JP2008528862A - Axial piston compressor - Google Patents

Abstract

An axial piston compressor, in particular for an automotive air conditioning system, which is variable with respect to the inclination relative to the drive shaft (1), is rotationally driven by the drive shaft (1) and is spaced from the drive shaft (1). A swash plate (2) articulated with at least one support element (6) rotating therewith, in particular a ring-type swash plate, the pistons slidingly meshing with the swash plate (2), respectively. The support element (6) rotates together with the drive shaft (1) and is radially outside the power transmission element (7) fixed to the drive shaft so as not to be displaced in the radial direction. At the end, the power transmission element (7) is attached to the drive shaft (1) so as to be rotatable about the longitudinal axis.
[Selection] Figure 1

Description

  The invention relates to an axial piston compressor as described in the preamble of claim 1, in particular for an automotive air conditioning system.

  In the field of compressor drive mechanisms, in the case of compressors having variable piston strokes, there is an increasing tendency to use tilt ring type swash plates. This should be called a ring-type swash plate, and comprises a joint arrangement that provides the necessary tilt for tilting the plate that is substantially integrated into the ring-type swash plate. For example, in a compressor known from EP 0 964 997 B1, the piston stroke movement is achieved by means of meshing means with a ring plate inclined with respect to the machine axis (in the meshing chamber). This mating chamber is adjacent to the sealed hollow space of the piston. In any tilting position of the swash plate or tilt ring, there is a sphere part called a slide block on both sides between the spherical inner wall of the meshing chamber and the meshing chamber without any play. Slide

  The driving force is transmitted from the driving shaft to the driving shaft by a pin for connecting movement, which is attached to the circular head engaged with the radial hole of the driving shaft and the tilt ring, and the position of the head of the member for connecting movement. Has a center point that coincides with the center of the spherical portion. Further, the center point is located on a circular line, connects the geometric axes of the seven pistons to each other, and further connects the center point of the spherical connecting member of the piston on the circular line. By this method, the top dead center center position of the piston is determined and the minimum clearance volume is secured. The inclination of the swash plate can be changed by the following facts by the shape of the head at the free end of the member for connection movement. In other words, the head of the connecting member forms a bearing body for tilting movement, which changes the stroke distance of the piston.

  An additional prerequisite for the inclination of the swashplate is the possibility of movement of the mounting shaft in the direction of the drive shaft. For this purpose, the mounting shaft is formed by two mounting pins mounted on the same shaft on each side of the slide sleeve, which mounting pins are further mounted in radial holes in the swash plate. For this purpose, it is desirable for the slide sleeve to have a mounting sleeve on each side, which straddles the annular space between the slide sleeve and the swashplate like a spoke.

  Limiting the mobility of the mounting shaft and, as a consequence, the maximum angular position depends on the pin for the coupling movement, which passes through a tapered hole formed in the sliding sleeve, which causes the sliding sleeve to Due to the fact that it ends at the end of the. The power of the swashplate angle change and compressor adjustment depends on the sum of the pressures acting on each side of the piston, but this power depends on the pressure in the drive chamber. According to existing technology, the pressure in the drive mechanism chamber can be adjusted between a high pressure and a low pressure, and as a result, it affects the balance of power in the swash plate and affects the inclination of the swash plate. The position of the slide sleeve can also be influenced by various springs encompassed by existing technology.

  Further, the position of the slide sleeve is determined by the inertial force acting on the swash plate, although the position dominates the transmission output. The position of the swash plate, that is, the angle of its inclination, changes as the speed of rotation increases. In modern compressors, the trend is to use a swashplate with inertial motion, leading to a decrease in piston stroke distance and thereby a decrease in delivery output when the rotational speed is increased.

  However, the problem with the arrangement described above is that the reaction power due to the high Hertzian stress in the region of the head and swashplate (system: circular / cylindrical) of the member for connecting motion and the gas pressure on the piston. And absorption of power by torque transmitted to the swash plate.

  A compressor similar to that known from EP 0 964 997 B1 can be found from JP2003-269330A, but this compressor uses a total of two members for connecting movements.

  The kinematics according to the two publications mentioned here, which are the kinematics of the subject matter of EP 0 964 997 B1 and JP 2003-269330 A, but what is important for this is that the head of the member for the linked movement is the sliding of the piston The central point of the block is coincident with the central point of the block, and the central point of the head of the connecting motion member is substantially tangent to the reference circle of the central axis of the piston.

