CN113710894B

CN113710894B - Reciprocating piston compressor

Info

Publication number: CN113710894B
Application number: CN202080028372.9A
Authority: CN
Inventors: 彼得·吉泽
Original assignee: OET GmbH
Current assignee: OET GmbH
Priority date: 2019-04-12
Filing date: 2020-04-06
Publication date: 2023-05-26
Anticipated expiration: 2040-04-06
Also published as: CN113710893A; CN113710894A; JP7494206B2; DE102019112245A1; CN113710893B; WO2020207936A1; JP2022527608A; JP2022528446A; JP7358501B2; DE102019112237A1; WO2020207937A1

Abstract

The invention relates to a reciprocating piston compressor having a wobble plate (30) and at least two reciprocating pistons (25), wherein the wobble plate (30) comprises at least one wobble cam (31, 32) and at least one balancing weight (38, 39), which are arranged on a first annular surface (41) of a plate base body (40), and the reciprocating pistons (25) each have a piston axis K, which are arranged with a circular diameter d _p And wherein the wobble plate (30) has: the mass m of the wobble plate; a density ρ; a center of gravity position y depending on a tilt angle ψ of the wobble plate (30); a thickness z, which corresponds to the distance of the first annular surface (41) from the parallel second annular surface (42) of the disk base body (40); and a wobble plate unbalance in operation dependent on the tilt angle ψ of the wobble plate (30), wherein the unbalance ratio M between the wobble plate unbalance and the reference unbalance is:

wherein the reference mass m _ref From the thickness z and the circular diameter d of the disk substrate (40) _p And the density ρ of the wobble disc (30), and wherein the root mean square value M of the imbalance ratio M at a plurality, in particular all, of the discrete full tilt angles ψ is in the tilt angle range between ψ=0° and ψ=23° _RMS The method comprises the following steps:

wherein M is _RMS <0.045。

Description

Reciprocating piston compressor

The present invention relates to reciprocating piston compressors (hubkolbenkompresor). Such a reciprocating piston compressor is known, for example, from EP 1 148 241 A2.

The known reciprocating piston compressor has a drive shaft to which a drive disc (mitnehmercheibe) is connected in a rotationally fixed manner. A wobble plate (tauxeischeibe) is connected to the plurality of reciprocating pistons via slide bearings and has a shaft hole through which a drive shaft is guided. Furthermore, a wobble cam is provided on the wobble plate, which comprises a curved cam tip which bears against the sliding surface of the drive plate.

In order to absorb forces generated during operation, the wobble plate is constructed to be relatively strong. This results in a relatively large mass moment of inertia, thereby causing vibrations. These vibrations create noise which is hardly perceived when the known reciprocating piston compressor is used in a vehicle with an internal combustion engine. More precisely, the noise of the internal combustion engine is covered by this noise.

However, in increasingly rising electric or hybrid vehicles, engine noise no longer covers the noise of the reciprocating piston compressor, particularly for the air conditioning system of the vehicle, and therefore the noise of the reciprocating piston compressor is considered objectionable. In this regard, there is a desire to reduce the noise of reciprocating piston compressors.

The object of the present invention is therefore to provide a reciprocating piston compressor which is characterized by a quiet operation and a high efficiency.

This task is achieved by the following aspects.

In particular, the invention is based on the idea of providing a reciprocating piston compressor having a wobble plate and at least two reciprocating pistons, wherein the wobble plate comprises at least one wobble cam and at least one balancing weight (ausgleichswicht). The oscillating cam and the balance weight are arranged on a first annular face of the disc base. The reciprocating pistons each have a piston axis K which is arranged with a circular diameter d _p Is on a common circumference of a circle. The wobble plate has:

the mass m of the wobble disc,

the density p,

depending on the position y of the center of gravity of the tilt angle ψ of the wobble plate,

a thickness z corresponding to the distance of the first annular face from the parallel second annular face of the disk substrate, an

Wobble disc unbalance in operation depending on the tilt angle ψ of the wobble disc.

The unbalance ratio M between wobble disc unbalance and reference unbalance is:

wherein the reference unbalance is a reference mass m _ref Sum circle diameter d _p Half of the product of (c). Reference mass m _ref From the thickness z, the circular diameter d of the disk substrate _p And the density p of the wobble plate.

