EP0371321A1 - Accumulateur de fluide - Google Patents

Accumulateur de fluide Download PDF

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Publication number
EP0371321A1
EP0371321A1 EP89121122A EP89121122A EP0371321A1 EP 0371321 A1 EP0371321 A1 EP 0371321A1 EP 89121122 A EP89121122 A EP 89121122A EP 89121122 A EP89121122 A EP 89121122A EP 0371321 A1 EP0371321 A1 EP 0371321A1
Authority
EP
European Patent Office
Prior art keywords
pressure accumulator
accumulator according
pressure
piston
contact plate
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
EP89121122A
Other languages
German (de)
English (en)
Other versions
EP0371321B1 (fr
Inventor
Wolfgang Forstner Siegfried Klett
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
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT89121122T priority Critical patent/ATE76676T1/de
Publication of EP0371321A1 publication Critical patent/EP0371321A1/fr
Application granted granted Critical
Publication of EP0371321B1 publication Critical patent/EP0371321B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • 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
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/41—Liquid ports

Definitions

  • the invention relates to a fluidic pressure accumulator, in which a pressure chamber can be acted upon by a fluid via a fluidic connection, the pressure chamber having at least one wall that can be moved against a supporting force.
  • Such pressure accumulators are used in pneumatic and hydraulic systems and are used for the z. B. due to a temperature increase expanding fluid, the pressure in the system should be kept as constant as possible. This is particularly important in the case of liquid systems, since such an increase in pressure could lead to leaks and destruction of individual components.
  • a so-called expansion vessel which consists of a pressure vessel divided by a rubber membrane.
  • This membrane is from one side with the water of the heating system and from the other side is pressurized with air, which is closed in its half of the vessel. When the water expands, the membrane is deflected against the air cushion, which is compressed more and more with increasing deflection and exerts a counter pressure.
  • the disadvantage of the known arrangement is on the one hand in the short life of the membrane and on the other hand in its low resistance to extreme temperatures and mechanical influences, so that the possible uses are very limited. The low aging and corrosion resistance also severely limits the area of application.
  • an elastic body made of wire material is provided to generate the supporting force, the wire material being knitted and / or corrugated and / or rolled and / or interwoven and / or intertwined.
  • Such an elastic body and thus the fluid pressure accumulator provided with it are extremely resilient, practically indestructible and maintenance-free. Aging of the wire material or destruction of the elastic body due to permanent fracture of the wire material subjected to bending is practically impossible.
  • the wire cross-sections and the permitted spring travel can be designed so that each elastic body always remains in the fatigue strength range below the horizontal branch of the Wöhler characteristic. For example, with 10% dynamic deflection of the unstressed height and a static surface pressure of 50 kp / cm2, an infinite number of load changes can be applied without destruction. Depending on the practically freely selectable material of the wire, a very high resistance to aging, corrosion and temperature can be achieved. A dynamic load capacity of 5 to 10 times the static load is possible.
  • the wire material which is preferably made of stainless steel, is knitted, corrugated and rolled.
  • the stainless steel material ensures high resistance to all possible influences.
  • the movable wall is designed as a piston movable in a corresponding cylinder, which has a contact plate for the elastic body.
  • a counter-contact plate is provided which is connected to the cylinder at a fixed, adjustable distance. This allows the elastic body to be adjusted and exchanged in a simple manner. Both plates can be formed by surfaces of any shape.
  • the bolt is expediently screwed into the fluidic connection, through-holes and / or longitudinal grooves being provided on the bolt for supplying the fluid at least in the screw-in region.
  • a particularly inexpensive lightweight construction is achieved in that the piston and / or the contact plate and / or the counter contact plate are formed as sheet metal parts. In this case, but also in the case of a solid design, the piston and the contact plate can be welded, pressed or soldered to one another, or the piston and the separate contact plate mesh with one another in the radial direction. This leads to simple assembly using a small number of inexpensive components.
  • the fluidic connection can be designed as a screw-in connection, so that the entire pressure accumulator can be connected to the fluidic system by screwing into a corresponding threaded bore.
  • the cylinder can also be designed as an edge-side piston bore on the fluidic device, so that the cylinder can be dispensed with as a separate component, which makes the arrangement even more cost-effective.
  • the pressure accumulator according to the invention can also be used particularly advantageously for reducing switching shocks or pressure peaks in fluid systems, for example in fluid channels or lines or other fluidic devices connected to valves and in particular shut-off valves.
  • Switching shocks which cause pressure waves, occur especially when changing the switching state of valves and can cause damage to fluidic devices.
  • These pressure peaks can be damped excellently with the pressure accumulator according to the invention, it being advantageous that the damping can take place directly at the point of origin of the fault.