  In addition to the above disadvantageous features, the fact that the subject matter of EP 0 964 997 B1 and JP 2003-269330 AA is a very complex structural arrangement, increases the number of parts and costs, and also the connecting movement Since the attachment of the means by means of two members is overdetermined, the deterioration and the strength of the parts are considered rather low, in particular due to the fact that a hole is provided in the shaft.

  The other compressors known from DE 101 52 097 A1 are quite different from the subject discussed here. In the case of the subject according to DE 101 52 097 A1, the connecting movement member, in particular the circular head of the connecting movement member, is replaced by a hinge pin or a spindle. However, this is integrated into the swash plate from the outside, and is fixed using a cup-type disk for connecting movement which is a drive shaft assembly. The subject of DE 101 52 097 A1 also has a complex structural arrangement. Furthermore, it must be taken into account that depending on the angle of inclination, a large unbalance is introduced. This accelerates the deterioration of the compressor and consequently reduces its service life.

  Another compressor is also known by FR 278 21 26 A1, which comprises a member for connecting movement that extends radially from the drive shaft and engages the swash plate. In a manner similar to the solution according to DE 101 52 097 A1, the swashplate of this arrangement is also fixed to the radially extending connecting motion member. This is also very different from the subject matter of EP 0 964 997 B1 and JP 2003-269330. On the other hand, in the latter case, the attachment point of the member head for connecting movement of the swash plate undergoes relative movement in the guide way (bore) of the swash plate, which is the joint connection of the swash plate on the drive shaft. In the arrangement according to FR 278 21 26 A1 and DE 101 52 097 A1, the rotational movement is achieved in the longitudinal joint configuration of the swash plate.

  The unpublished patent application DE 102 00 404 1645 belonging to the present applicant proposes a member for connecting movement that is movable and mounted on the shaft. As a result, power transmission between the member head for connecting motion and the swash plate is optimally achieved (power transmission as area contact). However, the movement of the member for connecting movement on the shaft can be problematic because the parts must be subjected to a strong force due to the bending moment and therefore the parts must have a very rigid structure. This rigid structure causes an increase in compressor mass.

  Finally, in DE 103 154 77 A1, there is a swash plate / member compressor for a connected motion structure type, in which the connected motion member does not transmit torque. This feature also applies to the embodiment of DE 102 00 404 1645. This coupled motion function limits the provision of support for the piston power acting on the axis of the swashplate and the torque transmitted by a further power transmission element independent of the coupled motion member. As a result, the power acting on the connecting motion member is low, because torque is not transmitted as described above. The advantage of this approach is that the power due to the applied power, or contact pressure (because these forces are relatively low) does not cause excessive deformation of the linked motion member, which results in Thus, a lightweight structure can be obtained, and the inclination of the swash plate can be achieved in a relatively hysteresis-free manner. However, a disadvantageous effect is that the circular head of the connecting motion member is located in a relatively large recess in the swash plate. As a result, Hertzian stress can or must be drawn by plane-circular geometric pairing, which increases the degree of Hertzian stress, which is relatively disadvantageous.

  Starting from the existing technology described below, the problem of the present invention is that the head of the member for connection movement, or its support element, can receive as much power as possible (low hertz stress) and at the same time It is to provide a compressor that avoids over-determining the power transmission function, which is a limitation.

This problem is solved by a compressor having the features according to claims 1 and 3.
The compressor according to the invention comprises a swash plate, in particular a ring-type swash plate, which is variable with respect to the inclination with respect to the drive shaft and is driven to rotate by the drive shaft and spaced from the drive shaft and rotates together. Articulated with two support elements. Each axial piston compressor has a joint configuration in a swash plate slide connection relationship. The power transmission element is a support element arranged at the outer radius of the power transmission element. The support element rotates with the drive shaft and is fixed to the drive shaft so as not to be displaced in the radial direction. The power transmission element is attached to the drive shaft so as to be rotatable at the center. By this means, undesired movements, in particular torsional moments, do not act on the power transmission element and the support element and do not increase degradation.

