WO2003033915A1 - Druckmittelspeicher - Google Patents
Druckmittelspeicher Download PDFInfo
- Publication number
- WO2003033915A1 WO2003033915A1 PCT/EP2002/011288 EP0211288W WO03033915A1 WO 2003033915 A1 WO2003033915 A1 WO 2003033915A1 EP 0211288 W EP0211288 W EP 0211288W WO 03033915 A1 WO03033915 A1 WO 03033915A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- closing body
- valve
- accumulator according
- bottom valve
- chamber
- Prior art date
Links
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
- F15B1/22—Liquid port constructions
-
- 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
- F15B2201/20—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
- F15B2201/315—Accumulator separating means having flexible separating means
- F15B2201/3153—Accumulator separating means having flexible separating means the flexible separating means being bellows
-
- 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
- F15B2201/315—Accumulator separating means having flexible separating means
- F15B2201/3158—Guides for the flexible separating means, e.g. for a collapsed bladder
-
- 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
- F15B2201/411—Liquid ports having valve means
Definitions
- the invention relates to a pressure medium accumulator with a housing, the interior of which is divided into two chambers by a media separation element, the first chamber being filled with a gas and the second chamber with a liquid, and with a hydraulic connection in which an actuatable by the media separation element Bottom valve is provided, which enables the second chamber to be filled with the liquid and, in the closed state, prevents the second chamber from being completely emptied, the closing body of which is pretensioned in the opening direction by means of a valve spring and can be actuated by the media separation element.
- Such a pressure medium accumulator is known from international patent application WO 00/31420.
- the bottom valve of the known pressure medium accumulator consists of an elastic sealing element which, when closed, interacts with a conical annular surface formed in the bore of the hydraulic connection.
- the closing process takes place in two phases.
- the first phase in which the pressurized pressure medium flows past the sealing element, the closing element of the bottom valve is subsequently expanded by the media separation element pressed down until the sealing element comes into contact with the conical ring surface and prevents the pressure medium from escaping from the second chamber.
- the closing body fulfills the function of a hydraulic piston, which is adjusted further downwards by the residual pressure prevailing in the second chamber.
- the media separating element moves further downward toward the bottom valve.
- a full opening of the bottom valve is not possible in the subsequent filling process, so that the sealing element attached to the closing body must be overflowed.
- a high differential pressure is required for the filling process, in particular at low temperatures and high viscosity of the pressure medium. Because of this, a high hydraulic force acts on the closing body, which presses the closing body against the bottom of the media separation element. This creates a relatively high pressure difference, up to 10 bar, between the two chambers, so that there is a risk of pre-damage to the media separation element. Due to the pre-damage, the target service life of the known pressure fluid accumulator cannot be fulfilled.
- This object is achieved in that means are provided between the media separation element and the bottom valve for reducing the force that can be transmitted from the closing body of the bottom valve to the media separation element.
- the means are designed as a spring, preferably a compression spring, which is supported on the closing body of the bottom valve and can be brought into contact with the media separation element.
- the pressure spring is in contact with the media separating element by means of a force transmission part which is guided displaceably in the closing body.
- the closing body is preferably biased against the closing direction by means of a valve spring, the spring rate of which is smaller than the spring rate of the compression spring.
- FIG. 1 shows an embodiment of the pressure medium reservoir according to the invention with the bottom valve closed in axial section
- FIG. 2 shows the bottom valve of the pressure medium accumulator according to FIG. 1 on a larger scale in the open state
- Figure 3 shows a second embodiment of the bottom valve on a larger scale in the open state.
- 11a, b show a tenth embodiment of the bottom valve in the closed and open state
- the media separation element 2 is preferably formed by a thin-walled metallic bellows, which on the one hand is pressure-tightly connected to a cover 9 closing the housing 1 and on the other hand is closed by a plate 8.
- the interior of the bellows 2 forms the first chamber 3, which can be filled with a gas, which is generally under high pressure, via a filling connection 29 provided in the cover 9.
- a hydraulic connection 5 is provided, in which a bottom valve 6 is arranged, the closing body 7 of which projects into the second chamber 4 in the open position of the bottom valve (FIG. 2).
- the bottom valve ⁇ is preferably designed such that on the one hand it enables the second chamber 4 to be filled with a pressurized liquid pressure medium, for example a brake fluid, and on the other hand prevents the second chamber 4 from being completely emptied.
- a pressurized liquid pressure medium for example a brake fluid
- a slotted ring 30 is provided which surrounds the plate 8 and the edge of which is in the assembled state at a short distance from the wall of the housing 1.
