Compressor, thermal management system and vehicle

Abstract

The invention discloses a compressor, a heat management system and a vehicle, the compressor comprises a plurality of compression units, each compression unit comprises a static vortex plate and a dynamic vortex plate which are matched with each other, the dynamic vortex plates of the plurality of compression units are in transmission connection, and the rotation angles of the dynamic vortex plates of at least two compression units have a phase difference. The gas force of the multiple compression units can be weakened or counteracted, and therefore pulsation such as gas exhaust mass, gas exhaust flow and gas torque is effectively reduced.

Description

Technical Field

[0001] The present application relates to the field of compressor technology, and in particular to a compressor, a thermal management system and a vehicle. Background Art

[0002] The scroll compressor is a core component of the thermal management system of electric vehicles. Its structure and performance affect the energy consumption, noise and vibration level of the entire vehicle. The improvement of people's living standards and the thermal management requirements of electric vehicles have put forward higher requirements for the performance, noise and vibration of compressors. The operating conditions of compressors vary widely, including low pressure ratio conditions and high pressure ratio conditions. Often, due to the insufficient volume ratio of the scroll structure design, the compressor cannot perform well under high pressure ratio conditions. Summary of the invention

[0003] An object of the present application is to provide a compressor.

[0004] Another object of the present application is to provide a thermal management system.

[0005] Yet another object of the present application is to provide a vehicle.

[0006] According to an embodiment of the present application, a compressor comprises a plurality of compression units, wherein the compression units comprise a fixed scroll and a movable scroll which cooperate with each other, the movable scrolls of the plurality of compression units are transmission-connected, and the rotation angles of the movable scrolls of at least two of the compression units have a phase difference.

[0007] In addition, the compressor according to the above embodiment of the present application may also have the following additional technical features:

[0008] In some embodiments, the plurality of compression units include a first compression unit and a second compression unit, and rotation angles of a movable scroll of the first compression unit and a movable scroll of the second compression unit have a phase difference.

[0009] In some embodiments, the phase difference between the rotation angles of the movable scroll of the first compression unit and the movable scroll of the second compression unit is 180°.

[0010] In some embodiments, the displacement of the first compression unit and the second compression unit are the same; or, the displacement of the first compression unit and the second compression unit are different.

[0011] In some embodiments, the plurality of compression units further includes a third compression unit.

[0012] In some embodiments, the rotation angle of the movable scroll of the third compression unit has a phase difference with that of the movable scroll of the second compression unit; or, the rotation angle phase difference between the movable scroll of the first compression unit and the movable scroll of the second compression unit is 120°, and the rotation angle phase difference between the movable scroll of the second compression unit and the movable scroll of the third compression unit is 120°; or, the rotation angle phase difference between the movable scroll of the first compression unit and the movable scroll of the second compression unit is 180°, and the rotation angle phase difference between the movable scroll of the second compression unit and the movable scroll of the third compression unit is 180°.

[0013] In some embodiments, the first compression unit, the second compression unit and the third compression unit are distributed at equal intervals; or, the interval between the first compression unit and the second compression unit is different from the interval between the second compression unit and the third compression unit.

[0014] In some embodiments, the displacements of the first compression unit, the second compression unit, and the third compression unit are the same; or, the displacements of at least two of the first compression unit, the second compression unit, and the third compression unit are different.

[0015] In some embodiments, the plurality of compression units further include a fourth compression unit and a fifth compression unit.

[0016] In some embodiments, the movable scroll of the fourth compression unit has a phase difference with the movable scroll of the fifth compression unit; or, the angular phase difference between the movable scroll of the first compression unit and the movable scroll of the second compression unit is 90°, the angular phase difference between the movable scroll of the second compression unit and the movable scroll of the fourth compression unit is 90°, and the angular phase difference between the movable scroll of the fourth compression unit and the movable scroll of the fifth compression unit is 90°; or, the angular phase difference between the movable scroll of the first compression unit and the movable scroll of the second compression unit is 180°, the angular phase difference between the movable scroll of the second compression unit and the movable scroll of the fourth compression unit is 0, and the angular phase difference between the movable scroll of the fourth compression unit and the movable scroll of the fifth compression unit is 180°.

[0017] In some embodiments, the first compression unit, the second compression unit, the fourth compression unit and the fifth compression unit are distributed at equal intervals; or, at least one of the first compression unit, the second compression unit, the fourth compression unit and the fifth compression unit has a different interval from the other intervals.

[0018] In some embodiments, the displacements of the first compression unit, the second compression unit, the fourth compression unit, and the fifth compression unit are the same; or, the displacements of at least two of the first compression unit, the second compression unit, the fourth compression unit, and the fifth compression unit are different.

