WO2005085638A1 - Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile - Google Patents

Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile Download PDF

Info

Publication number
WO2005085638A1
WO2005085638A1 PCT/EP2005/000021 EP2005000021W WO2005085638A1 WO 2005085638 A1 WO2005085638 A1 WO 2005085638A1 EP 2005000021 W EP2005000021 W EP 2005000021W WO 2005085638 A1 WO2005085638 A1 WO 2005085638A1
Authority
WO
WIPO (PCT)
Prior art keywords
additional
swivel
axial piston
moment
additional mass
Prior art date
Application number
PCT/EP2005/000021
Other languages
German (de)
English (en)
Inventor
Otfried Schwarzkopf
Matthias Mauritz
Original Assignee
Zexel Valeo Compressor Europe Gmbh
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 Zexel Valeo Compressor Europe Gmbh filed Critical Zexel Valeo Compressor Europe Gmbh
Priority to EP05700686A priority Critical patent/EP1718867B1/fr
Priority to DE502005003194T priority patent/DE502005003194D1/de
Publication of WO2005085638A1 publication Critical patent/WO2005085638A1/fr

Links

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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1054—Actuating elements
    • 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
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1206—Rotational speed of a rotating inclined plate

Definitions

  • Axial piston compressors in particular compressors for the air conditioning system of a motor vehicle
  • the invention relates to an axial piston compressor, in particular a compressor for the air conditioning system of a motor vehicle, with a housing and a compressor unit arranged in the housing and driven via a drive shaft for the suction and compression of a refrigerant, the compressor unit and a piston running axially back and forth in a cylinder block the swivel disk driving the pistons rotating with the drive shaft, eg in the form of a swivel ring, swashplate or swashplate.
  • Such an axial piston compressor is known for example from DE 197 49 727 AI.
  • This comprises a housing in which a plurality of axial pistons are arranged in a circular arrangement around a rotating drive shaft.
  • the drive force is transmitted from the drive shaft via a driver to an annular swivel disk and from this in turn to the pistons which are translationally displaceable parallel to the drive shaft.
  • the annular swivel disk is pivotally mounted on an axially displaceably mounted sleeve on the drive shaft.
  • An elongated hole is provided in the sleeve, through which the driver mentioned extends.
  • the axial mobility of the sleeve on the drive shaft is thus limited by the dimensions of the elongated hole. Installation takes place by pushing the driver through the slot.
  • Drive shaft, driver, sliding sleeve and swivel plate are arranged in a so-called engine room, in which a gaseous working medium of the compressor with a certain pressure is present.
  • the delivery volume and thus the delivery capacity of the compressor are dependent on the pressure ratio between the suction side and the pressure side of the pistons or accordingly on the pressures in the cylinders on the one hand and in the engine compartment on the other.
  • the swivel plate is designed as a swash plate, a non-rotatable receiving plate which is mounted opposite the swash plate being arranged between the swash plate and the pistons.
  • the compressors described in these publications include to take measures to avoid or reduce the imbalance of the engine during operation.
  • the known constructions have in common that the rotating components are relatively large compared to the translationally moving parts, namely pistons, piston rods, etc. and are accordingly heavy.
  • the known constructions have in common that an additional disk acts on the actual swivel disk device by means of a suitable coupling mechanism.
  • the plurality of rotating components are intended to cause the moment of the swivel disk device to be set in the direction of the minimum stroke of the pistons, as a result of which the control behavior is influenced.
  • the constructions mentioned are all relatively complex, expensive, not very compact and therefore unsuitable for the compressors for air conditioning systems that are now required by the automotive industry.
  • the aim is to dimension the moving components (in particular mass) in a suitable way in order to achieve the desired control behavior.
  • the series compressor 6SEU 12 C from DENSO has, for example, an engine with the following masses relevant for the control behavior:
