CN101990593A - rotary piston compressor - Google Patents

Abstract

The invention relates to a rotary piston compressor, comprising a housing (12), wherein at least one first piston (22) is provided, which can be pivoted about a rotational axis (30) fixed to the housing and, during pivoting about the rotational axis (30), executes a reciprocating movement between an end position close to the rotational axis and an end position remote from the rotational axis in order to periodically enlarge and reduce a working chamber (34) defined on an end face (38) of the piston (22) facing the rotational axis (30), the rotational axis (30) extending through the working chamber (34), the piston (22) having a control mechanism (70) which, during pivoting of the piston (22) about the rotational axis (30), runs along a control cam (66) fixed to the housing in order to guide the reciprocating movement of the piston (22) out of the pivoting movement, and the piston (22) being arranged in a receiving device of the piston holder (50), the piston (22) being connected to the piston holder in a rotationally fixed manner relative to the rotational axis (30) and the piston holder being connected to the piston holder in a rotationally fixed manner to the rotational axis (30 (22) Rotate together about the axis of rotation (30). The piston (22) has, in addition to the actuating mechanism (70), an auxiliary operating mechanism (88) on the side facing outward in the direction of the centrifugal force relative to the rotational axis (30), the running surface (108) of which rolls along the inner side of the piston cage (50) during the reciprocating movement of the piston (22), the direction of movement of the auxiliary operating mechanism (88) and the rotational axis (30) lying in a common plane.

Description

rotary piston compressor

technical field

The invention relates to a rotary piston compressor with a housing, in which at least one first piston is arranged, which is rotatable about a shaft fixed to the housing and which, when swiveling about the shaft, is in an end position close to the shaft A reciprocating movement is carried out between an end position away from and away from the rotating shaft, in order to periodically enlarge and reduce the working chamber defined by the end face of the piston facing the rotating shaft, wherein the rotating shaft extends through the working chamber, and the piston has a control operating mechanism, which When the piston rotates around the rotating shaft, it runs along the control cam fixed to the housing, which is used to derive the reciprocating motion of the piston from the rotating motion, and the piston is arranged in the receiving device of the piston cage, and the piston and the piston cage resist with respect to the rotating shaft. Torsionally connected, the piston cage rotates around the shaft together with the piston.

Background technique

Such a rotary piston compressor is known from DE 10 2006 009 197 A1.

The rotary piston compressor according to the invention can be used as an internal combustion engine (internal combustion engine), pump or compressor. The rotary piston compressor according to the invention is preferably used as an internal combustion engine and is described in this description as an internal combustion engine.

In the case of using such a rotary piston compressor as an internal combustion engine, the intake, compression, expansion of the fuel-air-mixture and the combustion of the fuel-air- Single working stage for the discharge of the mixture.

The rotary piston compressors known from the documents mentioned at the outset have a total of four pistons in their housing. The four pistons are each arranged in the respective receptacle in a piston holder, wherein the piston holder rotates together with the pistons about a rotational axis fixed to the housing. Between the respective end faces of the two facing pistons facing the rotational axis there is in each case a working chamber which is arranged centrally with respect to the rotational axis. Known rotary piston compressors accordingly have two working chambers, which are located on the shaft.

Both in the known rotary piston compressor and in the rotary piston compressor according to the invention, the rotational axis is understood to be a geometric axis.

Every two pistons with the working chamber between them form a piston pair. The pistons of the piston pair are implemented between an end position of the piston close to the axis of rotation (also referred to as upper dead center (OT)) and an end position remote from the axis of rotation (also referred to as lower dead center (UT)) of the piston during rotation about the axis of rotation reciprocating motion in opposite directions. The volume of the working chamber between the pistons is at a minimum in the OT position of the pistons of the piston pair and is at a maximum in the UT position of the pistons of the piston pair.

