EP2935892B1 - Compresseur à piston rotatif présentant un débit modifiable - Google Patents

Compresseur à piston rotatif présentant un débit modifiable Download PDF

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Publication number
EP2935892B1
EP2935892B1 EP13798644.4A EP13798644A EP2935892B1 EP 2935892 B1 EP2935892 B1 EP 2935892B1 EP 13798644 A EP13798644 A EP 13798644A EP 2935892 B1 EP2935892 B1 EP 2935892B1
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EP
European Patent Office
Prior art keywords
slide
rolling piston
cavity
radius
actuating means
Prior art date
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Not-in-force
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EP13798644.4A
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German (de)
English (en)
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EP2935892A2 (fr
Inventor
Simon Klink
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2935892A2 publication Critical patent/EP2935892A2/fr
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    • 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
    • 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
    • F04C18/356—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 outer member
    • F04C18/3562—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution

Definitions

  • the invention relates to a rotary compressor according to the preamble of claims 1 and 2 and a method for operating such a rotary compressor according to claim 9.
  • Rotary piston compressors are used to compress fluids, especially in refrigerant circuits.
  • a rolling piston is provided with a circular cross-section about an axis with a first radius.
  • This is arranged in a compressor housing, which for this purpose has a cavity with a circular cross-section about a central axis with a second radius.
  • the second radius is larger than the first radius.
  • the axis of the rolling piston extends parallel and at a distance eccentric to the central axis of the cavity. The eccentric distance corresponds essentially to the second radius minus the first radius, so that the rolling piston, which is rotatable and / or orbitally mounted about the central axis, rests in each rotational position on the wall of the cavity.
  • a rotary compressor is characterized by a slide. This is longitudinal, or aligned in the longitudinal direction to the central axis and arranged in a slide opening of the compressor housing, from which it is displaceable in the radial direction in the cavity.
  • a resilient mounting of the slide causes an abutment of an end face of the slide on the rolling piston.
  • An opening in the compressor housing opening into a partial space of the cavity opens adjacent to the slide opening on the rear suction side of the slider.
  • On the pressure side adjacent to the slide opening arranged side also opens an outlet opening in the other subspace of the cavity.
  • a check valve is arranged in this outlet opening.
  • Double scroll compressors are expensive and the known power modulation is possible only in two stages. By permanently lifting the slide of one of the pistons, the power can be reduced by a fixed proportion.
  • Object of the present invention is therefore to eliminate the disadvantages of the prior art, and to provide a rotary compressor whose delivery capacity can be modulated in a simple, inexpensive, efficient and reliable manner.
  • the invention relates to a rotary piston compressor comprising a rolling piston having a circular cross-section with a first radius around an axis, and a compressor housing having a cavity having a circular cross-section with a second radius about a central axis, wherein the second radius is greater than the first radius wherein the axis of the rolling piston is parallel and spaced eccentrically from the central axis of the cavity, the rolling piston being rotatable or orbitable about the central axis of the cavity, and comprising a slider aligned longitudinally with the central axis, having a front, a back and an end face; which is arranged in the radial direction in the cavity displaceable in a slide opening of the compressor housing, wherein the cavity with the slide and the rolling piston in a first subspace and a second subspace is divisible, and wherein an actuating means is provided, with a Que sectional area of a arranged in the stroke region of the slide connection between the first subspace and the second subspace is changeable.
  • a compound having a defined cross-sectional area may be employed to provide a continuous, limited overcurrent.
  • the compound in a defined angle of rotation of the rolling piston are released, so that in this rotation angle is a reduced compression.
