EP1766234A1 - Compresseur a pistons axiaux, notamment compresseur pour climatiseur de vehicule a moteur - Google Patents

Compresseur a pistons axiaux, notamment compresseur pour climatiseur de vehicule a moteur

Info

Publication number
EP1766234A1
EP1766234A1 EP05749686A EP05749686A EP1766234A1 EP 1766234 A1 EP1766234 A1 EP 1766234A1 EP 05749686 A EP05749686 A EP 05749686A EP 05749686 A EP05749686 A EP 05749686A EP 1766234 A1 EP1766234 A1 EP 1766234A1
Authority
EP
European Patent Office
Prior art keywords
swivel plate
swivel
compressor
compressor according
plate
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.)
Withdrawn
Application number
EP05749686A
Other languages
German (de)
English (en)
Inventor
Otfried Schwarzkopf
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
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 Valeo Compressor Europe GmbH filed Critical Valeo Compressor Europe GmbH
Publication of EP1766234A1 publication Critical patent/EP1766234A1/fr
Withdrawn legal-status Critical Current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
    • 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

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, a 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.
  • the 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 is present at a certain pressure.
  • the funding volume and thus the funding performance 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 compressor shown in FIG. 13 is known from EP 1 172 557 A2.
  • This has a swivel plate device with a swivel plate in the form of a swash plate 118, to which pistons 120 are articulated via sliding blocks 121.
  • the swivel plate device has a support device which simultaneously transmits a torque between a drive shaft 114 and the swash plate 118 as a driver component.
  • Swash plate 118 formed.
  • the above-described construction of the swash plate in the form of the paired driver components 117 and 119 ensures an exposed center of gravity of the swash plate device.
  • the center of gravity removed from the tilting axis and also the tilting joint causes an imbalance, since the engine can only be balanced for a preferably swashplate tilting angle. It should be noted that the center of gravity moves depending on the tilt angle at a considerable distance from the tilt joint, which is the center of the pivoting movement.
  • the tilting moment mentioned above always counteracts the deviation moment J.
  • different deviation moments act on a component, the deviation moment mentioned here being the deviation moment relevant for the tilting movement of the swash plate.
  • This moment of variation is caused by the only degree of freedom in the system that is caused by the tilting joint.
  • a construction such as that described above is implemented, for example, in the series compressor 6SEU 12 C from DENSO, in which R134a is used as a refrigerant.
  • the (relevant) deviation moment J of the swashplate causes a tilting moment M sw around the center of the tilting movement of the swashplate, which is effective at least in the area of medium and larger swashplate tilt angles such that the tilting angle of the swashplate attempts to decrease.
  • the inertial forces of the pistons (via their deflection) cause a tilting moment M k tot on the swash plate, which is also effective around the center of the tilting movement of the swash plate.
  • the tilting moment generated by the pistons acts in the direction of an increase in the tilt angle of the swash plate.
  • the center of gravity of the system which lies outside the swivel plate's tilt or pivot point, additionally supports the effect of the pistons.
  • the effect caused by the center of gravity is generally included in the calculation of the (total) moment of deviation, where it is taken into account via a so-called Steiner component.
  • Future compressors should not have an exposed center of gravity in the area of the swivel plate and the unbalance due to the engine, which is caused in particular by the swivel plate, should be low or ideally zero.
  • 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 delivery rate if the tilt angle of the swivel plate changes, e.g. delivery rate, oil spill or the like.
  • the resetting torque of the swivel disk is used for constant control of the delivery rate at changing speeds of rotation, since the swivel disk counteracts its inclined position due to the dynamic forces on the rotating disk part. 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 plate.
  • FIGS. 1 and 2 show the described tilting behavior as a result of a speed fluctuation.
  • Fig. 1 shows the dependence of the engine room pressure difference related to the suction pressure over the tilt angle o or "alpha" the swashplate. The following pressures were assumed for the calculation:
  • 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 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 rest and the number of pistons.
  • Jl 90 ° + ⁇ main axes of inertia ⁇ ⁇ - ⁇
  • ⁇ 3 ⁇ main axes of inertia ⁇ ⁇ - ⁇
  • Deviation moment J_ z -J 2 cos ⁇ sin ⁇ + J 3 cos ⁇ sin ⁇
  • M kjges m k R ⁇ z, - cosß
  • 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 kg "> M sw 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.
  • Fig. 4 the case is shown in which the regulating tilting moments due to the mass moments of inertia / deviation moments of the swivel plate or the swivel plate assembly are dimensioned such that a control behavior results in which the tilt angle of the swivel plate remains almost constant when the speed increases , or is reduced, whereby at least part of the increasing delivery rate resulting solely from the increase in speed is compensated.
  • FIGS. 5, 6 and 7 show the tilting moments M sw , M t corresponding to FIGS. 1, 2 and 4 as well as the sums of the two aforementioned moments for a speed as a function of the tilting angle of the swivel plate or the geometric stroke volume of the compressor.
  • the regulating characteristic of the compressor can be clearly seen on the basis of the sum of the moments in the positive range, while in FIG. 6 the sum of the moments is negative for all tilt angles of the swash plate.
  • a compressor that follows the course of the moments according to FIG. 6 has regulating characteristics.
  • FIG. 7, shows a torque curve with approximately identical torque of M k tot and M sw , so that the total torque is approximately zero for all tilt angles of the swash plate.
  • FIG. 8 a shows the sum M sw + M k gcs for different speeds.
  • FIG. 8a corresponds to FIGS. 1 and 5, and clearly shows the total torque that increases as the rotational speed increases.
  • FIGS. 8a and 8b shows the above-mentioned sum for the case dealt with in FIGS. 2 and 6, it being clear that an increasing regulating torque is obtained with increasing speeds. It should be noted that in the case of FIGS. 8a and 8b, the moment of variation of the swivel plate is zero at the tilt angle 0 °. This means that in this example the swashplate and tilt joint and center of gravity coincide, whereby no exposed center of gravity occurs.
  • FIG. 8c shows the behavior of a compressor in which the deviation torque and the resulting tilting moment M sw + M k gcs are not equal to zero at a swash plate tilt angle of 0 °.
  • M sw + M k gcs is not equal to zero at a very small tilting angle of, for example, 0 °
  • the amount mentioned is reflected over the whole Tilt angle range again. Accordingly, the curve is shifted approximately parallel to a curve with a starting value of M sw + M k ges equal to zero.
  • the upward effect is amplified by the additional tilting moment (cf. FIG. 8a). Because with modern compressors the trend towards one
  • Control behavior goes, which rather follows the course of Figures 2 and 6 or 4 and 7, an adjusting behavior in the region of larger tilt angles is undesirable.
  • the object of the present invention is to provide a compressor in which the deflection of the swash plate from a range of small tilt angles is supported in the simplest possible manner.