In order to derive the reciprocating movement of the piston from the pivoting movement of the piston about the axis of rotation, each piston has a control actuator on its rear side, ie on its side facing away from the associated working chamber. In addition, the control operation of the pistons of the same piston pair runs along a control cam of the cam mechanism fixed to the housing, which extends on all sides around the axis of rotation and has a corresponding Export its reciprocating motion.

In the known rotary piston compressors, each piston is also provided with a return mechanism in order to guide the piston from the OT position back into the UT position at higher rotational speeds. The respective return mechanism of each piston runs in a control cam adjacent to the control cam for controlling the operating mechanism, the two control cams extending substantially parallel to one another.

The control actuator of each piston is designed as a pulley, the axis of rotation of which forms a variable intercept point with the axis of rotation during the rotation of the piston, wherein the axis of rotation here can also be understood as a geometric axis.

The disadvantage of known rotary piston compressors at higher rotational speeds is that, during the movement of the piston from an end position close to the axis of rotation to an end position remote from the axis of rotation, the piston not only contacts the control cam with its respective operating mechanism, but also with its The piston body segments contact the cam mechanism, thereby creating sliding friction between the piston body segments and the cam mechanism. Sliding friction also occurs between the piston and the receptacle of the piston cage. The greater this sliding friction, the higher the speed of rotation of the piston around the axis of rotation, since the radial centrifugal force acting on the piston, which increases with increasing speed, gradually and strongly compresses the previously described segments of the piston body. Press against the cam mechanism.

Neither the running mechanism of the piston itself nor the additionally provided return mechanism of known rotary piston compressors can prevent the sliding friction of the raised plane caused by centrifugal force. The increased rotational speed results in a loss of power and increased wear in known rotary piston compressors.

Contents of the invention

It is therefore the object of the present invention to improve a rotary piston compressor of the type mentioned at the outset in such a way that power losses and wear due to centrifugal force-induced sliding friction of the pistons are avoided or at least reduced.

)，其中辅助运行机构的运动方向和转轴位于同一平面内。According to the invention, this object is achieved in view of the rotary piston compressor mentioned at the beginning of the article in that the piston, in addition to the control operating mechanism, has an auxiliary operating mechanism on the outward side (fliehkraftseitig) in the direction of centrifugal force with respect to the rotating shaft, the operating surface of which is When the piston reciprocates, it rolls along the inner surface of the piston cage (

), where the direction of motion of the auxiliary running mechanism and the axis of rotation are in the same plane.

Therefore, in the rotary piston compressor according to the invention, at least one piston not only has a control actuator for deriving the reciprocating motion of the piston from the rotary motion of the piston about the axis of rotation, but also additionally has an auxiliary actuator, which is not used for control. The reciprocating motion of the piston is controlled by the support on the inner side of the piston cage of the roller bearing on the outward side of the centrifugal force direction. In this way, the total movement path of the piston from an end position close to the rotational axis to an end position remote from the rotational axis is no longer subject to sliding friction, but only rolling friction. Rolling friction is significantly lower than flat friction and thus leads to significantly reduced power losses and wear in rotary piston compressors.

The auxiliary actuator is arranged on the piston in such a way that the direction of movement of the auxiliary actuator and the axis of rotation about which the piston pivots in the housing lie in a common plane. This ensures that the piston is always supported on the piston cage by means of the auxiliary running mechanism towards the outside in the direction of the centrifugal force. Since the piston cage rotates with the piston about the axis of rotation, no friction perpendicular to the running path of the auxiliary running gear occurs between the auxiliary running gear and the inner side of the piston cage on which the auxiliary running gear rolls.

In a preferred configuration, the auxiliary running mechanism is designed as a pulley, the axis of rotation of which is oriented perpendicularly to the axis of rotation of the pivoting movement of the piston.

The auxiliary running mechanism can also be designed in the form of a spherical part, which can be freely rotatably supported in ball bearings in all spatial directions on the back of the piston, and the advantage of designing the auxiliary running mechanism as a pulley is that if the auxiliary running mechanism If the axis of rotation of the piston is directed perpendicularly to the axis of rotation of the rotary motion of the piston, the rolling of the auxiliary running mechanism on the inner side of the piston cage is well defined and, as in the case of a ball that does not rotate about a defined axis of rotation, is avoided The sliding effect that increases friction.

