EP1872013B1 - Compresseur a pistons axiaux - Google Patents

Compresseur a pistons axiaux Download PDF

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Publication number
EP1872013B1
EP1872013B1 EP06723979.8A EP06723979A EP1872013B1 EP 1872013 B1 EP1872013 B1 EP 1872013B1 EP 06723979 A EP06723979 A EP 06723979A EP 1872013 B1 EP1872013 B1 EP 1872013B1
Authority
EP
European Patent Office
Prior art keywords
drive shaft
compressor according
support
power transmission
support element
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.)
Expired - Lifetime
Application number
EP06723979.8A
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German (de)
English (en)
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EP1872013A1 (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
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Valeo Compressor Europe GmbH
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Publication date
Application filed by Valeo Compressor Europe GmbH filed Critical Valeo Compressor Europe GmbH
Publication of EP1872013A1 publication Critical patent/EP1872013A1/fr
Application granted granted Critical
Publication of EP1872013B1 publication Critical patent/EP1872013B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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.
  • sliding blocks are provided between it and the spherically curved inner wall of the engaging chamber on both sides, so that the swivel ring slides in its orbit between them.
  • 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 point is on a circular line connecting the geometric axes of the seven pistons, and continues on a circular line, the centers the spherical joint body connects the pistons. In this way, the top dead center position of the piston is determined and ensures a minimum dead space.
  • the head shape of the free Mit supportiveendes allows the change in the inclination of the swash plate, in which the driver head forms a bearing body for a 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.
  • the force for the angular adjustment of the swash plate and thus for a control of the compressor results from the sum of each of the two 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 cavity can be regulated according to the state of the art between a high and a low pressure and accordingly engages in the equilibrium of forces at the swashplate. This affects the inclination of the same.
  • 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 adjusted with increasing rotational speed, ie 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.
  • the objects of the EP 0 964 997 B1 and the JP 2003-269330 AA are constructed very expensive, which requires a high number of parts and thus costs, in addition, the storage is overdetermined by two drivers and thus susceptible to wear and the strength of the components, in particular by a hole reveal the shaft is rather low.
  • DE 101 52 097 A1 Another compressor is out of the DE 101 52 097 A1 known, which differs significantly from the objects of the above-discussed documents.
  • 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 assembly.
  • the subject of DE 101 52 097 A1 has a complex construction, and in addition it should be noted that a large imbalance may occur depending on the tilt angle. This promotes the wear of the compressor and thus reduces its life.
  • Another compressor is out of the FR 278 21 26 A1 known, which has a driver which extends radially from the drive shaft and engages in the swash plate. Similar to the solution according to the DE 101 52 097 A1 , In this construction, the swash plate is fixedly mounted on the driver in the radial direction. This is also a key difference in terms of the objects of EP 0 964 997 B1 and the JP 2003-269330 AA.
  • 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-free. Disadvantageously, however, it may have the effect that the spherical driving head in a relatively large recess of the swash plate lies.
  • 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.
  • DE 10 2005 004 840 From the also unpublished and attributed to the applicant DE 10 2005 004 840 Finally, a compressor is known which offers an improvement in the problem of surface pressure.
  • the object of DE 10 2005 004 840 has a supporting element engaging with a pivoting ring, there being a line contact between the supporting element and the pivoting ring. This represents an improvement with respect to the Hertzian pressure in comparison to the prior art explained above.
  • it is advantageous for the object of the DE 10 2005 004 840 a drive torque and a twisting torque are decoupled from the gas power support.
  • a relatively large recess in the swash plate is necessary so as to ensure a sufficient length of the line contact and to achieve a correspondingly low surface pressure.
  • the large recess in the swash plate could lead to deformation of the swivel ring and thus wear due to the gas forces to be transmitted. Furthermore, the Abregel the swash plate (which is dependent on the Deviationsmoment respect to the tilting joint) and the imbalance thereof are adversely affected by a large recess.
  • the mass of the gas force support attacks the object of the DE 10 2005 004 840 not with the moment of deviation.