[0019] In some embodiments, the plurality of compression units are configured such that gas forces of the stationary scroll cancel each other out; or, the plurality of compression units are configured such that torques caused by gas forces of the stationary scroll cancel each other out.

[0020] In some embodiments, the compressor further includes a crankshaft, which is connected to the movable scrolls of the multiple compression units; and / or the multiple compression units are distributed along the axial direction; and / or an exhaust cavity is provided on the exhaust side of the fixed scroll, and an exhaust hole is provided on the wall of the exhaust cavity; and / or the multiple compression units are configured to be connected in parallel with each other.

[0021] In some embodiments, at least one of the plurality of compression units is configured as a multi-tooth scroll compression structure.

[0022] In some embodiments, the multi-tooth vortex compression structure includes a first scroll plate and a second scroll plate, the first scroll plate includes a first base plate and a plurality of first scroll teeth arranged on the first base plate, the second scroll plate includes a second base plate and a plurality of second scroll teeth arranged on the second base plate, the plurality of first scroll teeth construct a plurality of compression channels, the first base plate or the second base plate is provided with a plurality of exhaust holes respectively connected to the plurality of compression channels, the plurality of second scroll teeth are respectively arranged in the plurality of compression channels, and respectively cooperate with the plurality of first scroll teeth to drive the fluid along the compression channel to the corresponding exhaust holes, wherein one of the first scroll plate and the second scroll plate is a movable scroll and the other is a stationary scroll.

[0023] In some embodiments, the fixed scroll is provided with a first center through hole, the multiple exhaust holes are provided on the fixed scroll and distributed around the first center through hole, the movable scroll is provided with a second center through hole, the compressor also includes a crankshaft, the crankshaft includes a main journal and a connecting rod journal, the main journal is passed through the first center through hole, and the connecting rod journal is passed through the second center through hole.

[0024] In some embodiments, at least one of the plurality of compression units is configured as a single-tooth scroll compression structure.

[0025] In some embodiments, the single-tooth scroll compression structure includes a third scroll plate and a fourth scroll plate, the third scroll plate includes a third bottom plate and a third scroll tooth arranged on the third bottom plate, the fourth scroll plate includes a fourth bottom plate and a fourth scroll tooth arranged on the fourth bottom plate, the fourth scroll tooth cooperates with the third scroll tooth, wherein one of the third scroll plate and the fourth scroll plate is a movable scroll plate and the other is a fixed scroll plate.

[0026] In some embodiments, the compression unit also includes a crankshaft, the compression units are distributed along the crankshaft and are drivingly connected to the crankshaft, the crankshaft has a driving end and a free end, the driving end is used to connect a driving member, the compression unit connected to the free end is configured as a single-tooth scroll compression structure, and the other compression units are configured as multi-tooth scroll compression structures.

[0027] In some embodiments, the compression unit further includes an anti-self-rotation structure, which is relatively stationary with respect to the static scroll, and one of the movable scroll and the anti-self-rotation structure is provided with at least one anti-self-rotation ring, and the other is provided with a positioning portion, and the positioning portion can be positioned translationally on the anti-self-rotation ring around a fixed radius.

[0028] A thermal management system according to an embodiment of the present application includes the aforementioned compressor.

[0029] A vehicle according to an embodiment of the present application includes the aforementioned compressor; or includes the aforementioned thermal management system. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] Figure 1 It is a schematic diagram of a compressor according to an embodiment of the present application.

[0031] Figure 2 It is a schematic diagram of a compressor according to another embodiment of the present application.

[0032] Figure 3 Schematic diagram of the distribution of gas forces in multiple compression units.

[0033] Figure 4 It is a schematic diagram of a compressor according to yet another embodiment of the present application.

[0034] Figure 5 It is a schematic diagram of a compression unit according to an embodiment of the present application.

[0035] Figure 6 is a side view of a compression unit according to an embodiment of the present application.

[0036] Figure 7 yes Figure 6 Cross-sectional view of the middle section AA.

[0037] Figure 8It is a schematic diagram of one direction of the first scroll plate of the multi-tooth scroll compression structure of an embodiment of the present application.

[0038] Fig. 9 It is a schematic diagram of the first scroll plate of the multi-tooth scroll compression structure of one embodiment of the present application from another direction.

[0039] Fig.10 It is a schematic diagram of one direction of the second scroll plate of the multi-tooth scroll compression structure of an embodiment of the present application.

[0040] Fig.11 It is a schematic diagram of the second scroll plate of the multi-tooth scroll compression structure of one embodiment of the present application from another direction.

[0041] Fig.12 It is a schematic diagram of another direction of the second scroll plate of the multi-tooth scroll compression structure of an embodiment of the present application.

[0042] Fig.13 It is a schematic diagram of the first scroll plate of the multi-tooth scroll compression structure of another embodiment of the present application.

