EP0105152A1 - Accumulateur hydraulique pour la fourniture de fluide sous pression - Google Patents
Accumulateur hydraulique pour la fourniture de fluide sous pression Download PDFInfo
- Publication number
- EP0105152A1 EP0105152A1 EP83108104A EP83108104A EP0105152A1 EP 0105152 A1 EP0105152 A1 EP 0105152A1 EP 83108104 A EP83108104 A EP 83108104A EP 83108104 A EP83108104 A EP 83108104A EP 0105152 A1 EP0105152 A1 EP 0105152A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- hydraulic accumulator
- accumulator according
- pressure
- springs
- 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
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 29
- 230000006835 compression Effects 0.000 claims description 4
- 238000007906 compression Methods 0.000 claims description 4
- 230000008859 change Effects 0.000 claims description 3
- 238000004804 winding Methods 0.000 claims description 2
- 239000007789 gas Substances 0.000 description 18
- 239000003921 oil Substances 0.000 description 6
- 230000000712 assembly Effects 0.000 description 4
- 238000000429 assembly Methods 0.000 description 4
- 239000012528 membrane Substances 0.000 description 4
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
Images
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
- F15B2201/21—Accumulator cushioning means using springs
-
- 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
-
- 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 hydraulic accumulator for providing pressure fluid for a hydraulic system, in particular for actuating a medium or high-voltage circuit breaker, with a cylinder in which a piston is movable, on one side of which the pressure fluid is located, the piston being arranged by a spring arrangement for Generation of the pressure in the pressure fluid is applied.
- Hydraulic accumulators of the type mentioned at the outset have become known which are used to provide pressurized fluid, e.g. Hydraulic oil, for a hydraulic control system to control or actuate a high-voltage circuit breaker.
- pressurized fluid e.g. Hydraulic oil
- hydraulic accumulators which are designed as containers and have a membrane in the interior of this container.
- the pressure fluid is on one side of the membrane and gas on the other side.
- the gas will pressurized and, as it is compressible in comparison to the pressure fluid, acts as a gas pressure spring for generating the pressure in the pressure fluid.
- a piston is provided instead of a membrane, which is arranged so that it can be moved back and forth inside the container designed as a cylinder.
- nitrogen N 2 is generally used as the gas.
- gas as a gas pressure spring has advantages in that the pressure in the gas and thus also the pressure in the pressurized fluid can be kept approximately constant by suitable make-up.
- the object of the invention is therefore to provide a hydraulic accumulator in which the disadvantages of the known hydraulic accumulators described above are avoided.
- a hydraulic accumulator should also have a simple structure.
- the spring arrangement is formed by at least one spiral spring which drives the piston according to the characterizing part of claim 2.
- the roller is designed as a cam disk, which is dimensioned and shaped in such a way that the force on the piston remains constant even when the spring force of the coil springs changes during winding on the roller.
- the band is expediently designed as a chain and, consequently, the cam disc, on which the band or chain is wound, as a toothed wheel disc.
- tension or compression springs instead of coil springs according to the characterizing part of claim 6.
- the tension or compression springs act on.
- Rocker arms which, according to claim 7, transmit the spring force to the piston.
- rocker arms to screws and pistons also achieves a torque compensation in which the effective lever of the rocker arm is reduced or enlarged in accordance with the position of the springs or the tension state of the springs by pivoting the rocker arms.
- the particular advantages of the hydraulic accumulator according to the invention are that changes in the pressure in the pressure fluid, which can occur in gas pressure accumulators due to gas leakage and because of the temperature dependence of the gas, are avoided. This means that the amount of pressurized fluid need not be greater than necessary and also additional expenditure which is necessary to maintain the gas pressure, such as e.g. Devices for replenishing gas in the event of a leak can be eliminated. It is also only necessary to ensure sufficient tightness against the escape of pressure fluid; however, measures must not be taken to prevent gas from penetrating into the pressure fluid. As a result, the hydraulic accumulator according to the invention is significantly cheaper to manufacture and in particular in operation than a gas pressure hydraulic accumulator.