  • An essential point of the invention is therefore that a power transmission element is rotatably and / or radially displaceable articulated on the support element.
  • the power transmission element may be non-rotatably and / or radially immovably connected to the drive shaft, which ensures a simple construction of a compressor according to the invention.
  • the force transmission element can also be rotatably mounted in the drive shaft.
  • both the power transmission element and the support element are formed in the shape of a cylinder bolt.
  • such a structure is structurally or production-technically easy to implement and, in particular, ensures a low Hertzian pressure between the supporting element and the swashplate due to the cylinder-bolt-shaped design of the support element.
  • the support element and the force transmission element form an approximately T-shaped gas force support.
  • the support member optionally includes a recess into which engages the force transmission element.
  • This recess is in particular a bore, whereby a simple and cost-effective design of a compressor according to the invention is ensured.
  • the support element may also be mounted in a cylindrical recess, in particular in a bore in the swash plate.
  • the bore extends perpendicular to the drive shaft axis.
  • the support element and the force transmission element essentially serve only for the axial support of the pistons and / or a gas force support, while a device independent thereof, in particular a joint connection between Drive shaft and swivel disk essentially only the torque transmission is used.
  • a device independent thereof in particular a joint connection between Drive shaft and swivel disk essentially only the torque transmission is used.
  • the power transmission element is rotatably mounted in the drive shaft, while the support element is non-rotatably engaged with the force transmission element.
  • the power transmission element is optionally a bolt having an at least partially approximately circular or semi-elliptical cross-section.
  • the swash plate is preferably pivotally mounted on a longitudinally displaceably mounted along the drive shaft sliding sleeve, wherein the swash plate is connected via drive bolts with the sliding sleeve and / or the drive shaft.
  • the drive bolts may be pressed into the sliding sleeve or the swash plate or be secured by axial securing elements in the same.
  • the drive bolts preferably protrude into a recess, which may be present in particular in the form of a groove in the drive shaft.
  • a connecting element in particular in the form of a feather key, is arranged between the drive shaft and the sliding sleeve, which permits a transmission of forces or moments in the radial direction and is mounted axially displaceably on the drive shaft.
  • the support element facing away from the end of the power transmission element can project through the drive shaft and into a longitudinal slot on the sliding sleeve such that a drive torque is transmitted from the drive shaft to the sliding sleeve by the support member remote from the end of the power transmission element.
  • Areas of the recess in the swash plate which may be present in particular in the form of a bore, which are not filled by the support element, are preferably filled with a balance weight, in particular in the form of a closure element or with balancing weights in the form of closure elements.
  • a device for a reliable transfer of the torsional torque can be provided between the sliding sleeve and the swash plate, a device, in particular at least one cylindrical pin-like element or support or contact surfaces to support an attacking in the drive shaft twisting moment.
  • the force transmission element in particular the longitudinal axis of the same, is optionally arranged offset relative to the torque axis, in particular the drive shaft axis.
  • the support element and / or the power transmission element can be designed in several parts.
  • the force transmission element may further be formed angled, in particular it may comprise a perpendicular to the tilting moment axis and extending therethrough section.
  • the power transmission element may be arranged eccentrically in the drive shaft.
  • the swivel plate can be made of steel, brass or bronze. Also conceivable is a multicomponent or multi-material swash plate, which comprises combinations of the abovementioned materials. All the materials mentioned above provide good strength and rigidity for the structural design of the swivel disk. Due to the relatively high density of the materials, in particular of bronze or brass, results in an advantageous mass distribution, so that the translational moments of the piston masses can be optimally compensated by the rotational moments of the swash plate. In particular, but not exclusively, in the case where the swash plate is made of steel, it may have a low-wear coating, resulting in a long life of a compressor according to the invention.
  • the pistons are made in a preferred embodiment of aluminum or an aluminum alloy, whereby the weight of a corresponding compressor can be kept low.
  • the pistons may also be made of steel or a steel alloy, which leads to a high strength of the same, with a matched to the material of the swash plate choice of material (similar coefficients of thermal expansion) is advantageous.
