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WO2017016644A1 - Système de compression - Google Patents

Système de compression Download PDF

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Publication number
WO2017016644A1
WO2017016644A1 PCT/EP2016/001199 EP2016001199W WO2017016644A1 WO 2017016644 A1 WO2017016644 A1 WO 2017016644A1 EP 2016001199 W EP2016001199 W EP 2016001199W WO 2017016644 A1 WO2017016644 A1 WO 2017016644A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
piston
compression device
compression
wall
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.)
Ceased
Application number
PCT/EP2016/001199
Other languages
German (de)
English (en)
Inventor
Kurt Koch
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of WO2017016644A1 publication Critical patent/WO2017016644A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • F04C27/006—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type pumps, e.g. gear pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/20—Rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/001—Radial sealings for working fluid

Definitions

  • the invention relates to a compression device.
  • a conventional turbocharger such as an exhaust gas turbocharger of a gasoline engine, has a turbine and a compressor. These components can be constructed very similar and mounted on a common shaft.
  • the exhaust gas stream sets the turbine wheel in rotation. Its torque is transmitted via the common shaft to the compressor wheel in the intake system. As long as sufficient exhaust flows to the turbine wheel, the speed is sufficient to cause an overpressure on the intake side. However, this condition is reached only at higher engine speeds from about 1500 to 2000 min -1 , so that turbo engines in the lower speed range only work as naturally aspirated and delayed when retrieving a higher power at higher speeds with a conventional "turbo lag".
  • the invention has for its object to provide a compression device which is operable efficiently.
  • the compression device has at least one cylinder having an inner wall and a piston rotatably mounted in the cylinder eccentric to the longitudinal axis of circular cross-section, wherein the outer diameter of the piston for the formation of at least one compression space is smaller than the inner cross section of the cylinder and the piston in sealing contact with the inner wall of the cylinder is and has a movable in the radial direction of the piston means, which is also in sealing contact with the inner wall of the cylinder and rotates with the piston.
  • This device may have a lower mass than, for example, a traditional turbocharger due to its higher efficiency.
  • the compression device according to the invention with the same power with less energy consumption is operable.
  • the aforementioned construction principle of the compression device can be manufactured at comparable performance at a lower production price compared to a conventional turbocharger. This construction principle requires less weight per unit of power. Due to the simplified construction principle and the lower dead weight, the compression device can be operated at the same power with significantly less energy. It can be operated much easier with simple means without special technical effort.
  • the compression device according to the invention can, especially if several units are connected together to form a compressor group, and even in the very low speed range to develop a comparatively high performance, without such operation harms the technical parts or the mechanical components. In addition, the noise will be reduced compared to the conventional turbocharger, which also reduces the effort for the damping.
  • the dimensions of the compression device, its mass and weight are lower compared to the conventional turbocharger. It follows that at the same power the compression device has a lower weight than a corresponding conventional turbocharger. In this respect, the manufacturing and operating costs are reduced in the compression device according to the invention compared to a built-up in a known manner turbocharger corresponding power.
  • This construction principle of the compression device makes it possible to use this instead of a turbocharger in a gasoline engine. This will increase performance in practice already reached from the first revolution of the engine.
  • the compressed air generated by the compression device or the air mixture or fuel / air mixture can be passed in a simple process in a buffer memory and also flexibly retrieved and initiated as needed or calculation in the cylinder or the engine. Engine management can easily make it possible to adjust the volume of the absorbed and finally compressed or compressed air according to the demand per working cycle.
  • the compression device can thus be designed and operate as a compressor or compressor.
  • the movable in the radial direction of the piston means comprises two diametrically opposed wing parts, each biased radially outwardly biased against the inner wall of the cylinder. It is advantageous that such a compression device per revolution allows two compression or compression strokes. This results in a high efficiency for the compression device according to the invention. It runs like a simple AC motor always round and develops its two compression strokes per revolution during the orbit. Complicated valve controls can be omitted. The two diametrically opposite wing parts allow so far two compression strokes per revolution.