[0043] Fig.14 It is a schematic diagram of the second scroll plate of the multi-tooth scroll compression structure of another embodiment of the present application.

[0044] Figures 15 to 18 1 is a schematic diagram of the cooperation between the first scroll and the second scroll of the multi-tooth scroll compression structure of an embodiment of the present application, wherein: Figures 15 to 18 It is a process of dynamic coordination in chronological order.

[0045] Fig.19 It is a schematic diagram of one direction of the first scroll plate of the multi-tooth scroll compression structure of yet another embodiment of the present application.

[0046] Fig. 20 It is a schematic diagram of the first scroll plate of the multi-tooth scroll compression structure of yet another embodiment of the present application from another direction.

[0047] Fig.21 It is a schematic diagram of one direction of the second scroll plate of the multi-tooth scroll compression structure of yet another embodiment of the present application.

[0048] Fig. 22 It is a schematic diagram of the second scroll plate of the multi-tooth scroll compression structure of yet another embodiment of the present application from another direction.

[0049] Fig.23 It is a schematic diagram of another direction of the second scroll plate of the multi-tooth scroll compression structure of another embodiment of the present application.

[0050] Fig.24This is a rotation angle-torque comparison diagram of a multi-tooth scroll compression structure and a single-tooth scroll structure according to an embodiment of the present application.

[0051] Fig.25 This is a comparison diagram of the rotation angle-exhaust mass flow rate of a multi-tooth scroll compression structure and a single-tooth scroll structure in one embodiment of the present application.

[0052] Fig.26 It is a schematic diagram of a stationary scroll of a single-tooth scroll compression structure of a compression unit according to an embodiment of the present application.

[0053] Fig. 27 It is a schematic diagram of a movable scroll of a single-tooth scroll compression structure of a compression unit according to an embodiment of the present application.

[0054] Fig.28 It is a schematic diagram of a stationary scroll of a compression unit of a compressor according to an embodiment of the present application.

[0055] Fig.29 It is a cross-sectional view of a stationary scroll of a compression unit of a compressor according to an embodiment of the present application.

[0056] Fig.30 It is a schematic diagram of a movable scroll of a compression unit of a compressor according to an embodiment of the present application. DETAILED DESCRIPTION

[0057] Embodiments of the present application are described in detail below, and examples of the embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present application, and should not be construed as limiting the present application.

[0058] Combination Figures 1 to 8 According to the compressor 100 of the embodiment of the present application, it includes a plurality of compression units 10, and the compression unit 10 includes a fixed scroll 101 and a movable scroll 102 that cooperate with each other. The movable scrolls 102 of the plurality of compression units 10 are transmission connected, and the rotation angles of the movable scrolls of at least two compression units have a phase difference.

[0059] According to the compressor 100 of the embodiment of the present application, by setting the rotation angles of at least two movable scrolls to have a phase difference, the gas forces of multiple compression units can be weakened or offset, thereby effectively reducing pulsations such as gas exhaust quality, flow rate, and gas torque, reducing the vibration of the compressor 100, and improving the stability of the operation of the compressor 100. In addition, the noise reduction of the compressor 100 can also be achieved.

[0060] The rotation angles of the movable scrolls of the two compression units have a phase difference, which may include but is not limited to: Situation 1, multiple compression units are distributed along the axis of the compressor 100, and in the projection along the axis of the compressor 100, the line connecting the axis of the movable and stationary scrolls in one compression unit has an angle greater than zero with the line connecting the axis of the movable and stationary scrolls in another compression unit; Situation 2, the gas force direction of one compression unit has an angle greater than zero with the gas force direction of another compression unit, etc. When determining the phase difference, the stationary scrolls of the multiple compression units may be translated until the axes coincide.

[0061] In some embodiments, the compressor 100 further includes a crankshaft 30, which is connected to the movable scrolls of the plurality of compression units. The plurality of compression units are connected by the crankshaft 30, and the rotation angles of the movable scrolls of at least two compression units have a phase difference, which can weaken or offset the gas force applied by the movable scrolls of the plurality of compression units to the crankshaft 30, and can improve the stability of the rotation of the crankshaft 30, thereby improving the performance of the compressor 100.

[0062] In addition, multiple compression units can be connected to the same crankshaft 30. The crankshaft 30 may include a main journal and multiple connecting rod journals. The multiple connecting rod journals are respectively connected to the multiple compression units, and the deviation directions of the multiple connecting rod journals relative to the main journal are different, so that the movable scrolls of the multiple compression units have a phase difference.

[0063] Optionally, multiple compression units are distributed along the axial direction, which can facilitate the installation of multiple compression units and the connection between the crankshaft 30 and the multiple compression units, simplify the structure of the compressor 100, and facilitate driving the multiple compression units.

