EP1844234A1 - Compresseur a pistons axiaux - Google Patents

Compresseur a pistons axiaux

Info

Publication number
EP1844234A1
EP1844234A1 EP06701113A EP06701113A EP1844234A1 EP 1844234 A1 EP1844234 A1 EP 1844234A1 EP 06701113 A EP06701113 A EP 06701113A EP 06701113 A EP06701113 A EP 06701113A EP 1844234 A1 EP1844234 A1 EP 1844234A1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
swash plate
sliding sleeve
support
compressor according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06701113A
Other languages
German (de)
English (en)
Other versions
EP1844234B1 (fr
Inventor
Otfried Schwarzkopf
Jens Dittmar
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.)
Valeo Compressor Europe GmbH
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
Publication of EP1844234A1 publication Critical patent/EP1844234A1/fr
Application granted granted Critical
Publication of EP1844234B1 publication Critical patent/EP1844234B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04B27/10—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
    • F04B27/1072—Pivot mechanisms

Definitions

  • the present invention relates to an axial piston compressor, in particular compressor for motor vehicle air conditioning systems, according to the preamble of claim 1.
  • the engagement chamber is provided adjacent to the closed cavity of the piston.
  • ball segments so-called sliding stones, are provided on both sides between it and the spherically curved inner wall of the intermeshing chamber, so that the swiveling ring slides between them during its rotation.
  • the drive transmission from the drive shaft to the pivot ring is effected by a driving pin fixed in the drive pin, the spherical head engages in a radial bore of the pivot ring.
  • the position of the driver head is chosen so that its center coincides with that of the spherical segments.
  • this center is located on a circular line connecting the geometric axes of the seven pistons, and further on a circular line connecting the centers of the spherical body of the piston.
  • the top dead center position of the pistons is determined and a minimum dead space guaranteed. guaranteed.
  • the head shape of the free Mit supportiveendes allows the change in the inclination of the swash plate, in which the driver head a bearing body. forms for a the stroke of the piston changing pivotal movement of the swash plate.
  • the bearing axis is formed by two coaxially mounted on both sides of a sliding sleeve bearing pin, which are also mounted in radial bores of the swash plate.
  • the sliding sleeve preferably has bearing sleeves on both sides which bridge the annular space between the sliding sleeve and the swashplate in the manner of a spoke.
  • Pivoting disc and thus for a control of the compressor results from the sum of the mutually on both sides of the piston against each other acting pressures, so that this force is dependent on the pressure in the engine room.
  • the pressure in the engine room is according to the prior art between a high and a low pressure controllable and engages accordingly in the balance of power on the swash plate.
  • the position of the sliding sleeve can be influenced by springs, which also belong to the prior art in various variants.
  • the decisive for the delivery position of the sliding sleeve is co-determined by acting on the swash plate inertial forces, wherein the swash plate adjusts with increasing rotational speed, i. changes its tilt angle or tilt angle.
  • the trend is to use swash plates with such inertia, which cause a reduction in the stroke of the piston and thus a reduction in the capacity at increasing rotational speed.
  • DE 101 52 097 A1 Another compressor is known from DE 101 52 097 A1, which differs considerably from the objects of the publications discussed above.
  • the driver in particular the spherical driver head, is replaced by a hinge pin or bolt.
  • this is integrated from the outside into the swash plate and secured with a cup-shaped drive plate, which is part of the drive shaft shaving soup.
  • the subject matter of DE 101 52 097 A1 also has an elaborate construction, it being additionally noted that a large unbalance can occur depending on the tilt angle. This promotes the wear of the compressor and thus reduces its life.
  • FR 278 21 26 Al which has a driver which extends radially from the drive shaft and engages in the swash plate. Similar to the solution according to DE 101 52 097 Al, also in this construction, the swash plate is fixedly mounted on the driver in the radial direction. This is also a key difference with respect to the objects of EP 0 964 997 Bl and JP 2003-269330 AA. While there the bearing point of the driver head in the swash plate moves relatively in the guide (bore) of the swash plate, because the swash plate in a lying on the shaft axis joint performs the rotational movement is in the designs according to FR 278 21 26 Al and.