  • the wing parts are guided in the piston guided by spring force and / or provided in the piston connecting channels using the compressed air or a compressed fuel / air mixture radially outward to the inner wall of the cylinder.
  • a sliding contact of the wing parts along the inner wall of the cylinder by simple means can be brought.
  • the compressed air or the air mixture can also contribute to the fact that the wing parts are constantly in contact with the inner wall of the cylinder.
  • the cylinder has inlet and outlet valves for the fluid or fluid mixture involved in the compression process.
  • a rotary engine before each power stroke could compressed air or a compressed fuel / air mixture obtained in the combustion chamber of its cylinder.
  • the rotary engine would therefore have to compress no more air and no air mixture more.
  • a conventional gasoline engine prior to a power stroke, must compress the trapped air, with the volume of air possibly being increased by a charging device such as a turbocharger. In the Otto engine, therefore, the amount of air available for combustion without additional charging device corresponds approximately to the cylinder contents.
  • the compression device can be designed in any desired volume. In a gasoline engine with a turbocharger, the effect of the supercharger usually starts at a certain speed.
  • a free-running sealing plate is arranged on the head parts of the cylinder, which has on its wegholdden from the piston outer side grooves for a lubricant, wherein the grooves are preferably arranged at an acute angle obliquely to the radial direction of the sealing plate.
  • Such sealing plates meet, greatly simplified, approximately the function of the piston rings in a reciprocating engine.
  • Such an arrangement of the grooves makes it possible for the rotating sealing plates simultaneously to function as a circulating pump for the lubricant, for example an oil lubrication, in the sense of a double function.
  • the expenditure on equipment of the compression device according to the invention can be further reduced. Good lubrication allows lossless running as possible of the compression device according to the invention.
  • cylinder head covering plates with lubricant channels are arranged on the head sides of the cylinder such that the lubricant channels open into the region of the grooves provided on the respective sealing plate.
  • the lubricant can be easily passed to the sealing plates and thus to those locations and areas where lubrication should be provided.
  • FIG. 1 shows a schematic section through a compression device in a first working position
  • Fig. 2 is a schematic section through the compression device according to
  • Fig. 3 is a schematic section through the compression device according to
  • Fig. 4 is a schematic section through the compression device according to
  • Fig. 5 is a schematic section through the compression device according to
  • FIG. 6 shows a schematic section through the compression device according to FIG. 1 in a sixth working position
  • FIG. 7 shows a schematic section through the compression device according to another embodiment in an enlarged view
  • Fig. 9 is a schematic front view of a seal plate of the compression device.
  • FIG. 10 is a schematic section through a compression device according to another embodiment.
  • Fig. 1 is a schematic, partial cross section through a compression device 2 according to a first embodiment is shown.
  • the compression device 2 is, for example, a compressor or a compressor.
  • the compression device 2 has at least one cylinder 24, which has an inner wall 23.
  • the cylinder 24 has in the one shown in FIG Embodiment a circular cross-section. But it is also possible that the cylinder has a different, in particular an elliptical cross-section.
  • the compression device 2 has a piston 26 which is rotatably mounted in the cylinder 24 eccentrically to the longitudinal axis 25 thereof.
  • the longitudinal axis 25 of the cylinder 24 is shown in Figs. 1 and 8.
  • the piston 26 has a circular, namely circular cross section 27.
  • the outer diameter 30 of the piston 26 is for the formation of at least one compression space 31 smaller than the inner cross section of the cylinder 24, which is formed as shown in FIG. 1 as a circular surface with the inner diameter 28.
  • the piston 26 is shown in FIGS. 1 to 7 in sealing contact with the inner wall 23 of the cylinder 24.
  • the piston 26 has a movable in the radial direction of the piston 26 means 32, which also in sealing contact with the inner wall 23rd of the cylinder 24 and rotates with the piston 26.
  • the movable in the radial direction of the piston 26 means 32 has two diametrically opposite wing portions 33, 34.
  • the wing portions 33, 34 are respectively radially outwardly biased in the inner wall 23 of the cylinder 24 at. This is shown in an enlarged view in Fig. 7.
  • the wing portions 33, 34 are guided in the piston 26 guided by spring force and / or provided in the piston 26 connecting channels 37, 38 by means of the compressed compressed gas radially outward to the inner wall 23 of the cylinder 24 out.
  • the connecting channels 37, 38 are omitted in FIGS. 1 to 6 for the sake of simplicity and shown in more detail only in Fig. 7.
  • the springs 20 shown in Fig. 7 are therefore compression springs.
  • the cylinder 24 for the fluid or fluid mixture involved in the compression process inlet and outlet valves 51, 54, 77, 82; 22.
