Scroll compressor and method for operating the scroll compressor

Abstract

The present invention relates to a scroll compressor (10) and a method for operating the scroll compressor (10), wherein the scroll compressor (10) has a stator (15), a moving scroll (20) capable of moving relative to the stator (15) about a moving scroll axis (55), and a coupling device (50), wherein the stator (15) and the moving scroll (20) are interlocked and at least segmentally define at least one working chamber (105) for compressing a fluid (110) injectable into a working chamber (105), wherein the coupling device (50) has a first coupling unit (60) arranged at the stator (15) and a second coupling unit (65) arranged opposite the first coupling unit (60) at the moving scroll (20), wherein the first coupling unit (60) is magnetically coupled to the second coupling unit (65) and the second coupling unit (65) applies a coupling torque (M) acting about the moving scroll axis (55). K ) is imported into the moving vortex body (20).

Description

Technical Field

[0001] The present invention relates to a scroll compressor and a method for operating the scroll compressor. Background Technology

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

[0003] The objective of this invention is to provide an improved scroll compressor and an improved method for operating the scroll compressor.

[0004] This task is accomplished by means of a scroll compressor described below and a method for operating the scroll compressor. Advantageous embodiments are also described below.

[0005] An improved scroll compressor can be provided in such a way that the scroll compressor has a stator, a moving scroll body capable of moving relative to the stator about a moving scroll body axis, and a coupling device, wherein the stator and the moving scroll body are interlocked and at least segmentally define at least one working chamber for compressing a fluid that can be injected into the working chamber, wherein the coupling device has a first coupling unit disposed at the stator and a second coupling unit disposed opposite to the first coupling unit at the moving scroll body, wherein the first coupling unit and the second coupling unit are magnetically coupled, and the second coupling unit introduces a coupling torque acting about the moving scroll body axis into the moving scroll body.

[0006] This allows for the provision of a particularly durable and smoothly operating scroll compressor. It also allows for a less demanding selection of the drive motor used to drive the moving scroll, particularly regarding its maximum torque. Consequently, the scroll compressor can be manufactured particularly easily and cost-effectively overall.

[0007] In another embodiment, the scroll compressor has a drive motor that is torque-locked to the moving scroll body. The drive motor is configured to provide a drive torque acting around the axis of the moving scroll body, which drives the moving scroll body. The drive torque and a coupling torque act on the moving scroll body to form the compressor torque. While maintaining the rotation direction, the moving scroll body can move from a first position through a second position back to the first position, wherein the coupling torque acts in the opposite direction to the drive torque between the first and second positions, wherein the moving scroll body is deflected relative to the first position in the second position, and wherein the coupling torque and drive torque are oriented in the same direction between the second and first positions. This reduces and smooths the uneven torque variation curve of the drive torque, particularly in the first order. Furthermore, current fluctuations are reduced in the power supply to the drive motor when adjusting it. This reduces the load on the drive motor driving the moving scroll body and the bearing assembly supporting the moving scroll body.

[0008] In another embodiment, a gap is arranged between the first coupling unit and the second coupling unit. This keeps the wear of the scroll compressor relatively small.

[0009] In another embodiment, at least one of the two coupling units has a bipolar or multipolar permanent magnet for magnetic coupling with the other coupling unit. This design has the advantage of being particularly compact and accommodating fewer components.

[0010] In another embodiment, the first or second coupling unit has at least one lamination group, the at least one lamination group having at least two layers of ferromagnetic material arranged side by side in the stack. The layers are arranged side by side in the axial direction about the axis of the scroll compressor. This design has the advantage that only a small amount of eddy current is generated in the lamination group during the operation of the scroll compressor, thereby avoiding overheating of the coupling unit with the lamination group.

