WO2003002876A1 - Surpresseur - Google Patents

Surpresseur Download PDF

Info

Publication number
WO2003002876A1
WO2003002876A1 PCT/JP2002/006281 JP0206281W WO03002876A1 WO 2003002876 A1 WO2003002876 A1 WO 2003002876A1 JP 0206281 W JP0206281 W JP 0206281W WO 03002876 A1 WO03002876 A1 WO 03002876A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
pressure side
low
fluid
cylinder
Prior art date
Application number
PCT/JP2002/006281
Other languages
English (en)
Japanese (ja)
Inventor
Yukihiko Karasawa
Original Assignee
Karasawa Fine., Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Karasawa Fine., Ltd filed Critical Karasawa Fine., Ltd
Publication of WO2003002876A1 publication Critical patent/WO2003002876A1/fr

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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • F04B9/1053—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor one side of the double-acting liquid motor being always under the influence of the liquid under pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/107—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1172—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each pump piston in the two directions being obtained by a double-acting piston liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
    • F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1176—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
    • F04B9/1178—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor the movement in the other direction being obtained by a hydraulic connection between the liquid motor cylinders

Definitions

  • the present invention relates to a pressure intensifier for increasing the pressure of a fluid, and more particularly to a pressure intensifier suitable for a device in which a fluid having a high pressure is ejected from an opposed nozzle and the ejected fluids collide with each other.
  • FIG. 2 is a simplified view of the overall configuration of such a system for refining particles.
  • A is the low-pressure side fluid
  • B is the high-pressure side fluid.
  • the pipeline through which the low-pressure side fluid A flows is shown by a solid line
  • the pipeline through which the high-pressure side fluid B flows is shown by a dotted line. I have.
  • Oil is stored in the tank 1 as the low-pressure side fluid A.
  • This low-pressure fluid A is pumped by the pressure pump 2.
  • the low-pressure side fluid A discharged from the pressure pump 2 is adjusted to a predetermined pressure by the regulator 3 and reaches the two switching valves 4, 4. Excess fluid of low-pressure fluid A that reaches regulation 3 is returned to tank 1 by the relief valve in regulation 3.
  • Each switching valve 4, 4 5, the discharge conduit of each it it two are connected.
  • the switching valves 4 and 4 ′ can be switched to either a state in which the low-pressure side fluid A is supplied to one of these pipelines, or a closed state in which the low-pressure side fluid A is not supplied to either of them.
  • Discharge conduit connected to the switching valve 4 is connected to the intensifier 5, a discharge conduit connected to the switching valve 4 'is connected to the intensifier 5 5.
  • FIG. 3 is an enlarged sectional view of the pressure intensifier 5.
  • the pressure intensifier 5 is a stack of two upper and lower cases 51 and 52. Inside the lower pressure cylinder 53 and the high pressure cylinder 54 There are two cylindrical spaces. A piston 55 is fitted inside these.
  • the piston 55 is made up of a large-diameter piston and a small-diameter piston, and is shaped like a disk with a round bar.
  • the disk portion is a large-diameter piston, that is, a low-pressure piston 55a, which divides the low-pressure cylinder 53 into a primary space 53a and a secondary space 53b.
  • the portion of the round bar is a small diameter piston, that is, the high pressure side piston 55b, which moves in the high pressure side cylinder 54.
  • the cross-sectional area of the low-pressure side cylinder 53 and the cross-sectional area of the high-pressure side cylinder 54 are the inverse ratio of the pressure increase ratio of the pressure booster 5. For example, if the pressure increase ratio is 20 times, the sectional area of the high-pressure cylinder 54 is 1 Z20 which is the sectional area of the low-pressure cylinder 53.
  • one on the primary side space 5 3 a, 5 3 a 5, is connected to one of the switching valve 4, 4 5 discharge conduit of the secondary space 5 3 b, 5 3 b 'is The other end of the discharge line is connected.
  • the high pressure side cylinders 54, 54 ' are connected to the pipeline of the high pressure side fluid B, which are connected to the check valves 6, 6, respectively.
  • the check valves 6 and 6 ′ are configured such that the fluid flows in the direction of the arrow in the figure but does not flow in the reverse direction.
  • the high-pressure side fluid B is stored in the tank 7.
  • the high-pressure fluid B refers to a mixture of a plurality of immiscible liquids, such as water and oil, and various slurries.
  • the high-pressure side fluid B in the tank 7 reaches the air pump 8 through a pipe extending from below the tank 7, is sent out by the air pump 8, and is divided into two pipes. To reach check valves 6, 6,.
  • the pistons 55, 55 'descend and the intensifiers 5, 5, 5 are pressurized, the high-pressure fluid B from the air pump 8 cannot pass through the check valves 6, 6'.
