CN113710894A

CN113710894A - Reciprocating piston type compressor

Info

Publication number: CN113710894A
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: 2021-11-26
Anticipated expiration: 2040-04-06
Also published as: CN113710893A; JP7494206B2; DE102019112245A1; CN113710893B; WO2020207936A1; CN113710894B; 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 is arranged with a circular diameter d_pOn a common circumferential line of a circle of and wherein the wobble plate(30) Comprising: the mass m of the wobble plate; a density ρ; a position y of the center of gravity depending on the tilt angle ψ of the wobble plate (30); a thickness z corresponding to the distance of the first annular surface (41) of the disk substrate (40) from the parallel second annular surfaces (41, 42); and a wobble plate unbalance which in operation depends 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 reference mass m_refThe thickness z and the diameter d of the circle of the disk substrate (40)_pAnd the density p of the wobble disc (30), and wherein the root mean square value M of the unbalance ratio M at a plurality, in particular all, of the discrete full tilt angles psi in a tilt angle range between 0 DEG and 23 DEG_RMSComprises the following steps:

wherein M is_RMS<0.045。

Description

Reciprocating piston type compressor

The present invention relates to a reciprocating piston compressor (hubkolbenkampresursor) according to the preamble of claim 1. Such reciprocating piston compressors are known, for example, from EP 1148241 a 2.

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

To absorb the forces occurring during operation, the wobble plate is constructed to be relatively strong. This results in a relatively large mass moment of inertia, causing vibrations. These vibrations produce noise which, however, is hardly perceptible 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 covers this noise.

However, in the electric or hybrid vehicles which are becoming more popular, the noise of the engine no longer covers the noise of the reciprocating piston compressor, in particular for the air conditioning system of the vehicle, and the noise of the reciprocating piston compressor is therefore considered to be annoying. In this regard, efforts are made to reduce the noise of the reciprocating piston compressor.

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

This task is achieved by the subject matter of claim 1.

In particular, the invention is based on the idea of specifying a reciprocating piston compressor having an oscillating disk and at least two reciprocating pistons, wherein the oscillating disk comprises at least one oscillating cam and at least one balancing weight (ausgleichsgewich). The oscillating cam and the balance weight are arranged on the first annular surface of the disk base. The reciprocating pistons each have a piston axis K, which are arranged with a circular diameter d_pOn a common circumferential line of the circle. The wobble plate has:

-the mass m of the wobble plate,

-a density p,

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

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

-wobble plate unbalance in operation depending on the tilt angle ψ of the wobble plate.

The unbalance ratio M between the wobble plate unbalance and the reference unbalance is:

wherein the reference unbalance is the reference mass m_refAnd diameter d of circle_pThe product of half of (a). Reference mass m_refFrom the thickness z of the disc base body and the diameter d of the circle_pAnd the density p of the wobble disc.

According to the invention, the root mean square value M of the imbalance ratio M for a plurality of inclination angles psi of between 0 DEG and psi 23 DEG, in particular for all discrete full inclination angles psi_RMSComprises 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 inclination angles ψ (inclination angle number). Preferably, the number of inclination angles n is 23.

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

For calculating reference mass m_refDiameter d of circle_pCorresponding 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 axes of the reciprocating pistons.

Within the scope of the present application, a rounded protrusion arranged on the shaft or on the disc, which slides along the contact or sliding profile of the counter-element, is called a cam. The wobble cam is formed, for example, as a projection on the wobble plate.

Within the scope of the present application, a part of the wobble plate is understood to be a plate base body 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 as 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 disk base (or the mass of the entire oscillating disk is small relative to the mass of the disk 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_refMass ratio of (m/m)_refUp 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_refIn addition, the disk base can have a center plane E arranged parallel between the annular surfaces, 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 0.6 mm. In particular, the center of gravity S may be located outside the disk base and/or outside the axis of rotation of the disk 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 centre of gravity of the oscillating disc affects the vibrations generated when the oscillating disc operates and thus the noise of the reciprocating piston compressor equipped with the oscillating disc. It has been shown that a distance ratio f/z of the central plane of the disk substrate of up to 0.6mm ensures a particularly smooth running of the wobble disk.