  • the aforementioned compression device 2 may be arranged and configured such that via the outlet valve 22 of the cylinder 24 compressed air or a compressed fuel / air mixture in a combustion chamber not shown in detail of an engine (not shown) can be introduced.
  • the compressed air or the compressed fuel / air mixture thus passes from the compression device 2 via the exhaust valve 22, which may also serve as an intake valve for an engine, into the combustion chamber of a cylinder of the engine.
  • the exhaust valve 22 of the cylinder 24 involved in the compression process can thus form the inlet valve of a motor not shown in detail and be formed as a valve 36 for passing the compressed air or the compressed fuel / air mixture into the combustion chamber of the engine.
  • the latter valve 36 may be referred to simply as a transfer valve.
  • the piston 26 of the compression device 2 is drivingly connected, for example, with a not shown piston of a cylinder involved in the combustion process (not shown in detail) and driven by the latter.
  • a not shown piston of a cylinder involved in the combustion process (not shown in detail) and driven by the latter.
  • an electric motor could also be provided in a vehicle engine.
  • the piston 26 rotates in the counterclockwise direction as shown by the arrow B.
  • Fig. 8 is a schematic representation of a partial longitudinal section through the cylinder 24 is shown.
  • a free-running sealing plate 42 is arranged in each case.
  • a sealing plate 42 is shown in a schematic front view in Fig. 9.
  • the seal plate 42 has on its side facing away from the piston 26 outside 43 grooves 44 for a lubricant.
  • the grooves 44 are arranged at an acute angle 45 obliquely to the radial direction of the seal plate 42.
  • cylinder head cover plates 46, 47 are arranged on the head sides 40, 41 of the cylinder 24.
  • the cylinder head cover plates 46, 47 have lubricant passages 50 which open into the region of the grooves 44 provided on the respective seal plate 42.
  • the grooves of the Sealing plate 42 are omitted in the representation shown in Fig. 8 for the sake of clarity.
  • FIG. 1 shows that working position in which the compressed air 55 has almost completely left the cylinder 24 via the outlet valve 22 or the bypass valve 36.
  • the exhaust valve 22 will soon be closed.
  • a further inlet valve 51 is also provided, via which air can be introduced into the compression space 31.
  • the further inlet valve 51 can serve to introduce fresh air into a second cylinder chamber 60 of the compression space 31 in order to avoid a vacuum therein or to produce a pressure compensation.
  • the further inlet valve 51 can also be dispensed with (see FIGS. 1 to 6).
  • Pistons 26 and vane members 33, 34 in the cylinder 24 of the compression device 2 are arranged such that the exhaust valve 22 / bypass valve 36 is closed by the wing member 34 shortly and the inlet valve 54 of the compression device 2 is already partially closed by the wing member 33 of the device 32 becomes.
  • the compression space 31 is almost completely filled with fresh air.
  • the beginning of the compression process is imminent.
  • a further movement of the piston 26 in the direction of arrow B leads to the second operating position shown in FIG. 2.
  • the outlet valve 22 / transfer valve 36 is closed.
  • the introduced into the compression chamber 31 air is compressed by further rotation of the piston 26 by means of the wing portion 33.
  • the pressure compensation in the second cylinder chamber 60 of the cylinder 24 can take place.
  • fresh air flows in the direction of the arrow E into the second cylinder chamber 60.
  • the wing portion 34 of the piston 26 is located almost completely in the piston. It is clear that the wing parts 33, 34 are displaceably guided in the direction of the double arrows F in the piston (see FIG. 2).
  • FIG. 3 A third working position of the piston 26 is shown in Fig. 3.
  • the piston 26 has moved further including its means 32 in the direction of arrow B.
  • the air in the compression space 31 is further compressed.
  • Fresh air can continue to flow via the inlet valve 54 in the direction of arrow E in the second cylinder chamber 60 of the cylinder 24.
  • the wing portion 34 is located entirely within the piston 26 and lies directly opposite a pressure device 61 for sealing between the cylinder 24 and the piston 26.
  • the pressure device 61 may be a hydraulic, pneumatic or mechanical pressure device.
  • the compressed air in the compression space 31 is further compressed in the cylinder 24 of the compression device 2.
  • the outlet valve 22 / bypass valve 36 will soon open, so that the highly compressed air 55 in the direction of the arrow A can flow out of the compression space 31 of the cylinder 24, as indicated in Fig. 6.
  • each free base space 63 communicates with the compression chamber 31 and the second cylinder chamber 60.
  • the compressed air can at least temporarily reach the free base space; it is therefore guided under the respective wing part 33, 34, whereby the respective wing part in the radial direction applied to the outside is sealingly pressed against the inner wall 23 of the cylinder 24 at least when the air flowing into the base space 63 or the mixture is compressed.
  • the wing portions 33, 34 are guided by a slide pin 64 so that the slide pin serves as a seat for the inner end of each wing portion and the inner end of each wing portion circumferentially surrounds the respective end of the slide pin.