According to the invention, the root mean square value M of the imbalance ratio M at a plurality, in particular all, discrete full tilt angles ψ over the tilt angle range between ψ=0° and ψ=23° is calculated _RMS The method comprises the following steps:

wherein M is _RMS <0.045, in particular M _RMS <0.035, especially M _RMS <0.022, in particular M _RMS <0.01, especially M _RMS <0.006."n" represents the number of tilt angles ψ (the number of tilt angles). Preferably, the number of tilt angles n is n=23.

In the present invention, the wobble plate has a low mass moment of inertia, so that noise occurring in operation is low. The reciprocating piston compressor thus operates very quietly in the relevant angle of inclination and is therefore particularly suitable for electric vehicles or hybrid vehicles.

For calculating the reference mass m _ref Diameter d of circle of (2) _p Corresponding to the diameter of a circle oriented perpendicular to the drive shaft of the reciprocating piston compressor and connecting all the reciprocating pistons, in particular the longitudinal axis of the reciprocating pistons.

In the context of the present application, a rounded projection arranged on a shaft or a disk is referred to as a cam, which slides along the contact or sliding contour of the counter element. For example, the wobble cam is formed as a protrusion on the wobble plate.

Within the scope of the present application, a part of the wobble plate is understood to be a plate base which extends between two parallel annular faces and is delimited in the radial direction by the outer edge of the wobble plate. Preferably, the disc base is a one-piece component of the wobble disc. In particular, the wobble plate is preferably formed in one piece and comprises a plate base, at least one wobble cam and at least one balancing weight.

The wobble cam and the balance weight are essentially unbalanced masses that may cause vibrations when the wobble plate rotates. It has been shown that when the mass of the oscillating cam and the balance weight is small relative to the mass of the disc base (or the mass of the entire oscillating disc is small relative to the mass of the disc base), the vibration causes less noise. At the same time, the reduced mass improves efficiency.

In a preferred embodiment, the mass m of the entire wobble plate and the mass m of the plate base are arranged _ref Mass ratio m/m of (2) _ref Up to 2.2, in particular up to 1.9, in particular up to 1.85.

Alternatively or in addition to setting the mass ratio m/m _ref In addition, the disk base may have a center plane E arranged in parallel between the annular faces, wherein the distance ratio f/z between the distance f of the center of gravity S of the wobble disk from the center plane E and the thickness z of the disk base is at most 0.6mm. In particular, the center of gravity S may be located outside the disc base and/or outside the rotational axis of the disc base.

Furthermore, the center of gravity S may be arranged eccentrically with respect to the longitudinal axis of the drive shaft.

The position of the center of gravity of the wobble plate affects the vibration generated when the wobble plate operates, and thus affects the noise of the reciprocating piston compressor equipped with the wobble plate. It has been shown that a distance ratio f/z of the central plane of the disc base of at most 0.6mm ensures a particularly smooth running of the wobble disc.

In a preferred embodiment of the reciprocating piston compressor according to the invention, contact cams are arranged on the first annular surface and/or the second annular surface of the disk base body, respectively, which contact cams are fixedly connected to the disk base body, wherein the contact cams have an outwardly curved contact surface for the compression springs. Preferably, the contact cam directly abuts a shaft hole of the wobble plate, the shaft hole being provided for passing a drive shaft of the reciprocating piston compressor therethrough.

The curved abutment surface of the contact cam may tilt the wobble plate slightly, wherein a substantially constant contact with the compression spring is maintained. In particular, the contact surface between the contact cam and the compression spring can remain substantially unchanged at different inclinations of the wobble plate. Thus, in general, low noise tilting of the wobble plate can be achieved because the curved abutment surface generates low resistance when the wobble plate is tilted. This helps the reciprocating piston compressor operate smoothly and quietly.

Preferably, the wobble plate has two wobble cams oriented parallel to each other. The wobble plate may also have a central axis T which extends centrally between the wobble cams along the diameter of the plate base.