  In an embodiment of the compressor according to the invention, the support element and the power transmission element serve substantially only for the axial support of the piston or for the support of gas pressure, whereas the drive shaft and the swash plate The torque transmission between them is achieved by an independent mechanism. This mechanism is in particular a joint arrangement between the drive shaft and the swash plate. As a result of separating the mechanism that is useful for supporting the piston shaft and gas pressure from the mechanism dedicated to driving the swash plate and tilt ring, the mechanism that provides the gas pressure support is first slim and lightweight, It is possible to reduce the movement of the support element and the power transmission element, as described above, guaranteeing a reduction in the deterioration of the compressor according to the invention.

  A further solution to the problem of the invention is that the support element of the compressor according to the preamble of claim 1 is rounded so that its “corners” have a particularly different radius, with a substantially rectangular radial cross section, or Instead, it can be obtained if it is shaped like a compression or deformation circle or an ellipsoid, and vice versa, so that contact pressure and deformation in the area of the support element and the swashplate have an advantageous effect. Of course, combinations of the features of claims 1 and 3 are possible.

  These regions of the support element that contact the swash plate or tilt ring can be at least partially cylindrical or fuselage shaped. As a result of the cylindrical or torso profile, the swash plate is in almost line contact with the support element. It is pointed out that the contour of the support element can be molded and ground using a shaping machine, which is simple and as a result guarantees that the production is economical.

  In the case of a coolant compressor of the mode construction, or in the case of the coolant compressor described in the preamble of claim 1, two movements can be distinguished with respect to the inclination of the swash plate. These movements, on the one hand, are tilting movements (in the inclined plane) and on the other hand are torsional moments and act perpendicularly to said tilting movements. This torsional moment occurs especially because the highest gas pressure occurs when the valve is released and not at the top dead center of the piston. The resultant reaction power of all pistons will direct itself largely to the piston under the aforementioned conditions. In a preferred embodiment, the support for the torsional moment is provided in the drive shaft area, which is achieved in particular by means of an arrangement between a slide sleeve movably mounted on the drive shaft and a swash plate. . This type of arrangement can consist of one or more cylindrical pin-like element (s), or support or contact surfaces. At this point, it should be pointed out that the swash plate is pivotally attached to the slide sleeve and is axially movable along the drive shaft. As a result, as already mentioned, support is provided for the torsional moment acting in the region of the drive shaft. The power transmission element can further have a shoulder in the region of the drive shaft, at least on the peripheral part, and additionally or alternatively at the end remote from the support element. A fixing element can be provided that extends particularly in the axial direction. The shoulder in the region of the drive shaft ensures that the power transmission element has a fixed position with a simple structural arrangement in the drive shaft, and the fixing element ensures a fixed holding in the drive shaft. The swash plate is preferably connected to the slide sleeve and the drive shaft by means of a drive pin, especially when the power transmission element and the support element serve to support only the gas pressure. This ensures a reliable structurally simple drive for the swashplate, while at the same time having the effect of separating the drive from providing support for gas pressure. For fixed holding, the drive pin can be introduced into the slide sleeve or swash plate by crimping. In addition, the drive pin can project into a recess, in particular a groove, in the drive shaft, in which case further connection elements, in particular feather keys, can be arranged between the drive shaft and the slide sleeve, the connection element being a power source. Is attached to the drive shaft so as to be movable in the axial direction. This allows a relatively simple variant of the axial piston compressor according to the invention to be produced using only a few parts.

  Another structurally simple preferred embodiment of the compressor according to the invention is that the end of the power transmission element remote from the support element protrudes through the drive shaft and into the longitudinal slot of the slide sleeve. This is obtained when the drive torque is transmitted from the drive shaft to the slide sleeve by the end of the power transmission element remote from the support element.

  In a special embodiment, the structure of the support element causes the support element to be positioned in line contact with the swash plate in the recess of the swash plate, which also ensures optimal Hertzian stress and optimal power transmission. The height of the recess in the swash plate can be equal to the sum of the radius of curvature of the radially outer and inner contours, thereby ensuring an ideal curvilinear contour for the gas pressure support means.

  On one side of the swash plate that is more loaded by gas pressure, the wall thickness of the recessed area of the swash plate is preferably thicker than one side that is less loaded, but at the same time the clearance volume is Constant in angle. Normally, one side of the swash plate that is heavily loaded with gas pressure is the side facing the piston. This structural measure increases the stability of the swashplate, while at the same time savings the weight of the thinner wall thickness on the less loaded side.

