US20250059974A1

US20250059974A1 - Scroll compressor

Info

Publication number: US20250059974A1
Application number: US18/725,356
Authority: US
Inventors: Yusong Sun; Li Yao; Wanzhen Liu; Yan Lin; Xishuang Zhang; Sanxiang Liu
Original assignee: Danfoss Tianjin Ltd
Current assignee: Danfoss Tianjin Ltd
Priority date: 2021-12-31
Filing date: 2022-12-29
Publication date: 2025-02-20
Also published as: DE112022006266T5; WO2023125811A1

Abstract

A scroll compressor includes a compressor shell; a frame (4) installed in the compressor shell; a first scroll (5) located in the compressor shell; and a second scroll (6) located in the compressor shell and being co-rotatable with the first scroll (5), to define a compression chamber (56) between the first scroll (5) and the second scroll (6), the second scroll (6) having a hub (41) that extends downward from a lower surface thereof; a transformer flange (8) supported on the frame and supporting the first scroll (5) and the second scroll (6), the transformer flange (8) being connected to the first scroll (5); an actuating mechanism (7) installed in the compressor shell and connected to the transformer flange (8), for driving the transformer flange (8) to rotate, so that the first scroll (5) and the second scroll (6) are driven to co-rotate; a crankshaft (9) assembly located in the transformer flange (8) and including an oil screw (10), an upper end (101) of the oil screw (10) being fitted with a hub (61) of the second scroll (6), a lower end of the oil screw (10) extending into an oil sump (31); and a plurality of supports (11, 12, 13, 14, 15, 16), such as bearings or bushings or gaskets, located on the same side of the compression chamber (56).

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a National Stage application of International Patent Application No. PCT/CN2022/143402, filed on Dec. 29, 2022, which claims priority to Chinese Patent Applications No. 202111681231.X, filed on Dec. 31, 2021, and No. 202123449502.7, filed on Dec. 31, 2021, each of which is hereby incorporated by reference in its entirety.

TECHNICAL FIELD

The present disclosure relates to a scroll compressor.

BACKGROUND

Conventional co-rotating scroll compressors (CRC) are large in volume and therefore occupy a relatively big space.

SUMMARY

The present disclosure is aimed to solve the above-mentioned problems and potential other technical problems.
According to an aspect of the present disclosure, it provides a scroll compressor. The scroll compressor includes:

- a compressor shell;
- a frame installed in the compressor shell;
- a scroll assembly including:
- a first scroll located in the compressor shell; and
- a second scroll located in the compressor shell and being co-rotatable with the first scroll, to define a compression chamber between the first scroll and the second scroll;
- a flange rotatably supported on the frame and supporting the first scroll and the second scroll, the flange being connected to the first scroll; and
- an actuating mechanism installed in the compressor shell and connected to the flange, for driving the flange to rotate, so as to drive the first scroll to rotate so that the first scroll drives the second scroll to co-rotate, wherein the actuating mechanism includes an axial-flux motor.

In an embodiment, the axial-flux motor may be a disc motor. In particular, the axial-flux motor includes: a stator fixed on the frame, and a rotor connected to the flange for driving the flange to rotate.
In an embodiment, the rotor is located below the stator. The axial-flux motor has a rotational speed ranging from 0 rpm to 40000 rpm.
In an embodiment, the rotor and the flange are connected by interference fit, and the stator and the frame are connected by screws. The stator includes a stator yoke, a stator tooth, a stator supporting ring and windings wound on the stator teeth.
In an embodiment, the stator further includes winding frames mounted around the stator teeth, and the windings are wound on the winding frames.
In an embodiment, the stator yoke is fixedly connected to the stator supporting ring, and the stator supporting ring and the compressor shell are connected by interference fit.
In an embodiment, the stator is accommodated in the frame, threaded holes are provided on an outer edge of the frame and the stator supporting ring so that the frame and the stator supporting ring are fixedly connected by screws.
In an embodiment, heat dissipation ribs are provided on an outer surface of the stator. The heat dissipation ribs are components made separately from the stator, or integrally formed with the stator.
In an embodiment, the rotor includes permanent magnets, a rotor yoke and a rotor hub, wherein the permanent magnets are held and fixed by the rotor yoke, and the rotor hub and the flange are connected by interference fit.
According to another aspect of the present disclosure, it provides a scroll compressor.
The scroll compressor includes:

- a compressor shell;
- a frame installed in the compressor shell;
- a scroll assembly including: a first scroll located in the compressor shell; and a second scroll located in the compressor shell and being co-rotatable with the first scroll, to define a compression chamber between the first scroll and the second scroll;
- a flange rotatably supported on the frame and supporting the first scroll and the second scroll, the flange being connected to the first scroll; and
- an actuating mechanism installed in the compressor shell and connected to the flange, for driving the flange to rotate, the flange driving the first scroll to rotate so that the first scroll drives the second scroll to co-rotate, wherein the actuating mechanism includes a radial-flux motor.