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 with the disk base body, wherein the contact cams have an outwardly curved contact surface for the compression springs. Preferably, the contact cam directly abuts against a shaft hole of the wobble plate, which shaft hole is provided for the passage of a drive shaft of the reciprocating piston compressor.

The curved contact surface of the contact cam can slightly tilt the wobble plate, 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 constant at different inclinations of the wobble plate. Overall, therefore, a low-noise tilting of the wobble plate can be achieved, since the curved contact surfaces produce a low resistance when the wobble plate is tilted. This contributes to smooth and quiet operation of the reciprocating piston compressor.

Preferably, the wobble plate has two wobble cams oriented parallel to one another. The wobble plate can also have a central axis T that extends centrally along the diameter of the plate base between the wobble cams.

In a preferred embodiment of the reciprocating piston compressor, a first balancing weight is provided on the first annular surface of the disk base body, which first balancing weight is arranged to be rotated by a first angle α relative to the center axis T of the disk base body₁. The balance weight compensates for the imbalance or mass moment of inertia created by the wobble cam.

Alternatively or additionally, a second balancing weight may be provided on the second annular face of the disk base, which second balancing weight is arranged to be rotated by a second angle α relative to the central axis T of the disk base₂. Therefore, the second balance weight is disposed on the opposite side of the disk base from the wobble cam, and compensates for the unbalance of the wobble disk even in the case where the tilt angle is different. Overall, the second counterweight in this way further reduces the vibrations occurring during operation of the oscillating disc and thus reduces the noise in the reciprocating piston compressor.

Preferably, the first angle α₁And a second angle alpha₂With different quantities and/or different symbols. 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 the first wobble cam and the second wobble cam. The first oscillating cam may have a greater wall thickness than the second oscillating cam. Due to the piston force generated, the force acting on the first rocker cam is greater than the force acting on the second rocker cam. It is therefore provided that the first rocker cam, which is subjected to a greater force, is equipped with a greater wall thickness. The second oscillating cam, which is less loaded, may comprise a smaller wall thickness. Thus, a weight reduction is achieved, which contributes to a significant reduction of the total mass and noise of the reciprocating piston compressor.

Preferably, a transmission disc is provided, which has two transmission cams extending between the oscillating cams. The transmission disc may have a third balance weight arranged to be rotated by a third angle alpha with respect to the centre axis Z₃. Preferably, the centre axis Z extends centrally between the drive cams along the diameter of the drive disc.

The present invention will be explained in more detail below based on examples with reference to the attached schematic drawings. In the drawings:

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

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

fig. 3 shows a longitudinal sectional view of a drive shaft with a driving 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 having contact cams with curved abutment surfaces;

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

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

figure 7 shows a graph for comparing the unbalance ratio of the reciprocating piston compressor according to the invention according to figure 1 and a reciprocating piston compressor of the prior art;

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

FIG. 8b shows a side view of the transmission disc according to FIG. 8 a;

FIG. 8c shows a front view of the transmission disc according to FIG. 8 a;

figure 9 shows a schematic view of the relevant dimensions of the oscillating disc of the reciprocating piston compressor according to the invention; and

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

In fig. 1, a reciprocating piston compressor with a housing 15 is shown. The drive shaft 10 is mounted in a housing 15. The drive shaft 10 carries a transmission disc 20, which transmission disc 20 is connected in a rotationally fixed manner to the drive shaft 10. Furthermore, a wobble plate 30 is provided, which wobble plate 30 comprises a shaft bore 34, through which shaft bore 34 the drive shaft 10 is guided. The wobble plate 30 is force-transmitting engaged with the 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.