  • the distance between the axis of the rolling piston and the central axis of the cavity preferably corresponds substantially to the second radius minus the first radius.
  • a suction opening into the cavity should be formed in the compressor housing, which is arranged adjacent to the slide opening on the rear suction side of the slider.
  • the suction port is connected in a very large rotational range of the rolling piston with the first subspace.
  • an outlet opening into the cavity should be formed in the compressor housing, which is arranged adjacent to the slide opening on the front-side pressure side of the slider. This outlet opening is then connected to the second subspace in a very large rotational range of the rolling piston and can release pressure therefrom.
  • a check valve is preferably to be arranged in the outlet opening so that compressed fluid can not flow back into the second compartment. The efficiency of compaction is significantly improved.
  • the actuating means is kinematically coupled to the slide, wherein the cross-sectional area can be predetermined by changing a distance between the end face of the slide and the rolling piston.
  • the end face may in this case be designed so that it forms a tangent contact line upon contact with the rolling piston, e.g. by pointed, rounded or round design of the front page.
  • the distance between the end face of the slide and the rolling piston between zero and a maximum distance is the second radius minus the first radius corresponds.
  • a full compaction performance can be achieved when there is a zero clearance.
  • the maximum distance before, the first and second compartment are connected by a maximum large connection with each other, since the slider is completely recessed in the compressor housing. Energy losses are thus avoided in phases of maximum distance. Energy losses are thus avoided in periods of maximum distance and the efficiency of the compression is high.
  • the power regulation is thus essentially on the rotation angle at which the slide is closed. According to the invention, therefore, the slider is lifted at each revolution from top dead center to a certain angle of rotation. As long as the slide is still open, there is thus no compression. A partially opened slide is possible according to the invention, but leads to higher losses than the complete opening or closing described above.
  • the distance between the end face of the slide and the rolling piston by means of the actuating means is electronically controlled.
  • the compaction performance can be automated and precisely regulated.
  • the compression is determined by means of a pressure sensor, also influences, such as caused by the nature of an oil in the cavity and changes in fit by wear, can be corrected.
  • By means of an electronic control also very rapid changes in the cross-sectional area of the compound are vorappelbar. The power modulation is thus very flexible.
  • the actuating means is kinematically coupled to an adjustable spacer means which is positionable between the slide and the rolling piston, and with which a distance between the end face of the slide and the rolling piston is variable.
  • the spacer allows to perform the actual lifting movement of the slider by the rotational movement of the rolling piston.
  • the spacer is preferably fixed to the slide and has a running side for contacting the rolling piston.
  • the slider itself is then preferably force-loaded in the direction of the rolling piston, in particular by means of a spring.
  • the actuating means may be positioned outside the cavity, and to actuate the spacer means, for example. By means of a sliding rod extending through the slide.
  • the actuating means is kinematically coupled to a valve arranged in the slide, wherein the cross-sectional area is variable with the valve.
  • a valve in the slide.
  • the interface between slide and rolling piston can be protected by such a valve solution from damage by contacting movements.
  • an overflow even with very small cross-sectional area is thereby realized, which is not always ensured due to a tear of an oil film between the rolling piston and a lift-off slide. Therefore, such a valve according to the invention is not only suitable as an alternative solution, but also in combination with a lift-off slider, wherein the connection is then formed by the valve and the gap between the slide and rolling piston.
  • the actuating means is an electric servomotor.
  • Such can be designed and controlled inexpensively.
  • it allows fast positioning times:
  • it can be closed in reverse by analyzing a voltage present at the actuator to the rotational position and rotational speed of the rolling piston, when the slide and the rolling piston are kinematically coupled. A synchronization between the rotational movement of the rolling piston and the lifting movement of the slider is so feasible.
  • a further embodiment of the invention provides an electromagnet as actuating means. Electromagnets allow very fast positioning times without mechanical translation.
  • the slide opening can be formed enclosed in the compressor housing, so that no fluid escapes, no expensive sealing means for sealing the slide to the compressor housing are necessary, the slider is movable with low friction and high efficiency of compression is achieved.
  • the slider is resiliently mounted according to a training.
  • a resilient mounting a synchronization between the rolling piston and slide is particularly easy to implement, or not necessary due to a kinematic coupling. Damage caused by misalignments between slide and rolling piston can be avoided.
  • an active actuation by means of the actuating means in only one direction is sufficient.
  • the spring counteracts the actuating means as a return spring.
  • the slider should be resiliently acted upon here in the direction of the rolling piston.
  • the invention relates to a method of operating a rotary piston compressor comprising a rolling piston having a circular cross-section with a first radius around an axis, and a compressor housing having a cavity having a circular cross-section with a second radius about a central axis, the second radius being larger is as the first radius, wherein the rolling piston is rotatable or orbitally mounted about the central axis of the cavity, wherein the axis of the rolling piston parallel and spaced by a distance eccentric to the central axis of the cavity, and comprising a longitudinally aligned to the central axis slide with a front, a Rear side and a front side, which is arranged in the radial direction in the cavity displaceable in a slide opening of the compressor housing, wherein the cavity with the slide and the rolling piston in a first subspace and a second subspace is divisible, wherein the rolling piston to di e central axis of the cavity is rotated or orbitiert, and wherein a flow rate or flow rate of
  • connection can be released only in a defined rotation angle of the rolling piston, so that no compression takes place in this rotation angle.
  • a modulation of the capacity of the compressor is possible in a simple manner.
  • the connection can be released in the rotation angle of the rolling piston between the intake and outlet ports, in order to increase the efficiency. In this rotation angle, the intake and outlet openings are already in direct communication via the cavity. Compression and expansion of the fluid within the pressure and suction regions formed in this rotation angle therefore consumes only unnecessarily energy, which can be saved by releasing the connection.
  • the movement of the slider is synchronized with the rotational movement of the rolling piston by determining a maximum deflection of the slider in the presence of a contact between the Slider and the rolling piston.
  • the rotational position at the maximum deflection is sufficient to determine the exact rotational position with sufficient accuracy.
  • a further development of the method according to the invention provides for synchronizing the movement of the slide with the rotational movement of the rolling piston by analyzing an electrical voltage applied to the actuating means in the presence of a contact between the slide and the rolling piston. If there is contact between slide and rolling piston, can be closed by the kinematically induced displacement of the slider and thus induced voltage on the actuating means to the rotational position of the rolling piston. If the actuating means is subsequently actuated in such a way that the contact between slide and rolling piston no longer exists, the electronics have the most current possible value of the rotational position of the rolling piston, which can be updated again at the next contacting.
  • the Fig. 1 and 2 each show a rotary compressor 1 with a compressor housing 20, a rolling piston 10 and a slide 30.
  • the compressor housing 20 has a cavity 21 which has a circular cross-section about a central axis M with a second radius R2.
  • the rolling piston 10 is arranged in the cavity 21 and has a circular cross-section about an axis A with a first radius R1, wherein the first radius R1 is smaller than the second radius R2.
  • the axis A of the rolling piston 10 is also positioned parallel and at a distance a1 eccentric to the central axis M of the cavity 21.
  • the distance a1, ie the eccentricity, between the axis A of the rolling piston 10 and the center axis M of the cavity 21 is substantially the second radius R2 less the first radius R1.