- a filler 31 is provided, which is arranged on the bottom of the housing 1.
- the hydraulic connection 5 provided with a filling or outlet opening 15 has a bore 10 which is designed as a stepped bore and has four sections. While two sections 11, 12 of the same diameter serve to guide the closing body 7, a third section 13 of larger diameter is formed between them, which delimits an annular space 16 with the closing body 7.
- a fourth section 14 formed at the lower end of the connection 5 receives a snap ring 17 which is arranged on the closing body 7 and which serves to limit the movement of the closing body 7 in the opening direction of the bottom valve 6.
- the transition area between the cut 12, 13 is preferably formed by a conical ring surface 18.
- the aforementioned annular space 16 is connected to the second chamber 4 by means of radial passages 19, while the closing body 7 has a plurality of radial flow channels 20 which are connected to the filling or. Exit opening 15 of the hydraulic connection 5 are connected.
- the latter connection takes place via a cylindrical recess 21 formed in the closing body 7, which receives a valve spring 24 which prestresses the closing body 7 in the opening direction of the bottom valve 6.
- a second cylindrical recess 25 formed on the end of the closing body 7 facing away from the filling and outlet opening 15 accommodates a spring, preferably a compression spring 26, the spring rate of which is considerably greater than the spring rate of the valve spring 24 mentioned above.
- the compression spring 26, which is on the one hand supported on the bottom of the cylindrical recess 25, is supported at its other end on a force transmission part 27 which is guided displaceably in the closing body 7 and which cooperates with the plate 8 closing the bellows 2 during the closing process.
- the bottom valve 6 is closed in two phases. Shortly before the chamber 4 is emptied, the plate 8 closing the bellows 2 begins to touch the power transmission part 27. Because the rigidity of the Compression spring 26, as already mentioned above, is larger than that of the valve spring 24, the closing body 7 is adjusted against the force exerted by the valve spring 24 when the pressure medium continues to emerge or is pressed downwards in the drawing until the outer sealing lip of the first sealing sleeve 22 comes to rest on the wall of the stepped bore section 12 and thus prevents the flow around the closing body 7. At this moment, the closing body 7 begins to perform the function of a hydraulic piston and is adjusted further downward by the residual pressure prevailing in the chamber 4. As a result, the second sealing sleeve 23 also comes into the section 12 and seals against its wall.
- the bottom valve 6 is opened in that liquid pressure medium is pumped from the outside into the pressure medium reservoir 1 according to the invention. If the boost pressure exceeds the residual pressure or internal pressure prevailing in the chamber 4 (neglecting the opening force of the compression spring 24 and the closing force of the cuff friction), the closing body 7 is moved in the opening direction, whereby it already releases its own displacement volume into the second chamber 4.
- the contour of the annular space receiving the sealing collar 22 only changes when the pressure difference applied to the sealing collar is small.
- the closing body 7 is pressed further upwards by the compression spring 14 until the force transmission part 27 again bears against the plate 8 closing the bellows 2.
- the plate 8 withdraws and the path of the closing body 7 is limited by the stop 17.
- valve body 7 has a bore 28 on its end facing the plate 8, which bore serves to guide a preferably tappet-like force transmission part 27a extending through it.
- the valve spring 24 is supported on the end of the force transmission part 27a facing the filling and outlet opening 15 and thus fulfills both the function of the valve opening spring and the function of the previously mentioned compression spring for reducing the force acting on the closing body 7.
- An auxiliary spring 29 arranged between the closing body 7 and the force transmission part 27a ensures that the friction of the force transmission part 27a in the bore 28 is overcome, so that during the closing process no relative movement of the power transmission part 27a to the closing body 7 takes place.
- the sealing elements 22a, 23a arranged on the closing body 7 are designed as simple, robust O-rings in the embodiment shown.
- a further O-ring 30 is used to seal the power transmission part 27a in the closing body 7, which is secured in the closing body 7 by means of a pressed-in steel ring 31.
- Another steel ring 32 pressed into the closing body 7 serves as a stop for limiting the stroke of the opening movement of the closing body 7.
- the previously mentioned compression spring 26 is arranged coaxially to the closing body 7 outside the hydraulic connection 5.
- the open position of the bottom valve 6 is shown in Fig. 4a, while Fig. 4b shows the closed position.
- the force transmission element 27b interacts with a collar 33 formed on the closing body 7 and has a radial collar 34 on which the compression spring 26 is supported.