[0011] In another embodiment, the stator has a helically constructed first wall and the moving scroll body has a helically constructed second wall, wherein the first and second walls interlock and at least segmentally define a working cavity, wherein the first coupling unit is fixed to the stator housing and the second coupling unit is fixed to the second outer peripheral side of the second wall of the moving scroll body. It is particularly advantageous that the fixing is constructed, for example, by material locking. Furthermore, arranging the second coupling unit on the second outer peripheral side of the second wall has the advantage that, in this region, the second wall does not restrict the working cavity on its outer surface, and therefore there is sufficient structural space to accommodate the coupling device. Moreover, the external structural space of the scroll compressor is not expanded due to the placement of the coupling device on its inner surface.

[0012] In another embodiment, the center of the first coupling unit, which extends tangentially relative to the axis of the moving vortex, is arranged in a plane, wherein the axis of the moving vortex is arranged in this plane.

[0013] The aforementioned scroll compressor can operate by introducing fluid into the working chamber, wherein the moving scroll moves around the axis of the moving scroll and compresses the fluid in the working chamber, wherein the coupling torque is applied to the moving scroll through the magnetic coupling between the first coupling unit and the second coupling unit.

[0014] Particularly advantageous is that, while maintaining the direction of rotation about the axis of the moving scroll body, the moving scroll body is moved from a first position through a second position back to the first position, wherein a driving torque acting about the axis of the moving scroll body is provided at the moving scroll body to drive the moving scroll body, wherein the driving torque and the coupling torque act together on the moving scroll body to form a compressor torque, wherein between the first position and the second position of the moving scroll body, the coupling torque acts in the opposite direction to the driving torque, and wherein between the second position and the first position, the coupling torque and the driving torque are oriented in the same direction.

[0015] In another embodiment, the fluid in the working chamber is compressed between a first operating point and a second operating point that follows the first operating point in time, wherein at the first operating point, when the compression of the fluid begins, the coupling torque acts in the opposite direction to the drive torque. This allows for a particularly significant reduction in the variability of the drive torque. Attached Figure Description

[0016] The invention will now be explained in detail with reference to the accompanying drawings. Herein:

[0017] Figure 1A schematic diagram of a scroll compressor according to a first embodiment is shown;

[0018] Figure 2 It shows the passage through the 0° position. Figure 1 The scroll compressor shown in the image Figure 1 The cross-sectional view of section plane AA shown in the figure;

[0019] Figure 3 It shows the path along the passage in a 180° position. Figure 1 The scroll compressor shown in the image Figure 1 The cross-sectional view of section plane AA shown in the figure;

[0020] Figure 4 This illustrates a scroll compressor according to the second embodiment, positioned at 0°. Figure 1 The cross-sectional view of section plane AA shown in the figure;

[0021] Figure 5 This illustrates a scroll compressor according to the second embodiment, positioned at 180°. Figure 1 The section AA shown in the figure Figure 4 The sectional view shown;

[0022] Figure 6 The torque variation curve is shown for the rotation angle of the moving scroll body of the scroll compressor around the axis of the moving scroll body. Detailed Implementation

[0023] Figure 1 A schematic diagram of a scroll compressor 10 according to a first embodiment is shown.

[0024] The scroll compressor 10 has a stator 15, a moving scroll body 20, a drive motor 25, a drive shaft 30, a bearing device 35, an inlet 40, an outlet 45, a housing 46, and a coupling device 50.

[0025] The stator 15 is fixed in position and stationary, and is mechanically connected to the housing 46 of the scroll compressor 10. The moving scroll 20 is torsionally connected to the drive shaft 30, which torsionally connects the drive motor 25 to the moving scroll 20. The drive shaft 30 is supported in a manner rotatable about the axis 55 of the moving scroll. The moving scroll 20 is eccentrically arranged relative to the axis 55. When the drive motor 25 is activated, the moving scroll 20 is guided and rotated about the axis 55. The bearing assembly 35 is configured to support the forces from the moving scroll 20, which is eccentrically guided about the axis 55.

[0026] Figure 2 It shows the passage through the 0° position. Figure 1 The scroll compressor 10 shown in the figure Figure 1 The cross-sectional view of section plane AA shown in the figure.