  The drive shaft and the slide sleeve can have flat areas corresponding to each other, so that the slide sleeve is mounted on the drive shaft in a manner that ensures coupled rotation. This provides a simple structural means to ensure reliable driving of the slide sleeve. Furthermore, the swash plate can have at least one flat area corresponding to the flat area on the slide sleeve, which ensures a reliable relative position of the two components.

  In the following, further advantages and features of the present invention will be described by way of example and with reference to the accompanying drawings.

  A preferred embodiment of the compressor according to the present invention includes one housing, one cylinder block, and one cylinder head (not shown). The piston is mounted in the cylinder block and is movable in the axial direction back and forth. The driving force of the compressor is provided by the drive shaft 1 via the belt. The current compressor is a compressor having a variable piston stroke, and the piston stroke is controlled by a pressure difference determined by the gas pressure on the gas inlet side and the drive mechanism chamber. Depending on the degree of the pressure difference, the swash plate in the shape of the tilt ring 2 is deflected or inclined from the vertical position to a larger or smaller degree. The greater the resulting tilt angle, the greater the piston stroke and thus higher pressure outside the compressor.

  1, it can be seen that the swash plate mechanism of the first preferred embodiment of the compressor according to the present invention includes: a tilt ring 2, a slide sleeve 3 that is axially movable on the drive shaft, a spring 4, and a support. A gas pressure support means 5 constituted by an element 6, a power transmission element 7, a fixed element 8, and a drive pin 9 for transmitting torque between the drive shaft 1 and the tilt ring 2 are provided.

  The support element of the current first preferred embodiment is cylindrical or barrel shaped. The power transmission element is mounted in a corresponding recess 10 in the drive shaft so as to be rotatable about the longitudinal axis. As already indicated in terms, the gas pressure support means 6 only serves for axial support for the piston force, while the transmission of torque to the swash plate is effected by the drive pins 9.

  The slide sleeve 3 has two flat side surfaces 11 (only one flat side surface is visible in FIG. 1) and slides into and engages with a corresponding flat region 12 on the tilt ring 2. The power transmission element 7 has a shoulder 13 which determines its position in the drive shaft 1 (especially in the radial direction). On one side of the power transmission element 7 away from the support element 6, the fixing element 8 fixes the gas pressure support means 5 or the support element 6 and the power transmission element 7 in the drive shaft. In addition to the connection between the tilt ring 2 and the drive shaft 1 described above, the drive pin 9 also provides the connection between the slide sleeve 3 and the drive shaft 1 and the resulting power / torque transmission. The drive pin 9 protrudes into the recess of the drive portion of the drive shaft formed in the shape of the groove 14 (again, only one of the grooves is visible in FIG. 1). The drive pin 9 is introduced into the corresponding recess 16 of the tilt ring 2 by crimping.

  The spring 4 serves as a connecting element and is arranged between the drive shaft 1 and the slide sleeve 3 and transmits power in the axial direction. It is mounted such that it can move axially on the drive shaft 1. The end of the power transmission element 7 that is remote from the support element 6 passes through a longitudinal slot 17 formed in the slide sleeve 3 and projects to the drive shaft 1. In this case, it is possible to construct a slide sleeve as an alternative or in addition to power / torque transmission by the drive pin 9, whereby a longitudinal slot arranged opposite the longitudinal slot 17 is provided in the slide sleeve, It has to be pointed out that the end of the power transmission element 7 which is remote from the support element 6 protrudes into the slot and consequently transmits drive torque from the drive shaft 1 to the slide sleeve 3. In this connection, the following must be stated more simply: the drive shaft 1 and the slide sleeve 3 are connected to each other by means of the drive pin 9 and / or added to the torque transmission, or alternatively, flat areas corresponding to each other. This causes the slide sleeve to be mounted on a drive shaft for linked rotation (not shown in FIG. 1).

