SCROLL COMPRESSOR AND METHOD FOR OPERATING THE SCROLL COMPRESSOR

Description

[0001] The invention relates to a scroll compressor according to claim 1 and a method for operating the scroll compressor according to claim 8. State of the art

[0002] A scroll compressor is known from DE 10 2017 102 645 A1.

[0003] Document DE 10 2013 020763 A1 discloses a scroll compressor according to the preamble of claim 1. Disclosure of the invention

[0004] The object of the invention is to provide an improved scroll compressor and an improved method for operating the scroll compressor.

[0005] This problem is solved by means of a scroll compressor according to claim 1 and a method according to claim 7. Advantageous embodiments are specified in the dependent claims.

[0006] An improved scroll compressor can be provided by the scroll compressor comprising a stator, an orbiter movable about an orbiter axis relative to the stator, and a coupling device, wherein the stator and the orbiter interlock and at least partially delimit a working space for the compression of a fluid that can be filled into the working space, wherein the coupling device comprises a first coupling unit arranged on the stator and a second coupling unit arranged opposite the first coupling unit on the orbiter, wherein the first coupling unit is magnetically coupled to the second coupling unit and the second coupling unit introduces a coupling torque acting about the orbiter axis into the orbiter.

[0007] According to the invention, the scroll compressor has a drive motor that is torque-coupled to the orbiter. The drive motor is configured to provide a drive torque acting about the orbiter axis to drive the orbiter, wherein the drive torque and the coupling torque act on the orbiter to generate a compressor torque. The orbiter can be moved from a first position through a second position and back to the first position while maintaining a pivoting direction. Between the first and second positions of the orbiter, the coupling torque acts against the drive torque. In the second position, the orbiter is pivoted relative to the first position, and between the second and first positions of the orbiter, the coupling torque and the drive torque are in the same direction.This reduces and smooths out uneven torque curves in the drive torque, particularly in the first order. Furthermore, current ripple in the drive motor's supply line is reduced when the drive motor is controlled. This relieves the load on the drive motor powering the orbiter and on the bearing assembly supporting the orbiter.

[0008] This allows for the use of a particularly durable and quiet-running scroll compressor, as well as a less powerful drive motor for the orbiter, especially with a lower maximum torque. As a result, the scroll compressor can be manufactured in a particularly lightweight and cost-effective manner.

[0009] In another embodiment, a gap is arranged between the first coupling unit and the second coupling unit. This minimizes wear on the scroll compressor.

[0010] In a further embodiment, at least one of the two coupling units has a two-pole permanent magnet or a multi-pole permanent magnet for forming the magnetic coupling with the other coupling unit. This design has the advantage that the coupling device is particularly compact and requires few components.

[0011] In a further embodiment, the first coupling unit or the second coupling unit comprises at least one laminated core with at least two layers of a ferromagnetic material arranged side by side in a stack. The layers are arranged axially relative to each other. This design has the advantage that only small eddy currents are generated in the laminated core during operation of the scroll compressor, thus preventing overheating of the coupling unit and the laminated core.

[0012] In a further embodiment, the stator has a spirally shaped first wall and the orbiter has a spirally shaped second wall, wherein the first and second walls interlock and at least partially delimit the working space. The first coupling unit is attached to a housing of the stator, and the second coupling unit is attached to a second outer circumferential side of the second wall of the orbiter. It is particularly advantageous if the attachment is, for example, material-fit. The arrangement of the second coupling unit on the second outer circumferential side of the second wall also has the advantage that, in this area, the second wall does not externally delimit the working space, thus providing sufficient installation space to accommodate the coupling device. Furthermore, the external installation space of the scroll compressor is not increased by the internal placement of the coupling device.

[0013] In another embodiment, a center of a maximum extent of the first coupling unit in a tangential direction to the orbiter axis is arranged in a plane, wherein the orbiter axis is arranged in the plane.

[0014] The scroll compressor described above can be operated by introducing a fluid into the working space, moving the orbiter around the orbiter axis and compressing the fluid in the working space, whereby a coupling torque acts on the orbiter through the magnetic coupling between the first coupling unit and the second coupling unit.