  • the advantage of this concept is that the forces or the surface pressure due to the applied forces (due to the fact that it is relatively small forces) do not cause excessive deformation on and in the driver, whereby the driver can be designed according to lightweight and the tilting of the swash plate can be done relatively hysteresis. Disadvantageously, however, it may have the effect that the spherical driver head lies in a relatively large recess of the swash plate.
  • the Hertzian pressure can be or must be described by a geometry pairing plane / ball, which is relatively unfavorable, since it requires a high Hertzian pressure.
  • An inven tion according to compression he has a in their inclination to a drive shaft adjustable and the drive shaft nadoange drive ene, in particular annular swash plate, which is pivotally connected to at least one at a distance from the drive shaft with this co-rotating support member.
  • the pistons of the axial piston compressor each have a joint arrangement with which the swash plate is in sliding engagement.
  • the support member is disposed at the radially outer end of a co-rotating with the drive shaft and fixed within the Radakichtting non-displaceably fixed power transmission element, wherein an essential point of the invention is that the power transmission element is rotatably mounted in the drive shaft about its longitudinal axis. This ensures that no unwanted moments, in particular torsional torques, engage the force transmission element or the support element and lead to increased wear.
  • the support element and the force transmission element serve essentially only for the axial support of the pistons or for a gas force support, while the torque transmission between the drive shaft and swivel ring takes place via a separate device independent of the support and force transmission element.
  • this is a hinge connection between the drive shaft and swivel disk.
  • the device which serves to support the gas force can, on the one hand, be made slimmer and thus lighter, and furthermore the advantage that the forces acting on the support member and the force transmission element moments can be reduced, whereby, as already mentioned above, a low wear of the compressor according to the invention is ensured.
  • a further solution of the object of the present invention results when the support element in a compressor according to the preamble of claim 1 in the basic form in radial section approximately rectangular, the "corners" are strongly rounded in particular with different radii, alternatively in the form of a In this way, the surface pressure or deformation in the area of the support element and the swashplate is favorably influenced, and of course a combination of the features of claims 1 and 3 in question.
  • the regions of the support element which are in contact with the swash plate or the swivel ring can be at least partially cylindrical or barrel-shaped. By a cylindrical or barrel-shaped contour of the swash plate is approximately by line contact on the support element. It should be noted that a contour of the support element, as described above, for example, can be machined or ground by a mold, which ensures a simple and therefore cost-effective production.
  • the twisting moment is supported in a preferred embodiment in the region of the drive shaft, which is done in particular by a device which takes place between a displaceably mounted on the drive shaft sliding sleeve and the swash plate.
  • a device which takes place between a displaceably mounted on the drive shaft sliding sleeve and the swash plate.
  • Such a device may consist of one or more cylindrical pin-like element (s) or of support or contact surfaces.
  • the power transmission element may further comprise, at least over parts of its circumference, a shoulder in the area of the drive shaft and, additionally or alternatively on its side remote from the support element, comprise a securing element extending in particular in the axial direction.
  • the heel in the area of the drive shaft ensures a defined position of the force transmission element in the drive shaft in a simple structural design, a securing element ensures a secure hold in the same.
  • the swash plate is preferably connected via drive bolts to the sliding sleeve and to the drive shaft.
  • the drive bolts can be used for a secure hold in be pushed the sliding sleeve or the swash plate. Furthermore, the drive bolts can protrude into a recess, in particular into a groove in the drive shaft, wherein a dacaseler ⁇ ent, in particular a feather key, between the drive shaft and the sliding sleeve can be arranged, which allows transmission of forces or moments in the radial direction and axially slidably mounted on the drive shaft.
