EP2837823B1 - Hydraulikmaschine, insbesondere Hydraulikdruckaustauscher - Google Patents

Hydraulikmaschine, insbesondere Hydraulikdruckaustauscher Download PDF

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Publication number
EP2837823B1
EP2837823B1 EP13180505.3A EP13180505A EP2837823B1 EP 2837823 B1 EP2837823 B1 EP 2837823B1 EP 13180505 A EP13180505 A EP 13180505A EP 2837823 B1 EP2837823 B1 EP 2837823B1
Authority
EP
European Patent Office
Prior art keywords
pressure
drum
front plate
shoe
exchanger according
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.)
Not-in-force
Application number
EP13180505.3A
Other languages
English (en)
French (fr)
Other versions
EP2837823A1 (de
Inventor
Haraldur Sigurdsson
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.)
Danfoss AS
Original Assignee
Danfoss AS
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 Danfoss AS filed Critical Danfoss AS
Priority to EP13180505.3A priority Critical patent/EP2837823B1/de
Priority to IN1894DE2014 priority patent/IN2014DE01894A/en
Priority to US14/450,397 priority patent/US20150050177A1/en
Priority to CN201410400069.3A priority patent/CN104373316B/zh
Publication of EP2837823A1 publication Critical patent/EP2837823A1/de
Application granted granted Critical
Publication of EP2837823B1 publication Critical patent/EP2837823B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F04B1/24—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons inclined to the main shaft axis
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2007—Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F13/00—Pressure exchangers

