A damping device, a torsional vibration damping coupling, and a screw compressor

Abstract

The application discloses a damping device, a torsional vibration damping coupling and a screw compressor. The damping device comprises a positive stiffness elastic element and a negative stiffness elastic element which are arranged in parallel, and the mounting height of the positive stiffness elastic element and the negative stiffness elastic element is the same. The male screw rotor of the screw compressor and the motor rotor are coaxially connected through the torsional vibration damping coupling with the damping device, so that static torque transmission and dynamic fluctuation torque isolation can be realized between the motor rotor and the male screw rotor. Therefore, the mutual influence of excitation coupling and speed pulsation between the motor rotor and the screw rotor can be reduced, the negative influence of motor tooth slot torque fluctuation on screw rotor engagement is reduced, the screw engagement working condition is effectively improved, and vibration and noise are reduced. The motor rotor and the male screw rotor are both supported by simple beams, which is beneficial to reducing motor rotor dynamic eccentricity and reducing the vibration of the screw compressor motor.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of reducing vibration caused by torque transmission, and in particular to a vibration reduction device capable of reducing torsional vibration caused by rotor speed fluctuation, a torsional vibration reduction coupling having the vibration reduction device, and a screw compressor using the torsional vibration reduction coupling. BACKGROUND

[0002] At present, screw compressors are increasingly widely used in commercial refrigeration fields, but how to control the magnitude of the vibration and noise of the screw compressor is increasingly concerned by users. In view of the characteristics of the vibration and noise of the screw compressor of a traditional structure, it is found that the main prominent contribution frequency in the vibration acceleration and noise sound pressure level spectrum of the screw compressor is the meshing frequency of the screw rotors and the harmonic frequency thereof, that is, the generation of the vibration and noise of the screw compressor is mainly related to the meshing of the screw rotors. Further research shows that the speed fluctuation is one of the important factors affecting the meshing force of the meshing machine. Therefore, people reduce the speed fluctuation of the screw rotor system, improve the running stability, reduce the screw meshing force, and thus reduce the vibration and noise of the screw compressor.

[0003] The male rotor of the traditional screw compressor and the motor shaft are the same rigid shaft, the bearings are arranged at the left and right ends of the screw rotors, and the motor rotor is a cantilever beam support structure. This arrangement of the rotor has a simple structure, but the motor tooth slot torque pulsation and the pulsation of the screw gas load torque and the meshing excitation are superimposed on the same rigid shaft formed by the motor rotor and the male rotor, that is, they are coupled to each other to deteriorate the meshing of the male and female rotors of the screw, and thus intensify the speed fluctuation and generate greater vibration and noise. Further, the cantilever beam support structure of the motor rotor is prone to dynamic eccentricity at high speed, which makes the motor stator-rotor air gap uneven and generates unbalanced magnetic pull, further intensifying the motor vibration.

[0004] Therefore, how to overcome the defects of the severe speed fluctuation of the male and female rotors of the screw compressor, the serious vibration and noise, and the intensification of the motor vibration due to the cantilever beam support of the motor rotor is a problem to be solved in the field. SUMMARY

[0005] In order to solve the technical problem of the severe speed fluctuation of the male and female rotors of the existing screw compressor and the serious vibration and noise, the present application provides a vibration reduction device capable of realizing static torque transmission and dynamic fluctuation torque isolation, a torsional vibration reduction coupling having the vibration reduction device, and a screw compressor using the torsional vibration reduction coupling. At the same time, the support of the motor rotor and the male rotor of the screw is improved to reduce the dynamic eccentricity of the motor rotor, thereby reducing the vibration of the compressor motor.

[0006] The application provides a damping device, which comprises a positive stiffness elastic element and a negative stiffness elastic element arranged in parallel, and the mounting height of the positive stiffness elastic element and the negative stiffness elastic element is the same.

[0007] Preferably, the positive stiffness element is a ring-shaped elastic element, and the negative stiffness elastic element is a disc spring; the disc spring is arranged in the inner circle of the ring-shaped elastic element.

[0008] Preferably, the positive stiffness element is a ring-shaped elastic element, and the negative stiffness elastic element is a disc spring; the ring-shaped elastic element and the disc spring are arranged side by side.

[0009] Preferably, the ratio of the height and the thickness of the disc spring is greater than 1.5.

[0010] Preferably, the ratio of the height and the thickness of the disc spring is 2.75.

[0011] Preferably, the ring-shaped elastic element is a rubber ring or a metal rubber ring.