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

The first annular surface 41 faces the transmission disc 20 and the second annular surface 42 faces the cylinder 26. Starting from the first annular surface 41, the first rocker cam 31 and the second rocker cam 32 each comprise a cam tip 33. Each cam tip 33 bears against a corresponding sliding surface 21 formed on the transmission disc 20.

The transmission disc 20 comprises a first transmission cam 22 and a second transmission cam 23 extending between the

oscillating cams

31, 32. Sliding surfaces 21 are formed laterally outside the

drive cams

22, 23 and in the immediate vicinity of the

drive cams

22, 23, respectively. In fig. 1, the sliding surface 21 facing the second rocker cam 32 is covered by the second transmission cam 23 of the transmission disc 20. The sliding surface 21 is formed in one piece with the transmission disc 20.

A first counterbalance weight 38 and a second counterbalance weight 39 are also provided on the wobble plate 30 for low-vibration rotation. The first counterweight 38 originates from the first annular surface 41. The first balance weight 38 is substantially opposite the

oscillating cams

31, 32 with respect to the axis of rotation 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 swing disk 30 integrally with the

swing cams

31, 32 and the

balance weights

38, 39.

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

wobble cams

31, 32. Here, the first rocker cam 31 is provided with a larger wall thickness than the second rocker cam 32. The two rocker cams each bear with their inner surface against a

drive cam

22, 23 of the drive disk 20.

In operation, the driving disc 20 rotates with the drive shaft 10, thus transmitting a rotational force to the wobble disc 30. Since the resulting force of the reciprocating piston 25 acts mainly on the first rocker cam 31, it is provided that the first rocker cam 31 is provided with a greater wall thickness. The second swing cam 32 has a smaller wall thickness than the first swing cam 31, thus contributing to weight reduction 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 slide face 21. Therefore, the contact surfaces between the respective slide surfaces 21 and the

respective rocking 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 rocking cam 31 in the longitudinal axis direction, compared with the second rocking cam 32. This also contributes to achieving a good force transmission on the one hand and a weight reduction on the other hand.

In particular, the mass m of the entire wobble plate 30 and the reference mass m_refMass ratio of m/m therebetween_refUp to 2.2, which contributes to weight reduction and vibration reduction. Weight reduction 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 is reduced, but also the mass of the

balance weights

38, 39 can be reduced.

Reference mass m_refFrom the thickness z of the disk substrate 40, the diameter d of the circle_pAnd the density p of the wobble plate 30.

Reducing the vibration 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 at most 0.6 times the thickness z of the plate base 40 (fig. 9) away from the center plane E of the plate base 40 (distance f). Preferably, the center of gravity S of the wobble plate 30 is located outside of the plate base 40, as best seen in FIG. 9. Furthermore, the center of gravity S may be arranged outside, in particular above, the axis of rotation a, i.e. closer to the

oscillating 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 balancing

weights

38, 39 are not shown. The

oscillating cams

31, 32 are also not shown. The

rocker cams

31, 32 are, however, schematically indicated by a dash-dot line, i.e. do not have their true 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. Therefore, the noise of the reciprocating piston compressor is remarkably reduced.

For the sake of clarity, fig. 3 again shows a longitudinal sectional view of the drive shaft 10, the transmission disc 20 and the wobble disc 30. It is clear from fig. 3 how the driving disc 20 and the wobble disc 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 the back pressure in the reciprocating piston 25. As the wobble plate 30 pivots, the cam tips 33 slide along the sliding surface 21, which also affects the stroke of the respective reciprocating piston 25. The variable tilt angle ψ of the wobble disc 30 is also shown in fig. 9.

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

weights

38, 39 is shown. Here, the first counterweight 38 starts from the first annular surface 41 and the second counterweight 39 starts from the second annular surface 42 (fig. 5 b).