  • the piston 5 5, 5 5, intensifier 5 rises, 5 if 5 is being reduced pressure, the higher the direction of pressure of the high-pressure side fluid B of the air first pump 8 side, the high pressure side fluid B is the high pressure side cylinder Enter into 5, 4, 5 and.
  • Reference numeral 9 denotes a jet impingement portion where the jet of the high-pressure fluid impinges. Details of the configuration here are described in Japanese Patent Application Laid-Open No. 6-472264. To explain the point, check valve 6, 6 5 high pressure fluid came through the can, in the jet impingement portion 9, is split into two flow paths, provided opposite to each flow path terminal Injected from nozzles 91 and 91. When the fluid ejected from one nozzle collides with the fluid ejected from the other nozzle, the particles contained in the slurry are pulverized or the water and oil particles become finer and become emulsified. become.
  • the high-pressure side fluid B collided in the jet impingement section 9 returns to the ink tank 7 again, circulates and is repeatedly collided until the desired emulsification degree and particle diameter are reached.
  • the high-pressure fluid B to be increased in pressure is generally an incompressible fluid, but is in a high-pressure region.
  • the compressibility is not negligible (the compressibility of water at 200 MPa is about 8.5%). Therefore, the above-mentioned over-wrapping time also requires a time for compressing the high-pressure side fluid B, which is prolonged accordingly.
  • the pressure pump 2 needs a discharge pressure and a discharge amount capable of simultaneously increasing the pressures of the two pressure intensifiers 5 and 5 ′, and the pressure pump 2 has been increased in size.
  • the switching valve 4, 4 5 is a Sorenoido valve, loud sound when switching occurs, causing noise.
  • the present invention has been made in view of the above facts, and has as its object to provide a pressure intensifier capable of reducing the size of a pump and reducing pulsation during switching. Another object of the present invention is to provide a pressure increasing device which does not require a switching valve, has low noise, and has high durability. Disclosure of the invention
  • a pressure booster of the present invention includes a plurality of pressure boosters and a plurality of pumps for supplying a low-pressure side fluid for driving to the pressure boosters, wherein one of the pumps is a plurality of the plurality of pressure boosters.
  • One of the boosters is supplied with the low-pressure side fluid, and the other pressure boosters are combined with the pumps so that the low-pressure side fluid is not supplied.
  • the pressure intensifier includes a low pressure side cylinder, a high pressure side cylinder, a low pressure side piston that divides the low pressure side cylinder into a primary space and a secondary space, and the high pressure side formed integrally with the low pressure side piston.
  • the pump has a high-pressure side piston that moves forward and backward in the cylinder, and each of the pumps is rotatable forward and backward. The pump is connected to the primary space of each of the low-pressure cylinders. Connected to two or more pressurizers be able to.
  • the pump may be provided in the low-pressure side fluid, or the intensifier may be
  • Two high pressure side cylinders of both boosters are connected to both ends of a first check valve group and a second check valve group arranged in parallel, and the first check valve group is connected to both high pressure side cylinders.
  • the second check valve group is connected in such a direction as to allow the flow from the high pressure side fluid from the middle to the high pressure side fluid. Can be supplied.
  • FIG. 1 is a diagram showing a configuration of a pressure booster of the present invention
  • FIG. 2 is a diagram showing a configuration of a conventional pressure booster
  • FIG. 3 is a cross-sectional view showing a configuration of a pressure booster.
  • FIG. 1 is a diagram showing a configuration of a pressure booster of the present invention.
  • the same components as those of the conventional example, such as the pressure intensifiers 5 and 5 ′, the air pump 8, and the jet impingement section 9, are denoted by the same reference numerals and description thereof is omitted.
  • the tanks 10 and 10 ′ are filled with the low-pressure side fluid A.
  • Tank 10 has a pressure pump 11, and tank 10 ′ has a pressure pump 11 ′, which is immersed in the liquid.
  • the tank 1 0, 1 0 5 need not be divided into two tanks, two pressure pumps 1 1 in a single tank, 1 1 may be immersed.
  • the pressure pump 1 1, 1 I 5 by making crushed immersed in oil as the low-pressure side fluid A, it is possible to downsize and soundproofing spoon pressure pump.
  • the use of a hydraulic pressure-intensifying high-pressure pump in an explosion-proof area is based on the requirement of explosion-proof or intrinsically safe explosion-proof. Except for the above, there is an advantage that this necessity is inevitably eliminated because all the points where sparks such as electric contacts are present in the hydraulic oil.
  • the discharge port of the pressure pump 11 is connected to the primary space 5 3 a of the low-pressure cylinder 5 3 of the booster 5.