  • the support element is barrel-shaped or cigar-shaped or cylindrical, the cylinder having a tapering diameter from the cylinder center to the cylinder ends (axial direction).
  • This can ensure that there is only a line contact between the support member and the swash plate and thus jamming between the two components are excluded.
  • the line contact is particularly suitable in the case of a swashplate made of steel also for power transmission, so that the embodiment described above, both in combination with drive pin for transmitting torque as well as without the same, i. So in a case in which the force is transmitted via the force transmission element and the support element, is conceivable and advantageous.
  • All preferred embodiments of a compressor according to the invention include (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 pressure difference is a swash plate in the form of a swivel ring 2 more or less deflected from its vertical position or pivoted. The larger the resulting swing angle, the larger the piston stroke, and accordingly, the higher the pressure at an outlet side of the compressor.
  • the swashplate mechanism of a first preferred embodiment of a compressor according to the invention includes.
  • the support member 5 is rotatably and radially displaceable articulated on the power transmission element 6, while the power transmission element 6 rotatably and radially non-displaceably connected to the drive shaft 1.
  • Both the support element 5 and the force transmission element 6 is formed in the shape of a cylinder bolt.
  • the support element 5 is rotatably and radially displaceably articulated on the force transmission element 6, which takes place via a recess 8 in the support element 5, in which the force transmission element 6 engages.
  • This recess 8 is in the form of a hole in the support member 5.
  • the support element 5 and the force transmission element 6 form an approximately T-shaped gas force support 9 in the assembled state (cf., for example Fig. 3 ).
  • the support element 5 is mounted in the swivel ring 2 in a cylindrical recess 10, which is in the form of a bore in the first preferred embodiment described here.
  • the bore 10 extends perpendicular to the drive shaft axis 11.
  • the sliding sleeve 3 has two flattened sides 13 (off Fig. 1 only a flattened side is visible), which are in sliding engagement with corresponding flats 14 on the pivot ring 2.
  • the drive bolts 7 also ensure a connection between the sliding sleeve 3 and the drive shaft 1 and a resulting force or torque transfer.
  • the drive pin 7 protrude into a recess in the drive shaft in the form of grooves 15 (wherein Fig.
  • the drive pin 7 are pressed into corresponding recesses 17 in the pivot ring 2. It should be noted at this point that the drive pin 7 can also be pressed into the sliding sleeve 3 as an alternative to pressing in the pivot ring 2.
  • the spring 4 serves as a connecting element, which is arranged between the drive shaft 1 and the sliding sleeve 3, and allows a transfer of forces in the axial direction. It is mounted axially displaceably on the drive shaft 1.
  • the support element 5 facing away from the end of the power transmission element 6 projects through a longitudinal slot 18, 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 18 opposite longitudinal slot is provided on the sliding sleeve, in which the support member 5 opposite end of the power transmission element 6 projects and thus transmits a drive torque from the drive shaft 1 to the sliding sleeve 3.
  • Fig. 1 in an exploded view shown construction is in Fig. 2 shown in a joined state.
  • Fig. 2 can be seen that the support member 5, the bore 10 in the pivot ring 2 is not completely filled.
  • These areas, which are indicated by arrows 19, 20 and not filled by the support member 5 are (in the Fig. 2 not shown) closed with a balance weight in the form of a closure element and filled by this substantially.
  • the kinematics of the pivot ring 2 can be optimized so that a desired control behavior results in or amplified, which usually means in compressors modern design that the compressor for increasing speed has an increasingly abregard tendency.
  • Fig. 6a is a section along the plane EE of Fig. 3 shown. Since the cylinder-bolt-shaped or barrel-shaped contour of the support element 5 has a non-negligible extension perpendicular to the plane of the twisting torque (indicated by the axis of the twisting torque 22), a twisting moment (which acts perpendicular to the tilting moment of the pivoting ring and inter alia occurs because the maximum gas force occurs on a piston at the time of opening of the valve and not at the dead center of the piston) there, that is, therefore, be introduced to the cylindrical support member 5, if not according to the invention mounted rotatably about its central axis in the power transmission element 6.
  • a construction according to the invention ensures that the twisting moment (torsion) is introduced only into the elements provided for this purpose, which may be, for example, the pin-like drive bolts 7 or also any support surfaces.
  • An introduction of the torque in the power transmission element 6 is excluded by a construction according to the invention.