In a further preferred embodiment, the control actuator is designed as a pulley whose axis of rotation is at the same point inside the housing as the axis of rotation in each position of the piston between the end positions close to the axis of rotation and the end positions remote from the axis of rotation. intersect.

This measure is a further improvement over known rotary piston compressors. Although the control actuator is likewise designed as a pulley in the known rotary piston compressors, the orientation of the axis of rotation of the pulley in the known rotary piston compressors depends on the end position of the piston between the end positions close to the rotary axis and remote from the rotary axis. position changes. In known rotary piston compressors, the pulley of the control actuator is acted upon by a force directed obliquely to its axis of rotation, which stresses the pulley bearing of the pulley excessively and in unfavorable cases even locks up.

Detrimental effects are avoided in the aforementioned design of the rotary piston compressor according to the invention, in which the axis of rotation of the pulley is preferably directed radially towards the housing in each position of the piston between the end positions close to and remote from the shaft center point.

In another preferred refinement, the pulley of the auxiliary drive is arranged in a bearing in the pulley of the control drive, wherein the axes of rotation of the pulley of the auxiliary drive and the pulley of the control drive are arranged perpendicular to each other.

The advantage of this measure lies in the particularly space-saving configuration of the auxiliary and control actuators on the piston. Furthermore, the bearings of the pulleys of the control gear are designed accordingly as hollow bodies, which accommodate the pulleys of the auxiliary gears, wherein only the outer circumference of the pulleys of the auxiliary gears protrudes, which are used for rolling along the inner side of the piston cage. the running surface.

In another preferred configuration, the reciprocating movement of the piston is a pivoting movement about a pivot axis perpendicular to the rotating shaft, and the contact line of the running surface of the control operating mechanism and the control cam is oriented in each position of the piston between the pivot axis and the rotating shaft. at the point of intersection.

In this configuration, the design of the piston as a swivel piston advantageously ensures that the running surface of the control actuator lies in the normal direction of the control cam in each position of the piston and thus prevents the auxiliary actuator from moving along the control cam. inclined operation. This results in a perfect parallelism of the direction of travel of the control actuator relative to the control cam.

In a further preferred embodiment, the piston cage has a narrow shoulder, viewed in the direction of the circumference around the axis of rotation, for the auxiliary running mechanism of the piston, and an elongated shoulder in the direction of the axis of rotation. The auxiliary running gear extends in the direction away from the end position of the rotational axis.

The advantage here is not only that the auxiliary running mechanism is always only in contact with the inner side of the piston cage and not with the cam mechanism on which the control cam is designed, but also because The configuration of the narrow and thus limited shoulder is also not worth mentioning for the increased weight of the piston cage.

In a further preferred embodiment, guides for the sides of the auxiliary running gear are formed on the inner side of the piston cage along which the auxiliary running gear runs.

The advantage of this measure is that tilting of the piston perpendicular to the running path of the auxiliary running gear, or in other words in the direction of its pivoting about the axis of rotation, can be prevented better.

Further advantages and features emerge from the following description and the drawings.

It goes without saying that the features mentioned above and those still to be explained below can be used not only in the respectively stated combination but also in other combinations or on their own without departing from the scope of the present invention.

Description of drawings

Embodiments of the present invention are shown and described in detail below with reference to the accompanying drawings. in:

Fig. 1 is a longitudinal sectional perspective view of a rotary piston compressor along a plane containing a rotating shaft;

Fig. 2 is an enlarged longitudinal sectional view similar to Fig. 1 relative to the portion of the rotary piston compressor in Fig. 1 related to the piston, the piston cage and the cam mechanism;

Figure 3 is a view similar to Figure 2, wherein the piston is not shown in cross section;

FIG. 4 is a view similar to FIG. 2 of the structural arrangement of the piston, the piston cage and the cam mechanism, wherein the piston is shown in another end position relative to FIGS. 2 and 3 ;