  • the discharge port of the pressure pump 11 1 ′ is connected to the low-pressure cylinder 5 3 ′ of the pressure booster 5. It is connected to the primary side space 53 a 5.
  • the discharge pressures of the pressure pumps 11, 11 ' are monitored by pressure gauges 12, 12, and are controlled by a control device (not shown) so as to reach a predetermined pressure.
  • the secondary spaces 53b, 53b 'of the low-pressure cylinders 53, 53' are connected to the pressurizer 13.
  • an accumulator in which gas and fluid are sealed is used as the pressurizer 13.
  • a third pressure pump can be used as the pressurizer 13.
  • the pressure pump 11 is rotated in the forward direction, and the low-pressure side fluid A is sent to the primary space 53 a of the intensifier 5 while monitoring the discharge pressure with the pressure gauge 12.
  • the piston 55 descends, and the high-pressure fluid B in the high-pressure cylinder 54 is pressurized to a high pressure and sent out. Further, the gas contained in the secondary space 53b is compressed and stored in the pressurizer 13.
  • the pressure pump 11 To raise the piston 55 of the pressure intensifier 5, the pressure pump 11 is rotated in the opposite direction. As a result, the low-pressure side fluid A filling the primary space 53a is extracted. The piston 55 is raised by the negative pressure at the time of the removal. Further, since the pressure in the secondary space 53b decreases, the fluid that has entered the pressurizer 13 is pushed by the gas and returns here, and pushes up the piston 55.
  • the pressure intensifier 5 and the pressure intensifier 5 are arranged such that the pressure intensification of the high pressure side fluid B and the pressure fluctuation of the high pressure side fluid B start immediately before the compression stroke of the high pressure side fluid B in one of the pressure intensifiers ends. Pulsation is prevented from occurring. Therefore, the pressurizer 13 generally repeats the state of receiving the compressed gas from the secondary space of one of the pressure intensifiers and supplying the gas to the other secondary space while reversing the state.
  • the first check valve group 14 has two check valves 14a, 14a, both of which are in a direction that allows the flow of the high-pressure side fluid B from the high-pressure side cylinders 54, 54 '. .
  • a pipe is provided between the two check valves 14a and 14a, and the pipe communicates with the jet impingement section 9. That is, the high-pressure fluid B discharged from the high-pressure cylinders 54, 54, whose pistons 55, 55 'are descending, is sent to the jet impingement section 9 through the check valve 14a.
  • the high-pressure side fluid B pressurized to a high pressure is ejected from the opposed nozzles 91, 91 to collide with each other.
  • the second check valve group 15 has two check valves 15a, 15a, both of which are in the direction of blocking the flow of the high-pressure side fluid B from the high-pressure side cylinders 54, 54 '.
  • the pressure increase ratio of the pressure intensifier is determined by the ratio of the cross-sectional areas of the high-pressure cylinder 54 and the low-pressure cylinder 53. However, these are manufactured by machining, and it is difficult to manufacture an equal cross-sectional area ratio for any two intensifiers.
  • the pressure at the jet impingement section 9 will differ when the pressure intensifier 5 is activated and when the pressure intensifier 5 'is activated.
  • the present invention According to this embodiment, the pressure of the low-pressure side fluid A can be made different from each other, so that the pressure fluctuation in the jet impingement section 9 can be suppressed to a small value.
  • the present invention includes a plurality of pressure intensifiers and a plurality of pumps for supplying a low-pressure side fluid for driving to the pressure intensifiers, wherein one of the pumps is one of the plurality of pressure intensifiers
  • the low pressure side fluid is supplied to the pressure booster and the other pressure intensifiers are connected to each other so that the low pressure side fluid is not supplied.
  • the size of the pump can be reduced by eliminating waste of the pump.
  • the pressure intensifier includes a low pressure side cylinder, a high pressure side cylinder, a low pressure side piston that divides the low pressure side cylinder into a primary space and a secondary space, and the high pressure side formed integrally with the low pressure side piston.
  • the pump has a high-pressure side piston that moves forward and backward in the cylinder, and each of the pumps is freely rotatable forward and backward. The pump is connected to the primary space of each of the low-pressure cylinders. If the configuration is connected to two or more pressurizers,
  • the piping can be simplified.
  • the two pressure intensifiers are connected to each other, and the high pressure side cylinders of both pressure intensifiers are connected to both ends of a first check valve group and a second check valve group arranged in parallel.
  • the second check valve group is connected in a direction that allows the flow from the high-pressure side cylinder, allows the high-pressure side fluid to be discharged from the middle, and is connected in a direction that blocks the flow from both high-pressure side cylinders.