  • the pressure chamber of the pressure accumulator can communicate with at least one fluid channel or form a component of the same, which forms a flow channel for a flow medium which arises with different and, in particular, alternately higher and lower pressures.
  • the fluid channel can be formed here in a housing or in a plate, but it can also be a pressure medium line or the like. act. If the communication between the pressure chamber and the flow channel takes place in the area of a flow damming point or flow deflection point, it is ensured that a pressure wave triggered by pressure fluctuations does not run straight, but is briefly “jammed", so that the pressure accumulator can respond without problems.
  • a cylinder 10 is provided at one end with an axial, tubular threaded extension 11, which is provided with an external and an internal thread is and serves as a fluidic connection.
  • a bolt 13 is screwed into the threaded inner bore 12 and is provided with a thread at its two end regions.
  • the end region of the bolt 13 screwed into the threaded inner bore 12 has longitudinal grooves 14 on the edge, only one of which can be seen in the figure. These longitudinal grooves 14 extend beyond the threaded extension 11 into the interior of the cylinder 10 and thereby allow a fluid F, preferably a liquid, to flow into the cylinder.
  • a fluid F preferably a liquid
  • a piston 15 is slidably arranged on the pin 13.
  • This piston 15 is a sheet metal part by deep drawing, bulging, beading, pressing, flanging, stamping or the like. produced.
  • this piston 15 carries an outer piston seal 16, which is designed as an annular seal and is held in a circumferential groove 17 with a U-shaped cross section.
  • the piston 15 has a radially inwardly offset step 18, which engages in a corresponding indentation of a contact plate 19. This contact plate 19 protrudes radially over the cylinder 10 and rests against its open end.
  • an inner piston seal 21 is arranged, which seals the piston 15 to the bolt 13.
  • the piston 15 can be welded, soldered or pressed to the contact plate 19. However, it is also possible that the two parts are only inserted loosely into one another. In this case, the front end of the piston 15 must lie sealingly against the inner piston seal 21.
  • An elastic, cylindrical body 22 with an axial through opening 23 is formed as a body molded from wire material.
  • the wire material is knitted, corrugated, rolled, woven and / or intertwined. These types of structuring can be combined with one another in a variety of ways. Due to the compression and compression, the wire material lies close together and forms a compact, elastically reversibly deformable body. A very thin wire material is used, the wire thickness of which is preferably less than 1/50 of the diameter of the body.
  • This elastic body 22 is between an abutment surface of the abutment plate 19 and a facing abutment surface a correspondingly shaped counter plate 24 is held.
  • This counter abutment plate 24 is also pushed onto the bolt 13, the fixing being carried out by means of a washer 25 and two nuts 26 which are screwed onto the threaded end of the bolt 13.
  • the counter bearing plate 24 also has an indentation 27 in which the nuts 26 are arranged. The radial position is fixed by the indentations 27 and corresponding indentations in the elastic body 22.
  • a tubular stop body 28 is arranged in the through opening 23 of the elastic body 22 and limits the axial deformation of the elastic body 22. This stop body 28 is attached to the counter-contact plate 24.
  • the entire arrangement forming the pressure accumulator is screwed by means of the threaded extension 11 into a corresponding connection of a fluidic system, which is connected, for example, to a valve channel. If the fluid expands in this system, it gets there over the longitudinal grooves 14 in the cylinder 14 and moves the piston 15 to the right, whereby the contact plate 19 also moves to the right against the counter-contact plate 24, the distance to the cylinder 10 is fixed by means of the bolt 13. As a result, the elastic body 22 is compressed and moves the piston 15 to the left again as soon as the fluid contracts again. The displacement of the contact plate 19 is limited by the stop body 28.
  • a preload can be set, for example, which determines the release pressure for the movement of the piston 15.
  • a cylinder 30 is not designed here as a separate component, but as an edge-side bore in a solid housing 31 of a fluidic component.
  • a concentric, fluidic feed channel 32 opens into the front end of the cylinder 30 and is provided with an internal thread for receiving the bolt 13.
  • a piston 33 is solid and connected in one piece to a contact plate 34 for the elastic body 22. The piston 33 is in turn with an outer piston seal 35 in a circumferential groove and an inner piston seal 36 provided in an inner groove.
  • a counter-abutment plate 37 like the abutment plate 34, is designed as a solid, flat disc.
  • the bolt 13 is first screwed into the feed channel 32, after which the piston 33 is then pushed onto the bolt 13 and pushed into the cylinder 30. Now the elastic body 22 and the counter abutment plate 37 are pushed onto the bolt 13 and fixed by means of the nuts 26.
  • the remaining mode of operation corresponds to that of the first embodiment.
  • first exemplary embodiment can also be combined with elements of the second exemplary embodiment.
  • first exemplary embodiment can also be provided with a solid piston and / or one piece connected to the contact plate 19, while in the second exemplary embodiment an arrangement of the piston and contact plate corresponding to the first exemplary embodiment can be provided.
  • shoulders can be provided on the contact plate 34 and / or on the counter-contact plate 37 in order to fix the radial position of the elastic body 22.