Definitions

  • the invention relates to a pressure exchanger comprising a drum rotatable about a rotational axis, a motor connection for driving said drum, a first front plate arrangement at a first front face of said drum, a second front plate arrangement at a second face of said drum, said drum comprising a plurality of cylinders, said first front plate arrangement comprising a first front plate and a pressure shoe, said first front plate comprising at least a port.
  • a pressure exchanger of this kind can be used for example in a reverse osmosis system in which the liquid is pumped through a membrane under a rather high pressure. The liquid not passing the membrane is supplied to the high pressure supply port of the pressure exchanger. This high pressure is transferred to a fluid being supplied to the second front face of the drum.
  • a piston in each cylinder is used to affect the pressure transfer. When a cylinder is in fluid connection with the high pressure supply port high pressure fluid enters this cylinder and shifts the piston to the other side, thereby transferring the high pressure to the liquid on the other side. The drum rotates. After a predeterment rotational angle this cylinder comes in contact to a low pressure supply port in which fresh liquid under a lower pressure fills the cylinder shifting the piston back again.
  • each cylinder is provided with a bushing at each end. This bushing is pressed axially outwardly to contact the pressure shoe with a force being high enough to establish the necessary tightness. This force is also used to press the pressure shoe at each front face axially outwardly so that the pressure shoes rests against the front plates at each front face of said drum.
  • the object underlying the invention is to have a simple construction of a hydraulic machine.
  • a hydraulic machine as mentioned above in that said pressure shoe is movable relative to the drum in a direction of said rotational axis and comprises at least a high pressure channel connected to said port and an outer pressure area loaded by a pressure in said port in a direction towards said drum, said outer pressure area being larger than an inner pressure area on a side of said pressure shoe facing said drum, whereby the force on the pressure shoe acting in a direction towards the drum is larger than the force acting in the opposite direction so that the pressure shoe is firmly pressed against the drum.
  • drum is used for the purpose of explanation only. It is not necessary that the “drum” is cylindrical body.
  • drum just means a carrier of the cylinders mentioned above which is rotatable about the rotational axis.
  • the cylinders can have a cross section which may be circular or may have any other form.
  • the cylinders may be straight or curved in longitudinal direction.
  • the pressure shoe is pressed against the front face of the drum by means of the pressure at the high pressure supply port. A pressure shoe is necessary only on one side. The other side of the drum rests against the second front plate arrangement. In this way equal pressures on both front faces of the drum can be realised.
  • said pressure shoe is held unrotatable.
  • the first front face of the drum rests against the pressure shoe and friction is generated between this front face and the pressure shoe only. This reduces wear. Since the pressure shoe is not rotating, the number of bushings needed is dramatically reduced. Only one bushing is necessary for the high pressure port connecting said first front plate and said pressure shoe. A second bushing may be necessary between the first front plate and the pressure shoe in a region of another port. The pressure shoe can be moved in the direction of the rotational axis only, wherein such movement is very small.
  • said outer pressure area is arranged within said channel. No other areas are necessary.
  • the liquid entering the channel acts automatically on the outer pressure area.
  • said channel comprises a section area decreasing in a direction towards said drum.
  • the decreasing section area automatically provides the outer pressure area on which the pressure acts at the high pressure supply port.
  • said high pressure channel comprises a circle-shaped inlet on a side facing said first front plate and a kidney-shaped outlet on a side facing said drum.
  • the circle-shaped inlet comprises an area which is larger than the kidney-shaped outlet. The difference between the area of the circle-shaped inlet and the kidney-shaped outlet is the area on which the pressure at the high pressure supply port acts in a direction towards the drum.
  • a sleeve is inserted in said high pressure channel in said pressure shoe and in said port in said first front plate.
  • This sleeve makes a fluid tight path between the first front plate and the pressure shoe.
  • a circle-shaped inlet it is rather simple to use a cylindrical sleeve.
  • said sleeve is fixed in said pressure shoe and movable and sealed in said first front plate. The movement is restricted to the axial direction and allows to establish sufficient pressure contact between the pressure shoe and the front face of the drum.
  • said first front plate comprises two ports the centres of which are arranged on a first straight line and said second front plate arrangement comprises a second front plate with two ports the centres of which are arranged on a second straight line, said first straight line and said second straight line being angularly offset to each other.
  • said connecting lines on one side extending in a first direction and connection lines at the other side extending in a second direction which is angularly offset to the first direction. This gives a greater freedom in the arrangement of connecting lines.
  • one of said front plates comprises a connecting geometry having at least a first mounting surface in which one of the ports is arranged, said first mounting surface being arranged under a predetermined angle relative to the rotational axis of said drum, said angle being in the range of 10° to 80°, in particular in the range of 30° to 60°, and preferably in the range of 40° of 50°.
  • the mounting surface is arranged under an angle relative to the rotational axis and relative to a plane which is perpendicular to the rotational axis there is a larger area available for connecting a line to the mounting surface.