  • the influencing variables which act as moments around the tilting center of a swivel plate device, are the following moments in detail, the direction of the moments being indicated in brackets and (-) regulating (towards a minimum stroke) and (+) upward (towards the maximum stroke) mean:
  • pistons i.e. the translationally moving masses as small as possible, i.e. easy to build, e.g. Made of aluminum or other materials with a lower specific density.
  • hollow pistons there is also a proposal to use hollow pistons.
  • the compressor according to EP 0 809 027 AI there is a special embodiment of the coupling mechanism between the drive shaft and swivel plate device.
  • the coupling mechanism is designed for high pressure, for example when R744 is used as the refrigerant.
  • the last-mentioned prior art also involves a so-called constant control of the delivery rate. It is proposed to design the kinematics of the compressor in such a way that the regulating tilting moments acting on the swivel plate clearly dominate over the regulating tilting moments.
  • the term “delivery rate” is relatively fuzzy. The delivery rate could be regarded as constant if, for example, the tilting angle of the swashplate is halved when the speed is doubled. The delivery rate would thus be geometrically constant.
  • other parameters also have an effect the flow rate if the tilting angle of the swivel plate changes, e.g. degree of delivery, oil spill or the like.
  • the resetting torque of the swivel plate is used for constant control of the delivery rate at changing speeds of rotation, since the swivel plate counteracts its inclined position due to the dynamic forces on the rotating part of the disk.
  • This behavior can be supported by the force of a spring, so that the delivery rate that increases with increasing rotational speed or rotational speed is at least partially compensated for by resetting the inclined or swivel position of the swivel disk.
  • such behavior can in principle be achieved by, for example, integrating an additional mass into the engine, the mass inertia of which affects the swivel plate via a coupling mechanism.
  • Compressors are also known, in particular series compressors for R134a, in which the stroke volume tends to increase solely due to the acting moments of upward and downward inertial forces. This may have to be compensated for by appropriate control intervention by the control valves used. In recent developments, especially for CO 2 compressors, efforts are being made to reverse this behavior. The necessary control intervention can then be reduced or even dispensed with.
  • FIG. 1 From the diagram according to FIG. 1 it can be clearly seen that there are courses which cause the swivel plate to be displaced to larger tilting angles when the rotational speed increases. It should be mentioned that FIG. 1 is only to be regarded as an example with a simple geometry. However, the trend shown also applies to more complex geometries. The calculation was based on a swivel ring with a predetermined inner and outer diameter and a predetermined height.
  • piston mass is relevant, the pitch circle diameter on which the pistons lie and the number of pistons.
  • Mass moment of inertia greater than J 200,000-250,000 gmm 2 .
  • Jy z ⁇ (r a 2 + n 2 ) (r a 2 + r, 2 + -) ⁇ cos ⁇ sm ⁇
  • FIG. 1 was based on the following determination of the tilting moment of the swivel or swash plate, with ⁇ being varied from 0 ° to 16 °:
  • M k , ges > M s 2 shows a diagram for an almost identical engine, this diagram being obtained according to the following calculation scheme, ⁇ being varied from 0 ° to 16 °:
  • FIG. 1 shows the prior art.
  • the regulating behavior according to FIG. 1 can often be determined in the case of current R134a series compressors. With more recent developments, one tries to change this trend into the opposite, namely according to Fig. 2.
  • An essential aspect of the invention lies in the fact that the regulating tilting moments due to the mass moments of inertia / deviation moments of the swivel plate assembly are so large that a control behavior results which corresponds qualitatively to that according to FIG. 4. That is, if the speed of the compressor increases, it remains
  • Tilt angle of the swivel plate is almost constant, or it decreases, whereby at least part of the increasing delivery rate resulting solely from the increase in speed is compensated.
  • a design is therefore selected in which an additional mass, in particular an additional disk or ring, is coupled to the swivel disk mechanism, the tilting moment of which, as a result of its deviation moment, interacts with the tilting moment due to the moment of deviation of the swivel disk.