[0064] In addition, an exhaust cavity 1007 is provided on the exhaust side of the stationary scroll, and an air outlet 1008 is provided on the wall of the exhaust cavity 1007, which can facilitate the exhaust of the compression unit and improve the stability of the exhaust of the compression unit. In addition, multiple compression units are configured in parallel to increase the displacement of the compressor 100 and optimize the performance of the compressor 100.

[0065] The arrangement of multiple compression units in the present application may include but is not limited to the following embodiments.

[0066] In the first embodiment, the number of compression units in the present application may be greater than or equal to 1. When the displacement and structure of each compression unit are the same, the compressor 100 includes two compression units, and the phase difference between the two compression units may be 180°; the compressor 100 includes three compression units, and the phase difference between two adjacent compression units of the three compression units may be 120°; the compressor 100 includes four compression units, and the phase difference between two adjacent compression units of the four compression units is 90°, and so on. In other words, the phase difference between adjacent compression units may be 360° / N, where N is the number of compression units. With this arrangement, the gas force can be completely offset, while obtaining minimal gas torque pulsation and exhaust mass flow pulsation.

[0067] The second implementation method, such as Figure 1 The plurality of compression units include a first compression unit 10a and a second compression unit 10b, and the rotation angles of the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b have a phase difference. In this way, the resultant force of the gas force of the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b will offset or weaken each other, thereby improving the stability of the operation of the compressor 100.

[0068] Optionally, the rotation angle phase difference between the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b is 180°. In this way, the gas force of the movable scroll of the first compression unit 10a and the gas force of the movable scroll of the second compression unit 10b are opposite and can be effectively offset, especially when the displacement of the first compression unit 10a and the displacement of the second compression unit 10b are the same, the gas force can be completely offset.

[0069] In some examples, the displacements of the first compression unit 10 a and the second compression unit 10 b are the same, so as to offset the gas forces of the first compression unit 10 a and the second compression unit 10 b , so as to improve the stability of the compressor 100 .

[0070] In other examples, the displacements of the first compression unit 10a and the second compression unit 10b are different.

[0071] In addition, if Figure 1 The first compression unit 10a and the second compression unit 10b are connected in parallel to realize a large flow rate of compressed fluid. Figure 1 The arrows in the figure show the direction of fluid flow.

[0072] The third implementation method, such as Figure 2 and Figure 3 The plurality of compression units include a first compression unit 10a, a second compression unit 10b and a third compression unit 10c. A greater number of compression units may be used to increase the displacement or pressure ratio of the compressor 100 and optimize the performance of the compressor 100.

[0073] Optionally, the rotation angles of the movable scroll of the third compression unit 10c and the movable scroll of the second compression unit 10b have a phase difference. In addition, the rotation angles of the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b have a phase difference; or, the rotation angles of the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b do not have a phase difference.

[0074] In some examples, the rotation angle phase difference between the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b is 120°, the rotation angle phase difference between the movable scroll of the second compression unit 10b and the movable scroll of the third compression unit 10c is 120°, and the rotation angle phase difference between the movable scroll of the first compression unit 10a and the movable scroll of the third compression unit 10c is 120°. The gas force Fa of the first compression unit 10a, the gas force Fb of the second compression unit 10b, and the gas force Fc of the third compression unit 10c are as follows: Figure 3 As shown, when the displacements of the first compression unit 10a, the second compression unit 10b, and the third compression unit 10c are the same, the gas force can be offset.

[0075] For example, Figure 1 , including a crankshaft 30, which transmits the driving torque to the first compression unit 10a, the second compression unit 10b and the third compression unit 10c which are not necessarily equidistantly distributed. The displacement of the first compression unit 10a, the second compression unit 10b and the third compression unit 10c are not necessarily the same. The special arrangement is that when the displacement of the first compression unit 10a, the second compression unit 10b and the third compression unit 10c is the same, the phase difference of the rotation angles of the three is 120°, and at this time, the spacing of the three scroll plate assemblies should be the same.

[0076] In other examples, the rotation angle phase difference between the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b is 180°, and the rotation angle phase difference between the movable scroll of the second compression unit 10b and the movable scroll of the third compression unit 10c is 180°. In this way, the gas force of the first compression unit 10a, the gas force of the second compression unit 10b and the gas force of the third compression unit 10c can be offset, and at the same time, the torque formed by the gas force of the first compression unit 10a and the gas force of the second compression unit 10b is offset by the torque formed by the gas force of the third compression unit 10c and the gas force of the second compression unit 10b, so that the gas force between multiple compression units and the torque formed by the gas force can be effectively reduced, and the stability of the operation of the compressor 100 is further improved.