  • the axis of the torque is denoted by the reference numeral 22 (see. Fig. 6a ).
  • FIG. 6b An alternative embodiment is in Fig. 6b in a representation analogous to Fig. 6a shown.
  • the support element 5 has a cigar-shaped contour, ie the support element 5 is shaped like a cylinder, which in the cylinder center has its largest diameter and then decreases in diameter in the direction of the cylinder ends.
  • a separation of the Antziebsfunktion and the function is achieved as a gas force support, since there is no surface contact between the support member 5 and swivel ring 2.
  • both compressors are provided in the present invention, which can transmit the driving torque from the shaft to the pivot ring completely or partially by the nature of the support of the support member 5 and the power transmission element 6, and compressor provided are in which the transmission of the drive torque substantially not by the support member 5 and the power transmission element 6, but as described above, carried by the drive pin 7.
  • a line contact would be sufficient to transmit torques.
  • the representation of the barrel shape as in Fig. 6b may be very excessive, but it is also conceivable a kind of "crowning" in the micrometer range.
  • the swivel ring 2 made of steel and provided with a coating in the embodiment described above is wear and friction minimized between the sliding blocks of the piston and the pivot ring 2, alternatively can be made of brass or bronze.
  • the materials mentioned ensure that the design requirements are met.
  • the pivoting rings 2 used are namely rings that are very high compared to the prior art.
  • the height is desired in order to be able to support the gas force support, which is composed of support element 5 and force transmission element 6, on the other hand, the height is advantageous in order to be able to assign the component a sufficient mass inertia.
  • the mentioned materials such as steel, brass or bronze offer particular, since due to the height of the swivel ring 2 these materials Ensure sufficient strength and rigidity to prevent deformation. In swivel rings according to the prior art, this is often not secured.
  • the density of bronze or brass may be slightly greater than the density of steel or gray cast iron (a swivel ring 2 according to the invention may of course also be made of gray cast iron). The density increase or the higher density of bronze or brass can be used to even better compensate or overcompensate the piston masses.
  • the height of the swivel ring 2 causes the pistons, which in the application discussed here comprise the swivel ring 2 and are mounted by means of two sliding blocks on this, have to have a large opening for embracing the swivel ring 2.
  • the pistons are made of an aluminum alloy. Since brass has an aluminum-like thermal expansion, such a combination of materials for a reduced wear and increased life of a compressor according to the invention, since the play of the sliding blocks in the piston compared to the state during assembly increases only slightly or not at all. This leads to a low noise and prevents sliding blocks can fall out due to a large game. If the swivel ring 2 is made of steel, then pistons, which are also made of steel, offer the same advantages. Alternatively, however, other material combinations (in particular from the viewpoint of a weight reduction of a compressor according to the invention) are conceivable.
  • the gas power support 9 largely and preferably free of torque (insofar as a construction is chosen in which the power transmission element 6 on its side facing away from the support member 5 is not in torque transmitting Engagement with the sliding sleeve 3 is), the support function of the pivot ring 2 true with respect to the axially acting piston forces;
  • the support member 5 is a large area, ie cylinder bolt or barrel-shaped, with torsional torques can not be initiated because the gas force support 9 either at the transition between the power transmission element 6 and support member 5 or (as will be described below) by a rotatable mounting of the Power transmission element 6 can align in the drive shaft 1 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.
  • the pivot ring 2 is connected via the drive pin 7 with the sliding sleeve 3 and with 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 7 and the gas force support 9, the adjustment 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 21 is in other words equal to zero (tilting moments equal to zero).
  • the drive pin 7 are axially secured against falling out, which takes place in that the bolts are pressed into the sliding sleeve 3 or the pivot ring 2.
  • the transmission of the drive torque takes place in the present preferred embodiment directly via the drive pin 7 of the drive shaft 1 on the pivot ring 2.
  • Drive pin 7 there are elements (for example Drive pin 7), which are connected to the shaft 1 or project into this.
  • Fig. 1 is shown as the drive pin 7, which are connected to the pivot ring 2, project into a groove 15 in the drive shaft 1. Thereby, the drive torque is transmitted directly from the drive shaft 1 to the swing ring 2 by the drive bolts 7.
  • a connecting 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 allows the axial displacement of the sleeve.