  • An essential aspect of the invention lies in providing reduced material accumulation on the swivel plate or a swiveling portion of the same points and / or points which consist of a material which is different from the material of which the rest of the swivel plate or swivel part is made is the same.
  • Such a constructive measure makes it possible to support the tilting of the swivel plate at small tilt angles when the compressor is to be regulated.
  • a certain minimum piston stroke which is required in the case of compressors according to the prior art in order to provide a pressure on the high pressure side which is sufficient to regulate the compressor, can be reduced or become completely unnecessary.
  • compressors that are not permanently subjected to speed that is to say are connected to a drive via a clutch, such a construction makes it easier for the compressor to start up or enables it in the first place.
  • the swivel plate is ring-shaped, that is to say in the form of a swivel ring.
  • the geometry of a swivel ring is particularly well suited for the attachment of places with reduced material accumulation and / or places that are made of a different material. If a compressor has a swash plate, it is designed to be narrower than a swivel ring which has the same predetermined mass moment of inertia at a desired or required predetermined mass moment of inertia. Accordingly, the design measures described in more detail above are particularly easy to implement on a swivel ring.
  • the swivel plate when the swivel plate is designed as a swivel ring, it can be ensured in a simple manner that the stability and / or the strength of the swivel plate due to the points of reduced material accumulation and / or the steep parts on which the swivel plate or its swiveling portion consists of one material , which differs from the rest of the swivel plate or its swiveling portion, is only insignificantly or not at all impaired by the design measures. This ensures the longevity of the compressor according to the invention, since a swivel plate designed in this way is subject to little wear.
  • the locations of reduced material accumulation preferably include bores and additionally or alternatively grooves.
  • the material of the locations which consist of a material that is different from the material from which the essential rest of the swivel plate or the swiveling portion thereof is made, in a further preferred embodiment, has a lower density than the material which consists of the essential rest of the swivel plate or the swiveling portion thereof.
  • the aforementioned lower density material has a density less than about 7.83 g / cm 3
  • Density of steel the choice preferably being made of a material with a density of approximately 1.5 g / cm 3 . Due to the lower density of the material of the points, which consist of a material that is different from the material from which the essential rest of the swivel plate or the swiveling portion thereof is made, on the one hand the desired control behavior is favored, while the stability of the swivel ring or the swivel plate is not reduced. A particularly easy to manufacture embodiment has points made of plastic material; the density of plastics is of the order of about 1.5 g / cm 3 .
  • the moment of variation of the swivel plate or of the swiveling portion thereof is zero for a predetermined tilt angle in the range of small tilt angles, in particular a tilt angle in the tilt angle range from 0 ° to 8 °, in particular 0 ° to 3 °.
  • the deviation torque of the swashplate or the pivotable portion of the same favors a de-energization of the compressor at tilt angles that are greater than the predetermined tilt angle, while for angles smaller than the angle for which the deviation torque becomes zero, the aforementioned deviation torque regulates the Compressor supports.
  • Such a control behavior corresponds to the requirements placed on a modern axial piston compressor, particularly when used in the air conditioning system of a motor vehicle.
  • the center of gravity of the swivel disk which, as described in more detail above, has points of reduced material accumulation and / or points made of a different material are as the rest of the swivel plate, in a further preferred embodiment it does not differ noticeably from the center of gravity of a swivel plate which is single-material and / or without reduced material accumulation, that is to say solid throughout. Furthermore, the center of gravity of the swivel disk lies on a tilt axis assigned to it. This ensures that a compressor according to the invention runs smoothly.
  • the swivel plate is preferably made of cast iron, which enables it to be produced easily.
  • cast iron gray cast iron (GG), spheroidal cast iron (GGG), cast steel or cast aluminum are used.
  • at least some of the points of reduced material accumulation, for example grooves, are formed as part of the casting of the swivel plate.
  • the points of reduced material accumulation can be realized in a simple manner already when the swivel plate is manufactured.
  • at least part of the steep amount of reduced material accumulation is formed by machining. Processing (additional or alternative to casting) with machining means ensures that the swivel plate is fine-tuned.
  • machining is an increased processing effort, but can achieve good results, especially if the required precision is high. Furthermore, as already mentioned, a combination of casting and subsequent machining is also conceivable, in particular in order to obtain the necessary fine tuning or balancing of the swivel plate.
  • the points of reduced material accumulation and / or the points which consist of a different material from the rest of the swivel plate or the swivelable part of the same are arranged symmetrically to one another in a further preferred embodiment.
  • a special position occupies a point-symmetrical arrangement of the respective points with respect to the tilt joint. This constructive measure also ensures that the swivel plate runs smoothly. Unbalance and a wear-promoting run can be avoided.
  • an average radius and / or an average height of the swivel disk or the swiveling portion thereof are dimensioned such that in the area of the middle and Large tilt angle, in particular in the range of tilt angles that are greater than or a predetermined tilt angle for which the deviation torque of the swivel plate becomes zero, when the swivel plate is rotated, counteracting forces that counteract the swivel movement of the swivel plate via the pistons on the swivel plate acting forces causing a more far-reaching pivot movement, so that the piston stroke decreases with increasing speed by such an amount that an approximately constant delivery rate is established.
  • this constructive measure is designed in such a way that it comes into play in the range of medium and large tilt angles of the swashplate, while at the smallest and small tilt angles, i.e. in a range up to 8 °, more precisely up to the zero crossing of the deviation torque depending on Tilt angle, a tendency of the swivel plate that supports the adjustment can be observed.
  • control characteristic of a compressor according to the invention thus corresponds to the requirements of a modern compressor as used in air conditioning systems of motor vehicles.
  • the center of gravity of the swivel disk or the swivelable portion thereof preferably lies in or at least close to the axis of the drive shaft, where in particular the center of a tilt joint or its tilt axis is also located. This in turn ensures that a compressor according to the invention runs smoothly without an imbalance occurring.
  • an inner and an outer diameter are preferably selected to a maximum within the outer conditions.
  • the external conditions can be, for example, the inside diameter of the engine compartment, sufficient support for sliding blocks of a joint arrangement effective between the piston and swivel plates, or similar limiting or regulating factors. It should be noted at this point that in all of the above embodiments, the desired control behavior of the compressor is not primarily achieved with the component mass, but rather by taking into account or utilizing the moment of inertia of the swivel plate arrangement, which depends on its geometry.