[0077] In some other examples, the first compression unit 10a, the second compression unit 10b and the third compression unit 10c are distributed at equal intervals, so as to facilitate calculation or control of the torque and gas force of the plurality of compression units as a whole, and improve the stability and safety of the operation of the compressor 100.

[0078] Of course, the distance between the first compression unit 10a and the second compression unit 10b and the distance between the second compression unit 10b and the third compression unit 10c may also be different.

[0079] In some other examples, the displacements of the first compression unit 10a, the second compression unit 10b, and the third compression unit 10c are the same; or, the displacements of at least two of the first compression unit 10a, the second compression unit 10b, and the third compression unit 10c are different.

[0080] The fourth implementation method is Figure 4 The plurality of compression units further include a fourth compression unit 10d and a fifth compression unit 10e. A greater number of compression units can be used to increase the displacement or pressure ratio of the compressor 100 and optimize the performance of the compressor 100.

[0081] Optionally, the movable scroll of the fourth compression unit 10d has a phase difference with the movable scroll of the fifth compression unit 10e. In addition, the rotation angles of the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b have a phase difference; or, the rotation angles of the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b do not have a phase difference; the rotation angles of the movable scroll of the second compression unit 10b and the movable scroll of the fourth compression unit 10d have a phase difference; or, the rotation angles of the movable scroll of the second compression unit 10b and the movable scroll of the fourth compression unit 10d do not have a phase difference.

[0082] In some examples, the angular phase difference between the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b is 90°, the angular phase difference between the movable scroll of the second compression unit 10b and the movable scroll of the fourth compression unit 10d is 90°, the angular phase difference between the movable scroll of the fourth compression unit 10d and the movable scroll of the fifth compression unit 10e is 90°, and the angular phase difference between the movable scroll of the first compression unit and the movable scroll of the fifth compression unit 10e is 90°.

[0083] In other examples, the angular phase difference between the movable scroll of the first compression unit 10a and the movable scroll of the second compression unit 10b is 180°, the angular phase difference between the movable scroll of the second compression unit 10b and the movable scroll of the fourth compression unit 10d is 0, and the angular phase difference between the movable scroll of the fourth compression unit 10d and the movable scroll of the fifth compression unit 10e is 180°.

[0084] Specifically, Figure 4A preferred arrangement of the first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d and the fifth compression unit 10e is provided, comprising a crankshaft 30, which transmits the driving torque to the first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d and the fifth compression unit 10e arranged equidistantly. The first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d and the fifth compression unit 10e are scroll assemblies with the same structure and displacement, the rotation angles of the first compression unit 10a and the second compression unit 10b differ by 180°, the rotation angles of the second compression unit 10b and the fourth compression unit 10d are the same, and the rotation angles of the first compression unit 10a and the fifth compression unit 10e are the same. The first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d and the fifth compression unit 10e work in parallel, and the displacement of the system is equal to the sum of the displacements of the first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d and the fifth compression unit 10e. Arranged in this form, the gas forces Fa, Fb, Fd, and Fe generated by the first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d, and the fifth compression unit 10e are of the same magnitude, and Fa and Fe are in the same direction, which is opposite to the direction of Fb and Fd, so the gas forces can be completely offset; in addition, the torque M1 caused by Fa and Fb is opposite to the torque M2 caused by Fd and Fe, and M1 and M2 are in the opposite direction and of the same magnitude, and they are also completely offset. The gas force and gas torque in the compression process of the above structure can be completely eliminated in theory, which is a preferred solution for minimizing the vibration and noise of the compressor 100.

[0085] In some other examples, the first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d and the fifth compression unit 10e are distributed at equal intervals; or, at least one interval among the first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d and the fifth compression unit 10e is different from the other intervals.

[0086] In some other examples, the displacements of the first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d and the fifth compression unit 10e are the same; or, the displacements of at least two of the first compression unit 10a, the second compression unit 10b, the fourth compression unit 10d and the fifth compression unit 10e are different.

[0087] In a fifth implementation, multiple compression units are configured such that the gas forces of the static scrolls cancel each other out; or multiple compression units are configured such that the torques caused by the gas forces of the static scrolls cancel each other out. Thus, the gas forces of the multiple static scrolls or the torques generated by the gas forces are completely or partially offset by utilizing the phase difference of the static scrolls of the multiple compression units, thereby improving the operating stability of the compressor 100.

[0088] In addition, in some embodiments of the present application, the compressor 100 of the present application may include a drive structure, and the drive structure may be used to drive multiple compression units. Among them, the multiple compression units in the present application may be driven separately or in a linked form, for example, the multiple compression units are driven by the same crankshaft 30. Thereby, the drive and control of the compressor 100 can be simplified, and the failure rate and control cost can be reduced.

