WO2024132077A1 - Agencement de compresseur à membrane et son utilisation - Google Patents

Agencement de compresseur à membrane et son utilisation Download PDF

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Publication number
WO2024132077A1
WO2024132077A1 PCT/DK2023/050330 DK2023050330W WO2024132077A1 WO 2024132077 A1 WO2024132077 A1 WO 2024132077A1 DK 2023050330 W DK2023050330 W DK 2023050330W WO 2024132077 A1 WO2024132077 A1 WO 2024132077A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
piston
chamber
diaphragm compressor
diaphragm
Prior art date
Application number
PCT/DK2023/050330
Other languages
English (en)
Inventor
Christian Haastrup MERRILD
Original Assignee
Nel Hydrogen A/S
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 Nel Hydrogen A/S filed Critical Nel Hydrogen A/S
Publication of WO2024132077A1 publication Critical patent/WO2024132077A1/fr

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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
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
    • F04B45/043—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms two or more plate-like pumping flexible members in parallel
    • 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
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • 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
    • F04B45/00—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids
    • F04B45/04—Pumps or pumping installations having flexible working members and specially adapted for elastic fluids having plate-like flexible members, e.g. diaphragms
    • F04B45/053—Pumps having fluid drive
    • F04B45/0533—Pumps having fluid drive the fluid being actuated directly by a piston