The technical solutions of the present disclosure allow for a more compact scroll compressor.

BRIEF DESCRIPTION OF THE DRAWINGS

In order to facilitate understanding of the present disclosure, the present disclosure will be described below based on exemplary embodiments and in conjunction with the accompanying drawings. The same or similar reference numerals used in the accompanying drawings refer to the same or similar parts. It should be understood that the accompanying drawings are schematic only.

FIG. 1A is a longitudinal section view of a scroll compressor according to an exemplary embodiment of the present disclosure;

FIG. 1B is an exploded view of the scroll compressor shown in FIG. 1A, in which some components are omitted to make this view more clear;

FIG. 2 is a schematic view showing a suction path, a discharge path and a lubrication path of the scroll compressor shown in FIG. 1A;

FIG. 3 is a perspective view of a second scroll shown in FIG. 1B;

FIG. 4 is a longitudinal section view of a portion of the scroll compressor according to the exemplary embodiment of the present disclosure;

FIG. 5A, FIG. 5B, FIG. 5C and FIG. 5D are respectively a perspective view, a side view, a top view, and a cross-sectional view taken along a plane C-C in FIG. 5B of a stator of a disc motor according to the exemplary embodiment of the present disclosure;

FIG. 6A, FIG. 6B, FIG. 6C and FIG. 6D are respectively a perspective view, a side view, a top view, and a cross-sectional view taken along a plane D-D in FIG. 6B of a rotor of the disc motor according to the exemplary embodiment of the present disclosure;

FIG. 7A and FIG. 7B are respectively atop view and a side view of another modification of the stator shown in FIG. 5A;

FIG. 8A and FIG. 8B are respectively atop view and a side view of another modification of the stator shown in FIG. 5A;

FIG. 9A and FIG. 9B are respectively atop view and a side view of another modification of the stator shown in FIG. 5A; and

FIG. 10 is a longitudinal section view of a scroll compressor according to another exemplary embodiment of the present disclosure.

DETAILED DESCRIPTION

Specific embodiments and modifications of the present disclosure are described in detail with reference to the accompanying drawings below.

[Overall Structure of the Scroll Compressor]

