EP0078031B1 - Accumulateur de pression - Google Patents

Accumulateur de pression Download PDF

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Publication number
EP0078031B1
EP0078031B1 EP82109758A EP82109758A EP0078031B1 EP 0078031 B1 EP0078031 B1 EP 0078031B1 EP 82109758 A EP82109758 A EP 82109758A EP 82109758 A EP82109758 A EP 82109758A EP 0078031 B1 EP0078031 B1 EP 0078031B1
Authority
EP
European Patent Office
Prior art keywords
chamber
piston
recess
piston head
zone
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
Application number
EP82109758A
Other languages
German (de)
English (en)
Other versions
EP0078031A1 (fr
Inventor
Douglas Millard Gage
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP0078031A1 publication Critical patent/EP0078031A1/fr
Application granted granted Critical
Publication of EP0078031B1 publication Critical patent/EP0078031B1/fr
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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/24—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with rigid separating means, e.g. pistons
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/205—Accumulator cushioning means using gas
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
    • F15B2201/312—Sealings therefor, e.g. piston rings
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/32—Accumulator separating means having multiple separating means, e.g. with an auxiliary piston sliding within a main piston, multiple membranes or combinations thereof
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/41—Liquid ports
    • 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
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/415—Gas ports
    • F15B2201/4155—Gas ports having valve means