Figure 5a) and b) are a single piston of the rotary piston compressor in Figure 1, wherein Figure 5a) shows a perspective view of the piston and Figure 5b shows a longitudinal mid-section view of the piston;

Figure 6 is a perspective view of the structural arrangement of the piston together with the cam mechanism with the control cam, wherein the cam mechanism is shown in longitudinal mid-section;

Fig. 7 is a three-dimensional longitudinal mid-sectional view of the cam mechanism in a separate state;

Fig. 8 is a perspective view of the piston cage in a separate state;

Figure 9 is a longitudinal mid-section view of the piston cage in Figure 8; and

Figure 10 a) and b) are two sectional views of a cut-away part of the piston cage in the area of the shoulder of the piston cage of the auxiliary running mechanism for guiding either piston, wherein Figure 10 a) shows the absence of the piston and Fig. 10b) show the cutaway with the piston.

Detailed ways

In FIG. 1 there is shown a rotary piston compressor generally designated 10 . Further details of the rotary piston compressor 10 are shown in FIGS. 2 to 10 .

The rotary piston compressor 10 can generally be designed as an internal combustion engine, but also, with corresponding modifications, as a pump or compressor.

The rotary piston compressor 10 has a housing 12 with a spherically designed middle part 14 and end covers 16 and 18 . The housing 12 has a spherically symmetrical interior 20 .

According to FIGS. 1 to 3 , a total of four pistons 22 , 24 , 26 and 28 are arranged in housing 12 , wherein piston 28 is located in front of the plane of the illustration in the illustrations of FIGS. visible in the stereoscopic view of .

During operation of the rotary piston compressor 10 , the pistons 22 , 24 , 26 and 28 jointly rotate in the housing 12 about a rotational axis 30 fixed to the housing. The axis of rotation 30 is here understood to be a geometric axis. The direction of rotation of pistons 22 , 24 , 26 and 28 about rotational axis 30 is indicated by arrow 32 in FIG. 1 . The rotating shaft 30 passes through the spherical center point of the inner cavity 20 of the housing 12 .

The shaft 30 is fixed to the housing, which is understood in such a way that the position of the shaft 30 remains constant during the rotation of the pistons 22 , 24 , 26 and 28 .

Of the pistons 22 , 24 , 26 and 28 , the pistons 22 and 24 form a first piston pair and the pistons 26 and 28 form a second piston pair. The pair of pistons formed by pistons 26 and 28 is offset by 90° relative to the axis of rotation 30 relative to the pair of pistons 22 and 24 around the axis of rotation 30 , as can also be seen in particular from FIG. 6 , in which four A perspective view of the structural arrangement of the piston.

Each pair of pistons defines a working chamber, ie pistons 22 and 24 define a working chamber 34 and pistons 26 and 28 define a working chamber 36 (see FIG. 2 ). The rotational axis 30 , which is understood to be a geometrical axis, always passes through the working chambers 34 and 36 independently of the rotational position of the pistons 22 , 24 , 26 and 28 about the rotational axis 30 .

The working chamber 34 is delimited by the end faces 38 and 40 of the pistons 22 and 24 facing the rotary shaft 30 . The working chamber 36 is delimited accordingly by an end face 42 (of the piston 26 ) and an end face 44 (of the piston 28 ) facing the shaft 30 (see FIG. 4 ).

The individual working stages of intake of the fuel-air mixture, compression of the mixture, ignition of the mixture, impingement of the ignited mixture and discharge of the burned mixture take place in the working chambers 34 and 36 . For this purpose the working chambers 34 and 36 are enlarged and reduced periodically, ie in the exemplary embodiment shown the working chambers 34 and 36 are enlarged and reduced in the same direction as one another. However, the aforementioned single working stages in the two working chambers 34 and 36 differ by two stage phases, i.e., the working stage of the compression of the fuel-air-mixture in the working chamber 34, while the combustion process is carried out in the working chamber 36 The working phase of the discharge of the fuel-air-mixture, and so on.