[0015] It is particularly advantageous if the orbiter, while maintaining a pivot direction about the orbiter axis, is moved from a first position via a second position back to the first position, wherein a drive torque acting about the orbiter axis is provided to the orbiter for propulsion, wherein the drive torque and the coupling torque together act on the orbiter to form a compressor torque, wherein the coupling torque between the first position of the orbiter and the second position of the orbiter acts against the drive torque, and wherein between the second position and the first position the coupling torque and the drive torque are in the same direction.

[0016] In a further embodiment, between a first operating point and a second operating point following the first, the fluid in the working chamber is compressed, with the coupling torque at the first operating point acting against the drive torque at the beginning of the fluid compression. This allows for a particularly significant reduction in drive torque ripple.

[0017] The invention is explained in more detail below with the aid of figures. These show: Figure 1 is a schematic representation of a scroll compressor according to a first embodiment; Figure 2 is a sectional view along a Figure 1 shown section plane AA through the in Figure 1 The scroll compressor shown is in a 0° position; Figure 3 shows a sectional view along the [unclear text]. Figure 1 shown section plane AA through the in Figure 1 The scroll compressor shown is in a 180° position; Figure 4 shows a sectional view along the [unclear text]. Figure 1Sectional plane AA shown through a scroll compressor according to a second embodiment in a 0° position; Figure 5, which is shown in Figure 4 shown sectional view along the in Figure 1 The section plane AA shown through the scroll compressor according to the second embodiment in a 180° position and Figure 6 a torque curve over a swivel angle of an orbiter of the scroll compressor about an orbiter axis of the orbiter.

[0018] Figure 1 shows a schematic representation of a scroll compressor 10 according to a first embodiment.

[0019] The scroll compressor 10 has a stator 15, an orbiter 20, a drive motor 25, a drive shaft 30, a bearing arrangement 35, an inlet 40, an outlet 45, a housing 46 and a coupling device 50.

[0020] The stator 15 is stationary and immobile and is mechanically connected to the housing 46 of the scroll compressor 10. The orbiter 20 is rotationally fixed to the drive shaft 30, which in turn connects the drive motor 25 to the orbiter 20. The drive shaft 30 is rotatably mounted about an orbiter axis 55. The orbiter 20 is arranged eccentrically to the orbiter axis 55. When the drive motor 25 is activated, the orbiter 20 is guided and pivoted about the orbiter axis 55. The bearing arrangement 35 is designed to support forces from the orbiter 20, which is guided eccentrically about the orbiter axis 55.

[0021] Figure 2 shows a sectional view along a Figure 1 shown section plane AA through the in Figure 1 Scroll compressor 10 shown in a 0° position.

[0022] The stator 15 comprises a first base plate 70 and a first wall 75. The first base plate 70 extends essentially in a plane of rotation perpendicular to the orbiter axis 55. In the axial direction, the first base plate 70 can be arranged opposite the drive motor 25 and is mechanically connected to the housing 46. The first wall 75 is spirally wound around the orbiter axis 55 and is axially attached to and connected with the first base plate 70 on one side. The first base plate 70 and the first wall 75 can be manufactured in one piece from a non-magnetic material, such as aluminum. Radially on the outside of the first wall 75, the inlet 40 is arranged between the first wall 75 and the first housing 46. The outlet 45 can be arranged in the first base plate 70, essentially in the center of the orbiter axis 55.

[0023] The inlet 40 can, for example, be fluidically connected to a refrigerant circuit of a heat pump. A fluid 110, in particular a refrigerant, for example R410, preferably in a gaseous state, can be introduced into the scroll compressor 10 via the inlet 40. The outlet 45 can, for example, be fluidically connected to a heat exchanger of the heat pump.

[0024] The Orbiter 20 has a second base plate 80 (in Figure 1 shown) and a second wall 85 (cf. Figure 2The second wall 85 is spirally wound around the orbiter axis 55. The second wall 85 is axially connected to the second base plate 80 on one side. The second base plate 80 is axially offset from the first base plate 70. The second wall 85 is located on an axial side facing the stator 15, and thus on a side facing away from the first base plate 70, on the second base plate 80. Preferably, the second base plate 80 and the second wall 85 are manufactured in one piece and from a single material, for example, a non-magnetic material such as aluminum.