  • the support member is formed such that it is in line contact with a recess in the swash plate with this, which ensures optimal Hertzian pressure and also an optimal force transfer.
  • the height of the recess in the swashplate can be equal to the sum of the curvature radii of a radially outer and a radially inner contour, which ensures an ideal curve profile of the gas force support.
  • the wall thickness is greater in the region of the recess in the swash plate on the more heavily loaded by the gas force side of the swash plate than on the side of the swash plate, which is less loaded, further at the same time a dead space for all tilt angle of the swash plate is constant.
  • the more heavily loaded by the gas force side of the swash plate is normally the piston side facing. This structural measure increases the stability of the swash plate, while at the same time a weight saving is possible through the thinner wall on the less loaded side.
  • the drive shaft and the sliding sleeve may have mutually corresponding flats, so that the sliding sleeve is rotatably mounted on the drive shaft.
  • the swash plate may have at least one flattening, which corresponds to a flattening on the sliding sleeve, which ensures a safe relative position of the two components to one another.
  • FIG. 1 shows a swivel mechanism of a first preferred embodiment of a compressor according to the invention in an exploded view.
  • FIG. 3a + b the swashplate mechanism of FIG. 1 at a maximum tilt angle of the swash plate in longitudinal section (a) and in cross section
  • FIG. 4a + b show a detailed view of a gas force support according to the invention in longitudinal section (a) and schematic illustrations of the gas force support again in longitudinal section (b);
  • FIG. 5 shows a second preferred embodiment of a gas flow support of a compressor according to the invention in longitudinal section
  • FIG. 6 shows a third preferred embodiment of a gas force support of a compressor according to the invention, again in longitudinal section;
  • Fig. 7a + b a swashplate mechanism of the first preferred embodiment in cross section (a) and in longitudinal section (b).
  • All preferred embodiments of the compressor according to the invention comprise (not shown in the drawings) a housing, a cylinder block and a cylinder head.
  • pistons are mounted axially movable back and forth.
  • the compressors are driven by means of a belt pulley by means of a drive shaft 1.
  • the present compressors are variable piston-stroke compressors, the piston stroke being regulated by a pressure difference defined by the pressures on a suction-gas side and in an engine chamber.
  • the size of the pressure difference is a swash plate in the form of a swivel ring 2 more or less deflected or pivoted out of its vertical position. The larger the resulting swing angle, the larger the piston stroke, and accordingly, the higher the pressure at an outlet side of the compressor.
  • Fig. 1 it is seen that the swivel mechanism of a first preferred embodiment of a compressor according to the invention the pivot ring 2, a sliding sleeve 3, which is mounted axially displaceably on the drive shaft, a spring 4, a gas force support 5, which consists of a support element and a power transmission element 7, a securing element 8 and drive pin 9, which serve for torque transmission between the drive shaft 1 and pivot ring 2 comprises.
  • the support member is formed in the present first preferred embodiment cylinder or barrel-like.
  • the power transmission element is rotatably mounted in a corresponding recess 10 in the drive shaft about its longitudinal axis.
  • the gas force support 6 essentially serves only for the axial support of the piston forces, while the torque transmission to the swash plate takes place essentially by the drive bolts 9.
  • the sliding sleeve 3 has two flattened sides 11 (only one flattened side can be seen from FIG. 1), which are in sliding engagement with corresponding flattenings 12 on the swivel ring 2.
  • the power transmission element 7 has a shoulder 13, which determines the position thereof (in particular in the radial direction) in the drive shaft 1.
  • the securing element 8 ensures a safe whereabouts of the gas power support 5 and the support member 6 and the power transmission element 7 in the drive shaft.
  • the drive pin 9 and the connection between the sliding sleeve 3 and drive shaft 1 and a resulting force or torque transfer safely In addition to the already explained above connection between the pivot ring 2 and drive shaft 1, the drive pin 9 and the connection between the sliding sleeve 3 and drive shaft 1 and a resulting force or torque transfer safely.
