EP0825348A1 - Amplificateur de pression de fluide, particulièrement de fluide hydraulique - Google Patents

Amplificateur de pression de fluide, particulièrement de fluide hydraulique Download PDF

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Publication number
EP0825348A1
EP0825348A1 EP97111400A EP97111400A EP0825348A1 EP 0825348 A1 EP0825348 A1 EP 0825348A1 EP 97111400 A EP97111400 A EP 97111400A EP 97111400 A EP97111400 A EP 97111400A EP 0825348 A1 EP0825348 A1 EP 0825348A1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
line
connection
cylinder
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
EP97111400A
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German (de)
English (en)
Other versions
EP0825348B1 (fr
Inventor
Jesper Will Iversen
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.)
miniBOOSTER Hydraulics AS
Original Assignee
Iversen Hydraulics ApS
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
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Application filed by Iversen Hydraulics ApS filed Critical Iversen Hydraulics ApS
Publication of EP0825348A1 publication Critical patent/EP0825348A1/fr
Application granted granted Critical
Publication of EP0825348B1 publication Critical patent/EP0825348B1/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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids

Definitions

  • the invention relates to a pressure booster for fluids, especially for hydraulic fluids, with a Piston-cylinder arrangement that has a low pressure side with a low pressure connection and a high pressure side with a high pressure connection and a supply connection and one designed as a differential piston Booster piston between the low pressure and high pressure side has, and with a control valve that a Has valve spool, the low pressure connection alternately with a pressure source and a pressure sink connects and via a control line with the piston-cylinder arrangement is connected, the pressure in the control line on one side of the valve spool works.
  • Such pressure boosters are used to control the pressure in a fluid beyond the pressure of a pressure source increase.
  • the following explanation is based on the example of Hydraulic fluids are made. Basically the principle also applies to other fluids.
  • a pressure booster of the type mentioned is out DE 40 26 005 A1 known.
  • the booster piston has a low pressure piston arranged on in a low pressure cylinder is, and a high pressure piston in one High pressure cylinder is arranged. Both pistons are firmly connected to each other via a piston rod.
  • the Low pressure piston has a much larger cross section than the high pressure piston. The pressure translation between the low pressure side and the high pressure side then takes place in the ratio of the piston cross sections.
  • the Terms "low pressure” and "high pressure” are used here and in the following only to distinguish the two Pages. They do not represent absolute pressure values, but only relative relationships.
  • Hydraulic fluid is often on the high pressure side removed, which tracked with appropriate pressure must become.
  • the high pressure cylinder i.e. the pressure chamber acted upon by the high pressure piston, filled with hydraulic fluid from the pressure source is fed.
  • the high pressure piston and pushed the low-pressure piston back with it.
  • the low-pressure piston then displaces the hydraulic fluid from its pressure chamber to the tank. If the high pressure piston has been pushed back by a certain stroke length is, it releases the opening of the control line, so that the pressure of the pressure source on the valve spool of the control valve can act.
  • the control valve is as Three-way valve designed. With the corresponding Pressurizing the connection between the Low pressure cylinder and the tank interrupted and instead a connection between the pressure source and the low pressure cylinder. The low pressure piston and then become the high pressure piston again shifted towards the high pressure side, so that hydraulic fluid with the correspondingly high Pressure is released through the high pressure connection can.
  • valve slide becomes accordingly on the one hand from the pressure in the control line acted upon and on the other hand by the force of a spring.
  • the invention is based, such To overcome limitations.
  • valve spool is designed as a differential piston
  • the differential piston is on one Side pressurized from the control line and on the other hand with a constant pressure.
  • the constant pressure acts on a slightly smaller one Area than the pressure from the control line. Since the Pressure in the control line drops from time to time, depending on the position of the booster piston, the valve spool will alternate from a force difference in one direction and from one Force difference applied in the opposite direction. These force differences are independent of the path, i.e. they act practically over the entire adjustment range of the valve spool.
  • the creation of a force with the help pressure can be realized simply by that the fluid with the appropriate pressure on the The end of the valve spool. Since the Practical difference in force over the entire adjustment range is kept constant, relatively high accelerations achieve. This allows the movement times shorten.
  • the frequencies with which the Pressure booster works can be selected higher. This also allows a larger delivery amount of the high pressure fluid enable.
  • the other side is the valve spool pressurized by the pressure source.
  • This Printing is available anyway. It is in sufficient Dimensions constant. Then there are additional measures not mandatory.
  • the control line advantageously opens into the stroke range of the Booster piston in the high pressure side of the piston-cylinder arrangement, the booster piston being the control line at the beginning of its movement towards the High pressure connection closes. So that the pressure in the control line essentially to the pressure of the Limited pressure source. With appropriate balancing the two end faces of the valve spool can be then the force difference across the valve spool that too whose movement is necessary to the desired values to adjust. You can then choose the desired movement behavior achieve.
  • the valve spool is advantageously under training an annulus arranged in a valve housing, in a tank line and a pump line and in between open a cylinder line, the valve spool a control disk dividing the annular space has, which depends on the position of the Valve spool either between the mouths of the Pump line and the cylinder line or the cylinder line and the tank line.