- FIG. 2 Reference is first made to FIG. 2.
- FIG. 2 shows a cylinder arrangement 10, in the interior of which a piston 12 can be displaced between two end positions.
- the piston 12 is shown to the left of the center line when the cylinder is completely full and to the right of the center line is the piston 12 when the cylinder is completely empty.
- the space 14 above the piston is the space that receives the pressure fluid.
- the cylinder is closed in a pressure-tight manner by means of a cover 16 and at the top by means of a further cover 18, the further cover 18 having an annular extension 20 which projects into the interior of the space 12 and serves to limit the path of the piston 12.
- a piston rod 22 is attached to the upper surface of the piston and is guided outwards through the annular extension 20 and the further cover 18.
- a shoulder 24 is attached to which a chain 26 is attached.
- This chain 26 is designed like a bicycle chain and consists of several chain links.
- the cylinder In the area of the ring-shaped extension 20, the cylinder has an outlet 28 which runs transversely to the central axis of the cylinder and opens into a passage 30 which runs parallel to the central axis of the cylinder 10; this passage 30 also penetrates the cover 16. A further opening 32 is provided in the central region of the cover 16. If oil is now needed by the hydraulic control system, which is connected to the passage 30, then the oil, which acts under the pressure of the piston 12, in the direction of arrow F. strikes, stands and that is in the room 14, pressed in the direction of arrow G through the outlet 20 and the passage 30 to the hydraulic system.
- the piston 12 is of course guided tightly inside the cylinder, just as a seal is provided between the cover 16 and 18 and the cylinder 10, respectively. How the individual elements are held together is of less importance here; they can be coupled to one another, for example, by means of flange connections or other fastening elements.
- the chain 26 With its free end, the chain 26 is fastened to a cam disk 34, the radius R of which is reduced in a spiral shape, so that a cam surface 36 is formed, the task of which will be explained in more detail below.
- the cam disc 34 is attached to a drive shaft 38 which is coupled to a gear 40. This gear wheel is supported together with the drive shaft 38 on a base plate 42.
- Spiral spring assemblies 44 and 46, 48 and 50 are supported between the drive shaft 38 and the gear 40 and act on two axes 52 and 54, on which gear wheels 56 and 58 (see FIG. 2) are fastened.
- the gears 56 and 58 and the gear 40 are wrapped in a drive chain 60.
- a toothed belt or the like can also be used.
- a deflection wheel 62 Immediately in the area of the gear 40 is a deflection wheel 62, the periphery of which affects the extension of the center line of the piston rod, the shape that in the area between the tangential point T and the point of application of the chain 26 on the piston rod, the chain 26 always exactly in the direction of Piston rod runs.
- the cam surface 36 can also have a gear design that is adapted to the chain or the distance between the chain links of the chain 60.
- the coil springs have released a certain energy, their spring force will change due to the spring characteristic of the coil springs. This change in the spring force can be compensated for by the cam surface 36.
- the cam surface 36 When the chain 26 is wound onto the cam surface 36, the radius of the force application point on the chain 26 changes and thus the torque acting on the chain 26 and thus the driving force for the piston.
- a driving force or tightening force that is constant at any position of the piston and thus an approximately constant pressure in any position of the piston can be generated.
- FIG. 3 shows a further embodiment of the invention.
- a cylinder 74 which is tubular in shape, is formed on a base plate 70 by means of screw connections 72 is screwed on. Inside the cylinder 74, a piston 76 is movable back and forth. In the base plate 70 there is an outlet opening 76 which is connected to the hydraulic system.
- the high-pressure chamber 80 is located between the base plate 70, the cylinder 74 and the piston 76.
- a piston rod 82 is fastened to the piston on the side of the piston 76 opposite the high-pressure chamber.
- a container 84 is fastened on the end face of the cylinder opposite the base plate 70 by means of a screw connection 86 and has an outer wall 88 and an inner wall 90, the inner wall covering only approximately half of the outer wall 88.
- the inner wall 90 is covered by a cover 92 with a through opening 94.