[0027] The stator 15 has a first substrate 70 and a first wall 75. The first substrate 70 extends substantially in a plane of rotation perpendicular to the axis 55 of the moving scroll. Axially, the first substrate 70 is arranged opposite to the drive motor 25 and mechanically connected to the housing 46. The first wall 75 is helically guided around the axis 55 of the moving scroll and is axially positioned on one side of the first substrate 70 and connected to it. The first substrate 70 and the first wall 75 can be uniformly and integrally manufactured from a non-magnetic material, such as aluminum. An inlet 40 is arranged radially outward from the first wall 75 between the first wall 75 and the first housing 46. An outlet 45 is arranged substantially at the center of the first substrate 70 relative to the axis 55 of the moving scroll.

[0028] Inlet 40 can be fluidly connected, for example, to the coolant circuit of the heat pump. Through inlet 40, fluid 110, especially coolant, such as R410, can be introduced into the scroll compressor 10 in a preferably gaseous state. Outlet 45 can be fluidly connected, for example, to the heat exchanger of the heat pump.

[0029] The moving vortex body 20 has a second substrate 80 (in Figure 1 (shown in) and second wall 85 (see Figure 2 The second wall 85 is spirally guided around the axis 55 of the moving vortex body. The second wall 85 is axially connected to the second substrate 80 on one side. The second substrate 80 is axially offset from the first substrate 70. Here, the second wall 85 is located on the axial side facing the stator 15 and thus on the side opposite to the first substrate 70 of the second substrate 80. Preferably, the second substrate 80 and the second wall 85 are uniformly and integrally manufactured, for example, from a non-magnetic material, such as aluminum.

[0030] The first substrate 70 and the second substrate 80 are arranged axially offset from each other. A first wall 75 and a second wall 85 are arranged axially between the first substrate 70 and the second substrate 80 such that the first wall 75 and the second wall 85 fit together. The first wall 75 and the second wall 85, together with the first substrate 70 and the second substrate 80, define an inlet region 90, a compressor region 95, an outlet region 100, and a movement space 101. The inlet region 90 is located downstream of the inlet 40 and upstream of the compressor region 95. In the compressor region 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 second walls 75, 85 define a plurality of working chambers 105 arranged circumferentially separated from each other relative to the axis 55 of the moving vortex body. The outlet region 100 is adjacent to the downstream side of the compressor region 95. An outlet 45 opens into the outlet region 100. The movement space 101 is arranged radially outward of the second wall 85 and defined radially outward by a housing 46. The motion space 101 ensures that there is sufficient structural space inside the housing profile 125 of the housing 46 for the eccentric movement of the second wall 85 relative to the stator 15 and the housing 46 without causing the second wall 85 to collide with the housing 46 or the stator 15.

[0031] In the assembled state of the scroll compressor 10, for example in a heat pump, fluid 110 is introduced into the inlet region 90 through inlet 40. The fluid 110 flows circumferentially toward the compressor region 95 along the first outer peripheral side 115 of the first wall 75. The compressor torque M is... G When introduced into the moving scroll 20, the moving scroll 20 moves in an eccentric motion around the moving scroll axis 55. Here, in conjunction with the stationary stator 15, the working chamber 105 moves in the circumferential direction and follows the radially inward spiral structure of the first wall 75. As the stroke increases, the volume of the corresponding working chamber 105 decreases, and the fluid 110 present in the working chamber 105 is compressed. The compressed fluid 110 is conveyed in the working chamber 105 to the outlet region 100 and discharged from the scroll compressor 10 via the outlet 45.

[0032] The coupling device 50 has a first coupling unit 60 and a second coupling unit 65. The first coupling unit 60 is arranged on the inner side of the housing profile 125 of the housing 46 of the stator 15 and is mechanically connected to the housing 46. Figure 2In this embodiment, the first coupling unit 60 exemplarily has a multi-pole permanent magnet 131 oriented tangentially to the axis 55 of the moving vortex body in its main extension direction. The multi-pole permanent magnet 131 has multiple north and south poles, which are arranged alternately side by side along the tangential direction. The first coupling unit 60 is preferably mechanically connected to the housing profile 125 by means of a first material locking connection 130. The first coupling unit 60 provides a magnetic field 135 through the multi-pole permanent magnet 131, which in... Figure 2 The magnetic field 135 is schematically outlined using dashed lines. It extends radially into the motion space 101.