  • the control disc divides the annulus axially, i.e. in Direction of movement of the valve spool. It can be relative be kept thin.
  • the cylinder line is here with the low pressure area connected to the booster piston.
  • the tank line is connected to the pressure sink.
  • the pump line is with connected to the pressure source.
  • This funding takes place under the Pressure of the pressure source on the high pressure side of the Adjusting piston works.
  • a movement limitation for the valve slide is provided, which is the connection keeps its front side free for connecting the pressure source.
  • the connection keeps its front side free for connecting the pressure source.
  • the connection can sideways, i.e. radially into the corresponding pressure chamber flow out. In this case, if you make sure that this Muzzle always remains free, then the pressure on it the face of the valve spool does not work in any Case throttled.
  • a pressure booster shown schematically in FIG. 1 1 has an amplifier piston designed as a differential piston 2 out.
  • the booster piston 2 is formed by a low pressure piston 3 and a high pressure piston 4, with each other via a piston rod 5 are connected.
  • the low-pressure piston 3 is in here a low pressure cylinder 6 arranged and forms with this together the low pressure side.
  • the high pressure piston 4 is arranged in a high pressure cylinder 7 and forms the high pressure side together.
  • Of the Cross section of the high pressure cylinder 7, i.e. the effective Area on which pressure is exerted on the high pressure piston 4 can act is smaller than the cross-sectional area of the Low pressure cylinder 6.
  • the low pressure cylinder 6 is provided with a low pressure connection 8.
  • the high pressure cylinder 7 is provided with a high pressure connection 9.
  • the low-pressure piston 3 moves under the pressure of this fluid upwards.
  • the high pressure cylinder 7 is pressurized to to the ratio between the cross sectional area of the Low pressure piston 3 to the high pressure piston 4 is higher than the pressure in the low pressure cylinder 6.
  • the high pressure connection 9 is via a check valve 10 connected to a high pressure outlet 11.
  • the high-pressure cylinder 7 also has a supply connection 12 on that with a check valve 13 with a pressure source P is connected.
  • the pressure source P can be formed, for example, by a pump.
  • the control valve 14 is designed as a three-way valve that connects the low pressure 8 either with a cylinder line 24 the pressure source P or with a pressure sink T, for example a tank that connects.
  • a pump line 15 on the one hand, the as a branch line to the line between the pressure source P and the check valve 13 can be, and with a tank line 16 leading to the Pressure sink T leads.
  • the one Cylinder line 24 connected to the control valve.
  • the control valve 14 has a valve spool 17, which is arranged axially displaceably in a valve housing 18 is.
  • the valve slide 17 is also here designed as a differential piston.
  • the structure of the Control valve 14 is based on FIG. 2 below are explained in more detail.
  • an end face of the valve spool 17 with the pressure from a control line 19 can be applied is.
  • the control line 19 opens into the high pressure cylinder 7, at a point by the high pressure piston 4 is covered shortly after the high pressure piston 4 from its one end position towards has moved the high pressure port 9.
  • the other end of the valve spool 17 is the pressure of the pressure source P applied.
  • There is another branch line for this 20 provided in a pressure chamber 21 in Valve housing 18 opens.
  • the pressure chamber 21 has one smaller cross section than the bore 22 in which the end of the valve spool 17 moves that of the control line 19 is adjacent, and in which the control line 19 opens.
  • a line 23 can also be provided which the space between the low pressure piston 3 and the High pressure piston 4 connects to the pressure sink P.
  • Fig. 2 shows first of all the internal structure of the Control valve 14 with further details.
  • the valve spool 17 is axial in the valve housing 18 slidably mounted. Here he leaves on a part its length an annular space 25 between itself and the Valve housing 18 free.
  • the annulus is through one Control disk 26, which bears sealingly on the valve housing 18, divided into two axial areas that oppose each other are sealed.
  • Depending on the position of the valve spool 17 can therefore be an area of the annulus Mouth of the pump line 15 (P) with the cylinder line 24 (C) connect (Fig. 2a) or (Fig. 2d) the cylinder line 24 (C) with the tank line 16 (T).
  • the valve slide 17th necessary, which is the sum of the thickness of the control disc 26 and the axial extent of the mouth of the cylinder line 24 (C) corresponds. This route can be relative be small.
  • valve spool has 17 at the end that the mouth of the control line 19 (HP) faces a larger cross-sectional area (27) on than on its opposite end face 29, which is connected to the pressure chamber 21.
  • the valve slide 17 is graded accordingly.
  • the pressure room Accordingly, 21 also has a smaller one Cross section on as the end face 27 of the valve spool, to which the pressure HP from the control line 19 works.
  • valve spool 17 also has a movement stop 28, which ensures that the Pressure chamber 21 always has a predetermined minimum size. This size is such that the schematically shown Muzzle of the branch line 20 in any case is kept free. This stub 20 can be constructive Reasons here in the front of the Housing 18 are performed. This way, however ensured that no throttling and thus a pressure reduction takes place. On the valve spool So 17 always works regardless of position constant force.
  • Hydraulic fluid thus flows from the pressure source P. via the pump line 15, the control valve 14 and the Cylinder line 24 to the low pressure connection 8.
  • the low pressure cylinder 3 accordingly with the pressure the pump source P acts and moves the high pressure piston 4 up towards the high pressure connection 9 to.
  • the annular space is also 25 between the cylinder port C and the tank port T enlarged because here the thinner section of the valve spool 17 comes into play. This results in a relatively large cross section for the flow path of the Hydraulic fluid from cylinder port C to tank port T.
  • valve spool from a constant pressure is applied to its end face 29, can thereby achieve quite high frequencies that lead to a correspondingly faster refilling of the high pressure cylinder 7 and the low pressure cylinder 6.
  • the delivery amount of the fluid booster can be increased.