  • the moments add up.
  • the deviation moment defined by the additional mass is superimposed on the deviation moment of the swivel plate, namely the deviation moment J yz effective around the tilt axis of the swivel plate .
  • the additional mass does not transmit a moment to the swivel plate, but rather a force transmission takes place in such a way that a reaction force arises on the swivel plate, which triggers a corresponding additional deviation moment.
  • the additional mass preferably in the form of an additional disk or an additional ring, is advantageously optimized in such a way that the ratio “mass moment of inertia / component mass” is as large as possible.
  • the component mass should therefore be as small as possible at maximum mass moment of inertia.
  • the additional mass is particularly suitable an additional ring with an outer diameter that is only marginally is smaller than the inside diameter of the engine housing.
  • the outer circumference of the additional ring is preferably spherical in cross section in order to avoid a collision between the additional ring and the engine housing when the additional ring is pivoted about its tilting axis.
  • the distance between the additional ring and the inner wall of the housing should also be essentially constant regardless of the tilting position of the additional ring.
  • the focus of the additional mass e.g. of an additional ring preferably lie on the drive shaft center axis. It is also advantageous if the center of tilt of the additional mass coincides with its center of mass.
  • the mechanical control behavior is essentially determined by the moment of the additionally provided mass, e.g. Disc or ring affected.
  • a large set-up torque can be provided by the provision of this component, the component not producing any imbalances if the center of gravity and the tilt joint are provided congruently.
  • the high mass moments of inertia required for the desired control characteristic can be provided with a comparatively low component mass, as a result of which the necessary high deviation torque is obtained.
  • Such behavior is achieved by a ring shape of the additional mass with the largest possible mean diameter.
  • FIG. 4 shows that the characteristic curves have little scatter.
  • each operating point can be optimally taken into account when designing the compressor, ie placed in the map.
  • This is of particular interest for the C0 2 application, as compared to an R134a compressor, in addition to the AC (air conditioning) operating points, HP (heat pump / heat pump heater) operating points must also be taken into account.
  • FIG. 5 shows a compressor according to the invention in longitudinal section, the engine being in a position for maximum piston stroke
  • FIG. 6 shows the compressor corresponding to FIG. 5, the engine being in a position in which the piston stroke is minimal; 7 shows the engine of the compressor according to FIGS. 5 and 6 in a perspective exploded view;
  • Fig. 13 Exemplary representation of the course of the deviation moments J yz i and J yz2 of the swivel plate and additional mass over the tilt angle of the swivel plate .
  • the axial piston compressor for the air conditioning system of a motor vehicle shown in longitudinal section in FIGS. 5 and 6 comprises an engine housing 10 which is cup-shaped and has a cylinder block 12 connected to its peripheral edge.
  • a plurality of pistons, preferably 5, 6 or 7 axially reciprocating pistons, are arranged inside the cylinder block 12, the distribution of the pistons around the central housing axis 18 being uniform.
  • a drive shaft 11, which is driven by a pulley 21, extends through the bottom of the pot-shaped housing 10 into the housing interior or into the engine compartment.
  • the drive shaft is mounted, on the one hand, in the region of the bottom of the pot-shaped housing 10 and, on the other hand, within the cylinder block 12.
  • the engine compartment delimited by the housing 10 is identified by the reference number 22.
  • a swashplate mechanism is effective within the same, by means of which the rotary movement of the drive shaft 11 is converted into axial movement of the pistons 13.
  • a swash plate 14 engages with its peripheral edge via a hinge arrangement in C-shaped recesses on the rear of the pistons 13.
  • the hinge arrangement is defined by two spherical segment-like hinge blocks 16, 17, between which the swash plate 14 slidably engages.
  • Corresponding spherical troughs are assigned to the spherical bearing surfaces of the articulated blocks 16, 17 on the mutually facing end faces of the C-shaped recesses of the pistons 13.