  • the rolling piston 10 is rotatable about the central axis M of the cavity 21 and / or stored orbital. In an orbiting bearing, the rotation of the rolling piston 10 about the center axis M of the cavity 21 is decoupled from the self-rotation of the rolling piston 10 about its own axis A. The storage thereby complicates slightly, but the friction between the rolling piston 10, the compressor housing 20 and the slider 30 can be reduced.
  • Said slider 30 has a front side 31, a rear side 32 and an end face 33. In addition, it is longitudinal, or aligned longitudinally to the central axis M, and arranged in the radial direction in the cavity 21 slidably in a slide opening 22 of the compressor housing 10. In this way, the cavity 21 can be divided with the slider 30 and the rotary piston 10 in a first subspace V1 and a second subspace V2. By rotating the rolling piston 10 in the direction of rotation shown, the first subspace V1 now forms a suction side 35 and the second subspace V2 forms a pressure side 34.
  • Adjacent to the slide opening 22 lead a suction port 23 and an outlet opening 24 through the compressor housing 20 and open into the cavity 21.
  • the suction port 23 is adjacent to the slide opening 22 on the rear 32 suction side 35 of the slider 30.
  • Dayeren the outlet opening 24 opens adjacent to the slide opening 22 on the front side 31 pressure side 34 of the slider 30.
  • a check valve 25 is provided in this outlet opening 24, a check valve 25 is provided.
  • actuating means 40 is provided, with which a cross-sectional area F of a arranged in the stroke region of the slider 30 connection 50 between the first subspace V1 and the second subspace V2 is variable.
  • the actuating means 40 is kinematically coupled to the slider 30, wherein the cross-sectional area F can be predetermined by changing a distance a2 between the end face 33 of the slider 30 and the rolling piston 10.
  • the actuating means 40 is in particular an electric servomotor 41, which is designed as an electromagnet 42.
  • the distance a2 is effected in particular by lifting the slide 30 from the rolling piston 10. Consequently, the slider 30 is no longer moved over its end face 33 with the rolling piston 10 here. Rather, the movement of the slide 30 takes place exclusively by the actuating means 40, in particular without mechanical coupling between slide 30 and rolling piston 10.
  • the actuating means 40 is kinematically coupled via a push rod 71 with a valve 70 arranged in the slide 30, whereby the cross-sectional area F is also variable with the valve 70. While the gap between the slide 30 and the rotary piston 10 is present over the entire axial length, the valve 70 can be designed shorter and with a much smaller and more finely metered cross-sectional area.
  • the distance a2 between the end face 33 of the slider 30 and the rolling piston 10 is between zero and a maximum distance, wherein the maximum distance corresponds to at least the second radius R2 minus the first radius R1.
  • a resilient mounting of the slider 30 by means of a spring 80 is provided. This acts on the slide 30 in the direction of the rolling piston 10 with a force.
  • the slider 30 is always moved into abutment in the cavity 21.
  • the actuating means 40 is kinematically coupled via a push rod 61 with an adjustable spacer means 60.
  • the spacer 60 is positionable between the slider 30 and the rolling piston 10. In particular, it is mounted in the slide 30 and can be pushed out of this.
  • the axial extent of the spacer means 60 is smaller than that of the slider 30th
  • the invention is not limited to one of these embodiments, but can be modified in many ways.
  • a method may be performed in which the rolling piston 10 is rotated or orbit around the center axis M of the cavity 21, and in which the capacity of the rotary compressor 1 by changing the cross-sectional area F in the stroke region of the slider 30 is arranged Connection 50 between the first subspace V1 and the second subspace V2 by means of actuation of the actuating means 40 is changed.
  • a process supplement makes sense in which the movement of the slider 30 with the rotational movement of the rolling piston 10 by determining a maximum displacement of the slider 30 is synchronized in the presence of a contact between the slider 30 and the rolling piston 10.
  • This synchronization can be performed by analyzing an electrical voltage applied to the actuating means 40 in the presence of contact between the slider 30 and the rolling piston 10, as induced by the slider movement induction in the actuating means 40.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compressor (AREA)