[0025] The first base plate 70 and the second base plate 80 are arranged axially offset from each other. Axially between the first base plate 70 and the second base plate 80, the first wall 75 and the second wall 85 are arranged such that they interlock. Together with the first base plate 70 and the second base plate 80, the first wall 75 and the second wall 85 define an inlet area 90, a compressor area 95, an outlet area 100, and a movement space 101. The inlet area 90 is located downstream of the inlet 40 and upstream of the compressor area 95. In the compressor area 95, the first wall 75 and the second wall 85 define at least one working chamber 105 in the radial direction. Preferably, the first and the second wall 75, 85 define several working chambers 105 arranged separately from one another in the circumferential direction with respect to the orbiter axis 55.Downstream of the compressor section 95, the outlet section 100 is connected. The outlet 45 opens into the outlet section 100. The movement space 101 is arranged radially outside the second wall 85 and is bounded radially outwards by the housing 46. The movement space 101 ensures that sufficient space is available within a housing contour 125 of the housing 46 for the eccentric movement of the second wall 85 relative to the stator 15 and the housing 46, without the second wall 85 colliding with the housing 46 or the stator 15.

[0026] In the assembled state of the scroll compressor 10, for example in the heat pump, the fluid 110 is introduced into the inlet area 90 via the inlet 40. The fluid 110 flows circumferentially along a first outer circumferential side 115 of the first wall 75 towards the compressor area 95. When a compressor torque MG is introduced into the orbiter 20, the orbiter 20 is moved in an eccentric motion about the orbiter axis 55. In conjunction with the stationary stator 15, the working chamber 105 is moved circumferentially and follows the spiral shape of the first wall 75 radially inwards. With increasing length of travel, the volume of the respective working chamber 105 is reduced and the fluid 110 present in the working chamber 105 is compressed. The compressed fluid 110 is conveyed into the working chamber 105 into the outlet area 100 and exits the scroll compressor 10 via the outlet 45.

[0027] The coupling device 50 comprises a first coupling unit 60 and a second coupling unit 65. The first coupling unit 60 is arranged on the inside of a housing contour 125 of the housing 46 of the stator 15 and is mechanically connected to the housing 46. Figure 2For example, the first coupling unit 60 has a multipole permanent magnet 131, which is oriented tangentially to the orbiter axis 55 in its main direction of extension. The multipole permanent magnet 131 has several north and south poles arranged alternately next to each other in the tangential direction. The first coupling unit 60 is preferably mechanically connected to the housing contour 125 by means of a first material-fit connection 130. The first coupling unit 60 provides a magnetic field 135 through the multipole permanent magnet 131, which is schematically indicated by dashed lines in Figure 2. The magnetic field 135 projects radially inwards into the movement space 101.

[0028] Radially opposite the first coupling unit 60, the second coupling unit 65 is arranged in the movement space 101. The second coupling unit 65 is arranged on a second outer circumferential side 140 of the second wall 85 and connected to the second outer circumferential side 140 by means of a second connection 145. Preferably, the second connection 145 can be a material-fit and / or form-fit connection. In particular, the second coupling unit 65 can be attached to the second outer circumferential side 140 by means of an adhesive bond.

[0029] The second coupling unit 65 comprises a ferritic material. Preferably, the second coupling unit 65 comprises an arrangement of several layers 150 of ferritic material, for example, electrical steel. The layers 150 are arranged axially adjacent to one another in a stack. Additionally, a Figure 2A retaining device (not shown) is provided to connect the multiple layers 150 of electrical steel together and thus ensure a secure fastening of the second coupling unit 65 to the second wall 85.

[0030] Alternatively to the one in Figure 2 In the illustrated embodiment of the second coupling unit 65 with several layers 150 of electrical steel, the second coupling unit 65 can also have another permanent magnet, which, for example, has the same or a similar number of poles as the permanent magnet 131 of the first coupling unit 60. However, the pole arrangement of the additional permanent magnet differs from that of the permanent magnet 131 of the first coupling unit 60. Thus, in the radial direction opposite, for example, a south pole of the second coupling unit 65 is arranged to face a north pole of the permanent magnet 131.