  • a connector could e.g. to be a feather key.
  • the support member 5 opposite end of the power transmission element 6 is passed through the shaft and protrudes into a slot of the sliding sleeve 3, in which the power transmission element 6 is tightly guided and thereby can transmit the drive torque. Flattenings on the sliding sleeve 3 and the swivel ring 2 then transmit the torque to the swivel ring 2.
  • a central point of the present invention is the design of the gas force support 9.
  • a gas force support 9 is provided, which is relieved on the one hand, that it transmits no drive torque, but on the other hand with respect to the surface pressure, which results from the transmission of the gas forces , is optimized.
  • the power transmission element 6 is rotatably mounted in the drive shaft 1, while the support member 5 rotatably with the power transmission element 6 is engaged.
  • the power transmission element 6 is a bolt with a partially semi-elliptical cross section.
  • a partially semicircular cross section would come into question.
  • the said semi-elliptical cross-section is made in particular Fig. 8b clear.
  • the power transmission element 6 is rotatably mounted in the drive shaft 1 about its longitudinal axis.
  • the power transmission element 6 has a shoulder 23, which determines the position thereof (in particular in the radial direction) in the drive shaft 1.
  • a securing element 24 ensures a safe whereabouts of the gas force support 9 and the support member 5 and the power transmission element 6 in the drive shaft 1.
  • the drive pin 7 (from the FIGS. 8a and 8b not apparent) the connection between the sliding sleeve 3 and the drive shaft 1 and the resulting force or torque transfer safely.
  • Another possible embodiment comprises a force transmission element 6 which is angled and comprises a section parallel to the axis 22 of the torque and a section extending therethrough.
  • the imbalance due to the storage and tilting of the swash plate and other parts associated with the mass characteristics of the swash plate are very low.
  • the moment of inertia of the swashplate and other parts attributable to the mass characteristics of the swashplate with respect to the tilting axis are optimized in terms of installation space, i. the compressor has for high speeds and over the entire deflection angle range of the swivel ring 2, i. So in particular, even for small deflection on a regulatory behavior.
  • the support member 5 is able by the appropriate design to be able to absorb forces over a large area, resulting in a low Hertzian pressure.
  • the gas force support 9 is free of torque that is transmitted between the shaft and swash plate, so that an over-determination of the power transmission function (resulting in a terminal) is avoided. Furthermore, the rigidity of the pivot ring 2 is optimized and an articulation of the pivot ring 2 to the support element 5 is achieved with a low surface pressure, i. ensured a low Hertzian pressure.
  • the driving torque could be transmitted from the force-transmitting into the drive shaft 1 power transmission element 6 on the support member 5, but not directly on the pivot ring 2, since the power transmission element 6 in the radial direction (with respect to the drive or the shaft) is not applied (correspondingly large recess in the swivel ring).
  • the support member 5 has in the radial direction of the engine / the drive shaft (axial direction with respect to the support member 5) no contact or no contact with the pivot ring 2. Therefore, the gas force support 9, which consists of the power transmission element 6 and the support member 5, the Drive torque is not transmitted to the swivel ring 2.
  • the gas forces are transmitted through a bore in the pivot ring 2 on the cylinder pin-shaped support member 5 and then in turn from the bore in the support member 5 to the power transmission element 6. It will be the forces each transferred from a hole on a cylinder with a tight play. This results in significantly lower surface pressures (surface contact) and thus lower wear than in compressors according to the prior art.
  • a further significant advantage results with respect to the inertia properties of the swivel ring 2 in combination with the support member 5.
  • the support member 5 is connected to the swash plate so that the mass forces due to the mass of the support member 5 with respect to the tilting joint of the swivel ring 2 act directly on the swivel ring 2 (Deviation moment of the arrangement).
  • the components of the gas force supports 9 have a very simple geometry and few working surfaces (for example, two cylinders in which one has a bore).
  • the essential components of the forces occurring in the swivel ring are transmitted through the Gaskraftstüt2e 9 to the drive shaft and then ultimately collected in the storage of the shaft.
  • the support member 5, the recess in the pivot ring 2 as far as possible fills was taken to ensure that the support member 5 does not collide at any possible deflection angle of the pivot ring 2 with the piston.
  • the permanent recesses that are not filled by the support member 5, for example, can be filled by plug such that the kinematics of the compressor is optimized.