Claims (11)

  1. Compresseur à piston rotatif (1), comprenant
    a) un piston rotatif (10) avec une section transversale circulaire autour d'un axe (A), avec un premier rayon (R1), et
    b) un carter de compresseur (20) avec une cavité (21) qui comporte une section transversale circulaire autour d'un axe central (M), avec un deuxième rayon (R2),
    • le deuxième rayon (R2) étant plus grand que le premier rayon (R1),
    • l'axe (A) du piston rotatif (10) étant parallèle à l'axe central (M) de la cavité (21) et excentré d'une distance (a1) par rapport à celui-ci,
    • le piston rotatif (10) étant supporté de façon à pouvoir tourner et/ou orbiter autour de l'axe central (M) de la cavité (21),
    • et comprenant
    c) un curseur (30) orienté le long de l'axe central (M), avec un côté avant (31), un côté arrière (32) et un côté frontal (33), qui est disposé dans une ouverture de curseur (22) carter de compresseur (10) de façon à pouvoir, dans la direction radiale, coulisser dans la cavité (21), la cavité (21) avec le curseur (30) et le piston rotatif (10) pouvant être divisée en un premier espace partiel (V1) et en un deuxième espace partiel (V2),
    caractérisé en ce
    qu'il est prévu un moyen d'actionnement (40) avec lequel il est possible de faire varier une surface de section transversale (F) d'un raccordement (50) disposé dans la plage de course du curseur (30) entre le premier espace partiel (V1) et le deuxième espace partiel (V2),
    le moyen d'actionnement (40) étant accouplé de façon cinématique à un moyen d'espacement (60) réglable et son étendue dans la direction axiale étant plus petite que celle du curseur (30), lequel moyen d'espacement peut être positionné entre le curseur (30) et le piston rotatif (10), et avec lequel une distance (a2) entre le côté frontal (33) du curseur (30) et le piston rotatif (10) peut être modifiée.
  2. Compresseur à piston rotatif (1), comprenant
    a) un piston rotatif (10) avec une section transversale circulaire autour d'un axe (A), avec un premier rayon (R1), et
    b) un carter de compresseur (20) avec une cavité (21) qui comporte une section transversale circulaire autour d'un axe central (M), avec un deuxième rayon (R2),
    • le deuxième rayon (R2) étant plus grand que le premier rayon (R1),
    • l'axe (A) du piston rotatif (10) étant parallèle à l'axe central (M) de la cavité (21) et excentré d'une distance (a1) par rapport à celui-ci,
    • le piston rotatif (10) étant supporté de façon à pouvoir tourner et/ou orbiter autour de l'axe central (M) de la cavité (21),
    • et comprenant
    c) un curseur (30) orienté le long de l'axe central (M), avec un côté avant (31), un côté arrière (32) et un côté frontal (33), qui est disposé dans une ouverture de curseur (22) du carter de compresseur (10) de façon à pouvoir, dans la direction radiale, coulisser dans la cavité (21), la cavité (21) avec le curseur (30) et le piston rotatif (10) pouvant être divisée en un premier espace partiel (V1) et en un deuxième espace partiel (V2),
    caractérisé en ce qu'il est prévu un moyen d'actionnement (40) avec lequel il est possible de faire varier une surface de section transversale (F) d'un raccordement (50) disposé dans la plage de course du curseur (30) entre le premier espace partiel (V1) et le deuxième espace partiel (V2),
    le moyen d'actionnement (40) étant accouplé de façon cinématique à une soupape (70) disposée dans le curseur (30), la surface de section transversale (F) pouvant être modifiée avec la soupape (70).
  3. Compresseur à piston rotatif (1) selon la revendication 1,
    caractérisé en ce que le moyen d'actionnement (40) est accouplé de façon cinématique au curseur (30), la surface de section transversale (F) pouvant être prédéfinie par une variation d'une distance (a2) entre le côté frontal (33) du curseur (30) et le piston rotatif (10).
  4. Compresseur à piston rotatif (1) selon la revendication 3,
    caractérisé en ce que la distance (a2) entre le côté frontal (33) du curseur (30) et le piston rotatif (10) est comprise entre zéro et une distance maximale, la distance maximale correspondant au deuxième rayon (R2) moins le premier rayon (R1).
  5. Compresseur à piston rotatif (1) selon l'une des revendications 3 ou 4,
    caractérisé en ce que la distance (a2) entre le côté frontal (33) du curseur (30) et le piston rotatif (10) est réglée électroniquement au moyen du moyen d'actionnement (40).
  6. Compresseur à piston rotatif (1) selon l'une des revendications précédentes,
    caractérisé en ce que le moyen d'actionnement (40) est un servomoteur (41) électrique.
  7. Compresseur à piston rotatif (1) selon l'une des revendications précédentes,
    caractérisé en ce que le moyen d'actionnement (40) est un électroaimant (42).
  8. Compresseur à piston rotatif (1) selon l'une des revendications précédentes,
    caractérisé en ce que le curseur (30) est supporté de façon élastique.
  9. Procédé de fonctionnement d'un compresseur à piston rotatif (1) selon l'une des revendications précédentes,
    caractérisé par les étapes suivantes :
    • rotation et/ou mouvement orbital du piston rotatif (10) autour de l'axe central (M) de la cavité (21) ; et
    • variation d'un débit du compresseur à piston rotatif (1) par la variation de la surface de section transversale (F) du raccordement (50) disposé dans la plage de course du curseur (30) entre le premier espace partiel (V1) et le deuxième espace partiel (V2) au moyen de l'actionnement du moyen d'actionnement (40).
  10. Procédé selon la revendication 9,
    caractérisé par l'étape suivante :
    • synchronisation du mouvement du curseur (30) avec le mouvement de rotation du piston rotatif (10) par la définition d'une déviation maximale du curseur (30) en cas de contact entre le curseur (30) et le piston rotatif (10).
  11. Procédé selon l'une des revendications 9 ou 10,
    caractérisé par l'étape suivante :
    • synchronisation du mouvement du curseur (30) avec le mouvement de rotation du piston rotatif (10) par l'analyse d'une tension électrique présente sur le moyen d'actionnement (40) en cas de contact entre le curseur (30) et le piston rotatif (10).
EP13798644.4A 2012-12-18 2013-11-28 Compresseur à piston rotatif présentant un débit modifiable Not-in-force EP2935892B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201210024704 DE102012024704A1 (de) 2012-12-18 2012-12-18 Rollkolbenverdichter mit veränderbarer Förderleistung
PCT/EP2013/074968 WO2014095294A2 (fr) 2012-12-18 2013-11-28 Compresseur à piston rotatif présentant un débit modifiable