[0089] The compression unit in the present application can be configured as a scroll compression structure, which can fully utilize the characteristics of the scroll compression structure, facilitate the formation of a multi-stage compression structure, and facilitate better control of the operation of the compressor 100. Including but not limited to the following implementations.

[0090] In the first embodiment, at least one of the plurality of compression units is configured as a multi-tooth scroll compression structure. For example, the first compression unit 10a is configured as a multi-tooth scroll compression structure; the second compression unit 10b can be configured as a multi-tooth scroll compression structure; and the third compression unit 10c can be configured as a multi-tooth scroll compression structure.

[0091] In the second embodiment, at least one of the plurality of compression units is configured as a single-tooth scroll compression structure.

[0092] In the third embodiment, the compression unit also includes a crankshaft 30, the compression units are distributed along the crankshaft 30 and are connected to the crankshaft 30 in a transmission manner, the crankshaft 30 has a driving end and a free end, the driving end is used to connect the driving member, the compression unit connected to the free end is configured as a single-tooth scroll compression structure, and the other compression units are configured as multi-tooth scroll compression structures. It is convenient to connect the crankshaft 30 with the multi-tooth scroll compression structure, and for the compression unit located at the end of the crankshaft 30, the end of the crankshaft 30 can be directly connected to the corresponding compression unit, and the through-ground connection method can be omitted, which effectively improves the stability of the compressor 100.

[0093] The present application adopts a multi-tooth scroll structure, which utilizes the characteristics of multiple teeth. Compared with traditional positive displacement compressors, it has fewer moving parts, simpler assembly, less vibration and noise, smaller overall structural dimensions, and a smoother energy conversion process.

[0094] The multi-tooth scroll compression structure of an embodiment of the present application is described below with reference to the accompanying drawings.

[0095] like Figures 5 to 7The multi-tooth scroll compression structure includes a first scroll plate 11 and a second scroll plate 12. The first scroll plate 11 includes a first bottom plate 111 and a plurality of first scroll teeth 112. The plurality of first scroll teeth 112 are arranged on the first bottom plate 111. The second scroll plate 12 includes a second bottom plate 121 and a plurality of second scroll teeth 122. The plurality of second scroll teeth 122 are arranged on the second bottom plate 121. The plurality of first scroll teeth 112 construct a plurality of compression channels 1001. The first bottom plate 111 or the second bottom plate 121 is provided with a plurality of exhaust holes 1002. The plurality of exhaust holes 1002 are respectively connected to the plurality of compression channels 1001. The plurality of second scroll teeth 122 are respectively matched with the plurality of first scroll teeth 112 to drive the fluid to the corresponding exhaust holes 1002 along the corresponding compression channels 1001.

[0096] The plurality of first scroll teeth 112 and the plurality of second scroll teeth 122 are respectively configured to form a scroll compression structure, and respectively drive the fluid of the corresponding compression channel 1001 to flow to the corresponding exhaust holes 1002. The processes of compressing the fluid in the plurality of compression channels 1001 are relatively independent, which can reduce the mutual influence of the fluid compression processes in the plurality of compression channels 1001, and can reduce the clearance volume of the compression unit 10, thereby improving the performance of the compression unit 10. In addition, compared with the solution of discharging the fluid of the plurality of compression channels 1001 through the same opening, the present application exhausts the fluid through the plurality of exhaust holes 1002, which can avoid or reduce the problems such as turbulence caused by the fluid converging at the same opening and affecting the compression performance.

[0097] In the present application, the number of the first scroll teeth 112 may be two, three, four, six, etc., the number of the second scroll teeth 122 may be the same as the number of the first scroll teeth 112, and the number of the compression passages 1001 may be the same as the number of the first scroll teeth 112. The compression unit 10 of the present application includes but is not limited to the following examples.

[0098] Example 1, the first scroll 11 is a fixed scroll, and the number of the first scroll teeth 112 is two, and two compression channels 1001 are constructed between the two first scroll teeth 112, which are the first channel and the second channel respectively; the second scroll 12 is a movable scroll, and the number of the second scroll teeth 122 is two, one of which is arranged in the first channel and cooperates with the two adjacent first scroll teeth 112. When the second scroll 12 translates around the axis of the first scroll 11 with a fixed orbital radius, the fluid in the first channel is driven to flow to the corresponding exhaust hole 1002; the other second scroll tooth 122 is arranged in the second channel and cooperates with the two adjacent first scroll teeth 112, and when the second scroll 12 translates around the axis of the first scroll 11 with a fixed orbital radius, the fluid in the second channel is driven to flow to the corresponding exhaust hole 1002.