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

Claims (23)

  1. Compresseur à pistons axiaux, en particulier pour systèmes de climatisation de véhicules automobiles, comprenant un disque pivotant (2) pouvant être réglé dans son inclinaison par rapport à un arbre d'entraînement (1), entraîné en rotation par l'arbre d'entraînement (1), de préférence de forme annulaire, qui est relié, en particulier de façon articulée, avec au moins un élément de support (5) agencé à distance de l'arbre d'entraînement (1) en rotation commune avec celui-ci, les pistons présentant chacun un dispositif d'articulation avec lequel le disque pivotant (2) est en engagement par frottement et l'élément de support (5) étant agencé à l'extrémité extérieure d'un élément de transmission de puissance (6) en rotation commune avec l'arbre d'entraînement (1) et fixé sensiblement en direction radiale à l'intérieur de celui-ci,
    caractérisé en ce que
    l'élément de transmission de puissance (6) est articulé avec l'élément de support (5) de façon rotative et/ou coulissante dans le sens radial, l'élément de transmission de puissance (6) et l'élément de support (5) étant tous deux réalisés en forme de goujons cylindriques.
  2. Compresseur selon la revendication 1,
    caractérisé
    en ce que l'élément de transmission de puissance (6) est relié avec l'arbre d'entraînement (1) de façon non rotative et/ou non coulissante dans le sens radial.
  3. Compresseur selon l'une des revendications précédentes,
    caractérisé
    en ce que l'élément de support (5) et l'élément de transmission de puissance (6) forment un support de puissance des gaz (9) sensiblement en forme de T.
  4. Compresseur selon l'une des revendications précédentes, en particulier selon la revendication 3,
    caractérisé
    en ce que l'élément de support (5) comprend un évidement, en particulier un forage (8), dans lequel l'élément de transmission de puissance (6) s'engage.
  5. Compresseur selon l'une des revendications précédentes,
    caractérisé
    en ce que l'élément de support (5) est installé dans un évidement de forme cylindrique (10), en particulier un forage dans le disque pivotant (2), qui s'étend perpendiculairement par rapport à l'axe de l'arbre d'entraînement (11).
  6. Compresseur selon l'une des revendications précédentes,
    caractérisé
    en ce que l'élément de support (5) et l'élément de transmission de puissance (6) ne servent sensiblement qu'à fournir un support axial aux pistons ou à la puissance des gaz, tandis qu'un dispositif indépendant (7), en particulier un assemblage articulé, entre l'arbre d'entraînement (1) et le disque pivotant (2) ne sert sensiblement qu'à réaliser la transmission du couple.
  7. Compresseur selon l'une des revendications 1 ou 3 à 6,
    caractérisé
    en ce que l'élément de transmission de puissance (6) est logé de façon rotative dans l'arbre d'entraînement (1), tandis que l'élément de support (5) est en prise de façon non rotative avec l'élément de transmission de puissance (6).
  8. Compresseur selon l'une des revendications 1 ou 3 à 7, en particulier selon la revendication 8,
    caractérisé
    en ce que l'élément de transmission de puissance (6) est un boulon ayant une section au moins en partie sensiblement de forme semi-circulaire ou semi-elliptique.
  9. Compresseur selon l'une des revendications précédentes,
    dans lequel le disque pivotant (2) est installé de façon pivotante sur une douille coulissante (3) installée de façon coulissante dans le sens axial le long de l'arbre d'entraînement (1),
    caractérisé
    en ce que le disque pivotant (2) est relié à la douille coulissante (3) et/ou l'arbre d'entraînement (1) au moyen de boulons d'entraînement (7).
  10. Compresseur selon la revendication 9,
    caractérisé
    en ce que les boulons d'entraînement (7) sont enfoncés ou fixés au moyen d'éléments de blocage axiaux dans la douille coulissante (3) ou le disque pivotant (2).
  11. Compresseur selon la revendication 9 ou 10,
    caractérisé
    en ce que les boulons d'entraînement (7) pénètrent dans un évidement, en particulier une rainure (15), dans l'arbre d'entraînement (1).