  • said pressure shoe rests against said drum in a contact area, two different materials contacting each other in said contact area, one material being steel and the other material being a plastic material sliding with slow friction on steel, in particular a high-resistant thermoplastic plastic material on the basis of polyaryl etherketones, particularly polyetheretherketones (PEEK), polyamides, polyacetals, polyarylethers, polyethylene terephthalates, polyphenylene sulfides, polysulphones, polyether sulphones, polyether imides, polyamide imides, polyacrylates, phenol resins, like novolacquer resins or the like, preferably provided with a filling of glass, graphite, polytetraflourethylene or carbon, the fillings being particularly useful as fibres.
  • the hydraulic machine and advantages be used as a water hydraulic device.
  • Fig. 1 shows a hydraulic machine 1 in form of a hydraulic pressure exchanger in a schematically longitudinal section.
  • hydraulic machine can also be, for example, a pump, a motor, an energy converter, an amplifier etc.
  • the hydraulic machine 1 comprises a drum 2 rotatable about an axis 3.
  • the term "drum” is used to facilitate the explanation. It is not necessary that this drum 2 is of cylindrical form.
  • the main purpose of the drum 2 is to form a basis for cylinders 4.
  • the cylinders 4 can be considered as channels. It is not necessary that they are of circular cross section.
  • a first front plate arrangement 5 is arranged at a first front face of the drum 2.
  • a second front plate arrangement 6 is arranged at a second front face of the drum 2 which is opposite of the first front face of the drum 2.
  • the first front plate arrangement 5 comprises a first front plate 7 and a pressure shoe 8. Further more, sealing means 9 are provided at the first front plate arrangement 5.
  • the first front plate 7 comprises a first port 10 and a second port 11.
  • the first port 10 may be a high pressure supply port and the second port 11 may be a low pressure return port. However, other pressures and other flow directions may be possible.
  • the first front plate 7 is connected to a housing 12.
  • the housing 12 is connected to a second front plate 13 which is arranged on the opposite side of the housing 12 relative to the first front plate 7.
  • the second front plate 13 is part of the second front plate arrangement 6.
  • Means for rotatably supporting and driving the drum 2 are not shown in order to keep the illustration simple.
  • the drum 2 can be rotatable supported within the housing 12.
  • a driving shaft can be passed through the second front plate 13 and be connected to a motor (not shown).
  • the pressure shoe 8 is supported unrotatably in the housing 12 so that it remains stationary in rotating direction relative to the first front plate 7.
  • a bushing or sleeve 14 is inserted into an inlet 15 ( Fig. 2 ) of the pressure shoe 8.
  • This inlet 15 has the form of a circle, so that the sleeve 14 can be made as a hollow cylinder.
  • the sleeve 14 is inserted as well in the first port 10.
  • the sealing means 19 are used to form a fluid tight connection between the first port 10 and the inlet 15 of the pressure shoe 8.
  • the pressure shoe 8 shows at the side opposite to the inlet 15 an outlet 16 having the form of a kidney.
  • the side of the pressure shoe 8 in which the kidney-shaped outlet 16 is arranged faces the drum 2.
  • the kidney-shaped outlet 16 is arranged on the same radius as the cylinders 4. Therefore, the openings of the cylinders 4 come in overlapping relation with the kidney-shaped outlet 16 during a rotation of the drum.
  • the pressure shoe 8 comprises a high pressure channel 17 between the first port 10 and the drum 2.
  • the outer pressure area is larger than an inner pressure area 19 on a side of said pressure shoe 8 facing said drum 2.
  • the force on the pressure shoe 8 acting in a direction towards the drum 2 is larger than the force acting in the opposite direction so that the pressure shoe 8 is firmly pressed against the drum 2.
  • the effect is that a pressure tight connection is formed between the high pressure channel 17 and the cylinders 4 overlapping the kidney-shaped outlet 16.
  • the force acting in direction towards the drum 2 is a product of the pressure in the first port 10 and the outer pressure area 18.
  • the force acting in the opposite direction is the product of the same pressure and the slightly smaller inner pressure area 19.
  • the pressure shoe 8 can be moved in axial direction, i.e. parallel to the axis 3. Such a movement is necessary only to press the pressure shoe 8 against the drum 2. Therefore, such a movement can be kept very small.
  • the first front plate 7 comprises two ports (only the second port 11 is visible). These ports are arranged on a first straight line.
  • the second front plate 13 comprises two ports as well, i.e. a first port 20 and a second port (not visible).
  • the last two ports are arranged on a straight line as well.
  • these two straight lines are angularly offset to each other.
  • the first straight line is arranged vertically and the second straight line is arranged on the angle of 45° relative to the vertical direction.
  • the first front plate 7 comprises a connecting geometry having at least a mounting surface 21, 22.
  • the mounting surfaces 21, 22 are arranged under a predetermined angle relative to the rotational axis 3 of the drum 2. In the present case, this angle is approximately 45°. However, it can be in the range of 10° to 80°, and particular in the range of 30° to 60°and preferably in the range of 40° to 50°.
  • the pressure shoe 8 and the drum 2 rest against each other in a contact area.
  • this contact area at least the surfaces of the drum 2 and the pressure shoe 8, respectively, have different materials, one material is steel and the other material is a plastic material, said plastic material having a low friction coefficient on steel.
  • This plastic material is in particular a high-resistant thermoplastic plastic material on the basis of polyaryl etherketones, particularly polyetheretherketones (PEEK), polyamides, polyacetals, polyarylethers, polyethylene terephthalates, polyphenylene sulfides, polysulphones, polyether sulphones, polyether imides, polyamide imides, polyacrylates, phenol resins, like novolacquer resins or the like, preferably provided with a filling of glass, graphite, polytetraflourethylene or carbon, the fillings being particularly useful as fibres.
  • PEEK polyetheretherketones
  • polyamides polyacetals
  • polyarylethers polyethylene terephthalates
  • polyphenylene sulfides polysulphones
  • polyether sulphones polyether imides
  • polyamide imides polyacrylates
  • phenol resins like novolacquer resins or the like
  • Such a combination of materials guarantee a