[0012] The application further provides a torsional vibration damping coupling with the damping device, which comprises a load end connecting half shaft and a driving end connecting half shaft, the outer circle of the load end connecting half shaft radially extends at least one first stress plate, the outer circle of the driving end connecting half shaft radially extends at least one second stress plate, and the first and second stress plates are connected to each other to form a pair of connecting structures; at least one set of the damping device is arranged between the first and second stress plates, and the second stress plate of the driving end connecting half shaft first transmits driving force to the first stress plate through the damping device and then drives the load end connecting half shaft to rotate.

[0013] Preferably, the second stress plate on the driving end connecting half shaft is provided with an open slot, and the first stress plate on the load end connecting half shaft is inserted into the open slot of the second stress plate to form the connecting structure.

[0014] Preferably, the first stress plate on the load end connecting half shaft is provided with an open slot, and the second stress plate on the driving end connecting half shaft is inserted into the open slot of the first stress plate to form the connecting structure.

[0015] Preferably, the connecting structure can be two pairs, three pairs or four pairs.

[0016] Preferably, the connecting structure is connected and fixed by bolts.

[0017] The application further provides a screw compressor adopting the torsional vibration damping coupling, which comprises a screw male rotor and a motor rotor.

[0018] Preferably, the motor rotor is a simply supported beam support structure.

[0019] The application adopts a segmented structure for the screw male rotor and the motor rotor of the screw compressor and uses the torsional vibration damping coupling with the damping device to coaxially connect the screw male rotor and the motor rotor, so that the static torque transmission and the dynamic fluctuation torque isolation can be realized between the motor rotor and the screw male rotor. Thus, the mutual influence of the excitation coupling and the speed pulsation between the motor rotor and the screw rotor can be reduced, the negative influence of the motor tooth slot torque fluctuation on the meshing of the screw rotor can be reduced, the meshing working condition of the screw is effectively improved, and the vibration and noise are reduced. In addition, bearings are arranged at both ends of the motor rotor and both segments of the screw male rotor, i.e., the simply supported beam support structure is adopted for the two segments of the rotor. Therefore, the concentricity of the two segments of the rotor is better, which is beneficial to reducing the dynamic eccentricity of the motor rotor, and the air gap between the motor stator and rotor is more uniform, the unbalanced magnetic pull is reduced, and the vibration of the compressor motor is smaller. BRIEF DESCRIPTION OF DRAWINGS

[0020] Figure 1a It is a three-dimensional schematic view of an embodiment of the damping device of the application;

[0021] Figure 1b It is a three-dimensional schematic view of another embodiment of the damping device of the application;

[0022] Figure 2 It is a sectional view of the disc spring;

[0023] Figure 3 It is a sectional view of an embodiment of the screw compressor of the application;

[0024] Figure 4 It is an exploded view of the torsional vibration damping coupling with the damping device of the application;

[0025] Figure 5 It is Figure 4 an assembly view;

[0026] Figure 6 It is a total stiffness characteristic curve of the damping device of the application.

[0027] 1 is a screw male rotor left bearing, 2 is a screw male rotor, 3 is a screw male rotor right bearing, 4 is a motor rotor left bearing, 5 is a torsional vibration damping coupling, 6 is a motor rotor, and 7 is a motor rotor right bearing;

[0028] 51 is a load end connecting half shaft, 511 is a first force plate, 52 is a locking nut, 53 is a drive end connecting half shaft,

[0029] 531 is an upper second force plate, 532 is a lower second force plate, 54 is a bolt, 55 is a nut, 56 is a ring elastic element, and 57 is a disc spring. DETAILED DESCRIPTION

[0030] The application will be further described in conjunction with the embodiments and drawings, but it does not constitute a limitation to the application.