Landscapes

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

Abstract

L'invention porte sur un surpresseur permettant de réduire la taille d'une pompe, éliminant la nécessité d'une vanne de sélection et abaissant le bruit, et comportant deux unités de surpression (5, 5') et des pompes (11, 11') fournissant du fluide au côté basse pression des unités de surpression, un cylindre (53) côté basse pression, et un cylindre (54) côté haute pression. Le cylindre basse pression est divisé en un espace primaire (53a) et un espace secondaire (53b) par un piston côté basse pression (55a) d'une seule pièce avec un piston côté haute pression (55b). La pompe (11), qui peut tourner dans le sens positif et dans le sens inverse, est reliée à l'espace primaire du cylindre basse pression, tandis que l'espace secondaire du cylindre basse pression est relié à un pressuriser (13). Lorsque la pompe (11) tourne dans le sens positif, le fluide (A) pénètre dans l'espace primaire (53a) et comprime le fluide (B) du cylindre côté haute pression (54). Lorsque la pompe (11) tourne dans le sens inverse, du gaz provenant du pressuriseur (13) pénètre dans l'espace secondaire (53b) et soulève le piston (55) aspirant ainsi le fluide (B) dans le cylindre côté haute pression (54).
PCT/JP2002/006281 2001-06-27 2002-06-24 Surpresseur WO2003002876A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001194066A JP2003013904A (ja) 2001-06-27 2001-06-27 増圧装置
JP2001-194066 2001-06-27

Publications (1)

Publication Number Publication Date
WO2003002876A1 true WO2003002876A1 (fr) 2003-01-09

Family

ID=19032252

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2002/006281 WO2003002876A1 (fr) 2001-06-27 2002-06-24 Surpresseur

Country Status (3)