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)
  • Fluid-Driven Valves (AREA)
  • Multiple-Way Valves (AREA)
EP97111400A 1996-08-17 1997-07-05 Amplificateur de pression de fluide, particulièrement de fluide hydraulique Expired - Lifetime EP0825348B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19633258A DE19633258C1 (de) 1996-08-17 1996-08-17 Druckverstärker für Fluide, insbesondere für Hydraulikflüssigkeiten
DE19633258 1996-08-17

Publications (2)

Publication Number Publication Date
EP0825348A1 true EP0825348A1 (fr) 1998-02-25
EP0825348B1 EP0825348B1 (fr) 2001-09-19

Family

ID=7802934

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97111400A Expired - Lifetime EP0825348B1 (fr) 1996-08-17 1997-07-05 Amplificateur de pression de fluide, particulièrement de fluide hydraulique

Country Status (7)

Country Link
US (1) US6295914B1 (fr)
EP (1) EP0825348B1 (fr)
JP (1) JPH1078002A (fr)
KR (1) KR100225621B1 (fr)
CA (1) CA2211474C (fr)
DE (1) DE19633258C1 (fr)
DK (1) DK0825348T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008019889A1 (fr) * 2006-08-18 2008-02-21 Scanwill Aps Multiplicateur de pression comprenant une soupape à double siège