[0031] As shown in Figure 1a , Figure 1b and Figure 2 , an embodiment of a vibration damping device provided by the application is shown, which includes a positive stiffness elastic element and a negative stiffness elastic element arranged in parallel, and the installation height of the positive stiffness elastic element and the negative stiffness elastic element is the same. That is, when installed, the upper planes of the positive stiffness elastic element and the negative stiffness elastic element are in the same plane; the lower planes of the positive stiffness elastic element and the negative stiffness elastic element are also in the same plane. According to the needs, the positive stiffness element in the embodiment adopts a ring elastic element 56, and the negative stiffness elastic element adopts a disc spring 57. Please refer to Figure 1a , the disc spring 57 is placed in the inner circle of the ring elastic element 56 to form a set of vibration damping devices. As shown in Figure 1b , the disc spring 57 can also be arranged in parallel with the ring elastic element 56 to form a set of vibration damping devices. That is, the vertical distance from the lower surface to the upper surface of the ring elastic element 56 and the disc spring 57 is the installation height of the two elastic elements. Whether it is a set of arrangement or a parallel arrangement structure, it is necessary to ensure that the installation height of the positive and negative stiffness elastic elements is the same. According to the needs, multiple sets of vibration damping devices can also be used together, and the installation height of the multiple sets of vibration damping devices used together also needs to be the same. Generally, the ring elastic element 57 can adopt a rubber ring or a metal rubber ring. As shown in Figure 2 , the ratio of the height h and the thickness t of the disc spring 57 needs to be greater than 1.5. In the embodiment, the ratio of the height and the thickness of the disc spring 57 is 2.75. The stiffness characteristics of the ring spring element 56 can be designed according to the torque of the motor and the screw load.

[0032] As shown in Figure 3 , the torsional vibration damping coupling 5 provided by the application with a vibration damping device is applied to the torsional vibration damping between the motor rotor and the screw male rotor in the screw compressor. The screw compressor provided by the application adopts a segmented structure for the screw male rotor 2 and the motor rotor 6, and the motor rotor 6 is coaxially connected with the screw male rotor 2 into an integrated body through the torsional vibration damping coupling 5 provided by the application.

[0033] Please refer toFigure 4 、 Figure 5 The first embodiment of the torsional vibration damping coupling 5 with damping device is provided. The torsional vibration damping coupling 5 includes a load end connecting half shaft 51 connected with the male screw rotor 2 in the screw compressor through a key, and a driving end connecting half shaft 53 connected with the motor rotor 6 in the screw compressor through a key. In order to connect the load end connecting half shaft 51 and the driving end connecting half shaft 53, the outer circle of the load end connecting half shaft 51 radially extends a first force plate 511, and the outer circle of the driving end connecting half shaft 53 radially extends a second force plate, such as the upper second force plate 531 shown in Figure 4 . That is, the second force plate in this embodiment adopts a single piece structure, rather than a double piece structure with an open slot shown in Figure 4 . The first force plate 511 and the second force plate are connected to each other to form a pair of connecting structures. At least one set of the damping device is arranged between the first force plate 511 and the second force plate, that is, at least one set of the damping device can be arranged in a sleeving manner (as shown in Figure 1a ) or in parallel (as shown in Figure 1b ). The specific placement position of the damping device needs to be placed according to the input rotation direction of the driving end connecting half shaft 53. It is necessary to make the second force plate of the driving end connecting half shaft 53 first transmit driving force to the first force plate 511 through the damping device and then drive the load end connecting half shaft 51 to rotate. That is, the damping device must be subjected to pressure to transmit driving force during transmission. The annular elastic element 56 and the butterfly spring 57 are installed at the same height and are arranged between the first force plate 511 and the second force plate (such as the upper second force plate 531). When the driving shaft (the motor rotor 6) transmits torque, the first force plate 511 and the second force plate make the annular elastic element 56 and the butterfly spring 57 be compressed at the same time. Only when the negative stiffness elastic element, the butterfly spring 57, bears compression to transmit load can its negative stiffness characteristic be embodied. When the rotation direction of the driving end connecting half shaft 53 changes, the installation of the driving end connecting half shaft 53, the load end connecting half shaft 51 and the damping device needs to be adjusted accordingly. Only when the damping device bears compression to transmit load, can the setting ensure the purpose of static torque transmission and dynamic fluctuation torque isolation of the present application. For example, by referring to Figure 5As shown, the screw rotor 2 shaft segment is first projected axially onto the motor rotor 6 shaft segment. The drive end connecting half-shaft 53 rotates clockwise with the motor rotor 6. A vibration damping device, consisting of an annular elastic element 56 and a disc spring 57, is positioned between the upper second force plate 531 and the first force plate 511. If the drive end connecting half-shaft 53 rotates counterclockwise with the motor rotor 6, the upper second force plate 531 needs to be placed below the first force plate 511 during installation, and then the vibration damping device is positioned between the first force plate 511 and the upper second force plate 531. Both installation methods are designed to ensure that when the drive end connecting half-shaft 53 inputs torque, its upper second force plate 531 first transmits the driving force to the first force plate 511 through the vibration damping device before driving the load end connecting half-shaft 51 to rotate.