[0033] The second coupling unit 65 is arranged radially inwardly opposite the first coupling unit 60 in the motion space 101. The second coupling unit 65 is located at the second outer peripheral side 140 of the second wall 85 and is connected to the second outer peripheral side 140 by means of a second connection 145. Preferably, the second connection 145 can be a material locking connection and / or a shape locking connection. In particular, the second coupling unit 65 can be fixed at the second outer peripheral side 140 by means of an adhesive connection.

[0034] The second coupling unit 65 is made of ferritic material. Preferably, the second coupling unit 65 has an arrangement structure consisting of multiple layers 150, which are made of ferritic material, such as electrical steel sheets. The layers 150 are arranged axially side by side in a stack. Additionally, it is possible to set... Figure 2 The retaining device, not shown, is used to connect the multiple electrical steel sheet layers 150 to each other and thereby ensure that the second coupling unit 65 is reliably fixed at the second wall 85.

[0035] As Figure 2 An alternative to the design of the second coupling unit 65 with multiple electrical steel sheet layers 150 shown in the diagram is that the second coupling unit 65 can also have another permanent magnet, which has, for example, the same or similar number of poles as the permanent magnet 131 of the first coupling unit 60. However, the difference is that the pole arrangement of this other permanent magnet is opposite to that of the permanent magnet 131 of the first coupling unit 60. Therefore, the south pole is arranged facing the second coupling unit 65 in a radial direction opposite, for example, the north pole of the permanent magnet 131.

[0036] The first coupling unit 60 has an inner surface 155 on the side facing the second wall 85, wherein the inner surface 155 is exemplarily located on... Figure 2The inner surface 155 is flat. When facing the inner surface 155 radially, the second coupling unit 65 has an outer surface 160 on the side opposite to the second wall 85, wherein the outer surface 160 is exemplarily flat. Both the inner surface 155 and the outer surface 160 are exemplarily oriented tangentially to the axis 55 of the moving vortex body. Furthermore, the inner surface 155 and the outer surface 160 are arranged facing each other radially. A gap 165 is formed between the inner surface 155 and the outer surface 160. The gap 165 is defined radially by the distance 'a' between the inner surface 155 and the outer surface 160. Figure 2 In the middle, the distance 'a' between the inner side 155 and the outer side 160 is maximized.

[0037] The gap 165 ensures that the inner surface 155 does not contact the outer surface 160 when the moving vortex 20 moves around the moving vortex axis 15. This prevents wear, especially metal particles, from entering the fluid 110. Furthermore, it ensures that the second coupling unit 65 can still be removed from the first coupling unit 60 despite magnetic coupling.

[0038] exist Figure 2 The diagram shows the moving vortex 20 in a 0° position regarding its motion around the axis 55 of the moving vortex. In the 0° position, the spacing a is maximized. Here, for example, the second coupling unit 65 is arranged outside the effective range of the magnetic field 135, thereby substantially eliminating the magnetic coupling between the first coupling unit 60 and the second coupling unit 65.

[0039] Figure 3 It shows the path along the passage in a 180° position. Figure 1 The scroll compressor 10 shown in the figure Figure 1 The cross-sectional view of section plane AA shown in the figure.

[0040] exist Figure 3 In the middle, the moving vortex body 20 is relative to Figure 2 The diagram shown is deflected by 180° and is therefore in a 180° position. In this position, the distance 'a' between the inner surface 155 of the first coupling unit 60 and the outer surface 160 of the second coupling unit 65 is minimized. The second coupling unit 65 is within the range of the magnetic field 135, causing the first coupling unit 60 and the second coupling unit 65 to be magnetically coupled. Figure 3 In the middle, the second coupling unit 65 is attracted by the permanent magnet 131 of the first coupling unit 60 with force F.