Definitions

  • the invention relates to a pressure accumulator with the features of the preamble of claim 1.
  • a pressure accumulator As part of a hydraulic circuit, a pressure accumulator has the task of keeping a sufficient supply of a hydraulic fluid under pressure ready for the hydraulic circuit and, on the other hand, of absorbing pressure peaks occurring in the hydraulic circuit.
  • pressure accumulators are known in many embodiments.
  • a single free-floating piston head is slidably mounted in the housing, which divides the elongated cylindrical chamber of the housing into a gas pressure chamber and a liquid chamber connected to the hydraulic system.
  • the piston has an endless circumferential recess with a connecting channel between this recess and the chamber of the pressure accumulator that holds the hydraulic fluid.
  • a sealing ring is arranged on the circumference of the piston head, which is continuously in sealing contact with the inner surface of the housing.
  • a stop sleeve for the piston head can also be provided, which limits the migration of the piston head in the direction of the end cap having the gas valve (cf. US-A-4186 777).
  • a pressure accumulator with the features of the preamble of claim 1 is also known (cf. CH-A-591 020).
  • the multiple piston arrangement has two pistons, one of which has a recess and the other has a projection, which engage telescopically in the longitudinal direction of the housing. They thus form an overall piston consisting of two parts constantly in mutual engagement.
  • a generally incompressible fluid is enclosed between the mutually facing end face regions of the pistons arranged one behind the other in the longitudinal direction of the housing. This is sealed off by circumferential sealing arrangements on the two pistons from the compressed gas chamber area as well as from the chamber area containing the hydraulic fluid.
  • This multi-piston arrangement already offers a seal between the chamber areas, which keeps leakage of the compressed gas in the direction of the chamber area containing the hydraulic fluid within certain limits.
  • gas can also emerge from the compressed gas chamber area via the multi-piston arrangement into the other chamber area, so that the gas pressure drops and the pressure accumulator can no longer properly perform its task.
  • Such conditions are e.g. B. before when the multi-piston assembly comes to rest on the end cap, which includes the chamber area containing the hydraulic fluid. In this case there are maximum pressure differences on both sides of the multi-piston arrangement.
  • Critical conditions can also arise if the pressure accumulator is used in areas with low temperatures. Experience shows that here too the risk of the gas passing into the chamber area containing the hydraulic fluid is particularly high. This is probably due to a decrease in the flexibility and sealing effect of the seals on the multi-piston arrangement.
  • the generally incompressible fluid is enclosed between two piston heads that are independent and freely suspended. These are therefore not in direct contact with each other.
  • the peripheral recess of the piston head adjoining the compressed gas chamber area is filled due to the design with the incompressible fluid, which is enclosed under the same pressure as the incompressible fluid between this piston head and the piston head immediately following in the longitudinal direction of the housing. Since the incompressible fluid also comes into contact with the end cap, which closes the chamber area containing the hydraulic fluid, at approximately the same pressure that prevails in the pressure gas chamber area, the pressure drop between the pressure gas chamber area and the peripheral recess of the adjacent piston head is almost the same Zero.
  • the gas has difficulty passing the circumferential seal of the piston head arranged between the recess and the compressed gas chamber area. It is equally difficult to pass through the area remaining between the circumferential recess and the rear of this piston head, in which a sealing ring is preferably also arranged. It is therefore almost impossible for the compressed gas to pass the first piston head adjoining the compressed gas chamber 72. This process is additionally through the appropriate training of the the hydraulic fluid-containing chamber area adjacent piston head effectively supported. An extremely effective seal is thus obtained between the two chamber areas of the pressure accumulator.
  • the sealing effect is so excellent that the arrangement according to claim 2 can preferably be formed, in which only two piston heads are provided.
  • FIG. 1 A conventional accumulator is shown in FIG. 1, which has a housing 11. In this a cylindrical chamber 12 is formed, which is closed at both ends by end caps 27 and 29. In the chamber 12, a piston 13 is slidably mounted. The piston contains an annular recess 15 and an opening 17 which leads from the recess to the rear end face of the piston. Sealing devices are provided between the piston 13 and the wall of the cylindrical chamber 12. For this purpose, annular sealing packs 19 and 21 are used, which are arranged on both sides of the recess 15. The piston 13 divides the chamber 12 into two working chamber sections 23 and 25.
  • the end cap or end cap 27 has an oil connection opening 39 through which hydraulic fluid can get into the chamber 25 and from there into the hydraulic system.
  • the closure cap 29 at the other end has a compressed gas valve 41 through which compressed gas can be introduced into the chamber 23.
  • the conventional accumulator of Fig. 1 shows a tendency to lose its gas pressure over time, under certain extreme conditions.
  • a possible reason for the loss of gas pressure can be caused by the total amount of hydraulic supply being expelled from the second chamber 25, so that the piston 15 comes to bear on the closure cap 27. This creates a pressure imbalance across the packing 19 and 21. This can result in a loss of gas under pressure in the recess 15, with the result that the bias pressure of the gas decreases.
  • Another possibility can occur if the accumulator is used under extremely low temperatures. This reduces the flexibility of the seal packs 19 and 21, so that the seal loses its effect and gas can leak into the recess 15.
  • FIG. 2 This shows a new type of accumulator.
  • the accumulator comprises a housing 50 which delimits a cylindrical chamber 51.
  • a piston arrangement 52 consists of two freely floating piston heads 52a and 52b. These are slidably arranged in the cylinder chamber 51.
  • the pistons 52a and 52b each have on their circumference open recesses 54 and 64 which are open towards the cylinder wall.
  • the pistons also have corresponding openings 56 and 66. These extend rearward from the respective recesses 54 and 64.
  • a first stack of gasket 58 lies in front of the endless recess 54 and comprises a packing ring which is supported between two support rings.
  • a second seal stack 60 comprises a packing ring, behind which a support ring lies.
  • This seal pack is arranged behind the recess 54.
  • Another stack of sealing rings 68 lies in front of the endless recess 64 in the piston head 52b.
  • a sealing ring stack 70 lies behind the recess 54.
  • the sealing ring stacks 68 and 70 are each designed to match the sealing ring stacks 58 and 60.
  • the piston heads 52a and 52b divide the accumulator into a first chamber section 72 for receiving the gas under pressure and a second chamber section 74, in which the hydraulic fluid is received. Between the piston heads 52a and 52b, which are spaced apart, a generally incompressible fluid of relatively high density is enclosed, including the cylinder wall. The trapped fluid completely occupies the space between the piston heads 52a and 52b so that the piston heads 52a and 52b make a synchronous or common movement. It can therefore be said that the piston heads 52a and 52b and the enclosed incompressible fluid move in the longitudinal direction of the cylinder chamber 51 as a unit.
  • the ends of the housing 50 are sealed by caps 80 and 82.
  • the cap 80 is fixed and sealing to the housing 50 by appropriate measures, for. B.
  • the closure cap 80 has a conventional gas valve 92 through which the bias gas can be introduced into the chamber section 72.
  • the closure cap 82 is fixedly and sealingly mounted on the housing 52 with the aid of a snap ring 86 in the usual way.
  • a sealing ring stack 84 which corresponds to the sealing ring stack 58, lies in front of the snap ring 86.
  • An opening or bore 88 extends through the closure cap 82 in order to introduce the hydraulic fluid into the chamber section 74 or to lead it out of this into the hydraulic system.
  • the piston head 52b has a filling opening in the end face 76, which is subsequently closed pressure-tight and tightly by a stopper 78.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Claims (2)