[0034] like Figure 4 , Figure 5 The diagram shows a second embodiment of the torsional vibration damping coupling 5 with a vibration damping device provided by the present invention. The torsional vibration damping coupling 5 includes a load-end connecting half-shaft 51 connected to the screw male rotor 2 and a drive-end connecting half-shaft 53 connected to the motor rotor 6. To connect the load-end connecting half-shaft 51 and the drive-end connecting half-shaft 53, at least one first force-bearing plate 511 extends radially from the outer circle of the load-end connecting half-shaft 51, and at least one second force-bearing plate extends radially from the outer circle of the drive-end connecting half-shaft 53. The first force-bearing plate 511 and the second force-bearing plate are connected to each other to form a pair of connection structures. The difference is that the second force-bearing plate on the drive-end connecting half-shaft 53 has an opening slot, so that the second force-bearing plate has a parallel upper second force-bearing plate 531 and lower second force-bearing plate 532 double-piece structure, and the first force-bearing plate 511 on the load-end connecting half-shaft 51 is inserted into the opening slot formed by the upper and lower second force-bearing plates 531 and 532 to form a connection structure. Similar to the first embodiment, when the drive-end connecting half-shaft 53 rotates clockwise with the motor rotor 6, a vibration damping device consisting of an annular elastic element 56 and a disc spring 57 is positioned between the upper second force-bearing plate 531 and the first force-bearing plate 511. When the drive-end connecting half-shaft 53 rotates counterclockwise with the motor rotor 6, the vibration damping device is positioned between the lower second force-bearing plate 532 and the first force-bearing plate 511. This arrangement ensures that regardless of the direction of rotation of the motor rotor 6, the second force-bearing plate of the drive-end connecting half-shaft 53 first transmits the driving force to the first force-bearing plate 511 through the vibration damping device, and then drives the load-end connecting half-shaft 51 to rotate. Alternatively, the first force-bearing plate 511 on the load-end connecting half-shaft 51 can be configured as a double-plate structure with an open slot, while the second force-bearing plate on the drive-end connecting half-shaft is a single-plate structure, inserted into the open slot of the first force-bearing plate 511 to form the connection structure. The installation of vibration damping devices must adhere to the principle that the vibration damping devices must be subjected to pressure during the transmission process to transmit the driving force.

[0035] As Figure 4 shown in the second embodiment of the torsional vibration damping coupling 5 with the damping device, four first force plates 511 are provided on the load end connecting half shaft 51 and evenly arranged along the outer circumference of the load end connecting half shaft 51, and the upper and lower second force plates 531, 532 of the double-plate structure on the corresponding drive end connecting half shaft 53 also have four first force plates 511. Then the first force plates 511 and the upper and lower second force plates 531, 532 can be connected to each other to form four pairs of connecting structures. According to the condition of transmitting driving torque, the connecting structures can also be symmetrically arranged or evenly arranged in two pairs or three pairs, etc. Screw holes are opened on the first force plates 511 and the upper and lower second force plates 531, 532 of the connecting structures, and the first and second force plates can be connected and fixed by bolts 54 and nuts 55.

[0036] As Figure 3 shown is a preferred embodiment of the screw compressor with the torsional vibration damping coupling 5 provided by the application, the screw male rotor 2 and the motor rotor 6 adopt a segmented structure, and the motor rotor 6 is coaxially connected with the screw male rotor 2 into an integrated body through the torsional vibration damping coupling 5 with the damping device provided by the application. It is important that the motor rotor 6 and the screw male rotor 2 are both simply supported beam support structures. That is, the screw left bearing 1 and the screw right bearing 3 are respectively arranged at the two ends of the screw male rotor 2, and the motor left bearing 4 and the motor right bearing 7 are respectively arranged at the two ends of the motor rotor 6. Since the two ends of the motor rotor 6 and the two sections of the screw male rotor 2 both adopt a simply supported beam support structure, the concentricity of the two sections of the rotor is better, which is conducive to reducing the dynamic eccentricity of the motor rotor 6, and at the same time, the air gap of the motor stator 6 is more uniform, the unbalanced magnetic pull is reduced, and the vibration of the screw compressor motor is smaller.