  • the swash plate 14 is supported on a driver 20 which is connected to the drive shaft 11 in a rotationally fixed manner, preferably via roller ball, barrel or needle bearings, both axially and radially.
  • the tilt angle of the swash plate 14 can be changed between the positions according to FIG. 5 and according to FIG. 6, the tilt angle of the swash plate 14 being maximum in FIG. 5 and minimal in FIG. 6. Accordingly, the stroke of the pistons 13 is maximum or minimum.
  • the swash plate 14 is assigned an additional mass in the form of an additional ring 15 such that the swash plate 14 and the additional ring 15 tilt in the same way.
  • M S w ⁇ 2 * I yz
  • M S w ⁇ 2 * I yz
  • the characteristic shown in FIG. 4 is obtained with the embodiment shown.
  • the deviation moments of swash plate 14 and additional ring 15 are preferably dimensioned such that the sum M S w of the tilting moments M S w ⁇ + M S w 2 is greater than or equal to as a result of the aforementioned deviation moments Moment M k / tot due to all translationally moving masses, namely piston 13 and sliding blocks 16, 17.
  • the additional ring 15 is preferably dimensioned such that it has a greater moment of deviation than the moment of deviation of the swash plate 14.
  • a cylinder head is identified by reference numeral 23.
  • Inlet and exhaust valves are arranged in a conventional manner between cylinder head 23 and cylinder block 12.
  • Fig. 7 shows the engine according to FIGS. 5 and 6 in an exploded view.
  • the swash plate 14 can be tilted around a spherical segment ring 24 which is mounted on the drive shaft 11 in a longitudinally displaceable manner and is held in the operating position by a helical compression spring.
  • the additional ring 15 is articulated on the driver 20, in particular on an articulated fork 26.
  • the corresponding hinge pin is identified by reference number 27. This ensures that the association between the additional ring 15 and the swash plate 14 is maintained.
  • FIGS. 8a and 8b show the control behavior of a compressor with additional mass (FIG. 8a) or without additional mass (FIG. 8b). It can be seen that, with the aid of the additional mass, the characteristic curves lie closely together, as is shown in FIG. 8a.
  • the control behavior is such that there is almost a certain independence of the Tilt angle from the speed results (M sw »M k , tot ).
  • the behavior according to FIG. 8a (with additional mass) is slightly regulating in comparison to the behavior without additional mass according to FIG. 8b.
  • the characteristic curves in FIGS. 8a, 8b as well as in FIGS.
  • FIG. 9a shows the behavior with additional mass
  • FIG. 9b without additional mass.
  • Msw ⁇ M k / ges for ⁇ min ⁇ ⁇ limit; Msw> M k , ges for ⁇ limit ⁇ ⁇ max 12a, 12b contain a calculation based on the last additional mass used for operating conditions with about 20 bar suction pressure and 60 and 90 bar high pressure (HP mode heat pump operation).
  • the set control characteristic is also suitable for this application, since there is generally the problem in HP operation that the engine cannot achieve the maximum stroke. You can see that in the configuration calculated here, you get at least 70% of the maximum stroke volume. Better values would be achieved if a lower spring stiffness were used for the return spring 25. A lower spring rate would remove the characteristic curves a little more from the X axis.
  • a spring constant in the range 30 ... 200 N / mm is also claimed in connection with the additional mass, in particular 30 ... 90 N / mm and preferably about 60 N / mm.
  • FIGS. 12a and 12b each show the behavior with additional mass.
  • Deviation moments naturally depend on the design and geometry of the swashplate and additional mass.
  • FIG. 13 also shows that at larger tilt angles, here> 16 °, j y22 > j y2 ⁇ .
  • FIG. 13 shows that up to a tilt angle of approximately 4 ° to 5 °, the moments of deviation of the swivel plate and additional mass increase linearly approximately in a parallel manner.
  • the course of the deviation torque J yzl adjusts the swivel plate , ie the swivel plate then has a “regulating effect”.
  • the course of the deviation moment J yz2 of the additional mass increases essentially linearly.
  • FIG. 13 is an example that qualitatively reflects the basic idea of the teaching described.
  • the two deviation curves can be influenced and relative to one another in a predetermined manner by constructive changes to the swivel plate and / or additional mass move in order to obtain corresponding predetermined control behavior of the compressor.