  • the drive pins 9 protrude into a recess in the drive shaft in the form of grooves 14. in turn (from Fig. 1, in turn, only one of the grooves 14 can be seen).
  • the drive pins are pressed into corresponding recesses 16 in the pivot ring 2.
  • the spring 4 serves as connec tion element, which is arranged between the drive shaft 1 and the sliding sleeve 3 and allows a transfer of forces in the axial direction. She . is mounted axially displaceable on the drive shaft 1.
  • the support element 6 facing away from the end of the power transmission element 7 projects through a longitudinal slot 17, which is formed on the sliding sleeve 3, in the drive shaft 1 in.
  • the sliding sleeve may be formed such that a longitudinal slot 17 opposite longitudinal slot is provided on the sliding sleeve, in which the support member 6 opposite end of the power transmission element 7 protrudes and thus transmits a drive torque from the drive shaft 1 to the sliding sleeve 3.
  • the drive shaft 1 and the sliding sleeve 3 may additionally or alternatively to the connection or torque transfer via the drive pin 9 mutually corresponding flats, so that the sliding sleeve is rotatably mounted on the drive shaft (from Fig 1 not visible).
  • Fig. 2 The construction shown in exploded in Fig. 1 position is shown in Fig. 2 again in longitudinal section, which is apparent from Fig. 2 in addition to the already known from Fig. 1 features, such as the pivot ring 2 in a piston rods or the piston associated receptacle 18 is mounted.
  • sliding blocks 19 which are located between the pivot ring 2 and the receptacle 18.
  • the swivel ring 2 is in the illustration of Fig. 2 in a minimum deflection, i. the swivel ring has a minimum tilt angle. From this representation, especially the interaction of trained on the gas power support 5 paragraph 13 with the drive shaft 1 can be seen. Furthermore, the interaction between force transmission element 7 and securing element 8 can also be taken from this.
  • Fig. 3a is a corresponding to Fig. 2 representation, i.
  • Fig. 3b is still a cross section through the
  • FIG. 4a is again a detailed representation of parts of the power transmission element 7 and the support member 6 in engagement with the pivot ring 2 is given.
  • Fig. 4b two longitudinal sections of the gas force support 5 of the first preferred embodiment are shown, which emerge by a rotation by 90 ° apart. In this illustration, the cylindrical support member 6 is clearly visible.
  • a twisting moment (which acts perpendicular to the tilting moment of the swivel ring and, inter alia, occurs because the maximum gas force on a piston at the time of opening of the valve occurs and not at the dead center of the piston)
  • the cylindrical support element 6 if this is not according to the invention rotatably mounted about its central axis in the drive shaft 1. Therefore, a construction according to the invention ensures that the twisting torque is introduced only in the elements provided for this purpose, which may be, for example, the pin-like drive bolts 9 or else any support surfaces. An introduction of the torque in the gas power support 5 is excluded by a construction according to the invention.
  • the gas power support 5 largely and preferably woor ⁇ omentok (insofar as a construction is selected in which the power transmission element 7 on its side facing away from the support member 6 is not in torque transmitting Engagement with the sliding sleeve 3 is) the support function of the pivot ring 2 with respect to the axially acting piston forces true; the support element 6 or at least the head region of the support element 6 can be formed over a large area, ie cylindrical or barrel-shaped, wherein torsional torques can not be introduced, since the gas force support 5 can align about its central axis; the drive torques are transmitted in a defined manner in the plane perpendicular to the tilting plane of the pivoting ring, it being noted here that there are various possibilities of power transmission or torque transmission.
  • FIGS. 4a and 4b in which a gas force support 5 is shown, which has a cylindrical support element 6.
  • the swivel ring 2 is connected via the drive bolts 9 to the sliding sleeve 3 and to the drive shaft 1.
  • the sliding sleeve 3 is axially displaceably mounted on the drive shaft 1 and allows in conjunction with the spring 4, the drive pin 9 and the gas force support 5, the setting of the pivot angle of the pivot ring 2.
  • the adjusting pivot angle depends on the gas forces, the inertial properties of the pivot ring 2 and the engaging with this piston, as well as the spring force of the spring 4 from.