Definitions

  • the invention relates to a diaphragm compressor arrangement comprising a first diaphragm compressor including a first diaphragm arranged between a first hydraulic fluid chamber and a first gas chamber and a second diaphragm compressor including a second diaphragm arranged between a second hydraulic fluid chamber and a second gas chamber.
  • the invention further relates to use of a diaphragm compressor arrangement.
  • a diaphragm compressor is a variant of the classic reciprocating compressor where the compression of gas occurs by means of a flexible diaphragm (also called a membrane), instead of an intake element.
  • Diaphragm compressors are therefore known in many different forms and e.g. from Chinese utility model No.
  • CN101408168A it is known to form a double-acting two stage diaphragm compressor with two cylinders each having oil cavities with different size to each drive two diaphragm compressors having different size corresponding to the different oil cavities to create a low-pressure stage and a high pressure stage.
  • a two-stage diaphragm compressor design is complex and space consuming.
  • An object of the invention is therefore to provide for an advantageous diaphragm compressor arrangement.
  • the invention relates to a diaphragm compressor arrangement comprising a first diaphragm compressor including a first diaphragm arranged between a first hydraulic fluid chamber and a first gas chamber, and it comprises a second diaphragm compressor including a second diaphragm arranged between a second hydraulic fluid chamber and a second gas chamber.
  • the diaphragm compressor arrangement also includes a drive arrangement comprising a first cylinder and a second cylinder, wherein each of the first and second cylinders comprises a piston and a first piston chamber, wherein a piston rod is extending from the piston, through the first piston chamber, and out through a piston rod hole in an piston rod end of the first piston chamber and wherein each of the first and second cylinders comprises a second piston chamber formed on an opposite side of the piston in relation to the first piston chamber.
  • the drive means are connected to the piston rod of the first and second cylinders and the drive means are arranged to reciprocate the pistons in the first cylinder and the second cylinder synchronously.
  • the first piston chamber of the first cylinder and the second cylinder is in fluid communication with the first hydraulic fluid chamber
  • the second piston chamber of the first cylinder and the second cylinder is in fluid communication with the second hydraulic fluid chamber.
  • drive means refers to any kind of drive suited for reciprocating the pistons in two cylinders synchronously. I.e. the term includes any kind of motor driven crankshaft, motor driven camshaft and spring arrangement, any kind of rotating disk or arm arrangement or other.
  • the first and second cylinders comprise a guide rod extending from the piston, through the second piston chamber and out through a guide rod hole in a guide rod end of the second piston chamber.
  • Providing both cylinders with a guide extending from the piston and out of the cylinder in the opposite direction of the piston rod is advantageous in that this provide better and more linear guidance of the piston in the cylinder hereby enabling a better seal between the piston and the cylinder and thereby reducing pressure loss and leakage across the piston.
  • the piston typically comprises sealing means – e.g.
  • a piston rod diameter of the piston rod is substantially equal to a guide rod diameter of the guide rod.
  • both cylinders hereby deliver the same fluid amount at the same pressure no matter the stroke direction and this enables that the diaphragm compressors and any tubing or other between the cylinders and the diaphragm compressor can be formed identical. This is advantageous in that this reduces the number of unique parts thereby reducing assembly cost, handling cost, maintenance cost and it reduces assembly time. Furthermore, the identical cylinder volumes on both sides of the piston ensures a more uniform and balanced operation of the diaphragm compressor arrangement.
  • the first piston chamber of the first cylinder and the second cylinder is in fluid communication with the first hydraulic fluid chamber through a first tubing and the second piston chamber of the first cylinder and the second cylinder is in fluid communication with the second hydraulic fluid chamber through a second tubing.
  • Enabling fluid communication between the cylinders and the diaphragm compressors through dedicated tubing is advantageous in that this enables simple means for forming the relative complex fluid communication.
  • the first cylinder and the second cylinder are parallel.
  • Arranging the first cylinder and the second cylinder to be parallel is advantageous in that this generates a more balanced operation in which the synchronized operation of the pistons in the two cylinders will counteract each other and generate less stress and vibrations.
  • the first cylinder and the second cylinder are arranged on opposite sides of the drive means.