Abstract

L'invention concerne un compresseur à pistons axiaux, en particulier un compresseur pour la climatisation d'un véhicule automobile, qui comprend un carter (10) et un groupe compresseur installé dans le carter, entraîné par l'intermédiaire d'un arbre d'entraînement (11) et prévu pour aspirer et comprimer un fluide frigorigène, lequel groupe compresseur comporte des pistons (13), effectuant un mouvement de va-et-vient axial dans un bloc-cylindres (12), et un anneau pivotant (14) tournant avec l'arbre d'entraînement (11) et entraînant les pistons. Cet anneau pivotant (14) est pourvu d'une masse supplémentaire, sous la forme d'une bague supplémentaire (15), par l'intermédiaire de laquelle un moment de déviation, parallèle au moment de déviation de l'anneau pivotant (14), est maintenu de sorte que la somme (MSW) des moments de basculement (MSW1+MSW2) dus à ces moments de déviation est supérieure ou égale au moment (Mk,ges) du à toutes les masses effectuant un mouvement de translation, en particulier les pistons (13) ou analogues.
PCT/EP2005/000021 2004-02-26 2005-01-04 Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile WO2005085638A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP05700686A EP1718867B1 (fr) 2004-02-26 2005-01-04 Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile
DE502005003194T DE502005003194D1 (de) 2004-02-26 2005-01-04 Axialkolbenverdichter, insbesondere verdichter für die klimaanlage eines kraftfahrzeuges

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004009270.2 2004-02-26
DE200410009270 DE102004009270A1 (de) 2004-02-26 2004-02-26 Axialkolbenverdicher, insbesondere Verdichter für die Klimaanlage eines Kraftfahrzeuges

Publications (1)

Publication Number Publication Date
WO2005085638A1 true WO2005085638A1 (fr) 2005-09-15

Family

ID=34853688

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/000021 WO2005085638A1 (fr) 2004-02-26 2005-01-04 Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile

Country Status (3)

Country Link
EP (1) EP1718867B1 (fr)
DE (2) DE102004009270A1 (fr)
WO (1) WO2005085638A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008522103A (ja) * 2004-11-30 2008-06-26 ストリカー トラウマ エスエー クランプ要素のためのインサート、前記インサートを含むクランプ要素及びそれから製造される自在継手
CN114811741A (zh) * 2022-05-13 2022-07-29 宁波奥克斯电气股份有限公司 空调重心高度与支撑面半径的设计方法、结构及空调器

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008038436B4 (de) * 2008-08-20 2019-03-21 Robert Bosch Gmbh Verfahren zur Ermittlung einer Einstellgröße einer hydrostatischen Verdrängereinheit und entsprechendes System
DE102012006907A1 (de) * 2012-04-05 2013-10-10 Gea Bock Gmbh Verdichter

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4077269A (en) * 1976-02-26 1978-03-07 Lang Research Corporation Variable displacement and/or variable compression ratio piston engine
DE19808256A1 (de) * 1997-02-28 1998-09-03 Toyoda Automatic Loom Works Leistungsveränderlicher Kühlmittelkompressor
DE19839914A1 (de) * 1998-09-02 2000-03-09 Luk Fahrzeug Hydraulik Axialkolbenmaschine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CS172656B1 (fr) * 1974-06-24 1977-01-28
US4815358A (en) * 1988-01-27 1989-03-28 General Motors Corporation Balanced variable stroke axial piston machine
US4836090A (en) * 1988-01-27 1989-06-06 General Motors Corporation Balanced variable stroke axial piston machine
JP2892718B2 (ja) * 1989-11-17 1999-05-17 株式会社日立製作所 可変容量形圧縮機
DE19616961C2 (de) * 1996-04-27 2002-11-07 Daimler Chrysler Ag Hubkolbenmaschine mit Taumelscheibengetriebe
DE19749727C2 (de) * 1997-11-11 2001-03-08 Obrist Engineering Gmbh Lusten Hubkolbenmaschine mit Schwenkscheibengetriebe