  • the solid piston 33 can also be designed as a separate component with respect to the contact plate 34.
  • the piston seals shown can also be omitted if e.g. by an appropriate fit or by labyrinth seals or the like. an appropriate seal is guaranteed.
  • the dimensioning of the elastic body 22 can vary widely, e.g. the ratio of its length to its diameter.
  • the cylindrical shape can have a circular, oval, polygonal or similar cross section.
  • the central pin 13 can be omitted if the counter-contact plate is connected via external connecting means, e.g. a housing with which the cylinder 10 or the housing 31 is connected.
  • external connecting means e.g. a housing with which the cylinder 10 or the housing 31 is connected.
  • the pressure accumulators described are preferably suitable for high-pressure cleaners, tensioning systems, brake systems, valve arrangements or the like in which pressure peaks occur or pulsation damping appears to be necessary. Since no gas pressure accumulator is provided, monitoring by the TÜV is also not mandatory.
  • the elastic body is preferably made of stainless steel wire, but other types of wire can be used that have the necessary elastic properties.
  • the requirement for corrosion resistance depends not least on the aggressiveness of the environment or the fluid used.
  • the cylinder 30 is not designed as a separate component here, but is represented by an opening or recess of a housing 40 on the edge.
  • the latter is formed in the exemplary embodiment by a, for example, cuboid intermediate plate 41, or the like, between a valve arrangement 42 indicated by dashed lines and a base or distributor plate 43. is interposed.
  • the intermediate plate 41 for example, two fluid channels 44, 44 'designed as flow channels are provided, which can lead to consumers via the base plate or distributor plate 43 and which can be connected and controlled by means of the valve arrangement 42.
  • Each of the fluid channels 44, 44 ' is preferably in communication with an associated pressure chamber 46, which is the one axial Is assigned to the piston side, while on the other piston side, as already described above, there are elastic bodies 22. If pressure fluctuations occur in the fluid channels 44, 44 'on the part of the flow medium guided therein, the pressure accumulator effects a damping by means of the body 22.
  • the pressure accumulator according to the invention can be switched on.
  • the connection with channels supplying feed and / or control pressure is particularly advantageous. Pulsation damping of high efficiency can take place here, especially if the pressure is and / or gear pumps is supplied.
  • An intermediate plate construction according to FIG. 3 also allows effortless integration into existing systems. Any number of channels formed in the housing 40 can correspond to pressure accumulators as required. It is of course also possible to connect pressure accumulators directly to the channels of a respective fluidic device, e.g. of a valve.
  • the pressure chambers 46 are expediently part of the respectively assigned fluid channel 44, 44 'and directly switched on in its channel path.
  • the pressure chambers 46 which are formed by the inner end portion of the associated housing opening 30, communicate with the fluid channel 44, 44 'in the region of a flow baffle 47, which coincides here with a flow deflection point.
  • This has the advantage that the pressure wave does not run past the pressure accumulator, but has an effect on the movable wall 48 formed by a piston in the exemplary embodiment and counteracts this supplied by the body 22 supporting force.
  • the arrangement is such that two channel branches of the fluid channel 44, 44 'from opposite connection surfaces 49 penetrate into the intermediate plate 41, being arranged parallel to one another, but offset by an amount from one another.
  • the ends of the channel branches arranged inside the plate are connected to one another by the pressure chamber 46, the associated housing opening containing the piston or the movable wall 48 extending transversely and preferably at right angles to the course of the fluid channel 44, 44 '.
  • the direction of movement of the movable wall is therefore preferably at right angles to a plane containing the two channel branches and indicated by the section plane IV-IV. It is advantageous here if the respective channel branches dip obliquely into the intermediate plate with reference to the associated connecting surface 49.
  • the counter-abutment surface 24, which has counter-abutment surface 50, is here a component of a hollow cylindrical cap-shaped body 51 which, with a threaded section 52 arranged at the open edge region, fits into a Extension of the housing opening is screwed in.
  • the contact plate 19 having the contact surface 53 is arranged axially displaceably in the cap-shaped body 51. It is expediently, as in the exemplary embodiment according to FIG. 2, formed in one piece with the piston 33 and together with it represents the movable wall 48.
  • two of the elastic bodies 22 are in the direction of movement of the wall 48 arranged in a row. This shows that if necessary, several elastic bodies 22 can be used per pressure accumulator, which can be connected in series and / or in parallel.
  • a step of the housing opening can serve as a stop for the contact plate 19.
  • the pressure accumulator according to the invention can therefore advantageously be used for reducing or damping switching shocks or pressure peaks in fluid channels or lines or other fluidic devices connected to valves, for example directional control valves such as shut-off valves. Also for damping so-called water hammer in
  • the pressure accumulator according to the invention can be used effectively.
  • the sandwich construction shown in FIGS. 3 and 4 is only a preferred embodiment.