- the other end of the compression spring 26 is supported on a spring plate 35 fastened to the closing body 7.
- the sealing of the closing body 7 with respect to the hydraulic connection 5 is provided on the closing body 7
- valve spring 24 and the previously mentioned compression spring 26 are arranged coaxially to one another in the region of the hydraulic connection 5 which extends into the second chamber 4 (FIG. 1).
- the valve spring 24 biasing the closing body 7 in the opening direction has a larger diameter and is between the hydraulic connection
- the compression spring 26 which prestresses the force transmission element 45 with respect to the closing body 7 has a smaller diameter and, as in the third or fourth embodiment, is tion, clamped between the power transmission element 45 and the spring plate 35 mentioned in connection with FIG. 4.
- the hydraulic connection between the filling or outlet opening 15 and the second chamber 4 (not shown) (see FIG. 1) takes place in the embodiment shown by means of flow channels provided in the hydraulic connection 5, which are delimited by guide ribs 46 formed on the closing body 7.
- connection mentioned is shut off by means of a redundant sealing arrangement fastened to the closing body 7, which is formed by an O-ring 47 sealing against the wall of the bore 10 leading the closing body 7 and a plate seal 48.
- the plate seal 48 seals against the bottom of the hydraulic connection 5.
- Guide ribs 53 formed on the closing body 7 simultaneously serve as stop elements for limiting the stroke of the closing body 7 in the opening direction of the bottom valve.
- the structure of the sixth embodiment of the bottom valve 6 shown in FIGS. 7a, b largely corresponds to that of the embodiment according to FIG. 5, the arrangement of the valve spring 24 and the compression spring 26 corresponding to the embodiment according to FIG. 6.
- the sealing of the closing body 7 with respect to the hydraulic connection 5 only serves an O-ring 49 arranged in an annular groove of the hydraulic connection 5, which cooperates with a section 50 of larger diameter of the closing body 7.
- the hydraulic connection between the filling or outlet opening 15 and the second chamber 4 (not shown) takes place in the embodiment shown by means of a bore section 51 of larger diameter, which is formed in the area of the 0-ring 49.
- Guide ribs 52 formed on the closing body 7 also serve as stop elements to limit the stroke of the closing body 7 both in the opening and in the closing direction of the bottom valve 6, the “lower” stop being formed by a snap ring 60 inserted in the connection 5.
- This stop can of course also be screwed into the connection 5, for example Threaded sleeve to be executed.
- the seventh embodiment of the bottom valve 6 shown in FIGS. 8a, b largely corresponds to the embodiment according to FIG. 7.
- the only difference is the type of sealing of the closing body 7 with respect to the hydraulic connection 5, which in the example shown is designed redundantly and through two 0-rings 54, 55 arranged one behind the other in annular grooves of the hydraulic connection 5 are formed, which cooperate with correspondingly designed sections of larger diameter of the closing body 7.
- sealing arrangements of the bottom valve 6 which consist of combinations on the closing body 7 and sealing elements arranged in the hydraulic connection 5.
- multi-part seals such as metal rings with vulcanized rubber layers, can also be used as sealing elements.
- the eighth embodiment of the bottom valve 6 shown in FIGS. 9a to d largely corresponds to the embodiment according to FIG. 8.
- means are provided which prevent the redundant sealing arrangement 56, 57 of the closing body 7 from being damaged in critical operating phases of the bottom valve 6 too high Protect inflation pressure.
- an annular part 58 made of plastic, for. B. Teflon, or made of metal, which limits a ring gap or a defined flow cross section with a section 71 of the closing body 7. If the closing body 7 is moved in the opening direction during the filling process from the closed valve position (FIG. 9a), a defined volume of pressure medium flows through the aforementioned annular gap, so that the pressure acting on the sealing elements 56, 57 is reduced.
- valve device 59 which is actuated by the opening movement of the closing body 7 of the bottom valve 6.
- the valve device 59 is designed as a seat valve, the seat of which is formed in the closing body 7. Since the function of the valve device 59 corresponds to the mode of operation of the means mentioned above and is clear from the pictorial 10a-d, it need not be explained in detail.
- the representation of the tenth embodiment of the bottom valve 6 shown in FIGS. 11a, b corresponds to the manner of presentation of the previously described embodiments according to FIGS. 4-8, the closed position of the bottom valve 6 being shown in FIG. 11a and the open position being shown in FIG. 11b ,
- the structure of the embodiment shown corresponds essentially to that of the ninth embodiment according to FIG. 10.