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Hydraulic Motors (AREA)

Claims (10)

  1. Druckaustauscher (1), umfassend eine Trommel (2), die um eine Drehachse (3) drehbar ist, eine Motorverbindung zum Antreiben der Trommel (2), eine erste vordere Plattenanordnung (5) an einer ersten vorderen Fläche der Trommel (2), eine zweite vordere Plattenanordnung (6) an einer zweiten vorderen Fläche der Trommel (2), wobei die Trommel (2) mehrere Zylinder (4) umfasst, wobei die erste vordere Plattenanordnung (5) eine erste vordere Platte (7) und einen Druckschuh (8) umfasst, wobei die vordere Platte (7) mindestens eine Anschlussöffnung (10) umfasst, dadurch gekennzeichnet, dass der Druckschuh (8) in Bezug auf die Trommel (2) in einer Richtung der Drehachse (3) beweglich ist und mindestens einen Hochdruckkanal (17) umfasst, der mit der Anschlussöffnung (10) und einem äußeren Druckbereich (18), der durch einen Druck in der Anschlussöffnung (10) in einer Richtung zur Trommel (2) hin geladen wird, verbunden ist, wobei der Druckbereich (18) größer als ein innerer Druckbereich (19) auf einer Seite des Druckschuhs (8) ist, der zur Trommel (2) weist, wodurch die Kraft auf den Druckschuh (8), die in einer Richtung zur Trommel (2) hin wirkt, größer ist als die Kraft, die in Gegenrichtung wirkt, sodass der Druckschuh (8) fest gegen die Trommel (2) gedrückt wird.
  2. Druckaustauscher nach Anspruch 1, dadurch gekennzeichnet, dass der Druckschuh (8) nicht drehbar gehalten wird.
  3. Druckaustauscher nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der äußere Druckbereich (18) innerhalb des Kanals (17) angeordnet ist.
  4. Druckaustauscher nach Anspruch 3, dadurch gekennzeichnet, dass der Kanal (17) einen Schnittbereich umfasst, der in einer Richtung zur Trommel (2) hin abnimmt.
  5. Druckaustauscher nach Anspruch 4, dadurch gekennzeichnet, dass der Hochdruckkanal (17) einen kreisförmigen Einlass (15) auf einer Seite umfasst, die zur ersten vorderen Platte (7) weist, und einen nierenförmigen Auslass (16) auf einer Seite, die zur Trommel (2) weist.
  6. Druckaustauscher nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass eine Hülse (14) in den hohen Druckkanal (17) in den Druckschuh (8) und in die Hochdruck-Versorgungsanschlussöffnung (10) in der ersten vorderen Platte (7) eingeführt wird.
  7. Druckaustauscher nach Anspruch 6, dadurch gekennzeichnet, dass die Hülse (14) in dem Druckschuh (8) befestigt ist und in der ersten vorderen Platte (7) beweglich und abgedichtet ist.
  8. Druckaustauscher nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die erste vordere Platte (7) zwei Anschlussöffnungen (10, 11) aufweist, deren Mitten auf einer ersten geraden Linie angeordnet sind, wobei die zweite vordere Plattenanordnung (6) eine zweite vordere Platte mit zwei Anschlussöffnungen (20) umfasst, deren Mitten auf einer zweiten geraden Linie angeordnet sind, wobei die erste gerade Linie und die zweite gerade Linie in einem Winkel voneinander versetzt sind.
  9. Druckaustauscher nach Anspruch 8, dadurch gekennzeichnet, dass mindestens eine der vorderen Platten (7, 13) eine Verbindungsgeometrie umfasst, die mindestens eine erste Montagefläche (21, 22) aufweist, in der eine der Anschlussöffnungen (10, 11) angeordnet ist, wobei die erste Montagefläche (21, 22) in einem vorbestimmten Winkel in Bezug auf die Drehachse (3) der Trommel (2) angeordnet ist, wobei der Winkel in dem Bereich von 10° bis 80° liegt, insbesondere im Bereich von 30° bis 60° und bevorzugt im Bereich von 40° bis 50°.
  10. Druckaustauscher nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass der Druckschuh (8) an der Trommel (2) in einem Kontaktbereich anliegt, wobei zwei unterschiedliche Materialien in dem Kontaktbereich miteinander in Kontakt treten, wobei ein Material Stahl und das andere Material ein Kunststoffmaterial ist, das mit geringer Reibung auf Stahl gleitet, insbesondere ein hochbeständiges thermoplastisches Kunststoffmaterial auf Basis von Polyaryletherketonen, insbesondere Polyetheretherketonen (PEEK), Polyamiden, Polyacetalen, Polyarylether, Polyethylenterephthalaten, Polyphenylensulfiden, Polysulfonen, Polyethersulfonen, Polyetherimiden, Polyamidimiden, Polyacrylaten, Phenolharzen, wie Novolackharzen oder dergleichen, die vorzugsweise mit einer Füllung aus Glas, Graphit, Polytetraflourethylen oder Kohlenstoff bereitgestellt sind, wobei die Füllungen insbesondere als Fasern nützlich sind.
EP13180505.3A 2013-08-15 2013-08-15 Hydraulikmaschine, insbesondere Hydraulikdruckaustauscher Not-in-force EP2837823B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP13180505.3A EP2837823B1 (de) 2013-08-15 2013-08-15 Hydraulikmaschine, insbesondere Hydraulikdruckaustauscher
IN1894DE2014 IN2014DE01894A (de) 2013-08-15 2014-07-08
US14/450,397 US20150050177A1 (en) 2013-08-15 2014-08-04 Hydraulic machine, in particular hydraulic pressure exchanger
CN201410400069.3A CN104373316B (zh) 2013-08-15 2014-08-14 液压机，特别是液压压力交换器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13180505.3A EP2837823B1 (de) 2013-08-15 2013-08-15 Hydraulikmaschine, insbesondere Hydraulikdruckaustauscher