In a preferred embodiment of the reciprocating piston compressor, a first balancing weight is provided on a first annular face of the disk base body, which is arranged to rotate by a first angle α with respect to the center axis T of the disk base body ₁ . The balance weight compensates for the imbalance or mass moment of inertia created by the oscillating cam.

Alternatively or additionally, a second balancing weight may be provided on a second annular face of the disc base, which second balancing weight is arranged to rotate a second angle α with respect to the centre axis T of the disc base ₂ . Therefore, the second balance weight is disposed on the opposite side of the disk base from the swing cam, and compensates for unbalance of the swing disk even in the case of a difference in inclination angle. Overall, the second counterweight further reduces the weight on the wobble plate in this wayAnd thereby reduces noise in the reciprocating piston compressor.

Preferably, the first angle alpha ₁ And a second angle alpha ₂ Having different amounts and/or different signs. In other words, the first and second balancing weights are preferably arranged to rotate relative to each other.

In a further preferred embodiment of the invention, the wobble plate has two wobble cams, which form a first wobble cam and a second wobble cam. The first swing cam may have a larger wall thickness than the second swing cam. The force acting on the first rocking cam is greater than the force acting on the second rocking cam due to the generated piston force. It is therefore provided that the first rocker cam which is subjected to greater forces is equipped with a greater wall thickness. The second, less loaded rocker cam may comprise a smaller wall thickness. Thus, a weight saving is achieved, which contributes to a significant reduction of the total mass and noise of the reciprocating piston compressor.

Preferably, a drive disk is provided, which has two drive cams extending between the oscillating cams. The drive disc may have a third balancing weight arranged to rotate a third angle alpha with respect to the centre axis Z ₃ . Preferably, the central axis Z extends centrally between the drive cams along the diameter of the drive disk.

The invention will be explained in more detail below with reference to the attached schematic drawings and on the basis of embodiments. In the drawings:

fig. 1 shows a longitudinal section of a reciprocating piston compressor according to the present invention according to a preferred embodiment;

fig. 2 shows a top view of a drive shaft with a drive disk and a wobble plate of the reciprocating piston compressor according to fig. 1;

fig. 3 shows a longitudinal section through a drive shaft with a drive disk and a wobble disk of the reciprocating piston compressor according to fig. 1;

fig. 4 shows a side view of a portion of a wobble plate with contact cams having curved abutment surfaces;

FIG. 5a shows a rear view of a wobble plate having a second balance weight;

fig. 5b shows a side view of the wobble plate according to fig. 5 a;

FIG. 5c shows a front view of the wobble plate according to FIG. 5a with a first balance weight and a wobble cam;

fig. 6 shows a top view and a side view of a virtual reference wobble plate for calculating a reference mass;

FIG. 7 shows a chart for comparing unbalance ratios of the reciprocating piston compressor according to the present invention and the prior art reciprocating piston compressor according to FIG. 1;

FIG. 8a shows a rear view of a drive disk with a drive cam and a third balance weight;

FIG. 8b shows a side view of the drive disk according to FIG. 8 a;

FIG. 8c shows a front view of the drive disk according to FIG. 8 a;

fig. 9 shows a schematic view of the relevant dimensions of a wobble plate of a reciprocating piston compressor according to the invention; and

fig. 10 shows a side view of a drive train of a reciprocating piston compressor with a wobble plate, a drive plate and a drive shaft.

In fig. 1, a reciprocating piston compressor is shown with a housing 15. The drive shaft 10 is mounted in a housing 15. The drive shaft 10 carries a drive disk 20, which drive disk 20 is connected in a rotationally fixed manner to the drive shaft 10. Further, a wobble plate 30 is provided, the wobble plate 30 including a shaft hole 34, the drive shaft 10 being guided through the shaft hole 34. The wobble plate 30 is in force transmitting engagement with a plurality of reciprocating pistons 25 via slide bearings 37. The reciprocating pistons 25 are guided in cylinders 26, which each have an end face 28.

The wobble plate 30 has a first annular surface 41 and a second annular surface 42. These annular faces 41, 42 are arranged parallel to each other and define the disc base body 40. The disk substrate 40 has a thickness z. Thus, the thickness z corresponds to the distance between the first annular face 41 and the second annular face 42.