The arrangement shown in the exploded view of FIG. 1 is shown again in the longitudinal section of FIG. 2, but in addition to the known features according to FIG. 1, the tilt ring 2 is attached to a piston rod or a holder 18 connected to the piston. This can be clarified from FIG. A slide block 19 located between the tilt ring 2 and the holder 18 serves for attachment. In FIG. 2, the tilt ring 2 is at the minimum deflection position, and the tilt angle of the tilt ring is the lowest. In particular, this figure shows the cooperative operation of the shoulder 13 on the gas pressure support means 5 and the drive shaft 1.
Furthermore, the interaction between the power transmission element 7 and the fixed element 8 can also be seen.

  FIG. 3 (a) shows the appearance corresponding to FIG. 2, which is the longitudinal portion in the first preferred embodiment, in this case the maximum deflection angle of the tilt ring 2. FIG. FIG. 3 (b) further shows a transverse section through the tilt ring mechanism according to FIG. 3 (a). It should be pointed out again at this point that in the preferred embodiment, the drive torque is provided by the drive pin 9 (indicated by the arrow 25) and the gas pressure support means 5 and the support element 6 (in the arrows 23, 24). Not shown). This driving torque is indicated by an arrow 20 in FIG. Further, the tilt axis 21 of the tilt ring 2 can be seen in FIG.

  FIG. 4 (a) again provides a detailed view of the power transmission element 7 and the support element 6 meshing with the tilt ring 2. FIG. 4 (b) shows two longitudinal sections through the gas pressure support means 5 of the first preferred embodiment, which are rotated 90 ° relative to each other. This figure clearly shows that the support element 6 is cylindrical. Cylindrical or barrel profiles extend in a non-negligible direction relative to the tilt plane, so the torsional moment (perpendicular to the tilt ring tilting movement and maximum gas pressure occurs, especially during valve opening movements) That does not occur at the center of the dead center of the piston), that is, in the cylindrical support element 6, the power transmission element is attached to the drive shaft 1 and can be rotated about its central axis in the manner according to the invention Is a condition. For that reason, the mechanism according to the invention ensures that the torsional moment is only introduced into the element provided for that purpose, which is for example a drive pin 9 such as a spindle, or other suitable support. It can be a surface. The introduction of a torsional moment to the gas pressure support means 5 is excluded by the mechanism according to the invention.

  At this point, the benefits of the present invention are briefly described as follows: substantially, the gas pressure support means 5 where torque free is desired (the end of the power transmission element 7 away from the support element 6 is supported Accepting the support function of the tilt ring 2 with respect to the piston power acting in the axial direction (assuming that an arrangement with no torque transmission meshing is chosen at the end of the slide sleeve 3 away from the element 6; At least the head region of the support element 6 can be formed and can have a large area, but it is cylindrical or barrel-shaped and the gas pressure support means 6 can be directed around its central axis so that the torsional moment is introduced The drive movement is transmitted in a flat manner to the tilt ring tilt plane in a planar manner, but in that situation power and torque transmission It should be pointed out that there are a variety of ways. At this point, reference should again be made to FIGS. 4 (a) and 4 (b), in which a gas pressure support means 5 having a cylindrical support element 6 is shown. This support element 6 is engaged with the tilt ring 2. As a result of the fact that the power transmission element 7 of the gas pressure support means 5 is attached to the drive shaft 1 and can rotate about its own axis, a torsional moment (twist motion) cannot be transmitted substantially. As a result, limited transmission of the torsional moment is possible at other positions as described above, and the restriction of the mechanism is prevented. This also allows simple and quick assembly. An excessive determination of the torsional moment affecting the proposal for the cylindrical formation of the support element 6 of the gas pressure support means 5 is avoided as a result of the power transmission element 7 attached to the drive shaft 1 being able to rotate about its own axis. It becomes possible. The power in the direction of the recess 10 in the drive shaft 1 depends on the shoulder 13 of the gas pressure support means 5 and the fixed element 8 at the other end of the gas pressure support means 5 or the end of the power transmission element 7 away from the support element 6. Transmitted by the part. From FIG. 3 (a), and in particular FIG. 3 (b), the opening of the tilt ring 2 in which the support element 6 is engaged is formed so that the support element 6 cannot transmit any driving torque. I understand. As a result, as described above, the load on the gas pressure support means 5 is small, and the driving torque can be transmitted by a limited method and by another point (the driving pin 9 in the present embodiment).