- the outer wall 88 is closed at the top by means of an end cover 96.
- calmed oil with low pressure whereas outside the cover 92, but still within the space formed by the outer wall 88 and the end cover 96, there is oil foamed with low pressure.
- the piston rod 82 seals through the cover 96; at its upper end a support ring 98 is firmly attached, for example by means of a screw connection.
- This support ring 98 has on its side opposite the piston rod a pin 100 which is guided in a bore 102 of a cross member 106 which is fixedly connected to the base plate 70 by means of bolts 104.
- a radially extending support surface 108 is located on the support ring 98.
- the base plate 70 has recesses 110 distributed around the circumference, which serve for the passage of a tube 112.
- a support plate is supported above the base plate 120 on two bearing bolts 122 on the base plate.
- a support 124 At the upper end of the rod 112 there is a support 124, to which a tab 126 is attached, which is penetrated by a bolt 128 with which it is articulated on a double-arm lever 130.
- a plate spring assembly consisting of a number of plate springs 132. From FIG. 4 it can be seen that a total of six such plate spring constructions and six double-arm levers 130 are arranged on the circumference.
- the double arm lever 130 is articulated on an extension 134 on the cross member via an axis 136.
- the inner end of the double arm lever has a spherical shape 138, which rests on the surface 108.
- the plate 124 is displaceable against the plate 120 so that the plate springs 132 can be tensioned (see left of the center line) or relaxed (see right of the center line of FIG. 3).
- the plate spring assemblies 132 can be pivoted in the double arrow direction T due to their support in the bearing pin 122, as can be seen from the arrangement of the two plate springs to the left and right of the central axis. In the arrangement on the left, the distance D1 + D2 is small, and in the arrangement on the right, there is a distance.
- the arrangement on the left side of the center line is in the tensioned state, ie that the Piston is in the position in which the memory is completely filled with pressurized fluid.
- pressure oil is drawn off or extracted through the opening or the passage 76, the piston moves downwards under the pressure of the springs 132, whereby the plate spring assemblies at their upper end with their axis 128 swivel outwards; due to the increased leverage, the reduction in spring force is compensated for upon further relaxation, so that the leverage of the double-arm lever 130 keeps the pressure in the fluid approximately constant.
- coil springs can also be used; it is of course also possible to use only a single coil spring; However, this must be of a correspondingly large size and, moreover, it is also necessary to provide a support plate, which comprises the entire arrangement, in the upper region, which then acts on the angle levers 130, which, however, cannot be articulated with the screw.
- a relief valve 140 is accommodated in the piston 76, which extends through the piston 76 with a valve rod 142 and projects beyond it on the side opposite the high-pressure chamber 80.
- the valve rod 142 abuts against a boundary surface 144 on the low pressure container 84, 88, 90 and 96 and opens the relief valve 140, so that a passage from the high pressure chamber 80 to the low pressure chamber is released.