  • the sum of the moments about the tilting axis is in other words equal to zero (tilting moments equal to zero).
  • the drive pin 9 are axially secured against falling out, which is effected in that the bolts are pressed into the sliding sleeve 3 or the pivot ring 2.
  • the drive torque is transmitted directly via the drive bolts 9 from the drive shaft 1 to the swivel ring 2.
  • a connec tion element between the drive shaft 1 and sliding sleeve 3 which allows the transmission of forces or moments in the radial direction, but for example by sliding in a groove of the sliding sleeve 3, the axial displaceability of the socket permits.
  • a connecting element could for example be a feather key.
  • the end of the force transmission element 7 opposite the support element 6 is guided through the shaft and protrudes into a slot of the sliding sleeve 3, in which the force transmission element 7 is tightly guided and thereby the drive torque can be transmitted.
  • a central point of the present invention is the design of the gas force support 5.
  • a gas force support is provided which is relieved on the one hand, that it transmits no drive snavmoment, but on the other hand with respect to the surface pressure, which results from the transmission of the gas forces , is optimized.
  • the recess 22 in the pivot ring 2, in which engages the support member 6, is designed such that the gas force support 5 and in particular the support member 6 are radially free and thus transmit no drive torque. Furthermore, the gas force support 5 and the support member 6 are designed such that the tilting of the swivel ring 2 takes place by a rolling operation on the support member 6. Ideally, the height of the recess 22 for the support member 6 does not change. This simplifies the machining of the recess 22, but a change in the height of the recess 22 is theoretically possible.
  • the support element 6 is optimally designed if it allows the rolling movement by a suitable curve profile and continues linearly in the radial direction, so as to ensure a line contact and a low Hertzian pressure.
  • FIGS. 4a and 4b An example of a corresponding gas force support 5, in particular for a corresponding support element 6, is shown in FIGS. 4a and 4b.
  • the waveform is a circle, so that the support member is cylindrical.
  • the center of the circle or the circular shape of the cylinder coincides with the center of the Kolbenanlenkung, resulting in a constant dead space of the compressor according to the invention.
  • the following relationships also apply to FIG.
  • the curve profile of the gas force support is freely selectable under the following conditions:
  • the height Sl of the recess must be equal to the sum of the radii of curvature of the radially outer Rl and the radially inner R2 contour for each tilt angle.
  • Simple examples of profiles that roll in a recess 22 with the same height Sl, are shown in Figures 5 and 6.
  • Fig. 5 the second preferred embodiment of a compressor according to the invention is shown how by the choice of different radii while keeping the dead space the wall thickness of the pivot ring 2 in the region of the recess 22 at the heavily loaded by the gas force side (towards the piston directed side) can be increased.
  • the main load by the pressure force acts for this example on the line contact between the pivot ring 2 and a (sectional) cylinder surface, which is formed with the radius Rl.
  • the condition Rl> R2 results in the advantage of a lower surface pressure for the main load direction.
  • the pivot point of the joint (center of the radii Rl and R2) in the pivot ring 2 does not coincide with the pivot point of the Kolbenanschung, which is indicated by a distance S4, which is not equal to zero.
  • the present invention in addition to the design of the gas force support 5 in terms of surface pressure, the present invention, as already mentioned above, also facilitates the assembly and the machinability of the parts.
  • the gas power support 5 or in particular the power transmission element 7 is not fixed to the drive shaft s.1 connected, but rotatably mounted in the same.
  • the orientation of the tilt axis is By the drive bolt 9 and the flats 11 on the sliding sleeve 3 and the flats 12 on the swivel ring gate given (see Fig. 7a and 7b).
  • a firmly pressed into the drive shaft 1 gas force support 5 would also dictate the orientation of the tilting axis and thus create an over-determination that would at least complicate an assembly and easy tilting of the mechanism.
  • the present invention avoids this over-determination by the rotatable mounting of the power transmission element 7 and the gas power support 5 in the drive shaft 1 and facilitates the assembly.