In order for the working chambers 34 and 36 to periodically become larger and smaller during the revolutions of the pistons 22, 24 and 28, the pistons 22, 24, 26 and 28 are implemented during their revolutions around the axis of rotation 30 as illustrated in FIGS. 1 to 3. The reciprocating movement between the end position close to the axis of rotation and the end position away from the axis of rotation, such as shown in FIG. 4 . The end positions of pistons 22 , 24 , 26 and 28 close to the rotational axis according to FIGS. 1 to 3 are also referred to as upper dead center (OT) and the end positions remote from the rotational axis according to FIG. 4 as lower dead center (UT).

The reciprocating motion of the pistons 22, 24, 26 and 28 is an oscillating motion in the illustrated embodiment. Pistons 22 , 24 execute a pivoting movement about pivot axis 46 when pivoting about pivot axis 30 , which intersects the pivot axis approximately perpendicularly at the spherical center point of interior 20 of housing 12 . Pistons 26 and 28 correspondingly carry out a pivoting movement about pivot axis 48 (see FIG. 2 ), which intersects axis of rotation 30 perpendicularly at approximately the spherical center point of interior 20 of housing 12 and is also perpendicular to the pivot axis. 46 extensions.

Before describing the control mechanism by which the reciprocating motion of the pistons 22, 24, 26 and 28 is derived from the rotary motion of the pistons 22, 24, 26 and 28 about the axis of rotation 30, reference is first made to FIGS. The piston cage 50 (FIG. 8) in which the pistons 22, 24, 26 and 28 are housed is described in detail. Piston cage 50 is a rotor that rotates about rotational axis 30 together with pistons 22 , 24 , 26 and 28 . Pistons 22 , 24 , 26 , and 28 are correspondingly connected in a rotationally fixed manner to piston cage 50 relative to rotational axis 30 , but can carry out their pivoting movements relative to the piston cage.

According to FIGS. 8 and 9 , the piston cage 50 is joined in the direction of the rotation axis 30 by two halves 52 and 54 which are detachably connected to each other along a joint line 56 , such as the halves of the piston cage 50 52 and 54 are fixedly connected to each other by means of bolts. According to FIG. 4 , half 52 of piston holder 50 has a cylindrical or slightly curved bore 58 for receiving pistons 22 and 24 . Pistons 22 and 24 carry out reciprocating motions in opposite directions in bore 58 , wherein pistons 22 and 24 , which are substantially circular in cross section, are introduced slidingly into bore 58 . The walls of the bore 58 between the end faces 38 and 40 of the pistons 22 and 24 correspondingly form the circumferential delimitation of the working chamber 34 . Since the pistons 22 and 24 carry out a pivoting movement in the bore 58 , the pistons 22 and 24 are not designed cylindrically but in the shape of an elbow.

According to FIG. 2 , a cylindrical bore 60 is formed in the second half 54 of the piston holder 50 , in which bore the pistons 26 and 28 are accommodated. The cylindrical bores 58 and 60 of the piston holder 50 correspond to the structural arrangement of the pistons 22 , 24 , 26 and 28 as described above, offset relative to one another by 90° with respect to the rotational axis 30 . Pistons 26 and 28 are also designed like pistons 22 and 24 as elbows with a circular cross section. However, other cross sections (eg ellipsoidal) are also conceivable.

According to FIG. 1 , the piston cage 50 is mounted in the housing 12 so as to be rotatable about the rotational axis 30 .

The control mechanism with which the reciprocating movement of the pistons 22 , 24 , 26 and 28 is derived from the pivoting movement of these pistons about the axis of rotation 30 begins below.

For this purpose, according to FIG. 1 , a control cam 62 is arranged in the housing 12 fixed thereto. Fixed with the housing here means that the control cam 62 itself does not participate in the rotation around the rotating shaft 30, but the concept of "fixed with the housing" also includes this situation, that is, the position of the control cam 62 can be adjusted, for example, in order to move closer to the rotating shaft The strokes of the pistons 22, 24, 26 and 28 are adjusted between the end positions of the end position and the end position away from the axis of rotation.