  • Arranging the cylinders on opposite sides of the drive means is advantageous in that the load of the two cylinders hereby will act in opposite directions on the drive means and thereby generate a more balanced load which will prolong the life of the drive means – particularly of any bearings guiding the rotary motion of the drive means.
  • the diaphragm compressor arrangement is a high-pressure diaphragm compressor arrangement arranged for pressurising a gas in the first gas chamber and the second gas chamber to a pressure between 10 and 300 MPa, preferably between 20 and 200 MPa, and most preferred between 30 and 130 MPa.
  • the pressure is too low the capacity of the diaphragm compressor arrangement is too low and if the pressure is too high the risk of leakage or damage increases.
  • the present pressure ranges present an advantageous relationship between efficiently and function.
  • the present invention is particularly advantageous in relation to high-pressure diaphragm compressor arrangement operating in the present pressure ranges in that one chamber of two cylinders connected to a single diaphragm compressor is particularly suited for generating a high pressure.
  • the drive means are arranged to reciprocate the pistons in the first cylinder and the second cylinder at least 300 times per minute.
  • the drive means are too slow the capacity of the diaphragm compressor arrangement is too low, and it is therefore advantageous that the drive means reciprocate the pistons in the cylinders at least 300 times per minute.
  • the first diaphragm compressor is substantially identical to the second diaphragm compressor.
  • the volume of the first hydraulic fluid chamber substantially corresponds to a total cylinder volume of the first piston chambers of the first cylinder and the second cylinder
  • the volume of the second hydraulic fluid chamber substantially corresponds to a total cylinder volume of the second piston chambers of the first cylinder and the second cylinder.
  • Forming the hydraulic fluid chambers so that their volumes substantially correspond to the volumes of the piston chambers to which they are in fluid communication with is advantageous in that the full capacity of the diaphragm compressors can hereby be utilized even if the volumes of the piston chambers are not the same.
  • substantially correspond in this embodiment refers to that the total cylinder volume of the piston chambers typically is a few percent larger than the volume of the corresponding hydraulic fluid chamber to compensate for any elastic compression of the hydraulic fluid.
  • the drive means are arranged to reciprocate the pistons in the first cylinder and the second cylinder synchronously between a first cylinder end and a second cylinder end of the cylinders so that a maximum volume and a minimum volume of the first piston chamber and the second piston chamber are substantially identical in each cylinder.
  • the drive means are arranged to reciprocate the pistons in the first cylinder and the second cylinder so that the pistons travel in opposite directions.
  • the hydraulic fluid is a liquid, such as hydraulic oil.
  • liquid such as hydraulic oil
  • the invention further relates to use of a diaphragm compressor arrangement according to any of the previously discussed diaphragm compressor arrangements in a hydrogen fuelling station.
  • FIG. 1 illustrates a simplified representation of a diaphragm compressor arrangement comprising diaphragm compressors of different size.
  • the diaphragm compressor arrangement 1 comprises a first diaphragm compressor 2 including a first diaphragm 3 arranged between a first hydraulic fluid chamber 4 and a first gas chamber 5, and a second diaphragm compressor 6 including a second diaphragm 7 arranged between a second hydraulic fluid chamber 8 and a second gas chamber 9.
  • the compressors 2, 6 are arranged to compress a gas in the gas chambers 5, 9 when the diaphragms 3, 7 are pushed towards the gas chambers 5, 9 by a hydraulic fluid entering and expanding the hydraulic fluid chambers 4, 8.
  • the gas in the gas chambers 5, 9 have been compressed it leaves the diaphragm compressors 2, 6 through an exit port 24 and when the hydraulic fluid is sucked out of the hydraulic fluid chambers 4, 8, the exit ports 24 closes and gas to be compressed is drawn into the gas chambers 5, 9 through inlet ports 25.
  • the ports 24, 25 are provided with check valves (not shown).
  • the gas compressed by the diaphragm compressors 2, 6 is hydrogen but in another embodiment the gas could be methane, oxygen or another gas.
  • the diaphragm compressor arrangement 1 also comprises a drive arrangement 10 comprising a first cylinder 11 and a second cylinder 12, wherein the first cylinder 11 and the second cylinder 12 in this embodiment are substantially identical.
  • the cylinders 11, 12 are arranged for displacing the hydraulic fluid to and from the hydraulic fluid chambers 4, 8 and thereby drive the compression process in the diaphragm compressors 2, 6.
  • each of the cylinders 11, 12 comprises a piston 13 arranged to travel back and forth in the cylinders 11, 12 to thereby alter the volume of a first piston chamber 14 and a second piston chamber 17 formed on opposite sides of the piston 13 inside the cylinders 11, 12.
  • the travel of the piston 13 is enabled by a piston rod 26 connected to the piston 13 and the piston rod 26 is extending from the piston 13, through the first piston chamber 14, and out through a piston rod hole 15 formed in an piston rod end 16 of the first piston chamber 14.