[0041] The multi-layered structure of the second coupling unit 65 and the radial orientation of layer 150 relative to the axis 55 of the moving scroll have the following advantages: eddy currents are avoided when the second coupling unit 65 moves in the magnetic field 135 of the first coupling unit 60, and thus overheating of the second coupling unit 65 is avoided during the operation of the scroll compressor 10. Furthermore, this avoids thermal damage to the second connection 145, especially the hardened adhesive, particularly when the second connection 145 is designed as a material-locking connection.

[0042] exist Figure 2 and 3 In this design, the second coupling unit 65 is exemplary to be more elongated in the circumferential direction than the first coupling unit 60. This design has the advantage that the second coupling unit 65 moves within the influence of the magnetic field 135 for a particularly long period, thereby ensuring particularly good magnetic coupling between the first coupling unit 60 and the second coupling unit 65.

[0043] Figure 4 The image shows a scroll compressor 10 according to the second embodiment passing through the 0° position. Figure 1 The cross-sectional view of section plane AA shown in the figure.

[0044] Scroll compressor 10 in Figure 2 The orientation shown is illustrated in the diagram. The scroll compressor 10 is essentially the same as that according to the first embodiment. Figures 1 to 3 The scroll compressor 10 shown in the figure has the same construction. Only the following discussion focuses on... Figure 4 The scroll compressor 10 shown according to the second embodiment is relative to the scroll compressor 10 in Figures 1 to 3 The difference is shown in the first embodiment.

[0045] and Figures 1 to 3 The difference lies in that the first coupling unit 60 has an arrangement of multiple layers 150, each layer being made of electrical steel sheets. The second coupling unit 65 exemplarily has a permanent magnet 131. Figure 4 The design shown has the advantage that the mass rotating about the axis 55 of the moving vortex body is kept particularly small by the radially elongated permanent magnet 131. This is due to the relative position of the second coupling unit 65. Figures 1 to 3 The reduced mass results in a smaller mechanical load on the bearing assembly 35 when the moving scroll 20 is guided around the axis 55 of the moving scroll. This enables the provision of a particularly durable scroll compressor 10.

[0046] exist Figure 4 In 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 constructed in the radial direction and in the circumferential direction to be larger than that in the second coupling unit 65. Figure 2 and 3 The first coupling unit in the middle is 65mm wide.

[0047] Figure 5 It shows the path along the scroll compressor 10 Figure 1 The section AA shown in the figure Figure 4 The sectional view shown.

[0048] At the 180° position, the distance 'a' between the outer surface 160 and the inner surface 155 of the first coupling unit 60 is minimized. The wide circumferential structure of the first coupling unit 60 achieves particularly good magnetic coupling between the first coupling unit 60 and the second coupling unit 65.

[0049] Figure 6 A graph showing the torque acting at the moving vortex 20 is presented, plotted with respect to the rotation angle ω around the axis 55 of the moving vortex 20.

[0050] Here, with reference to the 0° position, the corresponding torque M starting at the 0° position is plotted with respect to the rotation angle ω. A M K M G While maintaining the rotation direction around the axis 55 of the moving vortex body, the moving vortex body 20 is rotated from the 0° position through the 180° position to the 360° position corresponding to the 0° position.

[0051] The compressor torque M is plotted in this graph with respect to the rotation angle ω. G The first curve (dashed line), where the compressor torque M G Loaded at the moving scroll 20 and used to compress the fluid 110 in the working chamber 105. The driving torque M of the drive motor 25 acting around the axis 55 of the moving scroll 55 is plotted as a solid line with respect to the rotation angle ω. A The second curve. The dotted line shows the coupling torque M of the coupling device 50 acting around the axis 55 of the moving vortex body and plotted with respect to the rotation angle ω. K The third curve. The first curve corresponds to the drive torque of the drive motor of a scroll compressor according to the prior art.