FIG. 7 shows a longitudinal mid-sectional perspective view of the control cam 62 in a plane perpendicular to the rotational axis 30 . The control cam 62 has a mounting ring 64 formed on all sides around the rotational axis 30 , via which mounting ring the control cam 62 is mounted in the housing 12 . The cam mechanism 62 has (preferably integrally formed on the mounting ring 64 ) a control cam 66 assigned to the pistons 22 and 24 and a control cam 68 assigned to the pistons 26 and 28 (see FIGS. 2 and 4 ).

The control cams 66 and 68 likewise extend on all sides around the axis of rotation 30 and have a profile with peaks and valleys relative to the axis of rotation 30 for deriving the motion of the pistons 22 , 24 , 26 and 28 from their rotary motion around the axis of rotation 30 . reciprocating motion.

Furthermore, the control cams 66 and 68 are arranged point-symmetrically with respect to the spherical center of the interior 20 of the housing 12 and are thus substantially perpendicular to the rotational axis 30 .

Each piston 22 , 24 , 26 and 28 has a control travel mechanism which travels along the control cam 66 or 68 as each piston 22 , 24 , 26 and 28 revolves around the axis of rotation 30 .

It can be seen, for example, in FIG. 2 that piston 22 has a control actuator 70 and piston 24 has a control actuator 72 , and according to FIG. 4 piston 26 has a control actuator 74 and piston 28 has a control actuator 76 .

The design of the control actuators 70 , 72 , 74 , 76 is identical to one another, so only the design of the control actuator 70 of the piston 22 will be described below.

The piston 22 is shown in a separate state in FIGS. 5 a ) and b ), see also FIG. 2 .

The control actuator 70 is designed as a pulley 78 , which is mounted rotatably about an axis of rotation 80 . Furthermore, the pulley 78 is mounted on a bearing housing 82 which is fixed in rotation relative to the axis of rotation 80 and is thus connected to the piston 22 . The control actuator 70 is located on the rear side of the piston 22 facing away from the end face 38 , which faces the working chamber 34 in the mounted state of the piston 22 . The pulley 78 has a running surface 84 which, according to FIG. 2 , extends along the control cam 66 of the control mechanism 62 . The pulley 78 rotates about the axis of rotation 80 when the running surface 84 runs along. As can be seen from FIG. 2 , the axis of rotation 80 is aligned radially with respect to the spherical center point of the inner chamber 20 of the housing 12 and in particular aligned or aligned with the pivot axis 46 around which the piston 22 pivots. The swing axes intersect. The axis of rotation 80 always intersects the axis of rotation 30 at the same point on the axis of rotation 30 irrespective of the position of the piston 22 with respect to the pivot axis 46 .

The running surface 84 is conical and is also aligned such that the contact line 86 ( FIG. 2 ) of the running surface 84 of the pulley 78 and the control cam 66 is aligned with the intersection of the pivot axis 46 and the rotation shaft 30 at any position of the piston, That is, align with the spherical center point of the inner cavity 20 of the housing 12 . This ensures that no tilting movement occurs between the pulley 78 and the control cam 66 , so that no tilting forces act on the pulley 78 either.

But pistons 22, 24, 26 and 28 not only have a control operating mechanism respectively (its function is to derive the reciprocating motion of these pistons from the rotary motion of pistons 22, 24, 26 and 28 around the shaft), in addition to each control operating mechanism , also has an auxiliary running mechanism, which will be described in detail below.

According to FIG. 2 the piston 22 has an auxiliary actuator 88 and the piston 24 has an auxiliary actuator 90 , and according to FIG. 4 the piston 26 has an auxiliary actuator 92 and the piston 28 has an auxiliary actuator 94 .