As can be seen in fig. 5a, a second counterweight 39 is formed generally U-shaped around the shaft hole 34 of the wobble plate 30. Shaft hole 34 is configured as a through hole. Furthermore, the second counterweight 39 is oriented to rotate by a second angle α starting from the median axis T₂。

Fig. 5c shows the wobble plate 30 in a front view, where the first balance weight 38 is visible. First counterbalance weight 38 has a generally trapezoidal shape and is immediately adjacent to shaft aperture 34. The first counterbalance weight 38 is disposed offset from the central axis T by a first angle α₁. First angle alpha₁And a second angle alpha₂Each 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 calculation of the reference mass m_refThe reference volume of (a). The reference volume corresponds to a cylinder with a thickness z, i.e. the thickness of the disk base 40 or the distance between the annular faces 41, 42 of the disk base 40. The diameter of the cylinder corresponds to the diameter of a circle extending through all hinge points or connecting all these hinge points, at which the reciprocating piston 25 is connected with the wobble plate 30. From thickness z and circular diameter d_pA reference volume is derived from which, together with the density of the material of the wobble plate 30, a reference mass m can be derived_ref。

In fig. 7, the unbalance ratio M is shown over a tilt angle range of the wobble plate 30 from 0 ° to 23 °. The solid line shows the unbalance ratio M of the reciprocating piston compressor according to the invention. The dashed and dotted lines relate to reciprocating piston compressors known from the prior art, respectively. It is clear that the reciprocating piston compressor according to the invention has a better overall, in particular a lower unbalance ratio M. Overall, therefore, the reciprocating piston compressor according to the invention has a smaller degree of unbalance over the entire range of inclination angles, which leads to lower noise. The reciprocating piston compressor according to the invention is therefore very quiet in operation.

By the

contact cams

43, 44, which cooperate with the compression springs 45, 46, each having an outwardly curved abutment surface 47 (fig. 4), a smooth movement of the wobble plate 30 is achieved. The

contact cams

43, 44 directly adjoin the shaft bore 34. Preferably, the

contact cams

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

contact cams

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

contact cams

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

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

Preferably, the

contact cams

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

In fig. 8a to 8c, the transmission disc 20 is shown. The transmission disc 20 comprises

transmission cams

22, 23, which

transmission cams

22, 23 are formed substantially identically, but axisymmetrically with respect to the central axis Z (fig. 8 a). Furthermore, the transmission disc 20 also carries a third balance weight 24, which third balance weight 24 projects beyond the circular outer contour of the transmission disc 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 balance weight is arranged to rotate by a third angle alpha starting from the central axis Z₃. Thus, the third angle α₃Is also determined according to the mass of the first rocking cam 31. In other words, the third balance weight 24 serves not only to balance the mass of the drive disc 20, but also to balance the mass within the entire drive train including the drive shaft 10, the drive disc 20 and the wobble disc 30.

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

where ρ represents the density of the wobble plate 30.

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

cams

31, 32 are at a predetermined ratio to each other or depend on the diameter d of the disc 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_pRatio b/d between_pBetween 0.2 and 0.5, in particular 0.34. The ratio c/a of the respective widths a, c of the

rocker cams

31, 32 to one another is preferably between 0.7 and 4.0, in particular 1.6.

List of reference marks

10 drive shaft

14 longitudinal axis

15 casing

20 drive plate

21 sliding surface

22 first transmission cam

23 second drive cam

24 third balance weight

25 reciprocating piston

26 cylinder body

28 end face

30 swing disk

31 first oscillating cam

32 second oscillating cam

33 cam tip

34 axle hole

37 sliding bearing

38 first counter weight

39 second balance weight

40 disc substrate

41 first annular surface

42 second annular surface

43 first contact cam

44 second contact cam

45 first compression spring

46 second compression spring

47 contact surface

α₁First angle

α₂First, theTwo angles

α₃Third angle

Psi, psi tilt angle

a width of the second swing cam 32

b distance of the rocking

cams

31, 32

c width of first swing cam 31

m mass of wobble plate 30

m_refReference mass

d_pPitch diameter of reciprocating piston 25 or cylinder 26

y eccentricity

S center of gravity

Thickness of the z-disk substrate 40

Axis of rotation A

E center plane

T axle wire

Z central axis

RMS root mean square value

K piston axis.

