mouths of the pump, operating as a delivery mouth, while the other one, operating as a suction mouth sucks and receives the hydraulic liquid returned from the user.
  • the flowrate of the delivery hydraulic liquid is substantially the same as the flowrate of the returned hydraulic liquid, in either operative directions, in the power unit according to the invention the hydraulic liquid tank substantially has the only purpose of compensating for any possible small differences of flowrate between the hydraulic liquid delivered to the user and that returned from the user.
  • the hydraulic liquid tank of the power unit according to the invention may be very small, i.e. of minimum dimensions, and it may be easily integrated with the power unit.
  • the two mouths of the reversible pump communicate with two annular circuits which are parallelly connected either to the hydraulic liquid tank by a common connecting conduit, and to the user by means of two connecting conduits operating alternately, one as a delivery conduit and the other as a return conduit, and vice versa, the two unidirectional valves being interposed in one of these annular circuits and the pressure relief valves in the other annular circuit, at opposite sides of the common connecting conduit to the hydraulic liquid tank.
  • the two mouths of the reversible pump of the power unit according to the invention may be connected directly to said user, each through a corresponding connection conduit, for example, to the hydraulic actuating cylinder on two opposite sides of its piston.
  • the reversible pump of the power unit is just to be activated in either direction by specifically selecting the corresponding direction of rotation of the respective actuating electric motor.
  • the activation of the actuating cylinder in either direction is immediate, in that said cylinder is connected to the pump of the power unit by means of a hydraulic circuit always completely full of oil which is pressurized immediately.
  • the power unit according to the invention comprises also a hydraulic distributor which is interposed between the two mouths of the reversible pump and the two connecting conduits communicating with opposite ends of the user, for example with a double-acting actuating cylinder at opposite sides of its piston, said distributor being urged by return springs towards an intermediate closure and locking position, wherein it will shut off the communication between the two mouths of the pump and the two communication conduits to the user, keeping the latter in its position, while it is alternately moved in either direction by a pilot pressure derived from the mouth of the pump acting as a delivery mouth, and is thus moved into either of two opening and actuating positions, wherein it connects the two mouths of the pump to the two connecting conduits
  • a preferred embodiment of the power unit according to the invention is characterized in that the pump is received and enclosed in the recess formed between two halves of the body of the power unit and used as a tank for the hydraulic liquid, one of said halves of the body of the power unit being secured to the flange of a reversible electric motor coupled to the pump, while the other half of the body of the pump contains the two unidirectional valves, the two pressure relief valves, the possible hydraulic distributor, the ducts connecting the various portions of the power unit and the connectors for the ducts for connection to the user.
  • This embodiment is of great constructional simplicity, and of extremely small dimensions.
  • the reversible pump is constituted by a grear pump, while the two halves of the body of the power unit constitute the two opposed covers of the body of the pump at both sides of the pair of gears and extend radially beyond the outline of the body of the pump and are peripherally sealingly connected to each other by means of a ring member so as to form the hydraulic liquid tank around the pump.
  • the illustrated power unit is designed to operate a hydraulic circuit for activating, for example, a double-acting hydraulic actuating cylinder (not shown).
  • the power unit comprises an oil tank H and a reversible oil pump A, that is a pump capable of delivering oil when actuated in either direction.
  • said reversible pump A is constituted by a gear pump.
  • the two mouths B and B' of this reversible pump A therefore, can each operate, alternately, as a delivery mouth and as a suction mouth.
  • the pump A is activated by a reversible electric motor 1, either D.C.-operated or A.C.-operated, of which the direction of rotation may be selected, for example, by means of an electric switch (not shown).
  • the two mouths B and B' of the reversible pump A are connected to an oil tank H, each through the associated branch D and D' of an annular circuit communicating with the tank H through a common communication conduit G.
  • a unidirectional valve F and P' Interposed in each branch D, D' of said circuit, at opposite sides of their common conduit G for communication with the oil tank H, is a unidirectional valve F and P' which opens in the direction of flow from the oil tank toward the respective mouth B or B' of the pump A, while it closes in the opposite direction.
  • the two unidirectional valves F, F' also prevent the oil delivered through a mouth B or B' of the pump A from reaching the other mouth B' or B.
  • the two mouth B, B' of the pump A are also connected each to the associated branch M and M' of a second annular circuit, parallel to the first annular circuit D, D' and communicating with the oil tank H through the same communication conduit G, to which it is connected at N.