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)
- Actuator (AREA)
- Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3232074 | 1982-08-28 | ||
DE19823232074 DE3232074A1 (de) | 1982-08-28 | 1982-08-28 | Hydrospeicher zur bereitstellung von druckfluid |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0105152A1 true EP0105152A1 (fr) | 1984-04-11 |
EP0105152B1 EP0105152B1 (fr) | 1986-11-26 |
Family
ID=6171942
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP83108104A Expired EP0105152B1 (fr) | 1982-08-28 | 1983-08-17 | Accumulateur hydraulique pour la fourniture de fluide sous pression |
Country Status (4)
Country | Link |
---|---|
US (1) | US4623134A (fr) |
EP (1) | EP0105152B1 (fr) |
JP (1) | JPS5958201A (fr) |
DE (2) | DE3232074A1 (fr) |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1861154A (en) * | 1931-04-02 | 1932-05-31 | Toledo Machine & Tool Company | Fluid pressure accumulator |
US2298512A (en) * | 1936-10-15 | 1942-10-13 | Edward A Rockwell | Accumulator for supplying liquid under pressure |
US2318065A (en) * | 1941-05-07 | 1943-05-04 | Mattia Peter De | Hydraulic drive |
AT204343B (de) * | 1955-09-03 | 1959-07-10 | Jean Louis Gratzmuller | Hydraulischer Energiespeicher |
US3581774A (en) * | 1969-04-01 | 1971-06-01 | Us Navy | Constant pressure accumulator |
US4046167A (en) * | 1976-02-06 | 1977-09-06 | Kawneer Company, Inc. | Mechanical accumulator |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1365030A (en) * | 1919-09-15 | 1921-01-11 | Flentje Ernst | Shock-absorber |
US1512736A (en) * | 1922-08-15 | 1924-10-21 | Aldrich Roscoe Hilton | Shock absorber for hydraulic systems |
US1663647A (en) * | 1927-02-07 | 1928-03-27 | Alanson P Brush | Energy-storage unit |
US2321093A (en) * | 1940-12-20 | 1943-06-08 | James A Lupfer | Pressure equalizer |
US3064093A (en) * | 1958-11-22 | 1962-11-13 | Asea Ab | Hydraulic means for stressing the springs of spring actuated electric switches |
DE1290226B (de) * | 1960-11-05 | 1969-03-06 | Liebknecht Transformat | Steueranordnung fuer Hochspannungsdruckgasschalter |
US3495508A (en) * | 1965-10-21 | 1970-02-17 | Earle F Allen | Hydraulic drive cylinder |
DE2105640A1 (de) * | 1971-02-06 | 1972-08-17 | Knorr-Bremse GmbH, 8000 München | Federspeicherzylinder |
DE2137108A1 (de) * | 1971-07-24 | 1973-02-01 | Fendt & Co Xaver | Speicherladeventil |
DE2419376C2 (de) * | 1974-04-22 | 1985-03-14 | Daimler-Benz Ag, 7000 Stuttgart | Regenerativ-Wärmetauscher einer Gasturbine, |
GB1496796A (en) * | 1975-01-30 | 1978-01-05 | Dewandre Co Ltd C | Spring brake actuators |
US4077303A (en) * | 1976-04-14 | 1978-03-07 | Peder Ulrik Poulsen | Apparatus for generating an impact force |
DE2629565A1 (de) * | 1976-07-01 | 1978-01-12 | Wabco Westinghouse Gmbh | Federspeicherzylinder |
GB1603420A (en) * | 1978-05-30 | 1981-11-25 | Woodhead Ltd Jonas | Hydraulic shock absorbers |
-
1982
- 1982-08-28 DE DE19823232074 patent/DE3232074A1/de not_active Ceased
-
1983
- 1983-08-17 DE DE8383108104T patent/DE3367963D1/de not_active Expired
- 1983-08-17 EP EP83108104A patent/EP0105152B1/fr not_active Expired
- 1983-08-26 JP JP58155106A patent/JPS5958201A/ja active Pending
-
1985
- 1985-12-16 US US06/810,822 patent/US4623134A/en not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1861154A (en) * | 1931-04-02 | 1932-05-31 | Toledo Machine & Tool Company | Fluid pressure accumulator |
US2298512A (en) * | 1936-10-15 | 1942-10-13 | Edward A Rockwell | Accumulator for supplying liquid under pressure |
US2318065A (en) * | 1941-05-07 | 1943-05-04 | Mattia Peter De | Hydraulic drive |
AT204343B (de) * | 1955-09-03 | 1959-07-10 | Jean Louis Gratzmuller | Hydraulischer Energiespeicher |
US3581774A (en) * | 1969-04-01 | 1971-06-01 | Us Navy | Constant pressure accumulator |
US4046167A (en) * | 1976-02-06 | 1977-09-06 | Kawneer Company, Inc. | Mechanical accumulator |
Also Published As
Publication number | Publication date |
---|---|
JPS5958201A (ja) | 1984-04-03 |
US4623134A (en) | 1986-11-18 |
EP0105152B1 (fr) | 1986-11-26 |
DE3232074A1 (de) | 1984-03-01 |
DE3367963D1 (en) | 1987-01-15 |
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