The first annular face 41 faces the drive disk 20 and the second annular face 42 faces the cylinder 26. The first and

second rocking cams

31, 32 each comprise a cam tip 33, starting from a first annular face 41. Each cam tip 33 rests against a corresponding sliding surface 21 formed on the drive disk 20.

The drive disk 20 comprises a first drive cam 22 and a second drive cam 23 extending between the

oscillating cams

31, 32. The sliding surfaces 21 are formed laterally outside the

drive cams

22, 23 and immediately adjacent to the

drive cams

22, 23, respectively. In fig. 1, the sliding surface 21 opposite to the second swing cam 32 is covered by the second transmission cam 23 of the transmission disk 20. The sliding surface 21 is formed in one piece with the drive disk 20.

For low vibration rotation, a first balance weight 38 and a second balance weight 39 are also provided on the wobble plate 30. The first balance weight 38 starts from a first annular face 41. The first balance weight 38 is substantially opposite to the

oscillating cams

31, 32 with respect to the rotation axis of the oscillating disc 30.

The

swing cams

31, 32 and the first balance weight 38 are formed integrally with the disk base 40. In other words, the disk base 40 forms the wobble disk 30 integrally with the

wobble cams

31, 32 and the

balance weights

38, 39.

In fig. 2, it can be seen in a top view that the wobble plate 30 has a total of two

wobble cams

31, 32. Here, the first swing cam 31 is provided with a wall thickness greater than that of the second swing cam 32. The two cams bear with their inner surfaces against the

drive cams

22, 23 of the drive disk 20.

In operation, the driving disk 20 rotates together with the driving shaft 10, thus transmitting a rotational force to the wobble plate 30. Since the resulting force of the reciprocating piston 25 mainly acts on the first oscillating cam 31, it is provided that the first oscillating cam 31 is provided with a larger wall thickness. The second swing cam 32 has a smaller wall thickness than the first swing cam 31, thus contributing to weight saving of the reciprocating piston compressor.

It can also be seen in fig. 2 that each of the two

rocker cams

31, 32 bears against the respective sliding surface 21. Accordingly, the contact surfaces between the respective sliding surfaces 21 and the

respective swing cams

31, 32 are different in size. In particular, the contact surface of the first rocking cam 31 with the sliding surface 21 is larger than the contact surface of the second rocking cam 32 with the sliding surface 21. This also increases the force transmission area of the first swing cam 31 in the longitudinal axis direction compared to the second swing cam 32. This also contributes to achieving a good force transmission on the one hand and a weight saving on the other hand.

In particular, the mass m of the entire wobble plate 30 and the reference mass m _ref Mass ratio m/m between _ref Up to 2.2, which contributes to weight saving and vibration reduction. Weight saving can be achieved by various measures. For example, the thickness z of the disk substrate 40 may be reduced. Thereby, not only the mass of the disk base 40 but also the mass of the

balance weights

38, 39 can be reduced.

Reference mass m _ref From the thickness z, the circular diameter d of the disk substrate 40 _p And the density p of wobble plate 30.

Reducing vibrations can be achieved by improving the position of the center of gravity. For this purpose, it can be provided that the center of gravity S of the wobble plate 30 is separated from the center plane E of the plate base 40 by an amount (distance f) corresponding to at most 0.6 times the thickness z of the plate base 40 (fig. 9). Preferably, the center of gravity S of the wobble plate 30 is located outside the plate base 40, as best seen in FIG. 9. Furthermore, the center of gravity S may be arranged outside the rotation axis a, in particular above, i.e. closer to the

swing cams

31, 32.

Fig. 9 shows in a very schematic view the dimensions of the wobble plate in connection with improved noise emission and weight reduction. In particular, a disk substrate 40 is shown. For clarity, the

balance weights

38, 39 are not shown. The rocking

cams

31, 32 are also not shown. However, the

oscillating cams

31, 32 are schematically indicated by dash-dot lines, i.e. do not have their actual outer contour.