FIG. 1A is a longitudinal section view of the scroll compressor according to an exemplary embodiment of the present disclosure. FIG. 1B is an exploded view of the scroll compressor shown in FIG. 1A, in which some components are omitted to make this view clearer. FIG. 3 is a perspective view of a second scroll shown in FIG. 1B from another angle.
As shown in FIG. 1A and FIG. 1B, the scroll compressor according to the present disclosure includes a compressor shell, and a frame 4, a scroll assembly (5,6), an actuating mechanism 7, a flange 8, a plurality of supports (such as bearings or bushings or gaskets) 11,12,13,14,15,16, a crankshaft 9, etc. installed in the compressor shell.
Specifically, the compressor shell includes an upper shell 1, a middle shell 2, and a lower shell 3. A discharge outlet 1001 is provided on the upper shell 1. A discharge chamber 1002 is formed between the upper shell 1 and an upper surface of the middle shell 2. A suction inlet 2001 is provided on the middle shell 2 for suction of fluids (e.g. refrigerant). An oil sump 31 is formed at the bottom of the lower shell 3 for storage of the lubricating oil. The middle shell 2 and the lower shell 3 form an enclosed space in which the frame 4, the scroll assembly (5,6), the actuating mechanism 7, the flange 8, the plurality of supports 11,12,13,14,15,16, the crankshaft 9, etc. are accommodated. In addition, a plurality of feet 32 are provided on the bottom surface of the lower shell 3, and a fixing hole 33 is provided on each foot 32 to fix the lower shell 3 to a support (e. g. ground) by fasteners such as the fixing screw.
The frame 4 includes a hub 41 and supporting arm(s) 42. A plurality of threaded holes 43 are provided on an upper surface of the supporting arm(s) 42. In addition, an oil leakage hole 44 is provided on the bottom surface at the connection part between the supporting arm 42(s) and a hub 41. The frame 4 can be fixed into the lower shell 3 of the compressor, such as into the lower shell 3 by the lower end of the hub 41.
The scroll assembly includes both the first scroll 5 and the second scroll 6. The second scroll 6 is co-rotatable with the first scroll 5 to define a compression chamber 56 between the first scroll 5 and the second scroll 6. The first scroll 5 has a downward extending wrap 51 and a central hole 52 on the top thereof. The second scroll 6 has a downward extending hub 61 and an upward extending wrap 62. The wraps 51 and 62 engages each other to form the compression chamber 56.
The flange 8 is supported on the frame 4 and includes a tray 81, a hub 82, and a central hole 83. Convex part(s) 831 and concave part(s) 832 can be provided in the central hole 83. The upper surface 811 of tray 81 supports the first scroll 5 and the second scroll 6. Specifically, the flange 8 can be connected to the first scroll 5 via the tray 81 to drive the first scroll 5 to rotate.
The actuating mechanism 7 can be an axial-flux motor (e.g., a disc motor) or a radial-flux motor (e.g., an interior permanent magnet motor). The rotational speed of the actuating mechanism 7 can reach 40,000 rpm.
According to an exemplary embodiment of the present disclosure, the disc motor includes a stator 71 and a rotor 72. The stator 71 can be fixed to the frame 4 or, optionally, directly fixed to the inner wall of the middle shell 2. A central hole 722 of the rotor 72 is fixedly connected with the hub 82 of the flange 8 (e.g. by interference fit, spline fit, etc.) to drive the flange 8 to rotate, and thus to drive the first scroll 5 and the second scroll 6 to co-rotate. For example, the first scroll 5 is driven to rotate, and gas force generated by the rotation of the first scroll 5 drives the second scroll 6 to co-rotate.
The crankshaft 9 is located in the central hole 83 of the flange 8. The upper end of the crankshaft 9 is connected to the hub 61 of the second scroll 6. In addition, the scroll compressor can also include an oil screw 10. An upper end 101 of the oil screw 10 is connected in a matching manner with the hub 61 of the second scroll 6, and a lower end 103 of the oil screw 10 extends into the oil sump 31.
The crankshaft 9 is generally cylindrical and has an axial through hole 91, an upper segment 92, and a lower segment 93. The oil screw 10 is provided in the axial through hole 91, and the central axis O₂of the oil screw 10 is parallel to but does not coincide with the central axis O₁of the crankshaft 9. In other words, the oil screw 10 is provided eccentrically with respect to the crankshaft 9. Outer and inner diameters of the upper segment 92 of the crankshaft 9 are larger than outer and inner diameters of the lower segment 93 respectively, thus forming an outer step surface 95 at the junction of the upper segment 92 and the lower segment 93. A return oil hole 97 is provided on the upper end face 94 of the crankshaft 9. The oil return hole 97 extends downward through the upper segment 92 and the lower segment 93, thus forming the oil return passages 99 and 100.
In the exemplary embodiment of the present disclosure, all of the supports 11,12,13,14,15,16 can be provided on the same side of the compression chamber 56. In the view of FIG. 1A, these supports are located on the lower side of the compression chamber 56.
Specifically, these supports can include a first sliding bearing 11, a second sliding bearing 12 and a third sliding bearing 13. The first sliding bearing 11 is located between the inner circumferential surface of the upper segment 92 of the crankshaft 9 and the outer circumferential surface of the hub 61 of the second scroll 6. The second sliding bearing 12 is located between the inner circumferential surface of the central hole 83 of the flange 8 and the outer circumferential surface of the upper segment 92 of the crankshaft 9. The third sliding bearing 13 is located between the inner circumferential surface of the central hole 83 of the flange 8 and the outer circumferential surface of the lower segment 93 of the crankshaft 9.