- the main differences are primarily in the design of the closing body 7 and in the function of the valve device 59 mentioned above.
- the closing body 7 is designed as a stepped piston and has a first step 72 of smaller diameter and a second step 73 of larger diameter.
- the first stage 73 carries the first sealing element 74, which is designed as a sealing sleeve with an L-shaped cross section.
- An annular space 75 delimited by the first stage 72 in the hydraulic connection 5 is connected via a transverse bore 76 to a flow channel 77 running axially in the closing body 7, the end of which forms the seat of the valve device 59 designed as a seat valve.
- the second stage 73 delimits a second annular space 78 in the bore of the hydraulic connection 5, which is connected to the flow channel 76 by means of a second transverse bore 79.
- the second sealing element 80 arranged on the second stage 73 is formed by a combination of an O-ring and a back ring.
- the illustration shows that the second stage 73 generates an increase in the hydraulic pressure in the annular space 75 during the filling process, the value of which approximately corresponds to the value of the Pressure medium storage prevailing pressure. It is thereby achieved that the first sealing element 74 is pressure-balanced and there is no risk of damage due to excessive pressure. If the hydraulic pressure in the annular space 75 reaches a predeterminable value, the valve device 59, which simultaneously fulfills the function of a pressure relief valve, is opened briefly, so that the pressure in the annular space 75 is reduced to a permissible value.
- the initially defined object of the invention is achieved by hydraulic means, which in the example shown are formed by a series connection of two valve arrangements 81, 82.
- the first valve arrangement 81 is formed by passages 83 formed in the closing body 7 and a sealing element 84 arranged immovably in the hydraulic connection 5, while the second valve arrangement 82 is designed as a central valve arranged in the closing body 7.
- the valve spring 86 of this central valve is preferably designed so that only a small differential pressure is required to open the central valve.
- the sealing element 85 arranged on the closing body 7 is designed as a sealing sleeve.
- the passages 83 are connected to the filling and outlet opening 15, so that when they pass over the sealing element 84 during the opening movement of the closing body 7, the pressure medium flows into an annular space 87 delimited by the closing body 7 in the hydraulic connection 5 and the central valve 82 also the filling pressure is applied. Due to the effect of the pressure difference between the pressure in the annular space 87 and the inner Half of the pressure prevailing in the pressure medium reservoir, the central valve 82 is opened and the filling pressure acting on the closing body 7 is reduced.
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)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003536617A JP2005505731A (ja) | 2001-10-16 | 2002-10-09 | 圧力媒体アキュムレータ |
US10/492,503 US20040250866A1 (en) | 2001-10-16 | 2002-10-09 | Pressure medium reservoir |
EP02781229A EP1438515A1 (de) | 2001-10-16 | 2002-10-09 | Druckmittelspeicher |
Applications Claiming Priority (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10151041 | 2001-10-16 | ||
DE10151041.1 | 2001-10-16 | ||
DE10151050 | 2001-10-16 | ||
DE10151050.0 | 2001-10-16 | ||
DE10157146.1 | 2001-11-22 | ||
DE10157146 | 2001-11-22 | ||
DE10214871.6 | 2002-04-04 | ||
DE10214871A DE10214871A1 (de) | 2001-10-16 | 2002-04-04 | Druckmittelspeicher |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003033915A1 true WO2003033915A1 (de) | 2003-04-24 |
Family
ID=27438021
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2002/011288 WO2003033915A1 (de) | 2001-10-16 | 2002-10-09 | Druckmittelspeicher |
Country Status (4)
Country | Link |
---|---|
US (1) | US20040250866A1 (de) |
EP (1) | EP1438515A1 (de) |
JP (1) | JP2005505731A (de) |