  12. Compresseur selon l'une des revendications 9 à 11,
    caractérisé
    en ce qu'un élément d'assemblage, en particulier une clavette, est agencé entre l'arbre d'entraînement (1) et la douille coulissante (3), lequel permet une transmission de puissances ou de couples dans la direction radiale et est installé sur l'arbre d'entraînement (1) de façon coulissante dans le sens axial.
  13. Compresseur selon l'une des revendications 9 à 12,
    caractérisé
    en ce que l'extrémité de l'élément de transmission de puissance (6) opposée à l'élément de support (5) s'étend à travers l'arbre d'entraînement (1) et dans une fente longitudinale sur la douille coulissante (3) de telle sorte qu'un couple d'entraînement est transmis de l'arbre d'entraînement (1) à la douille coulissante (3) par le biais de l'extrémité de l'élément de transmission de puissance (6) opposée à l'élément de support (5).
  14. Compresseur selon la revendication 5,
    caractérisé
    en ce que des zones de l'évidement (10), en particulier du forage dans le disque pivotant (2) qui ne sont pas comblées par l'élément de support (5) sont obturées, en particulier, sensiblement comblées, avec une masse d'équilibrage, en particulier sous la forme d'un élément de fermeture ou sous la forme d'éléments de fermeture.
  15. Compresseur selon l'une des revendications 9 à 14,
    caractérisé
    en ce qu'entre la douille coulissante (3) et le disque pivotant (2), il est prévu un dispositif, en particulier au moins un élément similaire à une fiche cylindrique ou des surfaces de support ou de contact, afin de supporter un couple de torsion s'exerçant dans la zone de l'arbre d'entraînement (1).
  16. Compresseur selon l'une des revendications précédentes,
    caractérisé
    en ce que l'élément de transmission de puissance (6), en particulier l'axe longitudinal de celui-ci, est agencé de façon décalée par rapport à l'axe du couple ou à l'axe du couple de torsion, en particulier à l'axe de l'arbre d'entraînement (1).
  17. Compresseur selon l'une des revendications précédentes, en particulier selon la revendication 16,
    caractérisé
    en ce que l'élément de support (5) et/ou l'élément de transmission de puissance (6) est ou sont réalisés en plusieurs pièces.
  18. Compresseur selon l'une des revendications précédentes, en particulier selon la revendication 17,
    caractérisé
    en ce que l'élément de transmission de puissance (6) est réalisé dans une forme d'angle, et comprend en particulier une section s'étendant perpendiculairement à l'axe du couple de renversement et une section s'étendant à travers celui-ci.
  19. Compresseur selon l'une des revendications précédentes, en particulier selon la revendication 16,
    caractérisé
    en ce que l'élément de transmission de puissance (6) est agencé de façon excentrée dans l'arbre d'entraînement (1).
  20. Compresseur selon l'une des revendications précédentes,
    caractérisé
    en ce que le disque pivotant (2) est fabriqué en acier ou en laiton ou en bronze.
  21. Compresseur selon l'une des revendications précédentes,
    caractérisé
    en ce que le disque pivotant (2) présente un revêtement résistant à l'usure.
  22. Compresseur selon l'une des revendications précédentes,
    caractérisé
    en ce que les pistons sont fabriqués en aluminium, ou dans un alliage d'aluminium, ou en acier, ou dans un alliage d'acier.
  23. Compresseur selon l'une des revendications précédentes,
    caractérisé
    en ce que l'élément de support est réalisé en forme de tonneau ou en forme de cigare ou en forme de cylindre avec un diamètre allant en rétrécissant depuis le centre du tonneau, cigare ou cylindre vers les extrémités du tonneau, cigare ou cylindre.
EP06723979.8A 2005-04-19 2006-04-03 Compresseur a pistons axiaux Expired - Lifetime EP1872013B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005018102A DE102005018102A1 (de) 2005-04-19 2005-04-19 Axialkolbenverdichter
PCT/EP2006/003021 WO2006111264A1 (fr) 2005-04-19 2006-04-03 Compresseur a pistons axiaux