  • the piston 13 in both the first cylinder 11 and the second cylinder 12 travels back and forth in the cylinders 11, 12 so that the maximum volume and the minimum volume of the first piston chamber 14 and the second piston chamber 17 are substantially identical so that both cylinders 11, 12 at all times displace substantially the same amount of hydraulic fluid to and from the respective hydraulic fluid chambers 4, 8.
  • the drive means 18 are arranged to reciprocate the pistons 13 in the first cylinder 11 and the second cylinder 12 synchronously between a first cylinder end and a second cylinder end of the cylinders 11, 12 so that a maximum volume and a minimum volume of the first piston chamber 14 and the second piston chamber 17 are substantially identical in each cylinder 11, 12.
  • the maximum volume and/or the minimum volume of the first piston chamber 14 could be different from the corresponding volume of the second piston chamber 17 if an asynchronous displacement was desired.
  • the piston rods 26 from both cylinders 11, 12 are connected to the same drive means 18 of the drive arrangement 10 by means of connection arms 27.
  • the drive means 18 comprises a crankshaft 28 being rotated by a motor (not shown) – in this case an electrical motor- but in another embodiment the drive means 18 could also or instead comprise other means for generating the reciprocating motion of the pistons 13 in the cylinders 11, 12 – such as a cam or camshaft and spring arrangement or similar known to the skilled person.
  • the connection arms 27 are connected to opposite sides of the crankshaft 28 – i.e. 1800 displaced – so that when the crankshaft 28 rotates it will reciprocate the pistons 13 in the first cylinder 11 and second cylinder 12 synchronously and so that the pistons 13 at all times travel in opposite directions – i.e.
  • the drive arrangement 10 is formed in a drive arrangement housing 30 formed separate from the two diaphragm compressors 2, 6 and in this embodiment the first piston chamber 14 of the first and second cylinders 11, 12 are in fluid communication with the first hydraulic fluid chamber 4 through a first tubing 22 and the second piston chamber 17 of the first cylinder 11 and the second cylinder 12 are in fluid communication with the second hydraulic fluid chamber 8 through a second tubing 23.
  • the tubing 22, 23 comprises fittings, manifolds, and pipes but in another embodiment the tubing 22, 23 could also or instead comprise valves, filters, pressure gauges and other.
  • the cylinders 11, 12 and the diaphragm compressors are formed in the same block or housing and the fluid communication between the piston chambers 14, 17 and the hydraulic fluid chambers 4, 8 are established by means of conduits formed internally in the block or housing – e.g., by drilling or casting channels in the block or housing.
  • conduits formed internally in the block or housing – e.g., by drilling or casting channels in the block or housing.
  • this enables that the diaphragm compressors 2, 6 and the drive arrangement 10 may be manufactured, stored and handled in separate processes thereby reducing cost and increasing flexibility.
  • the fluid communication between the piston chambers 14, 17 and the hydraulic fluid chambers 4, 8 would be established by means of conduits formed internally in the block or housing to avoid tubing 22, 23 – e.g., due to problems in forming the tubing 22, 23 leak tight due to the high hydraulic fluid pressure.
  • the first cylinder 11 and the second cylinder 12 are arranged to be parallel and coaxial on opposite sides of the drive means 18.
  • the cylinders 11, 12 could be arranged parallel on the same side of the drive means 18 with the centre axis displaced, the cylinders 11, 12 could be arranged parallel with the centre axis displaced on opposite sides of the drive means 18, the cylinders 11, 12 could be arranged slanting on the same side or on opposite sides of the drive means 18 with the centre axis crossed and/or in another embodiment the drive arrangement 10 could comprise more than two cylinders 11, 12 – such as three, four, six or even more.
  • the total cylinder volume of the first piston chambers 14 of the cylinders 11, 12 is different from the total cylinder volume of the second piston chambers 17 of the cylinders 11, 12 because in this embodiment the piston rod 26 in the first piston chambers 14 reduces the total cylinder volume of the first piston chambers 14 in relation to the total cylinder volume of the second piston chambers 17 and for the same reason the effective surface of the piston 13 is bigger in the second piston chamber 17 than in the first piston chamber 14. For this reason the hydraulic fluid volume delivered to the first hydraulic fluid chamber 4 is smaller than the hydraulic fluid volume delivered to the second hydraulic fluid chamber 8 per full back and forth movement of the pistons 13 and the given the difference in effective surface of the pistons 13 in the two piston chambers 14, 17, the pressure is also different.
  • the first diaphragm compressor 2 is smaller than the second diaphragm compressor 6 in that the volume of the first hydraulic fluid chamber 4 corresponds to the total cylinder volume of both first piston chambers 14 and the volume of the second hydraulic fluid chamber 8 corresponds to the total cylinder volume of both second piston chambers.