A pin groove 96 is provided on the inner surface of the upper segment 92 of the crankshaft 9. The pin 19 is embedded in the pin groove 96 and is fitted with the driving surface 111 of the first sliding bearing 11. The first sliding bearing 11 may include a substantially cylindrical sleeve body and a bearing sleeve fitted in the sleeve body by interference fit. The second sliding bearing 12 could be provided with concave part(s) 121 and convex part(s) 122 on the outer circumferential surface. The concave part(s) 121 and the convex part(s) 122 are configured to fit with the concave part(s) 831 and the convex part(s) 832 in the central hole 83 of the flange 8 respectively. In this way, the second sliding bearing 12 is driven by the flange 8 to rotate when the flange 8 rotates. The second sliding bearing 12 may include a substantially cylindrical sleeve body and a bearing sleeve fitted in the sleeve body by interference fit.
These supports (such as bearings or bushings or gaskets) can further include a first thrust support 15, a second thrust support 14 and a third thrust support 16. The first thrust support 15 is located between the inner step surface 84 of the flange 8 and the outer step surface 95 of the crankshaft 9. The second thrust support 14 is located between the lower surface of the second scroll 6 and the upper surface 811 of the tray 81 of the flange 8. The third thrust support 16 is located between the bottom surface of the flange 8 and the junction of the hub 41 and the supporting arm(s) 42 of the frame 4.
One or more of the first thrust support 15, the second thrust support 14 and the third thrust support 16 can be configured in the form of a thrust gasket or thrust bearing. Taking the first thrust support 15 as an example, as shown in FIG. 1B, the first thrust support 15 is configured in the form of a thrust gasket. The upper surface of the first thrust support 15 are provided with a plurality of oil grooves 151 staggered from a plurality of oil grooves 151 on the lower surface of the first thrust support 15 for storing lubricating oil in order to form an oil film on the surfaces of the friction pair. The oil groove 151 shown in FIG. 1B is generally rectangular in shape. It should be understood that the oil groove 151 can also be round or other suitable shapes. Configuration of other thrust supports 14 and 16 can be similar to that of the first thrust support. In addition, the material constituting the thrust supports may be wear-resistant metallic or non-metallic material.
The hub 61 of the second scroll 6 has an inner hole 610 (see FIG. 3 ) which has an inner shape matching the outer shape of the upper end 101 of the oil screw 10, thus allowing the upper end 101 of the oil screw 10 to fit into the inner hole 610. Specifically, the outer circumferential surface of the upper end 101 of the oil screw 10 can fit by interference fit with the inner circumferential surface of the inner hole 610 of the hub 61 of the second scroll 6, preventing the oil screw 10 from rotating with respect to the second scroll 6.
Optionally, as shown in FIG. 1B, the outer circumferential surface of the upper end 101 of the oil screw 10 includes a first plane 1011, and accordingly, the inner circumferential surface of the inner hole 610 of the hub 61 of the second scroll 6 includes a second plane 611 (see FIG. 3 ). When the upper end 101 of the oil screw 10 is fitted into the inner hole 610 of the hub 61 of the second scroll 6, the first plane 1011 and the second plane 611 press against each other, preventing the oil screw 10 from rotating with respect to the second scroll 6.
In addition, a stop 102 is provided on the outer circumferential surface of the upper end 101 of the oil screw 10. As shown in FIG. 3 , a clip groove 612 is provided on the inner circumferential surface of the inner hole 610 of the hub 61 of the second scroll 6, and a clip 20 is provided in the clip groove 612. When the upper end 101 of the oil screw 10 is fitted into the inner hole 610 of the hub 61 of the second scroll 6, the stop 102 is embedded into the clip groove 612, and the stop 102 can be caught by the clip 20 from below, preventing the upper end 101 of the oil screw 10 from falling out of the inner hole 610 of the hub 61 of the second scroll 6.
The scroll compressor according to the present disclosure further includes a protective sleeve 17. As shown in FIG. 1A, a wall 171 of the protective sleeve 17 is located between the suction inlet 2001 and the scroll assembly to avoid damage to the scroll assembly by direct impact of fluid, such as refrigerant, 1 when the fluid is suctioned by the scroll compressor. As shown in FIG. 1B, the protective sleeve 17 has a cylindrical thin-walled shape in general, with the wall 171 and a lower flange 172. A plurality of threaded holes (or through holes) 173 are provided on the lower flange 172. These threaded holes 173 correspond to the plurality of threaded holes 712 on the supporting ring 711 of the stator 71, and the protective sleeve 17 and the stator 71 can be fixed to the frame 4 by means of a plurality of screws 18.
As shown in FIG. 1A, a radial through hole 90 is provided on the crankshaft 9. The radial through hole 90 has one end opening on the outer circumferential surface of the crankshaft 9, and another end opening on the inner circumferential surface of the axial through hole 91 of the crankshaft 9. In addition, another one or more radial through hole 98 are provided on the crankshaft 9. Each of the radial through holes 98 has one end opening on the outer circumferential surface of the crankshaft 9, and another end opening communicating with the oil return passage 99. As will be described below, the radial through hole 90 is used to deliver the lubricating oil from the oil sump 31 to the components to be lubricated of the scroll compressor; and the radial through holes 98 are used for returning oil and can communicate oil return passages 99 and 100.