The position of the center of gravity S, which is arranged offset from the longitudinal axis 14 by an eccentricity y and from the center plane E of the wobble plate 30 by a distance f, is clearly visible in fig. 9. The illustrated position of the center of gravity S has proven to be particularly advantageous for reducing vibrations during operation of the wobble plate 30. Thus, the noise of the reciprocating piston compressor is significantly reduced.

For clarity, fig. 3 again shows a longitudinal section through the drive shaft 10, the transmission disk 20 and the wobble disk 30. It is clear from fig. 3 how the driving disk 20 and the wobble disk 30 are arranged relative to each other. The wobble plate 30 has a shaft hole 34 formed by two conical recesses. Thus, the wobble plate can change the pivot angle or tilt angle ψ within a predetermined angular range. This is preferably achieved based on back pressure in the reciprocating piston 25. As the wobble plate 30 pivots, the cam tips 33 slide along the sliding surfaces 21, which also affects the stroke of each of the reciprocating pistons 25. Fig. 9 also shows the variable tilt angle ψ of the wobble plate 30.

In fig. 5a to 5c, an embodiment of a wobble plate 30 with two balancing

weights

38, 39 is shown. Here, the first balancing weight 38 starts from a first annular face 41, while the second balancing weight 39 starts from a second annular face 42 (fig. 5 b).

As can be seen in fig. 5a, the second balance weight 39 is formed generally U-shaped around the shaft hole 34 of the wobble plate 30. The shaft hole 34 is configured as a through hole. Furthermore, the second balancing weight 39 is oriented to rotate a second angle α from the mid-axis T ₂ 。

Fig. 5c shows the wobble plate 30 in a front view, wherein the first balancing weights 38 are visible. The first balance weight 38 has a generally trapezoidal shape and is immediately adjacent the shaft bore 34. The first balance weight 38 is arranged offset from the center axis T by a first angle α ₁ . First angle alpha ₁ And a second angle alpha ₂ Each oriented in the same rotational direction, i.e. both balancing

weights

38, 39 are arranged to rotate in the same direction relative to the central axis T.

The diagram according to fig. 6 shows in simplified form the use as a calculated reference mass m _ref Is a reference volume of the base of (a). The reference volume corresponds to the thickness of a cylinder of thickness z, i.e. the thickness of the disc substrate 40 or the distance between the annular faces 41, 42 of the disc substrate 40. The diameter of the cylinder corresponds to the diameter of a circle extending through or connecting all the hinge points where the reciprocating piston 25 is connected with the wobble plate 30. From thickness z and diameter d of circle _p A reference volume is derived from which, together with the density of the material of wobble plate 30, a reference mass m can be derived _ref 。

In fig. 7, the unbalance ratio M in the range of the tilt angle of the wobble plate 30 from 0 ° to 23 ° is shown. The solid line shows the unbalance ratio M of the reciprocating piston compressor according to the present invention. The dashed and dash-dot lines relate to reciprocating piston compressors, respectively, known from the prior art. It is clearly visible that the reciprocating piston compressor according to the invention has a generally better, in particular lower, imbalance ratio M. Thus, in general, the reciprocating piston compressor according to the present invention has a smaller imbalance over the whole tilt angle range, which causes lower noise. The reciprocating piston compressor according to the invention is thus very quiet in operation.

Smooth movement of the wobble plate 30 is achieved by the

contact cams

43, 44 cooperating with the compression springs 45, 46 each having an outwardly curved abutment surface 47 (fig. 4). The

contact cams

43, 44 directly abut the shaft hole 34. Preferably, the

contact cams

43, 44 are formed annularly around the shaft hole 34. The

contact cams

43, 44 can each form a completely closed ring. The

contact cams

43, 44 may be a one-piece component of the wobble plate 30.

As can be seen in fig. 4, the first compression spring 45 abuts against an abutment surface 47 of the first contact cam 43 of the wobble plate 30. In contrast, the second contact cam 44 disposed opposite to the first contact cam 43 is spaced apart from the second compression spring 46. However, the abutment surface 47 of the second contact cam 44 abuts against the second compression spring 46 at an additional inclination angle.

Preferably, the

contact cams

43, 44 are formed in one piece with the wobble plate.

