WO2006081966A1

WO2006081966A1 - Axial piston compressor

Info

Publication number: WO2006081966A1
Application number: PCT/EP2006/000617
Authority: WO
Inventors: Otfried Schwarzkopf; Jens Dittmar
Original assignee: Zexel Valeo Compressor Europe Gmbh
Priority date: 2005-02-02
Filing date: 2006-01-24
Publication date: 2006-08-10
Also published as: EP1844234B1; EP1844234A1; JP2008528862A; DE502006003183D1; DE102005004840A1; US20090110568A1

Abstract

The invention relates to an axial piston compressor, in particular for motor vehicle air-conditioning systems, comprising an annular-shaped pivotable disk (2), whereby the inclination thereof can be adjusted in relation to the drive shaft (1), can be rotationally driven by the drive shaft (1), and is connected in an articulated manner to at least one support element (6) which is arranged at a distance from the drive shaft (1) and which rotates therewith. The pistons comprise, respectively, an articulated arrangement whereon the pivotable disk (2) can slide. The support element (6) is arranged on the radial external end of a force transmitting element (7) which rotates with the drive shaft (1) and is arranged in a fixed manner in the radial direction thereof. The force transmitting element (7) is rotationally mounted in the drive shaft (1) about the longitudinal axis thereof.

Description

"Axialkolb envet seals"

Description

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.

In the field of compressor engines, there is a tendency that with variable piston stroke compressors, swash plates in the form of a swivel ring, i.e., swivel shafts, are increasingly being used. So annular swashplates, use find. A necessary for the pivoting of the disc tilting joint is thereby integrated substantially in the annular swash plate. For example, from EP 0 964 997 Bl a compressor is known in which the lifting movement of the piston takes place by the engagement of an oblique to the machine shaft annular disc in an engaging chamber.

The engagement chamber is provided adjacent to the closed cavity of the piston. For an essentially play-free sliding engagement in each inclined position of the swash plate or of the swiveling ring, 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.

In addition, 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. In this way, the top dead center position of the pistons is determined and a minimum dead space guaranteed. guaranteed. The head shape of the free Mitnehmerendes 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.

Another requirement for pivoting the swash plate is the displaceability of its bearing axis in the direction of the drive shaft. For this purpose, 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. For this purpose, 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 limitation of the displaceability of the bearing axis and thus the maximum inclination of the swash plate results from the driving pin by this penetrates a slot provided in the sliding sleeve, so that the sliding sleeve finds at the ends of the slot stops. The force for the angular adjustment of the

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.

This affects the inclination of the same. Furthermore, the position of the sliding sleeve can be influenced by springs, which also belong to the prior art in various variants.

Furthermore, 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. In modern compressors, 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 problem with the construction described above, however, is the high Hertzian pressure in the region of the driver head and the swash plate (system: ball / cylinder) and the absorption of the (axial) reaction forces due to the gas force on the piston and the forces due to be transferred to the swash plate torque. A compressor similar to that known from EP 0 964 997 B1 is known from JP 2003-269330 AA, but in this case a total of two drivers are used.

Significant for the kinematics according to the two cited documents, i. So it is important for the kinematics of the objects of EP 0 964 997 Bl and JP 2003- 269330 AA is that the driving head coincides centrally with the center of the sliding blocks of the piston, and that the position of the center of the driving head at the same time in about the pitch circle Center axis of the piston tangent.

In addition to the unfavorable properties mentioned above, the objects of EP 0 964 997 B1 and JP 2003-269330 AA are designed to be very expensive, which requires a high number of parts and therefore costs, with the additional storage being overdetermined by two drivers and thus susceptible to wear is and the strength of the components in particular by a Lochlaibtmg the shaft is rather low estimate.

Another compressor is known from DE 101 52 097 A1, which differs considerably from the objects of the publications discussed above. In the article according to DE 101 52 097 Al, the driver, in particular the spherical driver head, is replaced by a hinge pin or bolt. However, 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.

Another compressor is known from 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. DE 101 52 097 Al realized the rotational movement in the lateral joint of the swash plate. In the unpublished and attributable to the applicant patent application DE 102 00 404 1645 a driver is proposed, which is mounted displaceably in the shaft. As a result, the power transmission between the driving head and the swash plate can be optimally executed (power transmission through surface contact). However, the problem may be the displacement of the driver in the shaft, since there are high forces to be absorbed as a result of the bending moment and the parts must therefore be made very stiff. This stiff ^" design requires an increased mass, the compressor.

From DE 103 154 77 Al finally a compressor of Schwenkscheiben- / Mitnehmerbauart is known in which the driver transmits no torque. Incidentally, this feature also applies to preferred embodiments of DE 102 00 404 1645. The driver function is limited to support the axial forces acting on the swash plate piston forces, the torque is provided by other independent of the driver power transmission elements. As a result, lower forces act on the driver, since, as mentioned above, no torque is transmitted. 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. Thus, 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.