[0031] The first coupling unit 60 has an inner surface 155 on one side facing the second wall 85, as exemplified in Figure 2 The inner surface 155 is planar. Radially opposite the inner surface 155, the second coupling unit 65 has an outer surface 160 on a side facing away from the second wall 85, the outer surface 160 being planar by way of example. Both the inner surface 155 and the outer surface 160 are oriented tangentially to the orbiter axis 55 by way of example. Furthermore, the inner surface 155 and the outer surface 160 are arranged opposite each other in the radial direction. A gap 165 is formed between the inner surface 155 and the outer surface 160. The gap 165 is defined in the radial direction by a distance a between the inner surface 155 and the outer surface 160. Figure 2 The distance a between the inside (155) and the outside (160) is maximized.

[0032] The gap 165 ensures that the inner surface 155 does not come into contact with the outer surface 160 when the orbiter 20 moves around its axis 15. This prevents wear, and in particular the introduction of metal particles into the fluid 110. Furthermore, it ensures that the second coupling unit 65 can be moved away from the first coupling unit 60 despite the magnetic coupling.

[0033] In Figure 2 The orbiter 20 is shown in the 0° position with respect to a movement around the orbiter axis 55. In the 0° position, the distance a is maximized. For example, the second coupling unit 65 is located outside the effective range of the magnetic field 135, so that magnetic coupling between the first coupling unit 60 and the second coupling unit 65 is essentially eliminated.

[0034] Figure 3 shows a cross-sectional view along the in Figure 1shown section plane AA through the in Figure 1 Scroll compressor 10 shown in a 180° position.

[0035] In Figure 3 Is Orbiter 20 rotated 180° relative to the one in Figure 2 The diagram shows the unit pivoted and is therefore in the 180° position. In this position, the distance a between the inner surface 155 and the first coupling unit 60 and the outer surface 160 of the second coupling unit 65 is minimized. The second coupling unit 65 is located within the effective range of the magnetic field 135, so that the first coupling unit 60 is magnetically coupled to the second coupling unit 65. Figure 3 The second coupling unit 65 is attracted by the permanent magnet 131 of the first coupling unit 60 with a force F.

[0036] The multi-layered design of the second coupling unit 65 and the radial orientation of the layers 150 to the orbiter axis 55 has the advantage that eddy currents are avoided when the second coupling unit 65 moves in the magnetic field 135 of the first coupling unit 60, thereby preventing overheating of the second coupling unit 65 during operation of the scroll compressor 10. Furthermore, this prevents thermal damage to the second connection 145, particularly to a cured adhesive, especially if the second connection 145 is designed as a metallurgical bond.

[0037] In the Figures 2 and 3As an example, the second coupling unit 65 is designed to be slimmer than the first coupling unit 60 in the circumferential direction. This design has the advantage that the second coupling unit 65 remains within the effective range of the magnetic field 135 for a particularly long time, thereby ensuring particularly good magnetic coupling between the first coupling unit 60 and the second coupling unit 65.

[0038] Figure 4 shows a cross-sectional view along the in Figure 1 Section plane AA shown through a scroll compressor 10 according to a second embodiment in the 0° position.

[0039] The Scroll Compressor 10 is equipped with the in Figure 2 The orientation shown is illustrated. The scroll compressor 10 is essentially identical to the one in the Figures 1 to 3 The scroll compressor 10 shown is designed according to the first embodiment. The following discussion focuses exclusively on the differences of the [unclear] Figure 4scroll compressor 10 shown according to the second embodiment compared to the one shown in the Figures 1 to 3 first embodiment of the scroll compressor 10 shown.

[0040] In contrast to the Figures 1 to 3 The first coupling unit 60 has an arrangement of several layers 150 made of electrical steel. The second coupling unit 65 has, by way of example, the permanent magnet 131. The in Figure 4 The embodiment shown has the advantage that the mass rotating around the orbiter axis 55 is kept particularly low by the radially slim permanent magnet 131. This is in contrast to the Figures 1 to 3 The reduced mass of the second coupling unit 65 means that the bearing arrangement 35 is subjected to less mechanical stress when guiding the orbiter 20 around the orbiter axis 55. This allows for the use of a particularly durable scroll compressor 10.

[0041] In Figure 4In order to ensure particularly good magnetic coupling between the first coupling unit 60 and the second coupling unit 65, the first coupling unit 60 is wider in the radial and circumferential directions than the one shown in Figures 2 and 3 the first coupling unit 65 was trained.