  • an automatic pressure relief valve L, L' Interposed in each branch M, M' of said second circuit is an automatic pressure relief valve L, L' designated also "maximum pressure valve".
  • the oil tank H communicates with a filling or connection conduit P the pouth of which is closed by a plug Q.
  • each mouth B and B' of the pump A is connected to the hydraulic actuating cylinder by a respective conduit C, C * derived from the respective branch D, D' of the first annular circuit.
  • the unidirectional valves F, F' are designed so that, though opening in the direction of flow from the tank H to the associated mouth B, B' of the pump A, they permit a limited seepage of oil also in the opposite direction, that is from the respective mouth B, B' to the tank H.
  • the pressure relief valves L and L' though opening at a pre-established maximum pressure, may be designed so as to permit - also in their closed position - a limited seepage of oil from the respective mouth B, B' to the tank H.
  • the above portion of the power unit can be used, as such, in hydraulic circuits for activating double-acting actuating cylinders that are not to be locked in position by the aid of said hydraulic circuit.
  • the pressurized oil is delivered through the conduit C to the hydraulic actuating cylinder onto one side of its piston, which, therefore, is moved in the corresponding direction, while the oil discharged from the actuating cylinder at the other side of its piston is returned through the conduit C' to the other mouth B' of the pump, operating as a suction mouth.
  • the mouth B' draws the difference from the oil tank H through the associated unidirectional valve F'.
  • the amount of oil returned from the actuating cylinder through the conduit C * is greater than that being sucked by the mouth B', a higher pressure is created on the side of the latter and the exceeding oil is returned to the tank H either by seeping through valves F' or L' or by partially opening the pressure relief valve L'.
  • the direction of rotation of the actuating motor 1 for the pump A is reversed, which pump is then activated in the opposite direction, whereby its mouth B' becomes a delivery mouth.
  • the flow of oil is then reversed, while any possible difference of rate between the flow of oil sent to the actuating cylinder and the flow of oil returned from the actuating cylinder is compensated for as described above.
  • the oil tank H substantially, has the only function to compensate for any difference of rade between the oil flow sent to the user and the oil flow returned from the user, whereby it may be of very small size and integrated with a structure of minimum dimensions, as described hereinafter.
  • the plug Q may be removed and the mouth of the connection conduit P may be connected to a supplementary oil tank.
  • a pilot conduit S opening into a pressure chamber formed at an end portion of the distributor sliding valve R, acted upon by the return spring T.
  • a pilot conduit S' opening into a pressure chamber formed at the other end portion of the distributor sliding valve R, acted upon by the return spring T'.
  • the distributor sliding valve R is thus moved to a first opening position wherein it connects the two conduits C and C' to the conduits C" and C"', whereby the delivery pressure created through the mouth B is allowed to act in the end portion of the hydraulic actuating cylinder connected to the conduit C", while the other end portion of the actuating cylinder is connected through the conduit C"' to the suction mouth B' of the pump.
  • the piston of the actuating cylinder is moved accordingly.
  • the pump A is then stopped, so as to eliminate the pressure acting through the pilot conduit S on the distributor sliding valve R and the latter is returned by the spring T' to its intermediate rest and closure position, wherein it locks the piston of the actuating cylinder in the position it has reached.
  • the delivery of the oil occurs through the mouth B' of said pump and the delivery pressure created in the conduit C' acts entirely or partially through the pilot conduit S' in the pressure chamber at the other end portion of the distributor sliding valve R acted upon by the return spring T'.
  • the pressure chamber at the opposite end of the distributor sliding valve R communicates through the pilot conduit S and conduit C with the mouth B of the pump, which operates now as a suction mouth.
  • the distributor sliding valve R is then moved against the action of the spring T in the direction of the arrow U1 (upwardly in Fig. 1 and toward the left in Fig. 6) to a second opening position, where it again communicates the conduits C and C' to the conduits C" and C"'.
  • the pressurized oil delivered by the mouth B' acts in the other end portion of the hydraulic actuating cylinder, connected to the conduit ct", while the opposite end of said actuating cylinder is connected through the conduit C" to the suction mouth B of the pump A.
  • the piston of the actuating cylinder is then moved in a direction opposite to the former and is locked in its new position when the pump A is stopped and the distributor sliding valve R is moved back to its intermediate closure position by the action of the return spring T.
  • the distributor sliding valve R may be selectively and also manually moved to either of its two opening positions, wherein it connects the mouths B and B' of the pump A through the respective conduits C, C * to the two conduits C", C"'.