  • a geometry of the swivel plate is available which ensures a combination of low component mass and (sufficiently) large moments of inertia.
  • the desired mass moment of inertia can also be influenced by a suitable choice of the swash plate thickness.
  • the swivel disk or the swiveling portion thereof preferably consists of two or more different materials which determine the mean radius for the calculation of the moment of inertia, the different materials being separated radially and / or axially from one another.
  • an outer or inner partial ring made of a first material, e.g. a higher density material such as lead or the like.
  • the moment of inertia of the compressor according to the invention can be optimized and, on the other hand, the introduction of places with reduced material accumulation or places of another material can be implemented relatively easily. This is particularly the case if the outer ring is made of lead, since this is a soft, easy-to-work material.
  • the swivel disk or the swiveling portion of the swivel disk is formed from several different materials
  • the radially outer parts preferably consist of a denser material, while the radially inner parts consist of a less dense material. This constructive measure also ensures an optimal distribution of the moment of inertia of the swivel plate.
  • 9a shows a “tube” of a swivel ring for a compressor according to the invention, ie an as yet unfinished swivel ring in a perspective oblique view; 9b shows the swivel ring from FIG. 9a in a sectional view;
  • FIG. 10a shows a first embodiment of a swivel ring for a compressor according to the invention in a perspective oblique view
  • FIG. 10b shows the swivel ring from FIG. 10a in a sectional view
  • 11a shows a second embodiment of a swivel ring for a compressor according to the invention in a perspective oblique view
  • FIG. 11b shows the swivel ring from FIG. 11a in a sectional view
  • FIG. 12 shows the deviation torque of the swivel rings according to FIGS. 9a to 11b as a function of the tilt angle of the respective swivel ring.
  • the compressor according to the invention comprises an engine housing which is cup-shaped and has a cylinder block connected to its peripheral edge.
  • Several, preferably five, six or seven axially reciprocating pistons are arranged within the cylinder block, the distribution of the pistons being uniform around a central axis of the housing.
  • a drive shaft driven by a pulley extends through the bottom of the pot-shaped housing into the housing interior or into an engine compartment. The drive shaft is mounted on the one hand in the area of the bottom of the pot-shaped housing and on the other hand within the cylinder block.
  • a swivel plate mechanism which among other things comprises a swivel ring, by means of which the rotary movement of the drive shaft is converted into an axial movement of the pistons.
  • intake and exhaust valves are arranged between a cylinder head and the cylinder block.
  • FIGS. 9a and 9b An example of the swivel plate in the form of a swivel ring 10 on which the two preferred embodiments of the present invention are based is shown in FIGS. 9a and 9b. It is a "blank" that is not in this form in a compressor according to the invention can be found; fundamental considerations can, however, be explained in a simple manner using such a “simplified” representation. Furthermore, a comparison of the moments of variation of the swivel rings of compressors according to the invention with that of a swivel ring according to FIGS. 9a and 9b is also drawn below in order to take advantage of an embodiment according to the invention to be able to explain illustratively.
  • the swivel ring on which the two embodiments are based is made of cast iron and has an inside diameter 11 of 42 mm and an outside diameter 12 of 74 mm with a height 13 of 18 mm. It should be noted at this point that the dimensions mentioned above are in no way to be understood as restrictive, but merely provide an example of the dimensions of such a swivel ring. The abovementioned variables are therefore used primarily for the orientation of the reader, but not for restricting a compressor according to the invention to certain dimensions. The idea of the invention itself is of course independent of any dimensions of the compressor.
  • the cutouts are arranged symmetrically with respect to an x-axis 16, the center of gravity of the swivel ring being formed by the cutouts in the form of bores 14 or grooves 15 compared to that in the figures 9a and 9b "Rohhng" is not changed.
  • the center of gravity of the swivel ring 10 lies on the x-axis 16, which at the same time represents a tilt axis assigned to the respective swivel ring 10.
  • the points of reduced material accumulation in the form of the bores 14 or grooves 15 are provided such that, depending on the embodiment (see also the diagram in FIG. 12, which will be explained in more detail below), at a tilt angle of approximately 1 ° to approximately 2 ° the deviation moment of the swivel ring, which results in a corresponding tilting moment of the swivel ring 10, has a zero crossing.
  • the aforementioned deviation moment favors tilting of the swivel ring 10 in a direction that adjusts the compressor, while for tilt angles greater than approximately 1 ° to approximately 2 °, the deviation moment favors a regulating tendency of a compressor according to the invention.
  • the regulating tendency in particular can be reinforced if necessary by attaching additional weights or else by a multi-material design of a swivel ring 10 of a compressor according to the invention.
  • the different materials are separated radially and / or axially from one another, in particular in such a way that an outer or inner partial ring is made of a first material, preferably of a higher density material such as lead or the like. is formed within an outer or inner circumferential groove of an inner or outer partial ring, which is made of harder and wear-resistant material such as steel or ceramic or the like.
  • the radially outer part is preferably made of denser material than the radially inner part.
  • the recesses in the form of bores or grooves and of course also recesses of any other shape are filled with a material, preferably of lower density, in order to achieve the desired control behavior, and thus locations which are made of a material which is different from that Is material from which the substantial rest of the swivel ring is formed.
  • This The measure serves to maintain the stability of the swivel ring, such an alternative also being of interest, in particular for swash plates in the form of swash plates, since it is precisely with swash plates that recesses which are too large cannot be made without impairing the stability of the swash plate.
  • other measures such as struts or the like that maintain the rigidity or strength of the swivel disk or swivel ring 10 are also conceivable.
  • inside and outside diameters are limited within the outside conditions, in the present case by the inside diameter of the engine room, but are selected to be the maximum in each case.
  • the center of gravity of the swivel ring 10 lies within the tolerances on the axis of the drive shaft, which at the same time represents the center of a tilting joint (not shown) or the associated tilting axis, which is identical to the x-axis 16.
  • the swivel ring without cutouts has a deviation torque over the entire tilting range, which favors a regulating behavior of the swivel ring, while the two swivel rings 10 provided with cutouts show a deviation torque which is in the range of a tilting angle of approximately 1 ° has a zero crossing up to about 2 °.
  • An regulating behavior of the compressor is induced for smaller angles, while a regulating behavior is induced for larger tilt angles of the swivel ring 10. This meets the requirements of a modern compressor.
  • the course of the deviation torque is almost linear as a function of the tilt angle of the swivel ring 10, which ensures an ideal control behavior of a compressor according to the invention.