[Fluid Paths of the Scroll Compressor]

Next, fluid paths inside the scroll compressor according to the present disclosure will be described with reference to FIG. 2 . FIG. 2 is a schematic view showing a suction path, a discharge path and a lubrication path of the scroll compressor shown in FIG. 1A. As shown in FIG. 2 , two suction paths XQ1, XQ2, four lubrication paths RH1, RH2, RH3, RH4, and two oil return paths HY1, HY2 are mainly shown. It should be understood that the fluid paths inside the scroll compressor according to the present disclosure described below are merely schematic and not restrictive or exhaustive. In practice, more or less fluid paths can be provided.
Specifically, along the suction path XQ1, the refrigerant enters the middle shell 2 of the scroll compressor through the suction inlet 2001, flows upward after being blocked by the wall 171 of the protective sleeve 17, then flows downward through the gap between the wall 171 and the scroll assembly (specifically the first scroll 5), and then enters the compression chamber 56 through the fluid passage provided in the tray 81 of the flange 8 and the first scroll 5.
Along the suction path XQ2, the refrigerant enters the middle shell 2 of the scroll compressor through the suction inlet 2001, flows downward after being blocked by the wall 171 of the protective sleeve 17, then flows through the gap (see FIG. 4 , the gap 720) between the stator 71 and the rotor 72 of the actuating mechanism 7 and the gap between the central hole of the stator 71 and the outer circumferential surface of the flange 8, and then enters the compression chamber 56 through the fluid passage provided between the tray 81 of the flange 8 and the scroll assembly.
Along the lubrication path RH1, with the rotation of the oil screw 10, the lubricating oil initially stored in the oil sump 31 rises to the second sliding bearing 12 and then reaches the first thrust support 15. Some of the lubricating oil flows downward through the oil return hole 97 into the oil return passage 99, and further into the oil return passage 100. Some other of the lubricating oil flows along the gaps on both sides of the second sliding bearing 12 and the gaps on both sides of the first sliding bearing 11, downward to the radial through hole 98, and then enters the oil return passage 99 through the radial through hole 98, and further enters the oil return passage 100. The lubricating oil in the oil return passage 100 finally flows back into the oil sump 31. Thus, the oil return path HY1 is established.
Along the lubrication path RH2, with the rotation of the oil screw 10, the lubricating oil initially stored in the oil sump 31 rises to the second thrust support 14, and then flows through the second thrust support 14 to the fluid passage provided between the tray 81 of the flange 8 and the scroll assembly, and finally enters the compression chamber 56 together with the refrigerant.
After the fluid in the compression chamber 56 is compressed, it flows into the discharge chamber 1002 through the central hole 52 on the top of the first scroll 5 and the central hole 2002 on the top of the middle shell 2, and then is discharged to the outside of the scroll compressor through the discharge outlet 1001. Thus, the discharge path PQ is established.
In addition, with the rotation of the oil screw 10, along the lubrication path RH2, the lubricating oil initially stored in the oil sump 31 rises to the radial through hole 90. It flows to the third sliding bearing 13 through the radial through hole 90. Then, some of the lubricating oil flows upward to the first thrust support 15, thus the lubrication path RH3 is established, and some other of the lubricating oil flows downward to the third thrust support 16, thus the lubrication path RH4 is established.
The lubricating oil after lubricating the third thrust support 16 and the lubricating oil from above can flow on the bottom surface of the connection between the supporting arm(s) 42 and the hub 41, and finally flow back to the oil sump 31 through the oil leakage hole 44 on the frame 4. Thus, the oil return path HY2 is established.