1. Accumulateur de pression comportant un carter (51) qui définit une chambre cylindrique allongée dans laquelle il est prévu de façon coulissante un système de piston multiple (52) dont au moins deux pistons disposés l'un derrière l'autre dans la direction longitudinale du carter retiennent entre eux un fluide d'une façon générale incompressible, ces pistons présentant un système d'étanchéité (54, 58, 60 et 64, 68, 70) sur leur face périphérique et subdivisant la chambre en une première et une seconde zones formant chambres (72 et 74), parmi lesquelles la première est fermée au moyen d'un chapeau d'extrémité comportant une soupape à gaz (92) et la seconde au moyen d'un chapeau d'extrémité (80, 82) comportant un perçage de raccordement pour le fluide (88), en étant rendues étanches, caractérisé en ce que le système de piston multiple (52) est constitué par des têtes de pistons (52a, 52b) indépendantes l'une de l'autre et librement flottantes, qui sont disposées selon un certain écartement relatif dans la direction longitudinale du carter (50), en ce que la tête de piston (52a) orientée vers la première zone formant chambre (72) comporte une cavité périphérique sans fin (54) munie d'un canal de communication (56), qui s'étend depuis la cavité (54) jusqu'à la face de la tête de piston (52a) opposée à la première zone formant chambre (72), et dont le système d'étanchéité associé comporte une bague d'étanchéité (58) entre la cavité (54) et la première zone formant chambre (72), et en ce que la tête de piston (52b) orientée vers la seconde zone formant chambre (74) comporte une cavité périphérique sans fin (64) munie d'un canal de communication (66) qui s'étend depuis la cavité (64) jusqu'au côté de la tête de piston (52b) orienté vers la seconde zone formant chambre (74), le système d'étanchéité associé comportant une bague d'étanchéité (68) entre la cavité (64) et le côté de la tête de piston (52b) opposé à la seconde zone formant chambre (74).
2. Accumulateur de pression suivant la revendication 1, caractérisé en ce que chaque tête de piston (52a, 52b) comporte une bague d'étanchéité (58, 60 et 68, 70) chaque fois sur les deux côtés de la cavité conjuguée (54, 64) et en ce que le système de piston (52) est constitué simplement par deux têtes de pistons (52a, 52b) disposées selon un écartement l'une par rapport à l'autre dans la direction longitudinale.
EP82109758A 1981-10-26 1982-10-22 Accumulateur de pression Expired EP0078031B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US31481281A 1981-10-26 1981-10-26
US314812 1999-05-19

Publications (2)

Publication Number Publication Date
EP0078031A1 EP0078031A1 (fr) 1983-05-04
EP0078031B1 true EP0078031B1 (fr) 1986-07-09

Family

ID=23221553

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82109758A Expired EP0078031B1 (fr) 1981-10-26 1982-10-22 Accumulateur de pression

Country Status (5)

Country Link
EP (1) EP0078031B1 (fr)
JP (1) JPS5881202A (fr)
CA (1) CA1180979A (fr)
DE (1) DE3271950D1 (fr)
ES (1) ES516793A0 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19701303A1 (de) * 1997-01-16 1998-07-23 Hydac Technology Gmbh Kolbenspeicher mit Dichtungsvorrichtung
DE10207181A1 (de) * 2001-11-05 2003-05-15 Continental Teves Ag & Co Ohg Kolbenspeicher
DE102007031525A1 (de) * 2007-07-06 2009-01-08 Agco Gmbh Kolbenspeicher mit mindestens zwei Kolben

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10228701A1 (de) * 2002-06-27 2004-01-15 Hydac Technology Gmbh Hydrospeicher
NO326166B1 (no) * 2005-07-18 2008-10-13 Siem Wis As Trykkakkumulator for a etablere nodvendig kraft til a betjene og operere eksternt utstyr, samt anvendelase derav
CN102536928B (zh) * 2011-12-26 2014-08-13 辽宁东工装备制造有限公司 一种气液三室液压系统过压缓冲平衡装置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4186777A (en) * 1978-10-27 1980-02-05 Deere & Company Pressure vessel retained energy measurement system

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2754847A (en) * 1951-07-20 1956-07-17 Electrol Inc Piston-type accumulators
US2683467A (en) * 1952-05-23 1954-07-13 Greer Hydraulies Inc Piston accumulator
DE1116950B (de) * 1960-01-30 1961-11-09 Teves Kg Alfred Abdichtung fuer Kolben bzw. Kolbenstangen von hydraulischen Zylindern
CH591020A5 (en) * 1975-08-15 1977-08-31 Gfeller Hans High pressure storage reservoir - has separator of two longitudinally displaceable pistons

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4186777A (en) * 1978-10-27 1980-02-05 Deere & Company Pressure vessel retained energy measurement system

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19701303A1 (de) * 1997-01-16 1998-07-23 Hydac Technology Gmbh Kolbenspeicher mit Dichtungsvorrichtung
DE10207181A1 (de) * 2001-11-05 2003-05-15 Continental Teves Ag & Co Ohg Kolbenspeicher
DE102007031525A1 (de) * 2007-07-06 2009-01-08 Agco Gmbh Kolbenspeicher mit mindestens zwei Kolben
DE102007031525B4 (de) * 2007-07-06 2009-09-10 Agco Gmbh Kolbenspeicher zur Dämpfung von zwei Fluidsystemen

Also Published As

Publication number Publication date
JPS5881202A (ja) 1983-05-16
ES8400553A1 (es) 1983-10-16
DE3271950D1 (en) 1986-08-14
CA1180979A (fr) 1985-01-15
EP0078031A1 (fr) 1983-05-04
ES516793A0 (es) 1983-10-16

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