Country Link
JP (1) JP2003013904A (fr)
TW (1) TW568982B (fr)
WO (1) WO2003002876A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007147914A1 (fr) * 2006-06-13 2007-12-27 Prextor Systems, S.L. Échangeurs de pression à chambres divisées (ipcd)
ES2321999A1 (es) * 2006-06-13 2009-06-15 Fernando Ruiz del Olmo Nuevas disposiciones de los intercambiadores de presion de camaras desdobladas (ipcd). camaras telescopicas, tipo fuelle, de membrana o mixtas e intercambiadores de presion de camaras desdobladas multietapa (ipcdm).
CN102251995A (zh) * 2011-07-06 2011-11-23 山东赛克赛斯氢能源有限公司 水压式气体增压机
WO2017197023A1 (fr) 2016-05-12 2017-11-16 Hewlett-Packard Development Company, L.P. Extraction d'objets imprimés en 3d
CN107660258A (zh) * 2015-03-27 2018-02-02 郭仓淳 增压泵一体整合式液压缸

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101655420B1 (ko) * 2013-03-04 2016-09-22 주식회사 하이시스 부스터펌프 장치 일체형 증압실린더
JP6572872B2 (ja) 2016-11-22 2019-09-11 Smc株式会社 増圧装置
CN112555206B (zh) * 2020-12-15 2023-01-06 潍柴动力股份有限公司 一种液压控制系统及青贮饲料收获机
CN117916473A (zh) * 2021-09-21 2024-04-19 伊格尔工业股份有限公司 流体回路

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61122402U (fr) * 1985-01-18 1986-08-01
JPH03128882A (ja) * 1989-10-13 1991-05-31 Mitsubishi Electric Corp 油圧エレベータのパワーユニット
JPH0727103A (ja) * 1993-07-14 1995-01-27 Daikin Ind Ltd 超高圧発生装置
US5894830A (en) * 1997-12-15 1999-04-20 Caterpillar Inc. Engine having a high pressure hydraulic system and low pressure lubricating system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61122402U (fr) * 1985-01-18 1986-08-01
JPH03128882A (ja) * 1989-10-13 1991-05-31 Mitsubishi Electric Corp 油圧エレベータのパワーユニット
JPH0727103A (ja) * 1993-07-14 1995-01-27 Daikin Ind Ltd 超高圧発生装置
US5894830A (en) * 1997-12-15 1999-04-20 Caterpillar Inc. Engine having a high pressure hydraulic system and low pressure lubricating system

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007147914A1 (fr) * 2006-06-13 2007-12-27 Prextor Systems, S.L. Échangeurs de pression à chambres divisées (ipcd)
ES2321999A1 (es) * 2006-06-13 2009-06-15 Fernando Ruiz del Olmo Nuevas disposiciones de los intercambiadores de presion de camaras desdobladas (ipcd). camaras telescopicas, tipo fuelle, de membrana o mixtas e intercambiadores de presion de camaras desdobladas multietapa (ipcdm).
ES2321997A1 (es) * 2006-06-13 2009-06-15 Fernando Ruiz del Olmo Intercambiadores de presion de camaras desdobladas (ipcd). funcionamiento a la inversa asistido y metodo de aprovechamiento energetico de las diferencias de nivel de cualquier material en cualquier forma de almacenamiento.
CN102251995A (zh) * 2011-07-06 2011-11-23 山东赛克赛斯氢能源有限公司 水压式气体增压机
CN107660258A (zh) * 2015-03-27 2018-02-02 郭仓淳 增压泵一体整合式液压缸
CN107660258B (zh) * 2015-03-27 2019-08-09 郭仓淳 增压泵一体整合式液压缸
WO2017197023A1 (fr) 2016-05-12 2017-11-16 Hewlett-Packard Development Company, L.P. Extraction d'objets imprimés en 3d

Also Published As

Publication number Publication date
TW568982B (en) 2004-01-01
JP2003013904A (ja) 2003-01-15

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