  In the following, details of the transmission of the drive torque will be given: as already mentioned in the description of FIG. 1, the tilt ring 2 is connected to the slide sleeve 3 and also connected to the drive shaft 1 by drive pins 9. The slide sleeve 3 is attached so as to be movable in the axial direction on the drive shaft 1, and is attached to the drive pin 9 and the gas pressure support means 5 in cooperation with the spring 4 to adjust the tilt angle of the tilt ring 2. It is possible. The resulting tilt angle depends on the gas pressure, the inertial nature of the tilt ring 2 and the piston engaging the tilt link, and also the elasticity of the spring 4. In other words, the sum of the motions related to the tilt axis is equal to zero (tilt motion equals zero). The drive pin 9 is fixed in the axial direction in order to prevent the fall, but this is done by crimping the slide sleeve 3 or the pin in the tilt ring 2. In the present embodiment, transmission of drive torque from the drive shaft 1 to the tilt ring 2 is performed directly by the drive pin 9. Instead, an indirect drive torque transmission by the slide sleeve 3 is convenient. However, both cases have elements that connect to the shaft or project inside. (For example, drive pin 9). Of course, it is also convenient to have only one element. As a result, the axial orientation of the slide sleeve 3 is fixed by a sufficiently large recess in the slide sleeve, and the part of the gas pressure support means 5 or the part of the power transmission element 7 facing the support element 6 is attached to the slide sleeve. Guarantees that no movement can be transmitted. FIGS. 3A and 3B show an example of the drive pin 9 connected to the tilt ring 2 protruding from the groove portion 14 in the drive shaft 1. As a result, the drive torque is directly transmitted from the drive shaft 1 to the tilt ring 2 by the drive pin 9.

  Instead, indirect transmission of driving torque for power transfer by means of a slide sleeve is convenient. This is achieved by the following structural conditions: power and movement are transmitted in the axial direction, for example, a drive shaft 1 that allows axial movement of the bush by sliding a groove in the slide sleeve 3. And a connecting element between the slide sleeve 3. Such a connection element may be a feather key, for example. The end of the power transmission element 7 away from the support element 6 passes through the shaft and protrudes into a slot in the slide sleeve 3, in which the transmission element 7 is reliably guided, so that the drive torque is increased. Can communicate.

  The central point of the present invention is the formation of the gas pressure support means 5. In the context of the present invention, a gas pressure support means is provided which, on the one hand, does not transmit any drive torque, thus reducing the load and, on the other hand, optimizing for contact pressure due to the transmission of gas pressure.

  The recess 22 in the tilt ring 2 is formed so that the support element 6 is engaged inside the recess, but the gas pressure support means 5 and in particular the support element 6 are free in the axial direction and therefore do not transmit any drive torque. Is done. Furthermore, the gas pressure support means 5 and the support element 6 are formed so that the tilt of the tilt ring 2 is achieved by a rotation process on the support element 6. Ideally speaking, the height of the recess 22 for the support element 6 does not change. This simplifies the processing of the recess 22, but the height change of the recess 22 is theoretically possible.

  In view of the above detailed description, the support element 6 is optimally constructed in the following cases. That is, when it allows rotational movement with an appropriate curved contour and continues straight in the axial direction, ensuring line contact and low Hertzian stress.

  An example of the corresponding gas pressure support means 5, in particular the corresponding support element 6, is shown in FIGS. 4 (a) and 4 (b). In this example, the curved shape is a circle, so that the support element is cylindrical. Furthermore, the point to be referred to as the center point of the main circle or the center point of the circular shape of the cylinder coincides with the center point of the piston joint, which leads to a constant clearance volume of the compressor according to the invention. The following relationship also applies to FIG. 4 (a): the wall thickness of the tilt ring or the walls S2 and S3 surrounding the recess 22 are equal (S2 = S3), and the radial outer contour (R1) and the inner The radius of curvature R1 and R2 of the contour (R2) is also equal due to the cylindrical shape of the support element 6 (R1 = R2). It is further true that the height S1 or the width of the recess 22 is equal to the sum of the two radii of curvature R1 and R2 (S1 = R1 + R2). Furthermore, this sum is constant. The center points of R1, R2 and R, where R denotes the radius of the slide block 19, which are identical and guarantee a constant clearance volume.