Since the auxiliary actuators 88 , 90 , 92 and 94 are designed identically to one another, only the auxiliary actuator 88 of the piston 22 will be described in detail below with reference to FIGS. 2 and 5 . The auxiliary running gear 88 is designed as a pulley 96 whose axis of rotation 98 according to FIG. 2 is oriented perpendicular to the axis of rotation 30 , but does not intersect it. Furthermore, the axis of rotation 98 is oriented perpendicularly to the axis of rotation 80 of the pulley 78 of the control carriage 70 . Furthermore, the pulley 96 of the auxiliary drive 88 is mounted, for example via a needle bearing, in the bearing housing 82 of the pulley 78 of the control drive 70 .

The auxiliary operating mechanism 88 and the auxiliary operating mechanisms 92, 92 and 94 of the other pistons 24, 26 and 28 are used to support the piston 22 and the pistons 24, 26 and 28 on the outward side in the direction of centrifugal force, wherein on the inner side.

According to FIGS. 8 and 9 , roof-shaped shoulders 100 (for auxiliary running gear 88 ), 102 (for auxiliary running gear 90 ) are provided on piston cage 50 for each auxiliary running gear 88 , 90 , 92 and 94 . ) and 106 (for auxiliary running mechanism 94). A corresponding roof-shaped shoulder 104 for the auxiliary running gear 92 can be seen in FIG. 4 . The shoulders 100, 102, 104 and 106 are designed to be narrow when viewed in the circumferential direction around the axis of rotation 30 and are elongated when viewed in the direction of the axis of rotation 30, wherein the shoulders 100, 102, 104, and 106 are formed towards the respective pistons. 22 , 24 , 26 and 28 extend in a direction away from the end position of the rotational axis. In particular, FIG. 4 shows corresponding shoulders 104 for the auxiliary running mechanism 92 of the piston 26 and shoulders 106 for the auxiliary running mechanism 94 of the piston 28 . FIG. 4 shows the pistons 26 and 28 in their end positions remote from the axis of rotation, in which the working chamber 36 has a maximum volume.

Furthermore, the auxiliary running gears 88 , 90 , 92 and 94 are rolled on the inner sides of the respective shoulders 100 , 102 , 104 and 106 , wherein the running paths of the respective running auxiliary gears 88 , 90 , 92 and 94 thus described In other words, its reciprocating running direction is in common parallel with the rotation axis 30 , as can be seen, for example, from FIGS. 2 and 4 . In FIG. 2 the current directions of movement of the auxiliary running gears 88 and 90 lie in the plane of the illustration, and in FIG. 4 the directions of movement of the auxiliary running gears 92 and 94 lie in the plane of the drawing. Due to the rotationally fixed connection of the pistons 22 , 24 , 26 and 28 to the piston cage 50 , the auxiliary running mechanisms 88 , 90 , 92 and 94 are implemented relative to the piston cage 50 only on the rollers on the piston cage 50 parallel to the axis of rotation 30 . pressure movement.

Since the pistons 22 , 24 , 26 and 28 are connected to the piston holder 50 in a rotationally fixed manner relative to the rotational axis 30 , this already ensures that tilting relative to the rotational axis 30 is prevented. In order to further increase the stability against tipping, lateral barrel-shaped guides are designed on the inner sides of the roof-shaped shoulders 100, 102, 104 and 106, and the respective auxiliary running mechanisms 88, 90, 92 and 94 are supported laterally. on the guide. 10 a) and b) show a shoulder 100 for a roof shape and an auxiliary running mechanism 88, the running surface 108 of which is rolled on the inner side of the shoulder 100 and passes laterally through the corresponding vat-shaped The protrusions 112 and 114 guide.

Auxiliary operating mechanisms 88, 90, 92 and 94 together with corresponding shoulders 100, 102, 104 and 106 of piston cage 50 prevent pistons 22, 24, 26 and 28 from resting on piston cage 50 to a large extent. friction and avoids sliding friction on parts fixed to the housing, which occur in known rotary piston compressors. In the known rotary piston compressors, this sliding friction on the piston cage 50 is reduced by the auxiliary running gears 88 , 90 , 92 and 94 to a significantly lower rolling friction.