[0042] Figure 5 shows the in Figure 4 shown sectional view along the in Figure 1 shown section plane AA through the scroll compactor 10.

[0043] In the 180° position, the distance a between the outer surface 160 and the inner surface 155 of the first coupling unit 60 is minimal. The wide circumferential design of the first coupling unit 60 ensures particularly good magnetic coupling between the first coupling unit 60 and the second coupling unit 65.

[0044] Figure 6shows a diagram of torques acting on orbiter 20 plotted against a swivel angle ω of orbiter 20 about the orbiter axis 55.

[0045] The respective torques MA, MK, MG are plotted against the swivel angle ω relative to the 0° position, starting at the 0° position. The orbiter 20 is swiveled from the 0° position, through the 180° position, towards a 360° position corresponding to the 0° position, while maintaining a swivel direction around the orbiter axis 55.

[0046] The diagram shows a first graph (dashed line) of a compressor torque MG versus the swivel angle ω, where the compressor torque MG is applied to the orbiter 20 and used to compress the fluid 110 in the working chamber 105. A second graph, shown as a solid line, represents a drive torque MA of the drive motor 25 acting about the orbiter axis 55 versus the swivel angle ω. A third graph, shown as a dashed line, represents a coupling torque MK of the coupling device 50, also plotted against the swivel angle ω and acting about the orbiter axis 55. The first graph corresponds to a drive torque of the drive motor of a scroll compressor according to the prior art.

[0047] The scroll compressor 10, during the pivoting movement of the orbiter 20 starting from the 0° position around the orbiter axis 55, has a first operating point 170 and a second operating point 175. The following briefly describes the operating procedure of the scroll compressor for a working space 105.

[0048] The example in the Figures 2 to 5 The orbiter 20 shown is pivoted about the orbiter axis 55. At the first operating point 170, the fluid 110 is essentially completely expelled from the working chamber 105 via the outlet 45. At the first operating point 170, the compressor torque MG for moving the orbiter 20 about the orbiter axis 55 reaches a first minimum 180. As an example, the first operating point 170 is reached after moving the orbiter 20 by a starting pivot angle ωS from the 0° position.

[0049] Between the first operating point 170 and the second operating point 175, the fluid 110, which is located in a (further) working chamber 105, is compressed. Between the first operating point 170 and the second operating point 180, the orbiter 20 is moved by a first swivel angle ω 1 about the orbiter axis 55. During compression, the compressor torque MG increases from the first minimum 180 to the first maximum 185. At the first maximum 185, the pressure of the fluid 110 in the working chamber 105 reaches a maximum pressure.

[0050] At the second operating point 175, the work chamber 105 reaches the outlet area 100. If the orbiter 20 is moved further around the orbiter axis 55 in the direction of rotation, the compressed fluid 110 is ejected from the work chamber 105 again via the rotation angle ω of the orbiter 20. During this process, the orbiter 20 is moved past the 0° position until the first operating point 170 is reached again. During the ejection, fluid 110 can be introduced radially outward on the orbiter 20, between the orbiter 20 and the stator 15, into a further radially outward-located work chamber 105, in order to then compress this fluid 110 again between the first operating point 170 and the second operating point 175. Due to the alternating compression and ejection, the compressor torque MG is wavy across the swivel angle ω and fluctuates between the first minimum of 180 and the first maximum of 185.The fluctuation in compressor torque MG places mechanical stress on the drive motor 25 and the bearing arrangement 35. Furthermore, a current ripple occurs when attempts are made to electrically regulate the ripple in compressor torque MG using a controller.

[0051] The coupling device 50 is designed to reduce this ripple of the compressor torque MG from the perspective of the drive motor, so that the functionality of the scroll compressor 10 is ensured, and the drive motor 25 is relieved.