In fig. 8a to 8c, a drive disk 20 is shown. The drive disk 20 comprises

drive cams

22, 23, which drive

cams

22, 23 are formed substantially identically, but symmetrically with respect to the central axis Z (fig. 8 a). The drive disk 20 furthermore carries a third balancing weight 24, which third balancing weight 24 protrudes beyond the circular outer contour of the drive disk 20. The protruding part is clearly visible in the rear view according to fig. 8 c. The third balance weight is designed to be substantially trapezoidal. In order to reduce the noise of the reciprocating piston compressor, the balancing weight is arranged to rotate a third angle α starting from the central axis Z ₃ . Thus, the third angle alpha ₃ Is also determined according to the mass of the first swing cam 31. In other words, the third balancing weight 24 serves not only to balance the mass of the drive disk 20, but also to balance the mass within the entire drive train including the drive shaft 10, the drive disk 20 and the wobble plate 30.

Fig. 10 shows the relevant dimensions for calculating the decisive parameters of the invention. In particular, reference mass m _ref The calculation is as follows:

where ρ represents the density of wobble plate 30.

It has been confirmed that the width c of the first swing cam 31, the width a of the second swing cam 32 and the distance b of the

swing cams

31, 32 are in a predetermined ratio to each other or depend on the diameter d of the disk base 40 _p (see fig. 2) is advantageous and preferred.

Therefore, it is preferable to set the distance b of the rocking

cams

31, 32 and the diameter d of the disk base 40 _p Ratio b/d between _p Between 0.2 and 0.5, in particular 0.34. The ratio c/a of the widths a, c of the

rocker cams

31, 32 to each other is preferably between 0.7 and 4.0, in particular 1.6.

List of reference marks

10. Driving shaft

14. Longitudinal axis

15. Shell body

20. Transmission disc

21. Sliding surface

22. First transmission cam

23. Second transmission cam

24. Third balance weight

25. Reciprocating piston

26. Cylinder body

28. End face

30. Swinging disc

31. First oscillating cam

32. Second oscillating cam

33. Cam tip

34. Shaft hole

37. Sliding bearing

38. First balance weight

39. Second balance weight

40. Disk substrate

41. A first annular surface

42. A second annular surface

43. First contact cam

44. Second contact cam

45. First compression spring

46. Second compression spring

47. Surface for sticking

α ₁ First angle of

α ₂ Second angle

α ₃ Third angle

Psi, psi tilt angle

a width of the second swing cam 32

b distance of oscillating

cam

31, 32

c width of first swing cam 31

mass of m wobble plate 30

m _ref Reference mass

d _p Pitch diameter of reciprocating piston 25 or cylinder 26

y-eccentricity

S center of gravity

Thickness of z-disk base 40

Arotation axis

E center plane

T central axis

Z central axis

RMS root mean square value

And K piston axis.

Claims

1. A reciprocating piston compressor having a wobble plate (30) and at least two reciprocating pistons (25), wherein the wobble plate (30) comprises at least one wobble cam (31, 32) and at least one balancing weight (38, 39), which are arranged on a first annular surface (41) of a plate base (40), and the reciprocating pistons (25) each have a piston axis K, which is arranged with a circular diameter d _p And wherein the wobble plate (30) has:

the mass m of the wobble disc,

the density p,

depending on the position y of the center of gravity of the tilt angle ψ of the wobble plate (30),

-a thickness z corresponding to the distance of a first annular face (41) from a parallel second annular face (42) of the disc substrate (40), and

a wobble disc unbalance in operation depending on the tilt angle psi of the wobble disc (30),

wherein the unbalance ratio M between the unbalance of the wobble plate and the reference unbalance is:

wherein the reference unbalance is a reference mass m _ref Sum circle diameter d _p And the reference mass m _ref From the thickness z of the disk base body (40), the circular diameter d _p And the density ρ of the wobble plate (30), and wherein the root mean square value M of the imbalance ratio M at a plurality of discrete full tilt angles ψ over a tilt angle range between ψ=0° and ψ=23° _RMS The method comprises the following steps:

wherein M is _RMS <0.045。

2. The reciprocating piston compressor of claim 1, wherein the wobble plate mass m is equal to the reference mass m _ref Mass ratio m/m of (2) _ref Up to 2.2.