[0052] When the moving scroll 20 rotates around the axis 55 of the moving scroll 20 from the 0° position, the scroll compressor 10 has a first operating point 170 and a second operating point 175. The working method of the scroll compressor for the working chamber 105 is briefly discussed below.

[0053] Exemplarily make in Figures 2 to 5The moving scroll body 20 shown rotates about the moving scroll body axis 55. At the first operating point 170, fluid 110 is discharged from the working chamber 105 almost completely through the outlet 45. At the first operating point 170, the compressor torque M for moving the moving scroll body 20 about the moving scroll body axis 55 is... G The first minimum value of 180 was reached. The moving vortex body 20 moved from the 0° position by the initial rotation angle ω. S Then, for example, the first working point 170 is reached.

[0054] Between the first operating point 170 and the second operating point 175, the fluid 110 arranged in the (other) operating chamber 105 is compressed. Between the first operating point 170 and the second operating point 180, the moving scroll 20 is moved around the moving scroll axis 55 by a first rotation angle ω1. During compression, the compressor torque M... G The pressure increases from a first minimum value of 180 to a first maximum value of 185. At the first maximum value of 185, the pressure of the fluid 110 in the working chamber 105 reaches its maximum value.

[0055] At the second operating point 175, the working chamber 105 reaches the outlet region 100. If the moving scroll 20 continues to move around the moving scroll axis 55 in the direction of rotation, the compressed fluid 110 will be discharged from the working chamber 105 again within the range of the rotation angle ω of the moving scroll 20. Here, the moving scroll 20 moves past the 0° position until it reaches the first operating point 170 again. During discharge, fluid 110 can be introduced into the working chamber 105 further outward radially at the radially outer side of the moving scroll 20, between the moving scroll 20 and the stator 15, so that the fluid 110 can be compressed again between the first operating point 170 and the second operating point 175. Through alternating compression and discharge, the compressor torque M G The rotation angle ω is wavy and fluctuates between a first minimum of 180° and a first maximum of 185°. This is due to the compressor torque M. G The fluctuations cause mechanical loads on the drive motor 25 and bearing assembly 35. On the other hand, attempts are made to electrically adjust the compressor torque M using a regulator. G When there are fluctuations in the current, current fluctuations occur.

[0056] Coupling device 50 is configured to reduce compressor torque M from the perspective of the drive motor. G The fluctuation of the scroll compressor 10 is reduced, thus ensuring its functionality and reducing the load on the drive motor 25.

[0057] The magnetic coupling of the first coupling unit 60 results in the magnetic attraction F, in terms of its value, fluctuating within the range of the rotation angle ω, along with the second coupling unit 65, due to the motion of the moving vortex body 20. In the 0° and 180° positions, the center of the second coupling unit 65, with respect to its main extension direction along the tangential direction, and the center of the first coupling unit 60, with respect to its main extension direction along the tangential direction, are arranged together in plane 200 (see...). Figure 2 and Figure 3 The attractive force F acts radially outward in plane 200. Therefore, the coupling torque M... K The third curve has a coupling torque M at the 0° and 180° positions of the moving vortex body 20, respectively. K The zero-crossing point. Between the 0° and 180° positions, the center of the second coupling unit 65 is positioned outside the plane 200. Therefore, the coupling torque M... K The attractive force F acts on the moving vortex body 20. Since the field strength of the magnetic field 135 decreases as the spacing a increases, combined with the offset of the center of the second coupling unit 65 depending on the rotation angle ω, the coupling torque M... K A fluctuating third curve exists within the range of the rotation angle ω, with a second maximum value of 190° and a second minimum value of 195°. Coupling torque M K The following torque of the drive motor 25 is described here: the drive motor 25 must apply this torque so that the moving vortex 20 can move around the moving vortex axis 55 even when the drive motor 25 only needs to operate the coupling device 50 (i.e. without compressing the fluid 110).