[0052] The magnetic coupling of the first coupling unit 60 causes the magnetic attraction force F to fluctuate in value over the swivel angle ω with the second coupling unit 65 due to the movement of the orbiter 20. In the 0° position and the 180° position, the center of the second coupling unit 65 of a principal direction of extension in the tangential direction is located in a plane 200 (cf. Figures 2 and 3The center of the first coupling unit 60 is arranged tangentially to a principal extension direction. The attractive force F acts radially outwards in the plane 200. As a result, the third graph of the coupling torque MK exhibits a zero crossing in the coupling torque MK at both the 0° and 180° positions of the orbiter 20. Between the 0° and 180° positions, the center of the second coupling unit 65 is located outside the plane 200. The attractive force F thus exerts the coupling torque MK on the orbiter 20. Due to a decrease in the field strength of the magnetic field 135 with increasing distance a, in conjunction with an offset of the center of the second coupling unit 65 depending on the swivel angle ω, the coupling torque MK exhibits the fluctuating third graph with a second maximum 190 and a second minimum 195 as a function of the swivel angle ω.The coupling torque MK represents a torque for the drive motor 25, which the drive motor 25 has to provide in order to move the orbiter 20 around the orbiter axis 55 without fluid 110, even if the drive motor 25 only has to actuate the coupling device 50 (i.e., without compression of the fluid 110).

[0053] The coupling device 50 is oriented such that the second maximum 190 and the second minimum 195 of the coupling torque MK occur between the first operating point 170 and the second operating point during the compression of the fluid 110 in the working chamber 105 at the orbiter 20. In other words, the second coupling unit 65 is located closer to the first coupling unit 60 during the compression of the fluid 110 than during the ejection and introduction of the fluid 110 into the working chamber 105.

[0054] The following explains the acting torques MG, MK, and MA, starting at the first operating point 170. The drive torque MA, which the drive motor 25 must provide to drive the orbiter 20, corresponds to the sum of the compressor torque MG and the coupling torque MK. The compressor torque MG is the torque required to move the orbiter 20.

[0055] Between the 0° position and the 180° position, the coupling torque MK acts against the drive torque MA. Between the 180° position and a 360° position corresponding to the 0° position, the coupling torque MK assists the drive torque MA.

[0056] The coupling device 50 is arranged on the orbiter 20 and the housing 46 such that, upon reaching the first operating point 170, the coupling torque MK acts against the drive torque MA and in the direction of the compressor torque MG. Following the first operating point 170, the fluid 110 in the working chamber 105 is compressed, causing the pressure of the fluid 110 to increase. The compressor torque MG required for compression is, in this phase of the scroll compressor 10, close to the first minimum 180 and increases slowly. Between the first operating point 170 and the 180° position, i.e., at the beginning of compression, the coupling torque MK acts in the direction of the compressor torque MG and against the drive torque MA. Therefore, the drive motor 25 must apply the coupling torque MK in addition to the compressor torque MG to move the orbiter 20.

[0057] In the 180° position, which lies between the first operating point 170 and the second operating point 175 with respect to the swivel angle ω, the distance a between the first coupling unit 60 and the second coupling unit 65, as well as the attractive force F to the plane 200, is at its minimum. After passing through the 180° position, the coupling torque MK acts against the compressor torque MG, so that the drive torque MA is reduced by the coupling torque MK and the drive motor 25 is relieved of load. During this compression phase, before reaching the first maximum of the compressor torque MG, the coupling torque MK assists the drive motor 25.

[0058] Preferably, the second coupling unit 65 on the orbiter 20 is arranged such that a second swivel angle ω2 between the first operating point 170 and the second maximum 190 during compression is smaller than a third swivel angle ω3 between the second maximum 190 and the second operating point 175. Furthermore, the second minimum 195 can be reached in a fourth swivel angle ω4 before the second operating point 175, which may be smaller than the second swivel angle ω2 or the third swivel angle ω3. The first swivel angle ω1 between the first operating point 170 and the second operating point 175 for compressing the fluid 110 is larger than a fifth swivel angle ω5 between the second maximum 190 and the second minimum 195.

[0059] Due to the design of the coupling device 50 described above, the ripple of the drive torque MA is greatly reduced and the drive torque MA is significantly smoother than the compressor torque MG .