  • a control stem Z provided with a side notch 19 cooperating with a corresponding small spring-urged retainer ball 20.
  • Said stem Z sealingly exits from the recess in the distributor sliding valve R and its outer end is provided with a transverse end cutout Z', wherein a screw-driver or the like can be engaged.
  • the control stem Z is retracted outwards in a rest position, shown in Fig. 6 and wherein it does not interfere with the distributor sliding valve R when the latter is moved to its opening end position near said control stem Z (to the right in Fig. 6).
  • the pump A is constituted by a reversible gear pump.
  • the two gears 7 and 7' are arranged, in a known manner, between two opposed dual wear-bushings 6 and 6', wherein the shafts 8 and 8' of said gears 7 and 7' are supported.
  • the dual bushings 6, 6' and the two gears 7, 7' interposed therebetween are accommodated in a corresponding recess of the pump body 5 which is sealingly tightened between the two covers 3 and 4 by means of tierods 10 passed through the pump body 5 and through the two covers 3 and 4.
  • the two covers 3 and 4 of the pump are formed by circular plates of such a diameter as to extend beyond the outline of the pump body 5.
  • the two covers are sealingly peripherally connected by an intermediate tubular member 12 and seals 13, 13' and thus form, together with said tubular member 12, around the pump body 5, a closed chamber constituting the oil tank H.
  • the circular plates constituting the covers 3 and 4 will mate by means of planar surfaces against the corresponding end faces of the pump body 5 and against the outer ends of the dual wear-bushings 6, 6' and are provided with gaskets 17 which are indicated by hatching in Fig. 4. These gaskets extend all around the bushings 6, 6' at the pump body 5 and around the shafts 8, 8' of the two gears 7, 7' at the wear-bushings 6, 6', while defining at the intermediate portion between the two shafts 8, 8' and on the side of the cover 4, two opposite chambers 18, 18' operating alternately, one as a delivery chamber and the other as a suction chamber, and vice versa, according to the direction of operation of the pump A.
  • These two chambers 18, 18' communicate with opposite sides of the meshing region of the two gears 7, 7' through corresponding openings 16 B and 16 B' formed between the pump body 5 and the dual wear-bushing 6 on the side facing towards the cover 4.
  • Said openings 16 B and 16 B' constitute the two mouths of the pump, operating alternately one as a delivery mouth and the other as a suction mouth, and vice versa, according to the direction of operation of the pump A.
  • the two chambers 18, 18' also communicate each with a hole formed in the cover 4.
  • These holes constitute the conduits D and D' and extend by means of co-axial lengths C, C' to the distributor sliding valve R which is accommodated in a corresponding substantially diametral bore formed in said cover 4.
  • Two parallel holes extend from the distributor sliding valve R and open at the outer end surface of the cover 4 and constitute the conduits or connectors C", C'" for coupling the power unit to the respective hydraulic circuit user, for example a hydraulic actuating cylinder.
  • two parallel holes M, M' are formed the diameter of which is reduced by steps as they extend inwards, and which intersect the two holes D and D r .
  • the larger diameter outer portion of these holes M, M' accommodates the two pressure relief valves L, L', while the reduced diameter inner portion thereof, at the opposite side with respect to the intersection with the holes D, D', accommodates the unidirectional valves F, F * as particularly clearly shown in Figs. 2 and 5.
  • the inner ends of the holes M, M' communicate at N with each other and with an adjacent angular hole G opening at the inner end surface of the cover 4 in the oil tank H, thus communicating said holes M, M' with said tank H.
  • the first stretch of the hole G extends to open at the periphery of the cover 4, where it is closed by means of a plug.
  • This extension of the first stretch of the angular hole G constitutes the conduit P for connection to a supplementary oil tank.
  • the intermediate tubular member 12 is provided at the periphery thereof with a filling hole which is closed by means of a threaded plug 14 having a filling and compensating small valve 15 in the form of a non-return valve which opens from the outside towards the interior.
  • the constructional embodiment of the power unit according to the Figs. 2 to 6 ensures a compact and small-sized unit containing the pump A, the oil tank H and every required auxiliary elements and is easily secured to the flange 101 of the reversible actuating electric motor 1 by means of the cover 3 and axial connecting tierods 11 passed through the two covers 3, 4 and through the oil tank H exteriorly of the pump body 5.
  • the shaft 8 of a gear 7 exits to the outside through the cover 3 and a sealing member 9, and is coupled to the co-axial shaft 2 of the motor 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Braking Systems And Boosters (AREA)
  • Control Of Transmission Device (AREA)
EP83101948A 1982-03-02 1983-02-28 Hydraulische Versorgungseinheit Expired EP0087794B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83101948T ATE24027T1 (de) 1982-03-02 1983-02-28 Hydraulische versorgungseinheit.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT335382 1982-03-02
IT03353/82A IT1156552B (it) 1982-03-02 1982-03-02 Centralina idraulica miniaturizzata con pompa a doppio senso di rotazione