  However, in principle, the curved contour of the gas pressure support means can be freely selected according to the following preconditions: For each inclination angle, the height S1 of the recess is the radius of curvature of the radiation outer contour R1 and the radiation inner contour R2. Must be equal to the sum of A simple example of a contour rotating in the concave portion 22 of the same height S1 is shown in FIGS.

  FIG. 5 (second preferred embodiment of the compressor according to the invention) shows a recess 22 on the side that is heavily loaded by the gas pressure (side facing the piston) by choosing different radii while keeping the clearance volume constant. It shows how the wall thickness of the tilt ring 2 in the region can be increased. For the arrangement according to FIG. 5, the following relationship applies: S2> S3, R1 <R2, S1 = R1 + R2 = constant (in the tilt region), which results in a constant clearance volume.

  A third preferred embodiment is shown in FIG. 6, which shows an example of a size (S2 = S3) in which the wall thickness of the tilt ring 2 remaining in the region of the recess 22 is equal. In this example, the main load resulting from the compressive force acts on the line contact between the tilt ring 2 and a partly cylindrical surface formed with a radius R1. The condition R1> R2 provides the benefit of less contact pressure in the main load direction. At this point, however, the following must be pointed out. That is, in this embodiment, it does not coincide with the center point of the joint configuration (center points of the radii R1 and R2) in the tilt ring 2, and it is indicated by the spacing S4 not equal to zero. This means that the clearance volume is not constant. In summary, the following relationship applies to FIG. 6: S3 = S2, R1> R2 (this leads to a decrease in contact pressure) S1 = R1 + R2 = constant (in the region of slope), the clearance volume is not constant.

  In addition to designing the gas pressure support means 5 with respect to contact pressure, the present invention also simplifies the assembly of parts and their processability, as already mentioned above. As already mentioned above, the gas pressure support means 5, and in particular the power transmission element 7, are not fixedly connected to the drive shaft 1, but rather are attached in a rotatable manner. The direction of the tilt axis is determined in advance by the drive pin 9, the flat region 11 on the slide sleeve 3, and the flat region 12 on the tilt ring (this case is compared with FIGS. 7A and 7B). . The gas pressure support means 5 having a fixed crimp on the drive shaft 1 will also predetermine the orientation of the tilt axis, and therefore at least an excess that can make assembly of the mechanism and trouble-free tilt difficult. A decision may occur. Such an arrangement is only possible with extremely precise play adjustments and extremely precise assembly, which would result in a considerable increase in processing and assembly costs. As a result of the rotatable mounting of the power transmission element 7 and the gas pressure support means 5 in the drive shaft 1, the present invention avoids over-determination and facilitates assembly.

  The last to be stated as a substantial benefit of the rotation possibility of the gas pressure support means 5 is a situation in which it is not possible to receive a movement that acts on the axis of rotation. Thereby, the power as a result of the torsional moment is not accepted by the gas pressure support means 5 (this case is compared with FIGS. 7A and 7B). The flat 12 of the tilt ring 2 and the flat region 11 of the slide sleeve 3 are more substantially suitable for receiving power as a result of torsional moments depending on the conditions of the laver arm. As shown in FIGS. 7A and 7B, power is transferred from the flat region of the tilt ring to the drive shaft 1 via the slide sleeve 3. Further, the torsion moment axis 26 and the resulting compression force application point 27 are also shown in FIGS. 7 (a) and 7 (b).

  Although the present invention has been described using an embodiment in which features are fixedly combined, this is further described in more detail by the appended claims, although not fully described in the appended claims. It includes a typical combination. All features disclosed in the present application are claimed as important to the present invention, as long as it is novel in itself or in combination with existing technology.

FIG. 1 is an exploded view showing a swash plate mechanism of a first preferred embodiment of a compressor according to the present invention. FIG. 2 is a longitudinal sectional view showing an embodiment at the minimum inclination angle of the swash plate of FIG. 3 (a) and 3 (b) are a longitudinal sectional view (a) and a transverse sectional view (b) showing an embodiment at the maximum inclination angle of the swash plate mechanism according to FIG. 4 (a) and 4 (b) are a longitudinal sectional view (a) showing details of the gas pressure supporting means in the present invention and a longitudinal sectional view (b) showing an outline view of the gas pressure supporting means. FIG. 5 is a longitudinal sectional view showing a second preferred embodiment of the gas pressure support means of the compressor according to the present invention. FIG. 6 is also a longitudinal sectional view showing a third preferred embodiment of the gas pressure support means of the compressor according to the present invention, and 7 (a) and 7 (b) are a transverse sectional view (a) and a longitudinal sectional view (b) showing the swash plate mechanism of the first preferred embodiment.