  • the reference numeral 65 denotes the axis of rotation of the piston 26. The axis of rotation 65 corresponds to the longitudinal axis of the piston.
  • the pressure device 61 comprises a pressure line 70, which is connected via an intermediate piece 71 to a pressure unit 72.
  • the pressure unit 72 acts on a sealing structure 73, which seals the cylinder 24 with respect to the piston 26.
  • the pressure line 70 may be a hydraulic or compressed air line.
  • the pressure structure 73 may, as shown in FIGS. 1 to 6, in one piece or, as indicated in Fig. 7, be formed of several parts.
  • Fig. 8 shows a partial longitudinal section through the cylinder 24 of the compression device 2.
  • At the head sides 40, 41 is located in the inner cross section of the cylinder 24 at each end of the seal plate 42.
  • Each seal plate has a central inner bore 74.
  • Each seal plate is free and moves , moved only by wing parts 33, 34, on a circular path. Since each seal plate 42 oscillates about a drive shaft 75, the inner bore 74 is larger than the outer diameter of the drive shaft 75, as shown in FIG. 8 can be seen.
  • Fig. 8 also the center line or longitudinal axis 25 of the cylinder 24 and the Longitudinal axis 65 of the piston 26 shown, the latter corresponds to the axis of rotation of the piston 26.
  • each of the plates operates as a separate lubricant pump and thereby keeps the lubricant, such as a lubricating oil, in circulation.
  • the direction of rotation of the cover plate 42 is indicated by the arrow G.
  • the longitudinal axis 65 of the piston 24 corresponds to its axis of rotation.
  • FIG. 10 shows a schematic, partial cross section through a further embodiment of the invention.
  • the cylinder 24 of the compression device 2 is larger than the cylinder shown in FIGS. 1 to 6. In this example, therefore, a larger amount of air for the compression process can be provided.
  • the compression device 2 operates here in the suction mode with respect to a fuel / air mixture.
  • the cylinder 24 of the compression device 2 has an intake valve 77 connected to a carburetor 80.
  • the volume of the aspirated fuel / air mixture can be optimally selected depending on the location or seat of the carburetor 80 and the intake valve 77 to the cylinder 24.
  • a further special feature of the embodiment shown in FIG. 10 is that a further inlet valve 82 is provided in the compression space 31 for its filling. Compressed air can be passed via a line 81 to the further inlet valve 82 of the cylinder 24 of the compression device 2 and flow into the compression space 31.
  • the further inlet valve 82 serves, in particular, for directing precompressed air into the compression space 31 of the cylinder 24 of the compression device 2. If necessary, in the embodiment shown in Fig. 10, the inlet valve 54 shown in Figs. 1 to 6 may be additionally provided.
  • the piston 26 thus work in the longitudinal direction, centrically aligned and radially movable, two-part wing parts 33, 34 in the space provided for them free base spaces 63.
  • the wing parts may also be called “paddle". They are always outwardly by spring and / or gas pressure, i. are biased towards the inner wall of the cylinder and so are constantly in sealing contact with the inner wall of the cylinder in question.
  • the rotatable piston 26 is fixedly pressed against the pressure device 61 in the wall of the respective cylinder 24.
  • the outlet valve 22 / transfer valve 36 may be, for example, a rotating perforated disc with valve function.
  • the process described with reference to FIGS. 1 to 6 is repeated twice within one revolution of the piston, so that the compression device according to the invention operates extremely effectively.
  • the compression device according to the invention can be used particularly advantageously like a compressor up to medium pressures. It can be used as a replacement for a turbocharger in gasoline engines.
  • the efficiency and technical design of the device with rotary piston are clearly superior to the traditional turbocharger, since the device according to the invention, as mentioned above, can provide the gasoline engine compressed air for combustion already from the first revolution, which a traditional turbocharger can not.
  • the device can direct compressed air into a memory, not shown, from which it can be supplied, for example, the individual cylinders of a motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un système de compression comprenant au moins un cylindre (24) présentant une paroi interne (23), et un piston (26) qui est monté rotatif dans le cylindre (24) de manière excentrique par rapport à l'axe longitudinal (25) de ce dernier et qui a une section transversale (27) circulaire, le diamètre extérieur (30) du piston (26) étant inférieur à celui de la section transversale intérieure du cylindre (24) aux fins de formation d'au moins une chambre de compression (31), et le piston (26) étant en contact hermétique avec la paroi interne (23) du cylindre (24) et présentant dans la direction radiale du piston (26) un dispositif mobile (32) qui est également en contact hermétique avec la paroi interne (23) du cylindre (24) et qui tourne avec le piston (26).
PCT/EP2016/001199 2015-07-24 2016-07-12 Système de compression Ceased WO2017016644A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202015005274.6 2015-07-24
DE202015005274.6U DE202015005274U1 (de) 2015-07-24 2015-07-24 Kompressionsvorrichtung