[Basic Configuration of the Actuating Mechanism]

The basic configuration of the actuating mechanism 7 is described above in conjunction with FIG. 1A and FIG. 1B. Refer further to FIG. 4 to describe the basic configuration of the actuating mechanism 7 in more detail.
FIG. 4 is a longitudinal section view of a portion of the scroll compressor according to the exemplary embodiment of the present disclosure. FIG. 4 mainly shows the basic configuration of the actuating mechanism 7, such as a disc motor, which is a kind of axial-flux motor.
As shown in FIG. 1A, FIG. 1B and FIG. 4 , the stator 71 has an outer rim (hereinafter also referred to as the stator supporting ring) 711, a stator frame 710, a stator yoke 713, a stator tooth 714, and a plurality of windings 717 wound on the stator teeth. The stator yoke 713 and the stator teeth 714 are actually two different segments of the same component, as shown in FIG. 4 , and the segment of the component on which the winding 717 is wound (the lower segment of the part in FIG. 1A, FIG. 1B and FIG. 4 ) is named as the stator teeth. The segment of the component where no winding is wound (the upper segment of the component in FIG. 1A, FIG. 1B and FIG. 4 ) is named as the stator yoke. The stator yoke 713 is fixedly connected to the stator supporting ring 711.
The stator supporting ring 711 and the compressor shell can be fitted by interference fit. Further, a plurality of threaded holes (or through holes) 712 are provided on the stator supporting ring 711, while the threaded holes 43 are provided on the outer edge of the frame 4 (i.e., the top of the supporting arm 42). There is a one-to-one match between the threaded holes 712 and the threaded holes 43 so that the stator 71 can be fixed to the frame 4 by a plurality of screws 18.
The stator 71 can further include a winding frame 716. The winding frame 716 is mounted around the stator teeth 714, and then the windings 717 are wound on the winding frames 716. After the winding frames 716 are mounted around the stator teeth 714, a tooth tip (not shown) can be further provided on the bottom surface of the stator teeth 714. The tooth tip is made of soft magnetic material and mounted on an end surface (i.e., the bottom surface) 715 of the stator teeth 714 towards the rotor 72. The tooth shoe has an area greater than that of the bottom surface 715 of the stator teeth 714 so as to limit the vertical movement of the windings 717 and the winding frames 716. Furthermore, the tooth tip made of soft magnetic material increases the area in which the magnetic field of the rotor 72 can be received.
It should be understood that the winding frames 716 is optional and the windings 717 can also be wound directly on the stator teeth 714. In addition, the tooth tip can also be integrated with the stator teeth 714 and be processed together.
The windings 717 can be fixed with resin and/or insulating coatings 718, and the windings 717, the winding frames 716, the stator teeth 714 and the stator yoke 713 can be encapsulated with resin. For example, the above fixing and/encapsulation may be performed using an insulating coating 718 to improve the cooling effects of the refrigerant to the windings 717.
The rotor 72 includes permanent magnets 723, a rotor yoke 725, and a rotor hub 721. The permanent magnets 723 are held and fixed by the rotor yoke 725. The central hole 722 is provided in the center of the rotor hub 721, and fits with flange 8 by interference fit so as to fix the rotor 72 to the flange 8. On the top of the permanent magnets 723, encapsulating resin 724 may be provided. A gap 720 is provided between the stator 71 and the rotor 72.
It can be seen from FIG. 1A and FIG. 4 that, the rotor 72 is positioned below the stator 71. Such arrangement of the stator 71 and rotor 72 is based on the following considerations.
In the scroll compressor according to the exemplary embodiment of the present disclosure, most of the gas force is balanced by the compression chamber 56. However, the downward gas force (i.e., the reverse thrust force) generated by the gas discharged from the central hole 2002 on the top of the middle shell 2 into the discharge chamber 1002 is not balanced. As a result, this gas force pushes the second scroll 6 downward and thus pushes the flange 8 downward, and then is transferred to the rotor 72 and applied on the frame 4.
In the arrangement where the rotor 72 is positioned below the stator 71 according to the exemplary embodiment of the present invention, the stator 71 applies an upward electromagnetic force on the rotor 72, and the rotor and the flange 8 are fixedly connected to each other. Thus, the upward electromagnetic force of the stator 71 acting on the rotor 72 is able to counteract/balance the downward thrust force generated by the above gas force and transmitted to the rotor 72. In this way, the force on the frame 4 can be reduced to protect the supports, especially the third thrust support 16. The magnitude of the gas force varies as working condition changes, so in the design of electromagnetic force, it can be considered that the electromagnetic force is greater than, or equals to, or less than the gas force in any working conditions, which mainly depends on the design of the supports and the force they can withstand.