Claims

1. Scroll compressor (10), - having a stator (15), an orbiter (20) which is movable about an orbiter axis (55) relative to the stator (15), and a coupling device (50), - wherein the stator (15) and the orbiter (20) engage each in one another and delimit at least in portions at least one working space (105) for compressing a fluid (110) which is able to be filled into the working space (105), - wherein the coupling device (50) has a first coupling unit (60) disposed on the stator (15), and a second coupling unit (65) disposed opposite the first coupling unit (60) on the orbiter (20), - wherein the first coupling unit (60) is magnetically coupled to the second coupling unit (65), and the second coupling unit (65) directs a coupling torque (MK) acting about the orbiter axis (55) into the orbiter (20), characterized in that the scroll compressor has a drive motor (25), which is connected to the orbiter (20) in a torque-fitting manner, - in that the drive motor (25) is designed to provide a driving torque (MA) acting about the orbiter axis (55) in order to drive the orbiter (20), - in that the driving torque (MA) and the coupling torque (MG) act on the orbiter (20) so as to form a compressor torque (MG), - in that the orbiter (20), while maintaining a pivoting direction from a first position (0°) by way of a second position (180°), is able to be moved back to the first position (0°), - in that the coupling torque (MK) acts counter to the driving torque (MA) between the first position (0°) of the orbiter (20) and the second position (180°) of the orbiter (20), - in that in the second position (180°) the orbiter (20) is pivoted relative to the first position (0°), - in that the coupling torque (MK) and the driving torque (MA) act in the same direction between the second position (180°) and the first position (0°) of the orbiter (20).

2. Scroll compressor (10) according to the preceding claim, - wherein a gap (165) is disposed between the first coupling unit (60) and the second coupling unit (65).

3. Scroll compressor (10) according to one of the preceding claims, - wherein at least one of the two coupling units (60, 65) has a two-pole permanent magnet (131) or a multi-pole permanent magnet (131) for forming the magnetic coupling to the other coupling unit (60, 65).

4. Scroll compressor (10) according to one of the preceding claims, - wherein the first coupling unit (60) or the second coupling unit (65) has at least one laminated core (146) having at least two layers (150) of ferromagnetic material disposed next to one another in a stack, - wherein the layers (150) are disposed next to one another in the axial direction in terms of the orbiter axis (55).

5. Scroll compressor (10) according to one of the preceding claims, - wherein the stator (15) has a helically designed first wall (75) and the orbiter (20) has a helically designed second wall (85), - wherein the first wall (75) and the second wall (85) engage in one another and delimit the working space (105) at least in portions, - wherein the first coupling unit (60) is fastened to a housing (46) of the stator (15), and the second coupling unit (65) is fastened to a second outer circumferential side (140) of the second wall (85) of the orbiter (20).

6. Scroll compressor (10) according to one of the preceding claims, - wherein a centre of a maximum extent of the first coupling unit (60) is disposed in a plane (200), in a tangential direction relative to the orbiter axis (55), - wherein the orbiter axis (55) is disposed in the plane (200).

7. Method for operating a scroll compressor (10) according to one of the preceding claims, - wherein a fluid (110) is directed into the working space (105), - wherein the orbiter (20) is moved around the orbiter axis (55) and the fluid (110) is compressed in the working space (105), - wherein the coupling torque (MK) acts on the orbiter (20) by way of the magnetic coupling between the first coupling unit (60) and the second coupling unit (65).

8. Method according to Claim 7, - wherein the orbiter (20), while maintaining a pivoting direction from a first position (0°) by way of a second position (180°) about the orbiter axis (55), is moved to the first position (0°) again, - wherein a driving torque (MA) acting about the orbiter axis (55) is provided on the orbiter (20) in order to drive the orbiter (20), - wherein the driving torque (MA) and the coupling torque (MG) act conjointly on the orbiter (20) so as to form a compressor torque (MG), - wherein the coupling torque (MK) acts counter to the driving torque (MA) between the first position (0°) of the orbiter (20) and the second position (180°) of the orbiter (20), - wherein the coupling torque (MK) and the driving torque (MA) act in the same direction between the second position (180°) and the first position (0°) of the orbiter (20).

9. Method according to Claim 8, - wherein the fluid (110), between a first operating point (170) and a second operating point (175) chronologically following the first operating point (170), is compressed in the working space (105), - wherein the coupling torque (MK) at the first operating point (170), at the beginning of the compression of the fluid (110), acts counter to the driving torque (MA).

10. Method according to Claim 8 or 9, - wherein the fluid (110), between a first operating point (170) and a second operating point (175) chronologically following the first operating point (170), is compressed in the working space (105), - wherein at the second operating point (175), at an end of the compression of the fluid (110), the coupling torque (MK) acts in the same direction as the driving torque (MA) .