[0058] The coupling device 50 is oriented in such a way that the coupling torque M K The second maximum value 190 and the second minimum value 195 are loaded onto the moving vortex body 20 between the first operating point 170 and the second operating point during the compression of the fluid 110 in the working chamber 105. In other words, the second coupling unit 65 is arranged closer to the first coupling unit 60 during the compression of the fluid 110 than during the discharge of the fluid 110 and its introduction into the working chamber 105.

[0059] The following explains the torque M that begins to take effect at the first operating point of 170°. G M K M A The driving torque M that the drive motor 25 must apply to drive the moving vortex body 20 A Equivalent to compressor torque M G and coupling torque M K The sum of the compressor torque M. G This is the torque required to make the moving vortex 20 move.

[0060] Between the 0° and 180° positions, the coupling torque M K Opposite to driving torque M A It is effective. Between the 180° position and the 360° position corresponding to the 0° position, the coupling torque M... K To provide auxiliary driving torque M A Its function.

[0061] The coupling device 50 is arranged at the moving vortex body 20 and the housing 46 such that the coupling torque M is coupled when the first operating point 170 is reached. K Reverse to driving torque M A And along the compressor torque M G The direction of the compression is affected. Immediately following the first operating point 170, the fluid 110 in the working chamber 105 is compressed, increasing the pressure of the fluid 110. During this stage of the scroll compressor 10, the compressor torque M required for compression... G It approaches the first minimum value of 180 and increases slowly. Between the first operating point of 170° and 180°, i.e., at the start of compression, the coupling torque M... K Along the compressor torque M G The direction and opposite to the driving torque M A It works. Therefore, besides the compressor torque M... G In addition, the drive motor 25 must also apply a coupling torque M K So that the vortex body 20 can move.

[0062] At the 180° position with respect to the rotation angle ω between the first operating point 170 and the second operating point 175, the distance 'a' between the first coupling unit 60 and the second coupling unit 65 and the attractive force F relative to the plane 200 are minimized. After passing the 180° position, the coupling torque M... K Reverse to compressor torque M G This is to take effect, making the driving torque M A Through coupling torque M K This reduces the load on the drive motor 25, thus lessening the coupling torque M. K During this compression phase, when the compressor torque M is reached... G The first maximum value is before the auxiliary drive motor 25.

[0063] Preferably, the second coupling unit 65 is arranged at the moving vortex body 20 such that the second rotation angle ω2 during compression between the first operating point 170 and the second maximum value 190 is smaller than the third rotation angle ω3 between the second maximum value 190 and the second operating point 175. Furthermore, the second minimum value 195 can be reached in a fourth rotation angle ω4 before the second operating point 175, which can be smaller than either the second rotation angle ω2 or the third rotation angle ω3. The first rotation angle ω1 between the first operating point 170 and the second operating point 175 for compressing the fluid 110 is greater than the fifth rotation angle ω5 between the second maximum value 190 and the second minimum value 195.

[0064] Through the configuration described above for the coupling device 50, the driving torque M A The volatility is greatly reduced, and the driving torque M A Compressor torque M G It is noticeably smoother.

Claims

1. Scroll compressor (10) - It has a stator (15), a moving vortex (20) capable of moving relative to the stator (15) about the axis (55) of the moving vortex body, and a coupling device (50), and - It has a drive motor (25), which is torque-locked to the moving scroll body (20). - wherein the stator (15) and the moving vortex body (20) are interlocked and at least segmentally define at least one working chamber (105), the at least one working chamber (105) being used for the compression of a fluid (110) injectable into the working chamber (105). -The coupling device (50) therein has a first coupling unit (60) arranged on the stator (15) and a second coupling unit (65) arranged opposite to the first coupling unit (60) on the moving vortex body (20). - wherein the first coupling unit (60) is magnetically coupled to the second coupling unit (65), and the second coupling unit (65) generates a coupling torque (M) acting around the axis (55) of the moving vortex body. K ) is introduced into the moving vortex body (20), -The drive motor (25) is configured to provide a driving torque (M) acting around the axis (55) of the moving vortex body. A The driving torque (M) A ) is used to drive the moving vortex body (20). - wherein the driving torque (M) A ) and the coupling torque (M K The torque (M) acts on the moving scroll body (20) to generate compressor torque. G ), -The moving vortex (20) is capable of moving from the first position back to the first position via the second position while maintaining the direction of rotation. -wherein, between the first position and the second position of the moving vortex body (20), the coupling torque (M) K ) in the opposite direction to the driving torque (M) A )kick in, - wherein the moving vortex (20) is deflected relative to the first position in the second position, -wherein, between the second position and the first position of the moving vortex body (20), the coupling torque (M) K ) and the driving torque (M A They are oriented in the same direction.