[0099] In Example 2, the first scroll 11 is a stationary scroll, and the number of the first scroll teeth 112 is three, and three compression channels 1001 are constructed between the three first scroll teeth 112, namely the first channel, the second channel and the third channel; the second scroll 12 is a movable scroll, and the number of the second scroll teeth 122 is three. The first second scroll tooth 122 is arranged in the first channel and cooperates with the two adjacent first scroll teeth 112. When the second scroll disk 12 translates around the axis of the first scroll disk 11 with a fixed orbital radius, the fluid in the first channel is driven to flow to the corresponding exhaust hole 1002; the second second scroll tooth 122 is arranged in the second channel and cooperates with the two adjacent first scroll teeth 112. When the second scroll disk 12 translates around the axis of the first scroll disk 11 with a fixed orbital radius, the fluid in the second channel is driven to flow to the corresponding exhaust hole 1002; the third second scroll tooth 122 is arranged in the third channel and cooperates with the two adjacent first scroll teeth 112. When the second scroll disk 12 translates around the axis of the first scroll disk 11 with a fixed orbital radius, the fluid in the third channel is driven to flow to the corresponding exhaust hole 1002.

[0100] Among them, Figure 7 , Figure 8 , the inner end of the compression channel 1001 is closed, and the exhaust hole 1002 is connected to the inner end of the corresponding compression channel 1001. When the first scroll 11 and the second scroll 12 cooperate to compress the fluid, the fluid will be driven to flow to the inner end of the compression channel 1001. When the inner end of the compression channel 1001 is closed, the fluid will be discharged through the corresponding exhaust hole 1002. Multiple compression channels 1001 can be separated, and each compression channel 1001 is independently exhausted through the corresponding exhaust hole 1002, which can reduce the influence of multiple compression channels 1001 on each other. Multiple first volutes 112 can be distributed along the circumference of the first bottom plate 111, and compression channels 1001 will be formed between adjacent first volutes 112, and the inner ends of the compression channels 1001 constructed between adjacent first volutes 112 are closed.

[0101] In addition, if Figure 8 and Fig. 9 The first scroll plate 11 also includes a protrusion 1003, which is arranged on the first bottom plate 111. A plurality of first scroll teeth 112 are connected to the protrusion 1003 and are arranged around the protrusion 1003 to form an integrated multi-tooth structure. The inner end of the compression channel 1001 constructed between adjacent first scroll teeth 112 can be closed by the protrusion 1003, and the connection of the protrusion 1003 can improve the structural strength of the plurality of first scroll teeth 112 and the first scroll teeth 112 and the first bottom plate 111.

[0102] Among them, Fig.10 and Fig.11The plurality of second volutes 122 are distributed along the circumference of the second bottom plate 121, and the adjacent second volutes 122 are spaced apart to form a vertical multi-tooth structure, so that the plurality of second volutes 122 and the plurality of first volutes 112 can respectively cooperate with each other to compress the fluid.

[0103] Among them, Fig.13 , the first scroll plate 11 is provided with a first central through hole 1004, and a plurality of first scroll teeth 112 are distributed around the first central through hole 1004; and / or, as Fig.14 , the second scroll plate 12 is provided with a second central through hole 1005, and a plurality of second scroll teeth 122 are distributed around the second central through hole 1005. When the compression unit 10 is connected to the crankshaft, the crankshaft can be passed through the first central through hole 1004 and the second central through hole 1005, so that when the crankshaft rotates, the first scroll plate 11 and the second scroll plate 12 are driven to perform relative translational motion. In this way, the crankshaft can be used to connect and pass through the compression unit 10, so that multiple compression units 10 can be connected by crankshaft transmission.

[0104] Of course, the first scroll 11 may not be provided with the first center through hole 1004, and the end of the crankshaft may be connected to the first scroll 11; or, the second scroll 12 may not be provided with the second center through hole 1005, and the end of the crankshaft may be connected to the second scroll 12.

[0105] Among them, Fig. 9 The first volute 112 includes a first tooth head correction section 1121, a first inner involute section 1122, a first tooth tail connection section 1123, and a first outer involute section 1124. The first tooth head correction section 1121 of one of the adjacent first volutes 112 is connected to the first outer involute section 1124 of the other, so as to close the inner end of the compression channel 1001 formed between the adjacent first volutes 112. The first volute 112 and the second volute 122 can be stably matched, the clearance volume of the tooth head part is eliminated, and the performance of the compressor is improved.