Publications (3)

Publication Number Publication Date
EP0087794A2 true EP0087794A2 (de) 1983-09-07
EP0087794A3 EP0087794A3 (en) 1984-09-05
EP0087794B1 EP0087794B1 (de) 1986-12-03

Family

ID=11105531

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83101948A Expired EP0087794B1 (de) 1982-03-02 1983-02-28 Hydraulische Versorgungseinheit

Country Status (4)

Country Link
EP (1) EP0087794B1 (de)
AT (1) ATE24027T1 (de)
DE (1) DE3368096D1 (de)
IT (1) IT1156552B (de)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2239488A (en) * 1989-12-19 1991-07-03 Marinex Ind Limited Hydraulic actuator for marine drives
FR2687206A1 (fr) * 1992-02-12 1993-08-13 Berruyer Jean Jacques Dispositif de commande pour vannes.
WO1996012108A1 (en) * 1994-10-13 1996-04-25 Applied Power Inc. Hydraulic operating device and gearbox provided with such an operating device
EP0932773A1 (de) * 1996-09-13 1999-08-04 Vickers, Inc. Elektrohydraulisches system und bidirektionale elektromotor-hydraulischpumpeeinheit
DE102011117486A1 (de) * 2011-10-26 2013-05-02 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Schaltanordnung für ein Kraftfahrzeuggetriebe
EP2045304B1 (de) 1999-12-22 2017-10-11 ExxonMobil Chemical Patents Inc. Klebstoffzusammensetzung auf polypropylenbasis

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2552624A (en) * 1948-09-13 1951-05-15 Frederick W Enzenbacher Door closing apparatus, including electrically driven gear pump and oscillating vanemotor hydraulic transmission
FR2009929A1 (fr) * 1968-05-21 1970-02-13 Bbc Brown Boveri & Cie Dispositif hydroelectrique de commande
FR2374543A1 (fr) * 1976-12-14 1978-07-13 Bosch Gmbh Robert Dispositif pour le deplacement d'elements de construction notamment d'elements pivotables

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2552624A (en) * 1948-09-13 1951-05-15 Frederick W Enzenbacher Door closing apparatus, including electrically driven gear pump and oscillating vanemotor hydraulic transmission
FR2009929A1 (fr) * 1968-05-21 1970-02-13 Bbc Brown Boveri & Cie Dispositif hydroelectrique de commande
FR2374543A1 (fr) * 1976-12-14 1978-07-13 Bosch Gmbh Robert Dispositif pour le deplacement d'elements de construction notamment d'elements pivotables

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
AUTOMATION, vol. 13, no. 2, February 1966, pages 102-104, Cleveland, Ohio, US *

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2239488A (en) * 1989-12-19 1991-07-03 Marinex Ind Limited Hydraulic actuator for marine drives
GB2239488B (en) * 1989-12-19 1993-11-03 Marinex Ind Limited Hydraulic actuator for marine drives
FR2687206A1 (fr) * 1992-02-12 1993-08-13 Berruyer Jean Jacques Dispositif de commande pour vannes.
WO1996012108A1 (en) * 1994-10-13 1996-04-25 Applied Power Inc. Hydraulic operating device and gearbox provided with such an operating device
NL9401692A (nl) * 1994-10-13 1996-05-01 Applied Power Inc Hydraulische bedieningsinrichting en versnellingsbak voorzien van een dergelijke bedieningsinrichting.
US5857381A (en) * 1994-10-13 1999-01-12 Applied Power Inc. Hydraulic operating device and gearbox provided with such an operating device
EP0932773A1 (de) * 1996-09-13 1999-08-04 Vickers, Inc. Elektrohydraulisches system und bidirektionale elektromotor-hydraulischpumpeeinheit
EP0932773A4 (de) * 1996-09-13 2001-08-08 Vickers Inc Elektrohydraulisches system und bidirektionale elektromotor-hydraulischpumpeeinheit
EP2045304B1 (de) 1999-12-22 2017-10-11 ExxonMobil Chemical Patents Inc. Klebstoffzusammensetzung auf polypropylenbasis
DE102011117486A1 (de) * 2011-10-26 2013-05-02 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Schaltanordnung für ein Kraftfahrzeuggetriebe
US9309968B2 (en) 2011-10-26 2016-04-12 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Shift arrangement for a motor vehicle gearbox

Also Published As

Publication number Publication date
EP0087794A3 (en) 1984-09-05
DE3368096D1 (en) 1987-01-15
EP0087794B1 (de) 1986-12-03
ATE24027T1 (de) 1986-12-15
IT8203353A0 (it) 1982-03-02
IT1156552B (it) 1987-02-04

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