[0037] As Figure 3 , Figure 4 , Figure 5As shown, the torque damping coupling 5 provided by this invention is used in semi-open machinery. That is, several sections of the machine body are connected by flanges in the axial direction, and the half-shafts are connected by a coupling device. The installation sequence of the torque damping coupling 5 of this invention is as follows: First, install the load-end connecting half-shaft 51 onto the shaft end of the screw male rotor 2. Lock the load-end connecting half-shaft 51 at the shaft end of the screw male rotor 2 with a locking nut 52 to prevent axial movement. The load-end connecting half-shaft 51 and the screw male rotor 2 are connected by a key to achieve circumferential limitation. Then, insert the first force plate 511 between the upper and lower second force plates 531 and 532 on the drive-end connecting half-shaft 53. Simultaneously, install the annular elastic element 56 and the disc spring 57 between the upper second force plate 531 and the first force plate 511. Connect and fix the first force plate 511, the upper and lower second force plates 531 and 532, the annular elastic element 56, and the disc spring 57 with bolts 54 and nuts 55. In other words, the above operations fix both the load-side connecting half-shaft 51 and the drive-side connecting half-shaft 53 in the circumferentially symmetrical direction. Finally, the shaft segment of the load-side screw male rotor 2 (with the torque damping coupling 5 installed) is aligned and brought close to the shaft segment of the drive-side motor rotor 6, so that the shaft segment of the motor rotor 6 is inserted into the inner hole of the drive-side connecting half-shaft 53. The shaft segment of the motor rotor 6 and the drive-side connecting half-shaft 53 are circumferentially limited by a key connection, while the external body is fixed by a flange. Through the above installation, the load-side connecting half-shaft 51 is axially locked and limited by the locking nut 52, and the drive-side connecting half-shaft 53 is fixedly connected to the load-side connecting half-shaft 51 by bolts 54 and nuts 55, thus effectively constraining the drive-side connecting half-shaft 53.

[0038] The torsional vibration damping coupling 5 with vibration damping device provided by this invention is mainly used to reduce the transmission of motor torque fluctuations to the screw rotor system and to reduce the impact of speed fluctuations on screw meshing. Specifically, this is achieved by setting an annular elastic element 56 with positive stiffness characteristics and a disc spring 57 with negative stiffness characteristics between the drive end half shaft and the load end half shaft.

[0039] like Figure 6 As shown, the overall stiffness characteristic curve of the vibration damping device provided by the present invention is displayed. The positive stiffness characteristic curve of the annular elastic element 56 is also shown. Figure 6 As shown by the dashed line. The stiffness is approximately linear over a fairly wide deformation range, meaning it always exhibits positive stiffness characteristics; while the stiffness characteristic curve of the disc spring 57, with a height-to-thickness ratio greater than 1.5, is as follows... Figure 6 As shown by the double-dotted line. When the torque is small and the deformation deflection of disc spring 57 is small, it also exhibits positive stiffness characteristics, as shown in "segment 1-2" of its curve; the total stiffness characteristic of the parallel connection of positive and negative stiffness elements is... Figure 6The total stiffness characteristic corresponding to this moment is approximately linear stiffness, as shown in the "A-B" section. As the load increases, the compression of the annular elastic element 56 and the disc spring 57 also increases, and the stiffness of the disc spring 57 exhibits a negative stiffness characteristic, as shown in the "2-3" section of the curve. At this time, the total stiffness characteristic curve of the annular elastic element 56 and the disc spring 57 after superposition is shown in the "B-C" section of the curve. The balance position of the vibration damping device under load is usually designed near the midpoint "O" of the "B-C" curve. The "O" point is the midpoint of the "2-3" section of the curve of the negative stiffness elastic element 57. The load corresponding to the "O" point on the total stiffness characteristic curve "B-C" section is the balance load or static load, which is the static load transmitted by the vibration damping device. The parallel arrangement of the annular elastic element 56 and the disc spring 57 obtains a relatively wide deflection range near the balance position, and the load changes little.

[0040] By Figure 6 It can be seen that the positive and negative stiffness element parallel vibration damping device provided by the application has the following advantages. When the device is slightly deformed under load, it exhibits a rigid characteristic, as shown in the "A-B" section of the total stiffness characteristic curve, and can thus transmit an increased static torque. When the load increases, the device is in the "B-C" section of the total stiffness characteristic curve, and if a dynamic fluctuation torque occurs, it will be absorbed by the flexibility of the positive and negative stiffness element parallel vibration damping device, that is, the device deforms greatly, but the load does not increase correspondingly, so that the transmission of the dynamic fluctuation torque can be isolated. That is, the stiffness in the approximately straight "B-C" section of the total stiffness characteristic curve is very small, and as the disturbance increases, the load changes little, which is equivalent to the fluctuating deflection of the positive and negative stiffness parallel elastic element being compensated by deformation. Since the load changes little, the transmitted torque is stable, which plays a damping role, that is, the fluctuating torque from the driving shaft to the load shaft is isolated, thereby reducing the influence of motor gear slot torque ripple on screw engagement, improving the stability of screw engagement, and reducing vibration and noise. When the device is in the "B-C" section of the total stiffness characteristic curve, it can bear the transmission of the static load.