Publications (2)

Publication Number Publication Date
EP1872013A1 EP1872013A1 (fr) 2008-01-02
EP1872013B1 true EP1872013B1 (fr) 2014-11-26

Family

ID=35070682

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06723979.8A Expired - Lifetime EP1872013B1 (fr) 2005-04-19 2006-04-03 Compresseur a pistons axiaux

Country Status (6)

Country Link
US (1) US7980167B2 (fr)
EP (1) EP1872013B1 (fr)
JP (1) JP5071810B2 (fr)
CN (1) CN101194104A (fr)
DE (1) DE102005018102A1 (fr)
WO (1) WO2006111264A1 (fr)

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EP2191133B1 (fr) * 2007-08-22 2013-04-03 ixetic Bad Homburg GmbH Machine à pistons alternatifs
WO2009027000A1 (fr) * 2007-08-25 2009-03-05 Ixetic Mac Gmbh Machine à piston alternatif
DE102008017263A1 (de) * 2008-04-04 2009-10-08 Schaeffler Kg Kompressor, insbesondere für Fahrzeugklimaanlagen
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DE102021112013A1 (de) * 2021-05-07 2022-11-10 ECO Holding 1 GmbH Antriebsvorrichtung für ein Luftfederventil
CN116717453B (zh) * 2023-08-09 2024-04-12 深圳市深旭机电工程设备有限公司 一种空调压缩机

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Also Published As

Publication number Publication date
JP5071810B2 (ja) 2012-11-14
DE102005018102A1 (de) 2005-11-03
WO2006111264A1 (fr) 2006-10-26
JP2008537052A (ja) 2008-09-11
US20090129947A1 (en) 2009-05-21
EP1872013A1 (fr) 2008-01-02
CN101194104A (zh) 2008-06-04
US7980167B2 (en) 2011-07-19

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