Starting from the above-described prior art, it is an object of the present invention to provide a compressor, the driver head or its support element as large as possible can absorb forces (low Hertzian pressure), at the same time an over-determination of power transmission functions, i. So a terminals, should be avoided.

This object is achieved by a compressor having the features according to the patent claim 1 or 3. An inven tion according to compression he has a in their inclination to a drive shaft adjustable and the drive shaft drehange 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.

In a preferred embodiment of a compressor according to the invention, 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. In particular, this is a hinge connection between the drive shaft and swivel disk. On account of the decoupling of the device, which serves as an axial support for the piston or gas force support and a device dedicated to the drive of the swashplate or the swivel ring, 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.

In a refrigerant compressor of the type described or in a refrigerant compressor according to the preamble of patent claim 1, a distinction can be made with respect to the tilting of the swash plate with respect to two moments. On the one hand, this is a tilting moment (in the tilting plane), and, on the other hand, a twisting moment which acts perpendicularly to the aforementioned tilting moment. The twisting torque occurs, inter alia, because the maximum gas force on a piston occurs at the time of opening the valve and not at the top dead center of the piston. The resulting reaction force of all the pistons is strongly oriented to the piston, which is in the described condition. 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. Such a device may consist of one or more cylindrical pin-like element (s) or of support or contact surfaces. It should be noted at this point that the swash plate on the above-mentioned sliding sleeve, which is mounted axially displaceably along the drive shaft, is pivotally mounted. As a result, as already mentioned above, a twisting torque acting in the region of the drive shaft is supported. 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. In particular, in a design in which the power transmission element and the support element merely serve as a gas force support, the swash plate is preferably connected via drive bolts to the sliding sleeve and to the drive shaft. This ensures a safe, structurally simple drive of the swashplate, while at the same time the advantages of a decoupling between the drive and support against gas forces come to fruition. 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 Verbindungselerαent, 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. As a result, a relatively simple variant of an axial piston compressor according to the invention which can be realized with a few individual parts is ensured.

Another structurally simple preferred imple mentation of a compressor according to the invention results when the support member facing away from the end of the transmission element through the drive shaft and projects into a longitudinal slot in the sliding sleeve such that by the support member remote from the end of the power transmission element a drive sdrehmoment of the drive shaft is transmitted to the sliding sleeve.

In a particular disclosed embodiment, 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.

Preferably, 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. This represents a simple structural measure to ensure a safe drive of the sliding sleeve. Furthermore, 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. The invention will now be described by way of example and with reference to further advantages and features with reference to the accompanying drawings. The drawings show in:.

1 shows a swivel mechanism of a first preferred embodiment of a compressor according to the invention in an exploded view.

Fig. 2, the imple mentation form of Figure 1 in longitudinal section at a minimum tilt angle of the swash plate.

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

(B);

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);

5 shows a second preferred embodiment of a gas flow support of a compressor according to the invention in longitudinal section;

6 shows a third preferred embodiment of a gas force support of a compressor according to the invention, again in longitudinal section; and

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. In the cylinder block 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. Depending on ¹ 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.

From 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. As already indicated by the terminology, 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. At the side facing away from the support member 6 of the force transmission element 7, 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. 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. At this point be noted that alternatively or in addition to the power or Drehmomentübettrag on the drive pin 9, 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. It should be briefly mentioned at this point that 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).

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. For storage serve 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.

In Fig. 3a is a corresponding to Fig. 2 representation, i. Thus, a longitudinal section of the first preferred imple mentation form shown, but here at an angle of maximum deflection of the pivot ring 2. In Fig. 3b is still a cross section through the

Swing ring mechanism shown in FIG. 3a. It should be pointed out again at this point that the drive sdrehmoment not in the preferred embodiment by the gas force support 5 and the support member 6 takes place (indicated by the arrows 23, 24), but by the drive pin 9 (indicated by the arrow 25) , The drive torque is indicated by an arrow 20 in FIG. 3b. Furthermore, the tilting axis 21 of the swivel ring 2 from FIG. 3b can be seen.

In 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. In 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. Since the cylindrical or barrel-shaped contour has a non-negligible extent perpendicular to the tilting plane, 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) There, that is to say are therefore introduced on 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.