  • the hydraulic fluid is a liquid in the form of hydraulic oil but in another embodiment the hydraulic fluid could be canola oil, glycol, paraffin oil or another liquid suited for use as a hydraulic fluid in a diaphragm compressor arrangement 1.
  • the diaphragms 3, 7 in the diaphragm compressors 2, 6 are illustrated by a single line.
  • FIG. 1 illustrates a simplified representation of a diaphragm compressor arrangement 1 cylinder comprising guide rods 19.
  • the first and second cylinders 11, 12 comprise a guide rod 19 connected to the piston 13 and extending from the piston 13, through the second piston chamber 17, and out through a guide rod hole 20 in a guide rod end 21 of the second piston chamber 17, wherein the guide rod end 21 is arranged in the opposite end of the cylinders 11, 12 in relation to the piston rod end 16.
  • the piston rod diameter PD of the piston rod 26 is substantially equal to the guide rod diameter GD of the guide rod 19 throughout the extend of the rods 19, 26 inside the cylinders 11, 12 so that the total cylinder volume of the first piston chambers 14 of the cylinders 11, 12 is substantially identical to the total cylinder volume of the second piston chambers 17 of the cylinders 11, 12.
  • the piston rod diameter PD could be different from the guide rod diameter GD – e.g., if different volumes and pressures was desired.
  • the holes 15, 20 in the ends of the cylinders 11, 12 are obviously provided with sealing means (not shown) to ensure that the pressurized hydraulic fluid does not escape the cylinders 11, 12 through the holes 15, 20.
  • Forming the cylinders 11, 12 with a guide rod 19 is advantageous in that the piston 13 hereby is suspended in both ends of the cylinders 11, 13 whereby the piston 13 is less affected by the torque the piston rod 6 is subject to by the drive means 18 – particularly rotating drive means 18 - and the risk of leakage across the piston 13 from one chamber 14, 17 to the other is reduced. Furthermore, by forming the guide rod 19 effectively identical to the piston rod 6, the total cylinder volume of the first piston chambers 14 are substantially identical to the total cylinder volume of the second piston chambers 17, whereby the first diaphragm compressor 2 can be identical to the second diaphragm compressor 6 - as in this embodiment.
  • the diaphragm compressor arrangement 1 is a single stage high-pressure diaphragm compressor arrangement 1 arranged for raising the pressure of the gas in the gas chambers 5, 9 from a pressure around 40 MPa to a pressure around 90 MPa.
  • the starting pressure of the gas could be lower – such as 30 MPa, 15 MPa, 5 MPa or even lower – or the starting pressure of the gas could be higher – such as 50 MPa, 60 MPa, 80 MPa or even higher.
  • the pressure could be raised less - such as to 80 MPa, 70 MPa, 50 MPa or even less – or the pressure could be raised more - such as to 100 MPa, 130 MPa, 160 MPa or even more.
  • the drive means 18 are arranged to reciprocate the pistons 13 in the first cylinder 11 and the second cylinder 12 at least 300 times per minute to ensure a high capacity of the diaphragm compressor arrangement 1.
  • the drive means 18 could be arranged to reciprocate the pistons less – such as at least 250, 150, 50 times per minute or even less – or the drive means 18 could be arranged to reciprocate the pistons more – such as at least 400, 600, 1,000 times per minute or even more – e.g.
  • the specific gas or hydraulic fluid, the specific use or other or the drive means 18 could be controlled to reciprocate the pistons 13 in the first cylinder 11 and the second cylinder 12 a variable times per minute e.g. in dependency with a specific desired variable output of the diaphragm compressor arrangement 1, in dependency of one or more operation parameters such as temperature of hydraulic, fluid, gas or other, time to maintenance, noise level or other.
  • the diaphragm compressor arrangement 1 is used for compressing hydrogen in a hydrogen fuelling station (not shown). I.e. in this embodiment the diaphragm compressor arrangement 1 is used for raising the pressure of hydrogen being delivered to a hydrogen fuelling station before it is stored in a storage vessel (not shown).
  • the diaphragm compressor arrangement 1 could be used for raising the pressure of hydrogen during a fuelling process, for maintain the pressure in a storage vessel or in another process in a hydrogen fuelling station.
  • the diaphragm compressor arrangement 1 according to the present invention could is used for compressing another type of gas and/or be used in relation to other processes – such as in a gas manufacturing or storing process, in an industrial facility or other.
  • the invention has been exemplified above with reference to specific examples of diaphragm compressor 2, 6, cylinders 11, 12, drive means 18 and other. However, it should be understood that the invention is not limited to the particular examples described above but may be designed and altered in a multitude of varieties within the scope of the invention as specified in the claims.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Reciprocating Pumps (AREA)