Publications (2)

Publication Number Publication Date
EP2837823A1 EP2837823A1 (de) 2015-02-18
EP2837823B1 true EP2837823B1 (de) 2017-04-26

Family

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Application Number Title Priority Date Filing Date
EP13180505.3A Not-in-force EP2837823B1 (de) 2013-08-15 2013-08-15 Hydraulikmaschine, insbesondere Hydraulikdruckaustauscher

Country Status (4)

Country Link
US (1) US20150050177A1 (de)
EP (1) EP2837823B1 (de)
CN (1) CN104373316B (de)
IN (1) IN2014DE01894A (de)

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DE102017121334A1 (de) * 2017-09-14 2019-03-14 Danfoss Power Solution GmbH & Co OHG Steuerscheibe mit erhöhter Steifigkeit und Verfahren zur Herstellung einer solchen Steuerscheibe
CN109003723A (zh) * 2018-07-17 2018-12-14 安徽润藤电缆材料科技有限公司 一种绝缘复合铝漆包线
US20230323900A1 (en) * 2022-03-24 2023-10-12 Energy Recovery, Inc. Minimizing mixing in a pressure exchanger

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DE3614257A1 (de) * 1986-04-26 1987-10-29 Ingo Valentin Hydraulische schiefscheiben-axialkolbenmaschine
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ATE422958T1 (de) 2003-08-22 2009-03-15 Danfoss As Umkehrosmose entsalzungssystem mit einem druckumwandler
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CN100450591C (zh) * 2007-01-04 2009-01-14 天津大学 海水或苦咸水反渗透淡化系统用双转盘耦合式压力交换器
ES2383394B1 (es) * 2007-10-05 2013-05-07 Energy Recovery, Inc. Dispositivo rotativo de transferencia de presion.
EP2078867B1 (de) * 2007-12-11 2018-05-30 Grundfos Management A/S Druckaustauscher zur übertragung von druckenergie von einem ersten flüssigkeitsstrom auf einen zweiten flüssigkeitsstrom
US7799221B1 (en) * 2008-01-15 2010-09-21 Macharg John P Combined axial piston liquid pump and energy recovery pressure exchanger
CN101440828B (zh) * 2008-12-18 2013-05-08 杭州帕尔水处理科技有限公司 一种压力交换器
DE102010026645A1 (de) * 2010-07-09 2012-01-12 Robert Bosch Gmbh Hydraulische Energiewandlungsmaschine
FR2981704B1 (fr) * 2011-10-25 2013-12-20 Arkling Ltd Echangeur de pression volumetrique pour une installation de dessalement d'eau de mer et installation de dessalement
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Also Published As

Publication number Publication date
CN104373316B (zh) 2016-08-24
CN104373316A (zh) 2015-02-25
EP2837823A1 (de) 2015-02-18
IN2014DE01894A (de) 2015-06-19
US20150050177A1 (en) 2015-02-19

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