2. The scroll compressor (10) according to claim 1. -A gap (165) is arranged between the first coupling unit (60) and the second coupling unit (65).

3. The scroll compressor (10) according to claim 1 or 2. - At least one of the first coupling unit (60) and the second coupling unit (65) has a bipolar permanent magnet (131) or a multipolar permanent magnet (131) to form a magnetic coupling with the other coupling unit (60, 65).

4. The scroll compressor (10) according to claim 1 or 2. -The first coupling unit (60) or the second coupling unit (65) has at least one stack (146), the at least one stack (146) having at least two layers (150) of ferromagnetic material arranged side by side in the stack. - wherein the layers (150) are arranged side by side in the axial direction about the axis (55) of the moving vortex body.

5. The scroll compressor (10) according to claim 1 or 2. -The stator (15) has a first wall (75) constructed in a helical shape and the moving vortex (20) has a second wall (85) constructed in a helical shape. - wherein the first wall (75) and the second wall (85) are fitted together and at least segmentally define the working cavity (105). - wherein the first coupling unit (60) is fixed at the housing (46) of the stator (15), and the second coupling unit (65) is fixed at the second outer peripheral side (140) of the second wall (85) of the moving vortex body (20).

6. The scroll compressor (10) according to claim 1 or 2. -The center of the maximum extension of the first coupling unit (60) relative to the axis (55) of the moving vortex body in the tangential direction is arranged in the plane (200). -The axis (55) of the moving vortex body is arranged in the plane (200).

7. A method for operating the scroll compressor (10) according to any one of claims 1 to 6, -The fluid (110) is introduced into the working chamber (105). -In this process, the moving vortex body (20) moves around the axis (55) of the moving vortex body and compresses the fluid (110) in the working chamber (105). -The coupling torque (M) is generated through magnetic coupling between the first coupling unit (60) and the second coupling unit (65). K ) acts on the moving vortex body (20), -While maintaining the rotational direction around the axis (55) of the moving vortex body, the moving vortex body (20) is moved from the first position back to the first position via the second position. -In order to drive the moving vortex (20), a driving torque (M) acting around the axis (55) of the moving vortex (20) is provided on the moving vortex (20). A ), - wherein the driving torque (M) A ) and the coupling torque (M K The combined forces act on the moving scroll body (20) to generate the compressor torque (M). G ), -wherein, between the first position and the second position of the moving vortex body (20), the coupling torque (M) K ) in the opposite direction to the driving torque (M) A )kick in, -wherein, between the second position and the first position of the moving vortex body (20), the coupling torque (M) K ) and the driving torque (M A Same orientation.

8. The method according to claim 7, -The fluid (110) in the working chamber (105) is compressed between the first working point (170) and the second working point (175) that follows the first working point (170) in time. -Where, at the first operating point (170), at the start of compression of the fluid (110), the coupling torque (M) K ) in the opposite direction to the driving torque (M) A )kick in.

9. The method according to claim 7 or 8, -The fluid (110) in the working chamber (105) is compressed between the first working point (170) and the second working point (175) that follows the first working point (170) in time. -Where, at the second operating point (175), at the end of the compression of the fluid (110), the coupling torque (M) K ) and the driving torque (M A They work in the same direction.

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