[0041] The torsional vibration damping coupling with damping device is used for coaxially connecting the male screw rotor of the screw compressor and the motor rotor, so that the static torque transmission and the dynamic fluctuation torque isolation between the motor rotor and the male screw rotor can be realized. Since the large rotor static stiffness is beneficial to the torque transmission, but the large stiffness is not conducive to the vibration isolation, and the small stiffness is conducive to the vibration isolation. The positive and negative stiffness elements are connected in parallel, so that after the torsional displacement of the driving shaft and the load shaft is balanced, the static torque is borne by the positive stiffness element, and the negative stiffness element is used, so that the overall damping device has small stiffness at the balance position, so that the fluctuation torque isolation effect is good. Thus, the mutual influence of the excitation coupling and the speed fluctuation between the motor rotor and the screw rotor can be reduced, the negative influence of the motor tooth slot torque fluctuation on the meshing of the screw rotor is reduced, the working condition of the screw meshing is effectively improved, and the vibration and noise are reduced.

[0042] The above only describes the embodiments of the present application, and is not used to limit the present application. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present application shall be included in the protection scope of the present application.

Claims

1. A torsional vibration damping coupling, characterized in that, The device includes a load-end connecting half-shaft and a drive-end connecting half-shaft. At least one first force-bearing plate extends radially from the outer circle of the load-end connecting half-shaft, and at least one second force-bearing plate extends radially from the outer circle of the drive-end connecting half-shaft. The first and second force-bearing plates are connected to each other to form a pair of connection structures. At least one set of vibration damping devices is disposed between the first and second force-bearing plates, so that the second force-bearing plate of the drive-end connecting half-shaft first transmits driving force to the first force-bearing plate through the vibration damping device and then drives the load-end connecting half-shaft to rotate.

2. The torsional vibration damping coupling as described in claim 1, characterized in that, The vibration damping device includes a positive stiffness elastic element and a negative stiffness elastic element arranged in parallel, and the positive stiffness elastic element and the negative stiffness elastic element are installed at the same height.

3. The torsional vibration damping coupling as described in claim 2, characterized in that, The positive stiffness elastic element is a ring-shaped elastic element, and the negative stiffness elastic element is a disc spring; the disc spring is disposed in the inner circle of the ring-shaped elastic element.

4. The torsional vibration damping coupling as described in claim 2, characterized in that, The positive stiffness elastic element is a ring-shaped elastic element, and the negative stiffness elastic element is a disc spring; the ring-shaped elastic element and the disc spring are placed side by side.

5. The torsional vibration damping coupling as described in claim 3 or 4, characterized in that, The ratio of the height to the thickness of the disc spring is greater than 1.

5.

6. The torsional vibration damping coupling as described in claim 5, characterized in that, The ratio of the height to the thickness of the disc spring is 2.

75.

7. The torsional vibration damping coupling as described in claim 3 or 4, characterized in that, The annular elastic element is a rubber ring.

8. The torsional vibration damping coupling as described in claim 3 or 4, characterized in that, The annular elastic element is a metal rubber ring.

9. The torsional vibration damping coupling as described in claim 1, characterized in that, The second force-bearing plate on the drive end connecting half shaft is provided with an opening slot, and the first force-bearing plate on the load end connecting half shaft is inserted into the opening slot of the second force-bearing plate to form the connection structure.

10. The torsional vibration damping coupling as described in claim 1, characterized in that, The first force-bearing plate on the load-end connecting half-shaft is provided with an opening slot, and the second force-bearing plate on the drive-end connecting half-shaft is inserted into the opening slot of the first force-bearing plate to form the connection structure.

11. The torsional vibration damping coupling as described in claim 1, characterized in that, The connection structure consists of two, three, or four pairs.

12. The torsional vibration damping coupling as described in claim 1, characterized in that, The connection structure uses bolts to connect and fix the first and second load-bearing plates.

13. A screw compressor, comprising a screw male rotor and a motor rotor, characterized in that, The motor rotor and screw The male rotor is segmented, and the motor rotor is connected to the screw male rotor via a torsional vibration damping coupling as described in any one of claims 1 to 12.

14. The screw compressor as described in claim 13, characterized in that, The motor rotor is a simply supported beam structure.

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