[Configuration of the Stator]

Configuration of the stator 71 is further described next. FIG. 5A, FIG. 5B, FIG. 5C and FIG. 5D are respectively a perspective view, a side view, a top view, and a longitudinal section view taken along a plane C-C in FIG. 5B of a stator of a disc motor according to the exemplary embodiment of the present disclosure.
The basic configuration of the stator 71 has been described with reference to FIG. 1A, FIG. 1B and FIG. 4 and will not be described any longer here, for the sake of brevity. In the longitudinal section view of the stator 71 shown in FIG. 5D, it is shown that, around the center of the stator 71, a plurality of windings 717 as well as their corresponding winding frames 716, the stator teeth 714 and an insulating coating 718 for encapsulating these components are evenly arranged.

[Configuration of the Rotor]

Configuration of the rotor 72 will further be described next. FIG. 6A, FIG. 6B, FIG. 6C and FIG. 6D are respectively a perspective view, a side view, a top view, and a longitudinal section view, taken along a plane D-D in FIG. 6B, of a rotor of the disc motor according to the exemplary embodiment of the present disclosure.
The basic configuration of the rotor 72 has been described with reference to FIG. 1A, FIG. 1B and FIG. 4 and will not be described any longer here, for the sake of brevity. In the longitudinal section view of the rotor 72 shown in FIG. 6D, it is shown that, around the rotation center of the rotor 72, a plurality of evenly arranged permanent magnets 723 as well as the rotor yoke 725 embedded between the permanent magnets 723 and the rotor hub 721, and encapsulating resin 724 is provided between these adjacent permanent magnets 723.

[Configuration of the Heat Dissipation Ribs]

FIG. 7A and FIG. 7B are respectively atop view and a side view of another modification of the stator shown in FIG. 5A. As shown in FIG. 7A and FIG. 7B, to improve the heat dissipation of the stator 71, a plurality of (four in FIG. 7A) heat dissipation ribs 719 are provided on the outer surface (i.e., the upper surface in FIG. 7A) of the stator 71. As shown in FIG. 7A, these heat dissipation ribs 719 are evenly distributed at equal center angles. In addition, the heat dissipation ribs 719 are components made separately from the stator 71. Alternatively, the heat dissipation ribs 719 are integrally formed with the outer surface of the stator 71.
FIG. 8A and FIG. 8B are respectively atop view and a side view of another modification of the stator shown in FIG. 5A. As shown in FIG. 8A and FIG. 8B, a plurality of (four in FIG. 8A) heat dissipation ribs 719′ are provided on the outer surface (i.e., the upper surface in FIG. 8A) of the stator 71. The number and layout of these heat dissipation ribs 719′ are similar to those in FIG. 7A and FIG. 7B, except the following difference: as shown in FIG. 8A and FIG. 8B, these heat dissipation ribs 719′ as a whole are positioned on the upper surface of the stator 71, and the radially outer ends of the heat dissipation ribs 719 don't extend to the stator supporting ring 711; as shown in FIG. 8A and FIG. 8B, the radial outer ends of the heat dissipation ribs 719′ extend to and are connected to the stator supporting ring 711, while the heat dissipation ribs 719′ are not integral with the stator supporting ring 711, namely components made separately.
FIG. 9A and FIG. 9B are respectively atop view and a side view of another modification of the stator shown in FIG. 5A. As shown in FIG. 9A and FIG. 9B, a plurality of (four in FIG. 9A) heat dissipation ribs 719″ are provided on the outer surface (i.e., the upper surface in FIG. 9A) of the stator 71. The number and layout of these heat dissipation ribs 719″ are similar to those in FIG. 7A and FIG. 7B, except the following difference: these heat dissipation ribs 719″ are formed in one piece with the stator supporting ring 711.

[Modification of the Scroll Compressor]

FIG. 10 is a longitudinal section view of a scroll compressor according to another exemplary embodiment of the present disclosure.
The scroll compressor according to the exemplary embodiment shown in FIG. 10 is distinguished from the scroll compressor according to the exemplary embodiment shown in FIG. 1A in the actuating mechanism. In the scroll compressor according to the exemplary embodiment shown in FIG. 10 , the actuating mechanism 7′ is a radial-flux motor. This radial-flux motor includes both a stator 71′ and a rotor 72′. The stator 71′ includes a stator supporting ring 711′ and a plurality of stator teeth 714′. Corresponding windings 717′ are wound in the periphery of each stator tooth 714′. The rotor 72′ is provided radially inside of the stator 71′. The rotor 72′ includes a plurality of permanent magnets 722′ and a rotor hub 721′. Configurations and way of connection of the stator supporting ring 711′ of the stator 71′ and of the rotor hub 721′ of the rotor 72′ are similar to those of the axial-flux motor described above. That is, the permanent magnets 722′ are fixed on the rotor hub 721′, and the inner circumferential surface of the rotor hub 721′ is fixedly fitted (e.g. in a manner of interference fit or spline fit) to the outer circumferential surface of the flange 8, while the stator 71′ is fixed to the frame 4. The rotational speed of this radial-flux motor ranges from 0 rpm to 40000 rpm.
Although the technical objects, technical solutions and technical effects of the present disclosure are described in detail by reference to specific embodiments and modifications above, it should be understood that the abovementioned embodiments and modifications are only exemplary and not restrictive. In the essential spirit and principles of the present disclosure, any modification, equivalent replacement or improvement made by those skilled in the art is contained in the scope of protection of the present invention.