Landscapes

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

Abstract

L'invention concerne un compresseur à pistons axiaux destiné à des climatisations de véhicules, comportant un plateau orientable (2) notamment annulaire, dont l'inclinaison par rapport à un arbre d'entraînement (1) peut être réglée, entraîné par l'arbre d'entraînement (1), connecté de façon articulée à au moins un élément support (6) disposé à distance de l'arbre d'entraînement (1), tournant avec celui-ci. Les pistons comportent un système d'articulation respectif sur lequel le plateau orientable (2) coulisse. L'élément support (6) est disposé sur l'extrémité radialement extérieure d'un élément de transfert de force (7) tournant avec l'arbre d'entraînement (1), disposé de façon fixe dans la direction radiale de celui-ci, l'élément de transfert de force (7) étant logé de façon à tourner autour de son axe longitudinal dans l'arbre d'entraînement (1).
EP06701113A 2005-02-02 2006-01-24 Compresseur a pistons axiaux Expired - Fee Related EP1844234B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005004840A DE102005004840A1 (de) 2005-02-02 2005-02-02 Axialkolbenverdichter
PCT/EP2006/000617 WO2006081966A1 (fr) 2005-02-02 2006-01-24 Compresseur a pistons axiaux

Publications (2)

Publication Number Publication Date
EP1844234A1 true EP1844234A1 (fr) 2007-10-17
EP1844234B1 EP1844234B1 (fr) 2009-03-18

Family

ID=36006801

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06701113A Expired - Fee Related EP1844234B1 (fr) 2005-02-02 2006-01-24 Compresseur a pistons axiaux

Country Status (5)

Country Link
US (1) US20090110568A1 (fr)
EP (1) EP1844234B1 (fr)
JP (1) JP2008528862A (fr)
DE (2) DE102005004840A1 (fr)
WO (1) WO2006081966A1 (fr)

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DE102005018102A1 (de) 2005-04-19 2005-11-03 Zexel Valeo Compressor Europe Gmbh Axialkolbenverdichter
WO2009010118A1 (fr) * 2007-07-13 2009-01-22 Ixetic Mac Gmbh Moteur à piston alternatif
WO2009015726A1 (fr) * 2007-07-27 2009-02-05 Ixetic Mac Gmbh Machine à piston alternatif
DE112008002028A5 (de) * 2007-08-22 2010-07-22 Ixetic Mac Gmbh Hubkolbenmaschine
WO2010126959A2 (fr) * 2009-04-30 2010-11-04 Tsc Offshore Group Limited Ensemble d'alignement biaxial pour dispositif de distribution de force
US8994837B2 (en) * 2010-11-26 2015-03-31 Intel Mobile Communications GmbH Image processing devices and image processing methods of moving objects
WO2015090880A1 (fr) * 2013-12-18 2015-06-25 Magna Powertrain Bad Homburg GmbH Compresseur frigorifique
DE102019117170B4 (de) * 2019-06-26 2023-01-12 Schaeffler Technologies AG & Co. KG Riemenspanner mit einer Pressfüge-Formschlussverbindung

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FR2782126B1 (fr) * 1998-08-10 2000-10-13 Valeo Climatisation Compresseur a cylindree variable
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JP4838485B2 (ja) * 2000-11-10 2011-12-14 ルーク ファールツォイク・ヒドラウリク ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト 往復動ピストン機械
JP2003097424A (ja) * 2001-09-27 2003-04-03 Sanden Corp 可変容量型圧縮機
KR100759423B1 (ko) * 2001-12-12 2007-09-17 한라공조주식회사 용량가변형 사판식 압축기
JP2003269328A (ja) * 2002-03-18 2003-09-25 Sanden Corp 可変容量圧縮機
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Also Published As

Publication number Publication date
WO2006081966A1 (fr) 2006-08-10
DE502006003183D1 (de) 2009-04-30
JP2008528862A (ja) 2008-07-31
DE102005004840A1 (de) 2006-08-10
US20090110568A1 (en) 2009-04-30
EP1844234B1 (fr) 2009-03-18

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