Publications (1)

Publication Number Publication Date
WO2017016644A1 true WO2017016644A1 (fr) 2017-02-02

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ID=54250279

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Application Number Title Priority Date Filing Date
PCT/EP2016/001199 Ceased WO2017016644A1 (fr) 2015-07-24 2016-07-12 Système de compression

Country Status (2)

Country Link
DE (1) DE202015005274U1 (fr)
WO (1) WO2017016644A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108252909A (zh) * 2018-04-16 2018-07-06 盐城中德劲博机电有限责任公司 直槽滑片式空气压缩机滑片导向端面密封结构

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102522994B1 (ko) 2021-10-28 2023-04-19 엘지전자 주식회사 로터리 압축기

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2097572C1 (ru) * 1992-12-01 1997-11-27 Чикин Герман Германович Ротолопастной двигатель
US5871342A (en) * 1997-06-09 1999-02-16 Ford Motor Company Variable capacity rolling piston compressor
WO2013131011A1 (fr) * 2012-03-01 2013-09-06 Torad Engineering, Llc Élément d'étanchéité pour compresseur rotatif

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2097572C1 (ru) * 1992-12-01 1997-11-27 Чикин Герман Германович Ротолопастной двигатель
US5871342A (en) * 1997-06-09 1999-02-16 Ford Motor Company Variable capacity rolling piston compressor
WO2013131011A1 (fr) * 2012-03-01 2013-09-06 Torad Engineering, Llc Élément d'étanchéité pour compresseur rotatif

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108252909A (zh) * 2018-04-16 2018-07-06 盐城中德劲博机电有限责任公司 直槽滑片式空气压缩机滑片导向端面密封结构

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