3. Reciprocating piston compressor according to claim 1 or 2, characterized in that the disk base (40) has a central plane E arranged in parallel between the first annular surface (41) and the second annular surface (42), wherein the distance ratio f/z between the distance f of the centre of gravity S of the wobble disk (30) from the central plane E and the thickness z of the disk base (40) is at most 0.6mm.

4. A reciprocating piston compressor according to claim 3, characterized in that the centre of gravity S is arranged outside the disc base (40) and/or outside the rotation axis a of the disc base (40).

5. Reciprocating piston compressor according to any one of claims 1-2 and 4, characterized in that contact cams (43, 44) are arranged on the first annular face (41) and/or the second annular face (42), respectively, which contact cams are fixedly connected with the disk base body (40), wherein the contact cams (43, 44) have outwardly curved abutment faces for compression springs (45, 46).

6. Reciprocating piston compressor according to claim 5, characterized in that the wobble plate (30) has a shaft hole (34) for passing a drive shaft (10) of the reciprocating piston compressor, wherein the contact cams (43, 44) are immediately adjacent to the shaft hole (34).

7. Reciprocating piston compressor according to any one of claims 1-2, 4 and 6, characterized in that the wobble plate (30) has two wobble cams (31, 32) oriented parallel to each other.

8. Reciprocating piston compressor according to claim 7, characterized in that a first balancing weight (38) is provided on the first annular face (41), which is arranged to rotate by a first angle α with respect to the central axis T of the disc base (40) ₁ Wherein the central axis T extends centrally between the rocker cams (31, 32) along the diameter of the disk base body (40).

9. Reciprocating piston compressor according to claim 7, characterized in that a second balancing weight (39) is provided on the second annular face (42), which is arranged to rotate by a second angle α with respect to the central axis T of the disc base (40) ₂ Wherein the central axis T extends centrally between the rocker cams (31, 32) along the diameter of the disk base body (40).

10. Reciprocating piston compressor according to claim 8, characterized in that a second balancing weight (39) is provided on the second annular face (42), which is arranged to rotate by a second angle α with respect to the central axis T of the disc base (40) ₂ Wherein the central axis T extends centrally between the rocker cams (31, 32) along the diameter of the disk base body (40).

11. The reciprocating piston compressor of claim 10, wherein the first and second balance weights are arranged to rotate relative to one another.

12. Reciprocating piston compressor according to any one of claims 1-2, 4, 6 and 8-10, characterized in that the wobble plate (30) has two wobble cams (31, 32), wherein the first wobble cam (31) has a larger wall thickness than the second wobble cam (32).

13. Reciprocating piston compressor according to any one of claims 1-2, 4, 6 and 8-10, characterized in that a drive disc (20) is provided, which has two drive cams (22, 23) extending between the wobble cams (31, 32).

14. Reciprocating piston compressor according to claim 13, characterized in that the drive disc (20) has a third balancing weight (24) arranged to rotate a third angle α with respect to the central axis Z ₃ Wherein the central axis Z extends centrally between the drive cams (22, 23) along the diameter of the drive disk (20).

15. The reciprocating piston compressor of claim 1 wherein the root mean square value M of the imbalance ratio M at all discrete full tilt angles ψ for a tilt angle range between ψ=0° and ψ=23° _RMS The method comprises the following steps:

wherein M is _RMS <0.045。

16. The reciprocating piston compressor of any one of claims 1-2, 4, 6, 8-10 and 14-15, wherein M _RMS <0.035。

17. The reciprocating piston compressor of claim 16, wherein M _RMS <0.022。

18. The reciprocating piston compressor of claim 17, wherein M _RMS <0.01。

19. The reciprocating piston compressor of claim 18, wherein M _RMS <0.006。

20. Reciprocating piston compressor according to any one of claims 1, 4, 6, 8-10, 14-15 and 17-19, characterized in that the wobble plate mass m is in relation to the reference mass m _ref Mass ratio m/m of (2) _ref Up to 1.9.

21. The reciprocating piston compressor of claim 20, wherein the wobble plate mass m is equal to the reference mass m _ref Mass ratio m/m of (2) _ref Up to 1.85.