Referring to FIG. 1 , the rotary piston compressor 10 , if embodied as an internal combustion engine, also has an ignition plug 115 and 116 for each working chamber 34 and 36 , which are guided at the end faces by the end caps 16 and 18 respectively. The working chamber 34 is also assigned an intake branch 118 for combustion air and an exhaust branch 120 for discharging the burned fuel-air mixture. Corresponding structures are also provided for the working chamber 36 .

The pivoting movement of pistons 22 , 24 , 26 and 28 together with piston cage 50 about rotational axis 30 is transmitted to working shaft 122 , which can then be used to drive a truck, for example.

Claims (7)

1. A rotary piston compressor having a housing (12) in which at least one first piston (22) is arranged, said first piston being rotatable around a shaft (30) fixed to the housing, and When revolving around the axis of rotation (30), a reciprocating movement is carried out between an end position close to the axis of rotation and an end position away from the axis of rotation, so that the working chamber defined on the end face (38) of the piston (22) facing the axis of rotation (30) (34) periodically becomes larger and smaller, wherein the shaft (30) extends through the working chamber (34) and the piston (22) has a control operating mechanism (70) that rotates around the shaft (30) when the piston (22) When running along the control cam (66) fixed with the housing, it is used to derive the reciprocating motion of the piston (22) from the rotary motion, and the piston (22) is arranged in the accommodation device of the piston cage (50), the piston (22 ) is connected to the piston cage in a rotationally fixed manner relative to the shaft (30) and the piston cage rotates around the shaft (30) together with the piston (22), characterized in that the piston (22) is in addition to having a control operating mechanism (70) There is also an auxiliary running mechanism (88) on the outward side of the centrifugal force direction for the rotating shaft (30), and the running surface (108) of the auxiliary running mechanism rolls along the inner side of the piston cage (50) during the reciprocating motion of the piston (22). pressure, wherein the direction of motion of the auxiliary running mechanism (88) and the axis of rotation (30) lie in a common plane. 2. The rotary piston compressor as claimed in claim 1, characterized in that the auxiliary operating mechanism (88) is designed as a pulley (96) whose axis of rotation (98) is perpendicular to the rotation of the piston (22) The axis of rotation (30) of the movement is oriented. 3. The rotary piston compressor according to claim 1 or 2, characterized in that the control operating mechanism (70) is designed as a pulley (78) whose axis of rotation (80) is between the piston (22) and the The same point within the housing (12) intersects the axis of rotation (30) at any position between the end positions near the axis of rotation and the end positions away from the axis of rotation. 4. Rotary piston compressor according to claims 2 and 3, characterized in that the pulley (96) of the auxiliary operating mechanism (88) is arranged in a bearing in the pulley (78) of the control operating mechanism (70), Wherein, the rotation axes (98, 80) of the pulleys (96, 78) of the auxiliary running mechanism (88) and the control running mechanism (70) are perpendicular to each other. 5. A rotary piston compressor according to any one of claims 1 to 4, characterized in that the reciprocating movement of the piston (22) is a pivoting movement about a pivot axis (46) perpendicular to the shaft (30), And in any position of the piston (22), the contact line (86) of the running surface (84) of the control running mechanism (70) and the control cam (66) is aligned with the intersection of the swing axis (46) and the rotating shaft (30). 6. The rotary piston compressor as claimed in any one of claims 1 to 5, characterized in that the piston cage (50) has, for the auxiliary operating mechanism (88) of the piston (22) around the axis of rotation (30) narrow and elongated shoulder (100) seen in the direction of the axis of rotation, which extends towards the end position of the piston (22) away from the axis of rotation and the auxiliary running mechanism (88) Run on the inner side of the shoulder. 7. Rotary piston compressor according to any one of claims 1 to 6, characterized in that lateral guides for the auxiliary running mechanism are formed on the inner side of the piston cage (50), wherein An auxiliary running mechanism (88) runs along said inner side.

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