Abstract

Est divulgué un agencement de compresseur à membrane (1) comprenant un premier compresseur à membrane (2) comprenant une première membrane (3) disposée entre une première chambre de fluide hydraulique (4) et une première chambre à gaz (5) et il comprend un second compresseur à membrane (6) comprenant une seconde membrane (7) disposée entre une seconde chambre de fluide hydraulique (8) et une seconde chambre à gaz (9). L'agencement de compresseur à membrane (1) comprend en outre un agencement d'entraînement (10) comprenant un premier cylindre (11) et un second cylindre (12), chacun des premier et second cylindres (11, 12) comprenant un piston (13) et une première chambre de piston (14), une tige de piston (26) s'étendant à partir du piston (13), à travers la première chambre de piston (14), et vers l'extérieur à travers un trou de tige de piston (15) dans une extrémité de tige de piston (16) de la première chambre de piston (14) et chacun des premier et second cylindres (11, 12) comprenant une seconde chambre de piston (17) formée sur un côté opposé du piston (13) par rapport à la première chambre de piston (14). L'agencement d'entraînement (10) comprend des moyens d'entraînement (18) reliés à la tige de piston (26) des premier et second cylindres (11, 12), et les moyens d'entraînement (18) étant agencés pour déplacer en va-et-vient les pistons (13) dans le premier cylindre (11) et le second cylindre (12) de manière synchrone. En outre, la première chambre de piston (14) du premier cylindre (11) et du second cylindre (12) est en communication fluidique avec la première chambre de fluide hydraulique (4) et dans laquelle la seconde chambre de piston (17) du premier cylindre (11) et du second cylindre (12) est en communication fluidique avec la seconde chambre de fluide hydraulique (8). L'utilisation d'un agencement de compresseur à membrane (1) est également divulguée.
PCT/DK2023/050330 2022-12-22 2023-12-21 Agencement de compresseur à membrane et son utilisation WO2024132077A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DKPA202270645 2022-12-22
DKPA202270645A DK181667B1 (en) 2022-12-22 2022-12-22 A diaphragm compressor arrangement and use thereof

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WO2024132077A1 true WO2024132077A1 (fr) 2024-06-27

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR925749A (fr) * 1946-02-05 1947-09-11 Hanvag Ges Fu R Tech Vervollko Compresseur à membrane
CN101408168A (zh) 2007-10-10 2009-04-15 北京汇知机电设备有限责任公司 双作用隔膜压缩机
CN106523333A (zh) * 2016-12-30 2017-03-22 张家港科康智能科技有限公司 一种四缸隔膜式气体压缩机
CN113007081A (zh) * 2021-04-15 2021-06-22 沈阳理工大学 基于工业互联网平台实现监控的完全平衡型高速隔膜压缩机

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR925749A (fr) * 1946-02-05 1947-09-11 Hanvag Ges Fu R Tech Vervollko Compresseur à membrane
CN101408168A (zh) 2007-10-10 2009-04-15 北京汇知机电设备有限责任公司 双作用隔膜压缩机
CN106523333A (zh) * 2016-12-30 2017-03-22 张家港科康智能科技有限公司 一种四缸隔膜式气体压缩机
CN113007081A (zh) * 2021-04-15 2021-06-22 沈阳理工大学 基于工业互联网平台实现监控的完全平衡型高速隔膜压缩机

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DK202270645A1 (en) 2024-08-12

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