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Publication Number Publication Date
EP2935892A2 EP2935892A2 (fr) 2015-10-28
EP2935892B1 true EP2935892B1 (fr) 2019-06-12

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EP13798644.4A Not-in-force EP2935892B1 (fr) 2012-12-18 2013-11-28 Compresseur à piston rotatif présentant un débit modifiable

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EP (1) EP2935892B1 (fr)
CN (1) CN104870821B (fr)
DE (1) DE102012024704A1 (fr)
WO (1) WO2014095294A2 (fr)

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CN106768566B (zh) * 2017-03-15 2023-05-05 广西大学 一种滚动活塞压缩机滑片与滑槽的摩擦力测量装置

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Publication number Priority date Publication date Assignee Title
DE2946906C2 (de) * 1979-11-21 1985-02-14 Bitzer Kühlmaschinenbau GmbH & Co KG, 7032 Sindelfingen Rollkolbenverdichter
FR2655093A1 (fr) * 1989-11-28 1991-05-31 Conception Applic Tech Electro Machine rotative a piston roulant.
KR100466620B1 (ko) * 2002-07-09 2005-01-15 삼성전자주식회사 용량가변형 회전압축기
CN1815029A (zh) * 2005-02-03 2006-08-09 李玉斌 一种用于旋转式压缩机的滑片
JP2008157101A (ja) * 2006-12-22 2008-07-10 Toshiba Kyaria Kk ロータリ式圧縮機及び冷凍サイクル装置
KR100816656B1 (ko) * 2006-12-27 2008-03-26 엘지전자 주식회사 용량 가변형 로터리 압축기
KR101116215B1 (ko) * 2007-02-14 2012-03-06 삼성전자주식회사 회전압축기
JP5289433B2 (ja) * 2008-05-19 2013-09-11 パナソニック株式会社 ２段ロータリ膨張機、膨張機一体型圧縮機および冷凍サイクル装置
JP2011064184A (ja) * 2009-09-18 2011-03-31 Toshiba Carrier Corp 圧縮機及び冷凍サイクル装置

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CN104870821B (zh) 2017-09-12
DE102012024704A1 (de) 2014-06-18
EP2935892A2 (fr) 2015-10-28
WO2014095294A3 (fr) 2014-12-31
WO2014095294A2 (fr) 2014-06-26
CN104870821A (zh) 2015-08-26

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