It should at this point again briefly on the advantages of the invention addressed, which are as follows: The gas power support 5 largely and preferably drehrαomentfrei (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. Reference should again be made at this point to FIGS. 4a and 4b, in which a gas force support 5 is shown, which has a cylindrical support element 6. The fact that the power transmission element 7 of the gas power support 5 is mounted rotatably about its own axis in the drive shaft 1, essentially no twisting torque (torsion) can be transmitted. This allows a defined transmission of the twisting torque elsewhere, as already mentioned above, and prevents jamming of the mechanism. Likewise, this ensures easy and quick installation. An overdetermination with respect to the twisting torque, which could result in the proposed cylindrical design of the support member 6 of the gas power support 5 is avoided by the rotatable mounting about its own axis in the drive shaft 1. The forces in the direction of the recess 10 in the drive shaft 1 by the paragraph 13 of the gas power support 5 and by the securing element 8 at the other end of the gas power support 5 and on the support element. 6 transferred remote end of the power transmission element 7. From the figures 3a and in particular from Fig. 3b it can be seen that the opening of the pivot ring 2, in which the support member 6 engages, is designed such that the support member 6 can transmit no drive rotational moment. As a result, as already mentioned above, the gas power support 5 is loaded less and the drive torque can be defined and transmitted elsewhere (in the present embodiment to the drive bolt 9).

As already mentioned in the description of FIG. 1, 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. In the present preferred embodiment, the drive torque is transmitted directly via the drive bolts 9 from the drive shaft 1 to the swivel ring 2. Alternatively, it is conceivable to transmit the drive torque indirectly via the sliding sleeve 3. In both cases, however, there are elements (for example drive bolts 9) which are connected to the shaft or protrude into it. Of course, it is also conceivable that there is only one element. Thus, the radial orientation of the sliding sleeve 3 is fixed, and by a sufficiently large recess in the sliding sleeve care is taken that the support member 6 facing part of the gas power support 5 and the power transmission element 7 can transmit no moment on the sliding sleeve. In the figures 3a and b an example is shown, in which the drive bolt s 9, which are connected to the pivot ring 2, protrude into a groove 14 in the drive shaft 1. As a result, the drive torque is transmitted directly from the drive shaft 1 to the swing ring 2 by the drive bolts 9.

Alternatively, an indirect transmission of the drive torque with a power flow via the sliding sleeve is conceivable. This could be done constructively as follows: 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. Such 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. In the present invention, a gas force support is provided which is relieved on the one hand, that it transmits no drive sdrehmoment, 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.

Taking into account the aspects explained in more detail above, 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.

An example of a corresponding gas force support 5, in particular for a corresponding support element 6, is shown in FIGS. 4a and 4b. In this example, the waveform is a circle, so that the support member is cylindrical. In addition, 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. 4a: The wall thicknesses of the pivot ring or the walls S2 and S3 surrounding the recess 22 are the same (S2 = S3) and the radii of curvature R1 and R2 are a radially outer (R1) and a radially inner (R2 ) Contours are also due to the cylindrical shape of the support member 6 (Rl = R2). It is also true that the height Sl or width der- recess 22nd is equal to the sum of the two radii of curvature Rl and R2 (Sl = Rl + R2). This sum is also constant. The centers of Rl, R2 and R, where R represents the radius of the sliding blocks 19, are identical, which ensures a constant dead space.

Basically, however, 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.

In 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 following relationships apply to the construction according to FIG. 5: S2> S3, R1 <R2, S1 = R1 + R2 = constant (in the region of the tilt), which leads to a constant dead space.

A third preferred embodiment is shown in Fig. 6, which shows an example in which the remaining wall thicknesses of the pivot ring 2 in the region of the recess 22 are equal (S2 = S3). 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. It should be noted at this point, however, that in this embodiment, 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 Kolbenanlenkung, which is indicated by a distance S4, which is not equal to zero. As a result, it is conditional that the dead space is not constant. In summary, the following relations apply to FIG. 6: S3 = S2, R1> R2 (which leads to a reduced surface pressure), S1 = R1 + R2 = constant (in the region of the tilt), the dead space is not constant.

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. As also already mentioned above, 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. Such a construction is possible only with a very precise setting of the games and extremely precise assembly and would considerably increase the processing and assembly costs. 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.

As a major advantage of the rotatability of the gas power support 5, the fact should finally be mentioned that the moments acting with respect to the axis of rotation can not be absorbed. It follows that the forces resulting from the twisting moment are substantially not absorbed by the gas force support 5 (cf., for this purpose, FIGS. 7a and 7b). The flats 12 of the swivel ring 2 and the flats 11 of the sliding sleeve 3 are due to the Hebelarmverhältnisse much better suited to absorb the forces resulting from the twisting moment. As shown in FIGS 7a and b, the power flow takes place from the Abfiachung of the swivel ring on the sliding sleeve 3 on the drive shaft 1. Further, in Figs. 7a and b, the axis 26 for the twisting moment and the point 27 for the resulting pressure force shown.

Although the invention will be described with reference to embodiments with a fixed combination of features, it also includes the conceivable further advantageous combinations of these features, as they are given in particular, but not exhaustively, by the subclaims. All disclosed in the application documents features are claimed as essential to the invention, as far as they are new individually or in combination over the prior art.