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  • 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, en particulier un compresseur pour le climatiseur d'un véhicule à moteur, ce compresseur comportant un carter et une unité de compression placée dans le carter, entraînée par un arbre d'entraînement et destinée à aspirer et à comprimer un réfrigérant. Cette unité de compression comporte des pistons effectuant un mouvement axial de va-et-vient dans un bloc-cylindres et un disque orientable (10) (disque oscillant ou en nutation ou plateau oscillant) tournant avec l'arbre d'entraînement et entraînant les pistons. L'invention est caractérisée en ce que le disque orientable (10) ou une partie orientable de celui-ci comporte des emplacements (14, 15) à accumulation de matière réduite et/ou des emplacements dont le matériau est différent de celui qui constitue le reste du disque orientable (10) ou de la partie orientable de celui-ci. Ces emplacements ont une influence ciblée sur un comportement de régulation du compresseur, de sorte que, dans une zone d'angles d'inclinaison réduits du disque orientable (10) ou de la partie orientable de celui-ci, notamment dans une zone d'angles d'inclinaison allant de 0° à 8°, en particulier de 0° à 3°, on obtient un couple allant sensiblement dans le même sens qu'un couple de redressement du disque orientable (10), le couple de renversement du disque orientable (10) étant accru dans la zone d'angles d'inclinaison susmentionnée (régulation accélérée du compresseur).
EP05749686A 2004-06-16 2005-06-06 Compresseur a pistons axiaux, notamment compresseur pour climatiseur de vehicule a moteur Withdrawn EP1766234A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004029021A DE102004029021A1 (de) 2004-06-16 2004-06-16 Axialkolbenverdichter, insbesondere Verdichter für die Klimaanlage eines Kraftfahrzeuges
PCT/EP2005/006059 WO2005124150A1 (fr) 2004-06-16 2005-06-06 Compresseur a pistons axiaux, notamment compresseur pour climatiseur de vehicule a moteur