Claims (16)

It is an axial piston compressor, the inclination with respect to the drive shaft (1) is variable, is rotationally driven by the drive shaft (1), and is arranged at a distance from the drive shaft (1) and rotates together with the drive shaft. A ring-shaped swash plate (2) articulated and at least one support element (6), and a piston having a connecting portion slidingly engaged with the swash plate (2). 6) is an axial piston compressor disposed at the tip of the power transmission element (7) fixed to the drive shaft so as not to be displaced in the radial direction,
The axial piston compressor, wherein the power transmission element (7) is attached to the drive shaft (1) so as to be rotatable about a longitudinal axis.   The support element (6) and the power transmission element (7) serve substantially only for the axial support of the piston or for the support of gas forces, but in an independent configuration, in particular with the drive shaft (1) 2. Compressor according to claim 1, characterized in that the articulated connection with the swash plate (2) serves substantially only for torque transmission.   Said support element (6) has a substantially rectangular basic shape in the radial cross section, its corners being very rounded, compressed, circular or deformed, in particular with different radii The compressor according to claim 1, wherein the compressor has a shape of a circle or an ellipse.   Compressor according to any one of claims 1 to 3, characterized in that the region of the support element (6) in contact with the swash plate (2) is at least partially cylindrical or barrel-shaped. . The swash plate (2) is pivotally mounted on a slide sleeve (3) mounted so as to be movable in the axial direction along the drive shaft (1),
Between the slide sleeve (3) and the swash plate (2) at least one cylindrical pin-like element or support for providing support for torsional moments occurring in the region of the drive shaft (1) The compressor according to claim 1, wherein a contact surface is provided.   The power transmission element (7) has one shoulder (13) in the region of the drive shaft (1) and / or one end away from the support element (6) at least at the outer periphery thereof. The compressor according to claim 1, further comprising a fixing element (8), in particular extending in the axial direction.   The swash plate (2) is connected to the slide sleeve (3) and / or the drive shaft (1) by a drive pin (9). compressor.   The compressor according to claim 7, wherein the drive pin (9) is introduced into the slide sleeve (3) or the swash plate (2) by pressure bonding.   9. Compressor according to claim 7 or 8, characterized in that the drive pin (9) projects into a recess (22) in the drive shaft, in particular a groove (14), in the drive shaft (1).   A connecting element, in particular a feather key, is arranged between the drive shaft (1) and the slide sleeve (3), which connects the transmission of radial power and moment and also on the drive shaft (1). The compressor according to claim 1, wherein the compressor is attached so as to be movable in an axial direction.   The end of the power transmission element (7) that is remote from the support element (6) has a drive torque that is remote from the support element (6) from the drive shaft (1). Projecting through the drive shaft (1) and projecting into the vertical slot (17) of the slide sleeve (3) so as to be transmitted into the slide sleeve (3) through the end of The compressor according to any one of claims 1 to 10.   12. The support element (6) is constructed so as to be located inside a recess (22) of the swash plate (2) and is in line contact with the swash plate. The compressor in any one of.   The height (S1) of the recess (22) of the swash plate (2) is equal to the sum of the radius of curvature (R1) of the radially outer contour and the radius of curvature (R2) of the radially inner contour. The compressor according to any one of claims 1 to 12. On the swash plate (2) side facing the piston, the wall thickness (S2) of the region of the recess (22) in the swash plate (2) is larger than the thickness on the side away from the piston (S2). > S3), on the other hand, the clearance volume is constant for all angles of the swash plate (2). The drive shaft (1) and the slide sleeve (3) have flat areas corresponding to each other, so that the slide sleeve (3) is mounted on the drive shaft (1) so as to ensure connection rotation. The compressor according to any one of claims 1 to 14, wherein the compressor is provided. 16. The swash plate (2) has at least one flat region (12) corresponding to a flat region (11) on the slide sleeve (3). The compressor described.

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