Families Citing this family (37)

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DE29818762U1 (de) * 1998-10-21 1998-12-24 Festo AG & Co, 73734 Esslingen Fluidbetätigte Arbeitsvorrichtung
JP4588161B2 (ja) * 2000-04-11 2010-11-24 株式会社コスメック 増圧ポンプ
DE10158181C1 (de) * 2001-11-28 2003-05-28 Minibooster Hydraulics As Soen Hydraulischer Druckverstärker
DE10158178C1 (de) * 2001-11-28 2003-07-17 Minibooster Hydraulics As Soen Hydraulischer Druckverstärker
KR100471264B1 (ko) * 2002-10-17 2005-03-08 현대자동차주식회사 공압 시스템의 공기 증압장치
DE10249523C5 (de) 2002-10-23 2015-12-24 Minibooster Hydraulics A/S Druckverstärker
DE10249524B4 (de) * 2002-10-23 2005-12-29 Minibooster Hydraulics A/S Fluid-Versorgungseinheit, insbesondere hydraulische Versorgungseinheit
DE20307245U1 (de) * 2003-05-08 2003-08-07 DBT GmbH, 44534 Lünen Ventil, insbesondere Rückschlagventil
PL202250B1 (pl) * 2003-05-08 2009-06-30 Dbt Gmbh Zawór hydrauliczny, zwłaszcza zawór zwrotny i podpora hydrauliczna, zwłaszcza stojak obudowy górniczej
DE10328286B4 (de) * 2003-06-23 2015-05-13 Caterpillar Global Mining Europe Gmbh Hydraulischer Schildausbau
DE102004007684C5 (de) * 2004-02-16 2010-01-07 Minibooster Hydraulics A/S Tragbares hydraulisches Werkzeug
DE102004017743A1 (de) * 2004-04-10 2005-12-08 Zöller-Kipper GmbH Verfahren und Vorrichtung zum Entleeren von Müllbehältern
DE102007017665A1 (de) 2007-04-14 2008-10-16 Uwe Hammer Hydraulischer Druckverstärker
DE102007031166A1 (de) 2007-07-04 2009-01-08 Uwe Hammer Hydraulischer Druckverstäker
DE102007031282A1 (de) 2007-07-05 2009-01-08 Uwe Hammer Hydraulischer Druckverstärker
KR101109539B1 (ko) * 2009-06-16 2012-01-31 한국기계연구원 정밀제어가 가능한 오일공급구조를 가지는 증압기
MY164106A (en) * 2011-10-19 2017-11-30 Cameron Int Corp Subsea pressure reduction system
DE102011088594A1 (de) * 2011-12-14 2013-06-20 Robert Bosch Gmbh Druckübersetzer, Verfahren zum Betreiben eines Druckübersetzers sowie Verwendung eines Druckübersetzers
FI124350B (en) * 2012-03-09 2014-07-15 Wärtsilä Finland Oy Hydraulic actuator
US8928161B2 (en) 2012-05-25 2015-01-06 Kcf Technologies, Inc. Apparatuses and methods for harvesting energy from prosthetic limbs
ITMO20120305A1 (it) * 2012-12-13 2014-06-14 Carelli Nicola Ing Metodo di produzione di energia da moto di rotolamento
JP6336862B2 (ja) 2014-09-04 2018-06-06 東芝テック株式会社 液体吐出装置
EP3034889B1 (fr) * 2014-12-18 2018-09-12 Scanwill Fluid Power ApS Multiplicateur de pression doté de douille de serrage
DE202015102590U1 (de) 2015-05-20 2016-08-23 Minibooster Hydraulics A/S Hydraulischer Druckverstärker
EP3242017B2 (fr) * 2016-05-04 2023-10-11 Scanwill Fluid Power ApS Multiplicateur de pression en tant que visseuse
JP6764272B2 (ja) * 2016-07-06 2020-09-30 芝浦機械株式会社 射出装置及び成形機
EP3318767B1 (fr) * 2016-11-04 2021-06-23 PistonPower ApS Actionneur hydraulique à amplificateur de pression
ES2891335T3 (es) * 2016-11-04 2022-01-27 Pistonpower Aps Actuador hidráulico con amplificador de presión de cartucho
EP3369927B1 (fr) * 2017-03-03 2019-04-24 PistonPower ApS Amplificateur de pression
EP3473863B1 (fr) * 2017-10-19 2021-02-24 PistonPower ApS Agencement amplificateur de pression hydraulique
PL3543460T3 (pl) 2018-03-19 2021-08-09 Caterpillar Global Mining Europe Gmbh Hydrauliczny układ wspornika osłony i wzmacniacz ciśnienia
CN108644162B (zh) * 2018-05-18 2019-10-08 佛山市力能液压机械有限公司 一种紧凑型液压增压器
SG11202100692TA (en) 2018-12-19 2021-02-25 Halliburton Energy Services Inc Methods and tools to deploy downhole elements
EP3730806B1 (fr) * 2019-04-24 2023-01-18 Piston Power s.r.o. Agencement d'actionneur hydraulique
DK3859166T3 (da) 2020-01-31 2022-03-21 Minibooster Hydraulics As Hydraulisk trykforstærkningsanordning
IT202000012133A1 (it) 2020-05-27 2021-11-27 Nicola Carelli Nuovo sistema per la produzione di energia elettrica e criptovalute mediante moto di rotolamento
US11808289B2 (en) * 2021-10-25 2023-11-07 Deere & Company Fluid pressure boost system and method