Landscapes

  • 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)
EP89121122A 1988-11-30 1989-11-15 Accumulateur de fluide Expired - Lifetime EP0371321B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89121122T ATE76676T1 (de) 1988-11-30 1989-11-15 Fluidischer druckspeicher.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3840369 1988-11-30
DE3840369 1988-11-30
DE3916854A DE3916854A1 (de) 1988-11-30 1989-05-24 Fluidischer druckspeicher
DE3916854 1989-05-24

Publications (2)

Publication Number Publication Date
EP0371321A1 true EP0371321A1 (fr) 1990-06-06
EP0371321B1 EP0371321B1 (fr) 1992-05-27

Family

ID=25874692

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89121122A Expired - Lifetime EP0371321B1 (fr) 1988-11-30 1989-11-15 Accumulateur de fluide

Country Status (5)

Country Link
EP (1) EP0371321B1 (fr)
DE (2) DE3916854A1 (fr)
ES (1) ES2031338T3 (fr)
GR (1) GR3005051T3 (fr)
HU (1) HU210419B (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10334763A1 (de) * 2003-07-30 2005-03-17 Lucas Automotive Gmbh Druckspeicher für eine Fahrzeugbremsanlage und mit einem Druckspeicher ausgestattete Fahrzeugbremsanlage

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2456238A1 (fr) * 1979-05-08 1980-12-05 Europ Propulsion Accumulateur d'energie
DE3622445A1 (de) * 1986-07-04 1988-01-21 Schubert Werner Von innen druckstossunempfindlicher hohlkoerper

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE94429C (fr) *
US3383853A (en) * 1966-05-17 1968-05-21 Fed Pacific Electric Co Energy storage mechanism for actuating circuit breakers and the like
DE2105640A1 (de) * 1971-02-06 1972-08-17 Knorr-Bremse GmbH, 8000 München Federspeicherzylinder
CA1232824A (fr) * 1983-11-30 1988-02-16 Shoso Ishimori Mecanisme de motorisation pour vehicule agricole
DE3632988A1 (de) * 1986-09-04 1988-06-30 Schubert Werner Sonde zur minderung von druckstosswirkungen im inneren eines hohlkoerpers

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2456238A1 (fr) * 1979-05-08 1980-12-05 Europ Propulsion Accumulateur d'energie
DE3622445A1 (de) * 1986-07-04 1988-01-21 Schubert Werner Von innen druckstossunempfindlicher hohlkoerper

Also Published As

Publication number Publication date
DE3916854A1 (de) 1989-09-28
HU210419B (en) 1995-04-28
HU896313D0 (en) 1990-02-28
DE3916854C2 (fr) 1991-02-21
EP0371321B1 (fr) 1992-05-27
GR3005051T3 (fr) 1993-05-24
ES2031338T3 (es) 1992-12-01
DE58901541D1 (de) 1992-07-02
HUT55873A (en) 1991-06-28

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