Publications (1)

Publication Number Publication Date
EP1766234A1 true EP1766234A1 (fr) 2007-03-28

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EP05749686A Withdrawn EP1766234A1 (fr) 2004-06-16 2005-06-06 Compresseur a pistons axiaux, notamment compresseur pour climatiseur de vehicule a moteur

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Country Link
US (1) US8230773B2 (fr)
EP (1) EP1766234A1 (fr)
DE (1) DE102004029021A1 (fr)
WO (1) WO2005124150A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE202007002352U1 (de) * 2007-01-17 2008-05-29 Liebherr-Hausgeräte Ochsenhausen GmbH Kühl- und/oder Gefriergerät
DE102007058064A1 (de) * 2007-12-03 2009-06-04 Valeo Compressor Europe Gmbh Verdichter
JP4924464B2 (ja) * 2008-02-05 2012-04-25 株式会社豊田自動織機 斜板式圧縮機

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DE19616961C2 (de) * 1996-04-27 2002-11-07 Daimler Chrysler Ag Hubkolbenmaschine mit Taumelscheibengetriebe
JPH10246181A (ja) * 1997-02-28 1998-09-14 Toyota Autom Loom Works Ltd 可変容量型圧縮機
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WO2005124150A1 (fr) 2005-12-29
US8230773B2 (en) 2012-07-31
US20110164994A1 (en) 2011-07-07
DE102004029021A1 (de) 2005-12-29

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