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US3540349A (en) * 1965-05-20 1970-11-17 Hermann Joseph Pennther Fluid-operated continuously actuated reciprocating piston drive
US3720484A (en) * 1970-03-04 1973-03-13 W Kirshsieper Hydraulic pressure transformer
US4288987A (en) * 1978-11-11 1981-09-15 Eugen Rapp Pneumo-hydraulic booster with rapid-traverse feature
DE3032430A1 (de) * 1980-08-28 1982-03-04 F.E. Schulte Strathaus Kg, 4750 Unna Vorrichtung zur erhoehung des druckes eines an einer druckmittelleitung anstehenden fluids fuer einen verbraucher
DE4026005A1 (de) * 1989-08-15 1991-02-21 Johannes Vagn Baatrup Fluid-druckverstaerker
GB2275969A (en) * 1993-03-01 1994-09-14 Europ Gas Turbines Ltd Hydraulic intensifier

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Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3540349A (en) * 1965-05-20 1970-11-17 Hermann Joseph Pennther Fluid-operated continuously actuated reciprocating piston drive
US3720484A (en) * 1970-03-04 1973-03-13 W Kirshsieper Hydraulic pressure transformer
US4288987A (en) * 1978-11-11 1981-09-15 Eugen Rapp Pneumo-hydraulic booster with rapid-traverse feature
DE3032430A1 (de) * 1980-08-28 1982-03-04 F.E. Schulte Strathaus Kg, 4750 Unna Vorrichtung zur erhoehung des druckes eines an einer druckmittelleitung anstehenden fluids fuer einen verbraucher
DE4026005A1 (de) * 1989-08-15 1991-02-21 Johannes Vagn Baatrup Fluid-druckverstaerker
GB2275969A (en) * 1993-03-01 1994-09-14 Europ Gas Turbines Ltd Hydraulic intensifier

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008019889A1 (fr) * 2006-08-18 2008-02-21 Scanwill Aps Multiplicateur de pression comprenant une soupape à double siège
US8613602B2 (en) 2006-08-18 2013-12-24 Scanwill Fluidpower Aps Pressure booster with double-seat valve

Also Published As

Publication number Publication date
DE19633258C1 (de) 1997-08-28
DK0825348T3 (da) 2002-01-21
JPH1078002A (ja) 1998-03-24
CA2211474C (fr) 2001-02-27
EP0825348B1 (fr) 2001-09-19
KR19980018740A (ko) 1998-06-05
CA2211474A1 (fr) 1998-02-17
KR100225621B1 (ko) 1999-10-15
US6295914B1 (en) 2001-10-02

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