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4077269A (en) * 1976-02-26 1978-03-07 Lang Research Corporation Variable displacement and/or variable compression ratio piston engine
DE19808256A1 (de) * 1997-02-28 1998-09-03 Toyoda Automatic Loom Works Leistungsveränderlicher Kühlmittelkompressor
DE19839914A1 (de) * 1998-09-02 2000-03-09 Luk Fahrzeug Hydraulik Axialkolbenmaschine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008522103A (ja) * 2004-11-30 2008-06-26 ストリカー トラウマ エスエー クランプ要素のためのインサート、前記インサートを含むクランプ要素及びそれから製造される自在継手
CN114811741A (zh) * 2022-05-13 2022-07-29 宁波奥克斯电气股份有限公司 空调重心高度与支撑面半径的设计方法、结构及空调器
CN114811741B (zh) * 2022-05-13 2024-01-19 宁波奥克斯电气股份有限公司 空调重心高度与支撑面半径的设计方法、结构及空调器

Also Published As

Publication number Publication date
EP1718867A1 (fr) 2006-11-08
DE102004009270A1 (de) 2005-09-15
DE502005003194D1 (de) 2008-04-24
EP1718867B1 (fr) 2008-03-12

Similar Documents

Publication Publication Date Title
WO2006079525A1 (fr) Compresseur a piston axial
DE102007004130A1 (de) Taumelscheiben-Verstellkompressor
WO2005085638A1 (fr) Compresseur a pistons axiaux, en particulier compresseur pour la climatisation d'un vehicule automobile
WO2005038253A1 (fr) Compresseur a pistons axiaux, en particulier compresseur pour le dispositif de climatisation d'un vehicule a moteur
WO2005124150A1 (fr) Compresseur a pistons axiaux, notamment compresseur pour climatiseur de vehicule a moteur
DE10329393A1 (de) Axialkolbenverdichter, insbesondere Kompressor für de Klimaanlage eines Kraftfahtzeuges
EP1778977A1 (fr) Compresseur a pistons axiaux
EP1602829A2 (fr) Compresseur à plateau en biais
DE10354038B4 (de) Axialkolbenverdichter, insbesondere Verdichter für die Klimaanlage eines Kraftfahrzeuges
DE102005033706A1 (de) Axialkolbenverdichter
WO2007019903A1 (fr) Compresseur a pistons axiaux
EP2021630B1 (fr) Procédé de régulation du flux massique de fluide frigorigéne d'un compresseur
EP1636492B1 (fr) Compresseur a piston axial, notamment compresseur pour installation de climatisation d'automobile
EP2021631B1 (fr) Procédé de régulation du débit massique de fluide frigorigène d'un compresseur
DE10354039B4 (de) Axialkolbenverdichter, insbesondere Verdichter für die Klimaanlage eines Kraftfahrzeuges
DE102006029875A1 (de) Verfahren zum Regeln des Kältemittel-Massenstroms eines Verdichters
WO2005111418A1 (fr) Compresseur a piston axial, notamment compresseur destine a une installation d'air climatise d'un vehicule automobile
EP2067995A1 (fr) Compresseur ä disque pivotant
WO2008025412A1 (fr) Compresseur à piston axial
DE102007024367A1 (de) Verdichter
DE102008008355A1 (de) Verdichter
WO2005021967A1 (fr) Compresseur a piston axial, notamment compresseur co2 pour systemes de climatisation de vehicules

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DE DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SM SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 2005700686

Country of ref document: EP

WWP Wipo information: published in national office

Ref document number: 2005700686

Country of ref document: EP

WWG Wipo information: grant in national office

Ref document number: 2005700686

Country of ref document: EP