, C o m p a n c e m e n t i o n s

1 drive shaft

2 swivel ring

3 sliding sleeve

4 spring

5 gas force support

6 support element 7 power transmission element

8 fuse element

9 drive bolts

10 recess in the drive shaft 1 11 flattened side of the sliding sleeve. 3

12 flattening on the swivel ring 2

13 paragraph

14 groove

15 recess in the sliding sleeve 3 16 recess in the pivot ring 2

17 longitudinal slot

18 recording

19 sliding block

20 arrow 21 tilting axis

22 recess in the pivot ring 2 for receiving the support element. 6

23 arrow

24 arrow

25 arrow 26 axis

27 attack point

Claims

claims

1. Axialkolbenver seals, in particular for motor vehicle air conditioning systems, with a in their inclination to a drive shaft (1) adjustable, rotationally driven by the drive shaft (1), in particular annular swash plate (2) with at least one at a distance from the drive shaft (1 ) is pivotally connected to this rotatably arranged support member (6), wherein the pistons, each having a hinge assembly on which the swash plate (2) is in sliding engagement, and wherein the support member (6) at the radially outer end of one with the drive shaft (1) co-rotating and within the same non-displaceably fixed in radial direction power transmission element (7) is arranged, characterized in that the force transmission element (7) in the drive shaft (1) is rotatably mounted about its longitudinal axis.

2. A compressor according to claim 1, characterized in that the support element (6) and the force transmission element (7) are used essentially only for the axial support of the piston or gas power support, while a device independent thereof, in particular a hinge connection between the drive shaft (1) and Swing plate (2), essentially only the torque transmission is used.

3. compressor, in particular according to one of the preceding claims, characterized in that the support element (6) in the basic form in Radiais chnitt approximately rectangular, the corners are in particular strongly rounded with different radii, or compressed or circular or deformed circular or ellipsoidal.

4. Compressor according to one of the preceding claims, in particular according to claim 3, characterized in that the regions of the support element (6) which are in contact with the swash plate (2) are at least partially cylindrical or barrel-shaped.

5. A compressor according to one of the preceding claims, wherein the swash plate (2) on a longitudinally of the drive shaft (1) axially displaceably mounted sliding sleeve (3) is pivotally mounted, characterized in that between the sliding sleeve (3) and the swash plate (2) a device, in particular at least one cylinder tiftartiges element or support or contact surfaces, are provided to support a in the range of the drive shaft (1) attacking torque.

6. A compressor according to any one of the preceding claims, characterized in that the force transmission element (7) at least over parts of its circumference has a step (13) in the region of the drive shaft (1) and / or on its side facing away from the support element (6) , In particular, in the axial direction extending securing element (8).

7. A compressor according to any one of the preceding claims, characterized in that the swash plate (2) via drive bolts (9) with a / the sliding sleeve (3) and / or with the drive shaft (1) is connected.

8. A compressor according to claim 1, characterized in that the drive pin (9) in the sliding sleeve (3) or the swash plate (2) are pressed.

9. A compressor according to claim 7 or 8, characterized in that the drive bolt (9) protrude into a recess (22), in particular groove (14) in the drive shaft (1).

10. A compressor according to any one of the preceding claims, characterized in that a connecting element, in particular key, between the drive shaft (1) and sliding sleeve (3) is arranged, which allows transmission of forces or moments in the radial direction and axially displaceable on the drive shaft

(1) is stored.

11. Compressor according to one of the preceding claims, characterized in that the support element (6) facing away from the end of the force transmission element (7)

, through the drive shaft (1) through and into a longitudinal slot (17) on the sliding sleeve (3) projects such that by the support element (6) abgewaήdte end of the power transmission demes s (7) sdrehmoment a drive from the drive shaft (1) is transferred to the sliding sleeve (3).

12. A compressor according to any one of the preceding claims, characterized in that the supporting element (6) is designed such that it is within a recess (22) in the swash plate (2) with this in line contact.

13. A compressor according to any one of the preceding claims, characterized in that a height (Sl) of the recess (22) in the swash plate (2) equal to the sum of the radii of curvature of a radially outer (Rl) and a radially inner (R2) contour is.

14. A compressor according to any one of the preceding claims, characterized in that the wall thickness (S2) in the region of / a recess (22) in the swash plate (2) on the piston side facing the swash plate (2) is greater than on the Side, which faces away from the piston (S2> S3), at the same time a dead space for all tilt angles of the swash plate (2) is constant.

15. A compressor according to any one of the preceding claims, characterized in that the drive shaft (1) and the sliding sleeve (3) mutually corresponding Abfla- chungen, so that the sliding sleeve (3) rotatably mounted on the drive shaft (1).

16. A compressor according to any one of the preceding claims, characterized in that the swash plate (2) has at least one flattening (12), which with a

Flattening (11) on the sliding sleeve (3) corresponds.