WO (1) | WO2003033915A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10333014A1 (de) * | 2003-07-18 | 2005-02-03 | Volkswagen Ag | Druckspeicher zur Aufnahme und/oder Abgabe eines unter Druck stehenden Mediums |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7121304B2 (en) * | 2001-12-19 | 2006-10-17 | The United States Of America As Represented By The Administrator Of The U.S. Environmental Protection Agency | Low permeation hydraulic accumulator |
JP2005155785A (ja) * | 2003-11-26 | 2005-06-16 | Nok Corp | アキュムレータ |
JP4853292B2 (ja) * | 2007-01-10 | 2012-01-11 | 国産電機株式会社 | エンジンの燃料噴射・点火制御方法及び燃料噴射・点火制御装置 |
DE112008002343B4 (de) * | 2007-10-10 | 2024-05-23 | Eagle Industry Co., Ltd. | Speicher |
DE102008003664B4 (de) * | 2008-01-09 | 2023-03-23 | Robert Bosch Gmbh | Bremssystem und Verfahren zum Betreiben eines Bremssystems |
DE102008061221A1 (de) * | 2008-12-09 | 2010-06-10 | Hydac Technology Gmbh | Hydrospeicher, insbesondere Balgspeicher |
DE102009048668A1 (de) | 2009-09-29 | 2011-03-31 | Siemens Aktiengesellschaft | Integrierte Hydraulikspeicheranordnung |
US8844575B2 (en) * | 2009-12-30 | 2014-09-30 | Hydac Technology Gmbh | Guiding device for metal bellows |
DE102011117752A1 (de) * | 2011-11-05 | 2013-05-08 | Hydac Technology Gmbh | Hydrospeicher in Form eines Balgspeichers |
FR3001774B1 (fr) * | 2013-02-04 | 2015-03-13 | Vianney Rabhi | Moteur-pompe hydraulique a cylindree fixe ou variable |
DE102016008882A1 (de) * | 2016-07-20 | 2018-01-25 | Hydac Technology Gmbh | Spannzylindervorrichtung |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4526205A (en) * | 1979-10-18 | 1985-07-02 | Kazuo Sugimura | Pulsation absorption device for high pressure liquid |
DE8900483U1 (de) * | 1989-01-18 | 1990-05-17 | Robert Bosch Gmbh, 7000 Stuttgart | Druckbehälter, insbesondere Druckspeicher |
WO2000031420A1 (de) | 1998-11-25 | 2000-06-02 | Continental Teves Ag & Co. Ohg | Druckmittelspeicher |
WO2001083997A1 (de) * | 2000-04-28 | 2001-11-08 | Continental Teves Ag & Co. Ohg | Druckmittelspeicher mit zwei ventilen |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2385016A (en) * | 1943-06-21 | 1945-09-18 | Mercier Jean | Locking valve |
US2880758A (en) * | 1953-12-09 | 1959-04-07 | Mercier Jean | Closure valve for the outlet port of a pressure accumulator |
US3182685A (en) * | 1959-05-27 | 1965-05-11 | Mercier Jean | Closure valve for the outlet port of a pressure vessel |
US3148702A (en) * | 1960-07-06 | 1964-09-15 | Mercier Jean | Closure valve for the outlet port of a pressure vessel |
GB1284060A (en) * | 1970-05-23 | 1972-08-02 | Pirelli | Volume-compensation apparatus for oil-filled electric power cables |
DE2536484A1 (de) * | 1975-08-16 | 1977-02-24 | Bosch Gmbh Robert | Ventil fuer die fluessigkeitsoeffnung eines druckspeichers |
US6619325B2 (en) * | 2001-12-04 | 2003-09-16 | The United States Of America As Represented By The Administrator Of The U.S. Environmental Protection Agency | Hydraulic hybrid accumulator shut-off valve |
-
2002
- 2002-10-09 EP EP02781229A patent/EP1438515A1/de not_active Withdrawn
- 2002-10-09 WO PCT/EP2002/011288 patent/WO2003033915A1/de not_active Application Discontinuation
- 2002-10-09 US US10/492,503 patent/US20040250866A1/en not_active Abandoned
- 2002-10-09 JP JP2003536617A patent/JP2005505731A/ja not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4526205A (en) * | 1979-10-18 | 1985-07-02 | Kazuo Sugimura | Pulsation absorption device for high pressure liquid |
DE8900483U1 (de) * | 1989-01-18 | 1990-05-17 | Robert Bosch Gmbh, 7000 Stuttgart | Druckbehälter, insbesondere Druckspeicher |
WO2000031420A1 (de) | 1998-11-25 | 2000-06-02 | Continental Teves Ag & Co. Ohg | Druckmittelspeicher |
WO2001083997A1 (de) * | 2000-04-28 | 2001-11-08 | Continental Teves Ag & Co. Ohg | Druckmittelspeicher mit zwei ventilen |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10333014A1 (de) * | 2003-07-18 | 2005-02-03 | Volkswagen Ag | Druckspeicher zur Aufnahme und/oder Abgabe eines unter Druck stehenden Mediums |
Also Published As
Publication number | Publication date |
---|---|
EP1438515A1 (de) | 2004-07-21 |
JP2005505731A (ja) | 2005-02-24 |
US20040250866A1 (en) | 2004-12-16 |
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