Claims

1. Reciprocating piston compressor with an oscillating disc (30) and at least two reciprocating pistons (25), wherein the oscillating disc (30) comprises at least one oscillating cam (31, 32) and at least one balancing weight (38, 39) which are arranged on a first annular face (41) of a disc base (40), and the reciprocating pistons (25) each have a piston axis K which is arranged with a circular diameter d_pAnd wherein the wobble disc (30) has:

-the mass m of the wobble plate,

-a density p,

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

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

-a wobble plate unbalance in operation depending on the tilt angle ψ of the wobble plate (30),

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

wherein the reference unbalance is a reference mass m_refAnd diameter d of circle_pAnd the reference mass m, and_refthe thickness z of the disc base body (40) and the diameter d of the circle_pAnd the density p of the wobble plate (30), and wherein the root mean square value M of the unbalance ratio M at a plurality, in particular all, of the discrete full tilt angles psi in a tilt angle range between 0 DEG and 23 DEG_RMSComprises 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。

2. Reciprocating piston compressor according to claim 1, characterized in that the wobble disc mass m and the reference mass m_refMass ratio of (m/m)_refUp to 2.2, in particular up to 1.9, in particular up to 1.85.

3. The reciprocating piston compressor according to any one of the preceding claims, wherein the disc base (40) has a centre plane E arranged in parallel between annular faces (41, 42), wherein a distance ratio f/z between a distance f of a centre of gravity S of the wobble disc (30) from the centre plane E and a thickness z of the disc base (30) is at most 0.6 mm.

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 axis of rotation a of the disc base (40).

5. The reciprocating piston compressor as claimed in any one of the preceding claims, characterized in that contact cams (43, 44) are arranged on the first and/or second annular face (41, 42), respectively, which are fixedly connected with the disc base body (40), wherein the contact cams (43, 44) have outwardly curved abutment faces for compression springs (45, 46).

6. A reciprocating piston compressor according to claim 5, characterised in that the wobble disc (30) has a shaft bore (34) for passing a drive shaft (10) of the reciprocating piston compressor, wherein the contact cams (43, 44) are in immediate vicinity of the shaft bore (34).

7. The reciprocating piston compressor as claimed in any one of the preceding claims, characterized in that the wobble disc (30) has two wobble cams (31, 32) oriented parallel to each other.

8. The reciprocating piston compressor of claim 7, wherein a first balance weight (38) is provided on the first annular face (41), the first balance weight being arranged to be rotated by a first angle a relative to the centre axis T of the disc base (40)₁Wherein the center axis T extends centrally between the rocker cams (31, 32) along a diameter of the disk base body (40).

9. The reciprocating piston compressor of claim 7 or 8, wherein a second balancing weight (39) is provided on the second annular face (42), the second balancing weight being arranged to be rotated by a second angle α with respect to the centre axis T of the disc base (40)₂Wherein the center axis T extends centrally between the rocker cams (31, 32) along a diameter of the disk base body (40).

10. The reciprocating piston compressor of claim 9, wherein the first angle a₁And the second angle alpha₂With different quantities and/or different symbols.

11. The reciprocating piston compressor as claimed in any one of the preceding claims, characterized in that the wobble disc (30) has two wobble cams (31, 32), wherein a first wobble cam (31) has a larger wall thickness than a second wobble cam (32).

12. A reciprocating piston compressor according to any one of the preceding claims, characterised in that a transmission disc (20) is provided having two transmission cams (22, 23) extending between the oscillating cams (31, 32).

13. The reciprocating piston compressor of claim 12, wherein the drive plate (20) has a third balance weight (24) arranged to be rotated a third angle a with respect to the centre axis Z₃Wherein the centre axis Z extends centrally between the drive cams (22, 23) along the diameter of the drive disc (20).