Claims

1. A scroll compressor, comprising:

a compressor shell;

a frame installed in the compressor shell;

a scroll assembly comprising:

a first scroll located in the compressor shell; and

a second scroll located in the compressor shell and being co-rotatable with the first scroll, to define a compression chamber between the first scroll and the second scroll;

a flange rotatably supported on the frame and supporting the first scroll and the second scroll, the flange being connected to the first scroll; and

an actuating mechanism installed in the compressor shell and connected to the flange for driving the flange to rotate, so that the first scroll drives the second scroll to co-rotate, wherein the actuating mechanism comprises an axial-flux motor.

2. The scroll compressor according to claim 1, wherein the axial-flux motor is a disc motor.

3. The scroll compressor according to claim 1, wherein the axial-flux motor comprises a stator fixed to the frame, and a rotor connected to the flange for driving the flange to rotate.

4. The scroll compressor according to claim 3, wherein the rotor is located below the stator.

5. The scroll compressor according to claim 4, wherein the axial-flux motor has a rotational speed ranging from 0 rpm to 40000 rpm.

6. The scroll compressor according to claim 4, wherein the rotor and the flange are connected by interference fit, and the stator and the frame are connected by a screw.

7. The scroll compressor according to claim 4, wherein the stator comprises a stator yoke, a stator tooth, a stator supporting ring and windings wound on the stator tooth.

8. The scroll compressor according to claim 7, wherein the stator further comprises a winding frame mounted around the stator tooth, and the windings are wound on the winding frames.

9. The scroll compressor according to claim 7, wherein the stator yoke is fixedly connected to the stator supporting ring, and the stator supporting ring is connected to the compressor shell by interference fit.

10. The scroll compressor according to claim 7, wherein the stator is accommodated in the frame, and threaded holes are provided on an outer edge of the frame and the stator supporting ring so that the frame and the stator supporting ring are fixedly connected by a screw.

11. The scroll compressor according to claim 3, wherein one or more heat dissipation ribs are provided on an outer surface of the stator; and

the heat dissipation ribs are components made separately from the stator, or integrally formed with the stator.

12. The scroll compressor according to claim 4, wherein the rotor comprises a permanent magnet, a rotor yoke and a rotor hub, wherein the permanent magnet is held and fixed by the rotor yoke, and the rotor hub and the flange are connected by interference fit.

13. A scroll compressor, comprising:

a compressor shell;

a frame installed in the compressor shell;

a scroll assembly comprising:

a first scroll located in the compressor shell; and

an actuating mechanism installed in the compressor shell and connected to the flange for driving the flange to rotate, so that the first scroll drives the second scroll to co-rotate, wherein the actuating mechanism comprises a radial-flux motor.

14. The scroll compressor according to claim 13, wherein the radial-flux motor has a rotational speed ranging from 0 rpm to 40000 rpm.

15. The scroll compressor according to claim 13, wherein the radial-flux motor comprises a stator fixed to the frame, and a rotor provided radially inside the stator and connected to the flange for driving the flange to rotate.

16. The scroll compressor according to claim 15, wherein the rotor and the flange are connected by interference fit, and the stator is fixed to the frame.

17. The scroll compressor according to claim 15, wherein the stator comprises a stator supporting ring, and a plurality of stator teeth each having a corresponding winding wound around it.

18. The scroll compressor according to claim 2, wherein the axial-flux motor comprises a stator fixed to the frame, and a rotor connected to the flange for driving the flange to rotate.

19. The scroll compressor according to claim 18, wherein the rotor is located below the stator.

20. The scroll compressor according to claim 19, wherein the rotor and the flange are connected by interference fit, and the stator and the frame are connected by a screw.