[0106] In addition, the first tooth head correction segment 1121 is configured as a circular arc, a spline curve, a B-spline curve or an elliptical arc; and / or, the first inner involute segment 1122 is configured as a circular involute, a triangular involute, a straight involute or an algebraic spiral; and / or, the first outer involute segment 1124 is set to a circular involute, a triangular involute, a straight involute or an algebraic spiral; and / or, the first tooth head correction segment 1121, the first inner involute segment 1122, and the first outer involute segment 1124 are parts that need to be matched with the corresponding curve of the second scroll disk 12, and therefore must be light Smooth, optionally, the first tooth head correction segment 1121, the first inner involute segment 1122 and the first outer involute segment 1124 are configured as a smooth curve; and / or, the first tooth tail connection segment 1123 is configured as an arc, a straight line or any other type of line segment, and there is no restriction on its form because it does not need to participate in the matching; and / or, the contour of the contour of the first bottom plate 111 is the first reference plane, the projection area of ​​the plurality of first volute teeth 112 on the first reference plane is A1, and the contour area of ​​the first bottom plate 111 is A2, wherein the ratio of A1 to A2 is greater than 1%. It can facilitate the stable matching of the first volute tooth 112 and the second volute tooth 122, and improve the structural stability of the compression unit 10. In addition, the structural strength of the first volute tooth 112 can be improved while ensuring the displacement of the compressor.

[0107] Among them, Fig.10 The second volute 122 includes a second tooth head correction section 1221, a second inner involute section 1222, a second tooth tail connection section 1223 and a second outer involute section 1224, and the second tooth head correction section 1221 is connected to the second outer involute section 1224. The first volute 112 and the second volute 122 can be stably matched, the clearance volume of the tooth head part is eliminated, and the performance of the compressor is improved.

[0108] In addition, the second tooth head correction segment 1221, the second inner involute segment 1222, and the second outer involute segment 1224 are the parts that need to be matched with the corresponding curve of the first scroll disk 11, and therefore must be smooth. The second tooth head correction segment 1221 is configured as a circular arc, a spline curve, a B-spline curve, or an elliptical arc; and / or, the second inner involute segment 1222 is configured as a circular involute, a triangular involute, a straight involute, or an algebraic spiral; and / or, the second outer involute segment 1224 is set to a circular involute, a triangular involute, a straight involute, or an algebraic spiral; and / or, the second tooth head correction segment 1221, the second inner involute segment 1222, and the second outer involute segment 1224 are configured as smooth curves. The second tooth tail connection segment 1223 is configured as a circular arc, a straight line, or any other type of line segment. Since it does not need to participate in matching, there is no restriction on its form.

[0109] Optionally, the contour of the second bottom plate 121 is taken as the second reference plane, the projection area of ​​the plurality of second volutes 122 on the second reference plane is A3, the contour area of ​​the second bottom plate 121 is A4, wherein the ratio of A3 to A4 is greater than 1%. This can facilitate the stable matching of the first volute 112 and the second volute 122, thereby improving the structural stability of the compression unit 10. In addition, the structural strength of the first volute 112 can be improved while ensuring the displacement of the compressor.

[0110] In addition, combined Figure 7 , Figures 15 to 18 , at least two of the plurality of first scroll teeth 112 have a phase difference in cooperation with the corresponding second scroll teeth 122. With this arrangement, when at least two first scroll teeth 112 compress the fluid, the corresponding exhaust holes 1002 will not exhaust at the same time, so that the fluids in the plurality of compression channels 1001 will be discharged from the compression unit 10 in sequence, and the vibration caused by the plurality of exhaust holes 1002 emitting gas at the same time or stopping the emission of gas at the same time can be avoided.

[0111] Furthermore, the coordination between the plurality of first vortex teeth 112 and the corresponding second vortex teeth 122 has a phase difference, and the coordination phase difference α between the first vortex teeth 112 and the corresponding second vortex teeth 122 adjacent in timing satisfies, α=360° / i, where i is the number of the first vortex teeth 112 .

[0112] For example, the number of first scroll teeth 112 is 2, and the phase difference between the adjacent first scroll teeth 112 and the corresponding second scroll teeth 122 in timing is 180°. In other words, when the compression flow path corresponding to one first scroll tooth 112 is in the exhaust stage, the compression flow path corresponding to another first scroll tooth 112 is in the intake stage; for another example, the number of first scroll teeth 112 is 3, and the phase difference between the adjacent first scroll teeth 112 and the corresponding second scroll teeth 122 in timing is 120°. In other words, when the compression flow path corresponding to one first scroll tooth 112 is in the intake stage, the compression flow path corresponding to another first scroll tooth 112 is in the compression stage, and the compression flow path corresponding to one first scroll tooth 112 is in the exhaust stage; for another example, the number of first scroll teeth 112 is 4, and the phase difference between the adjacent first scroll teeth 112 and the corresponding second scroll teeth 122 in timing is 90°. Of course, in the present application, the number of the first scroll teeth 112 may also be 5, 6, etc., which will not be elaborated in this application.

[0113] In the present application, one of the first scroll 11 and the second scroll 12 may be a fixed scroll, and the other may be a movable scroll. The movable scroll may move around the axis of the fixed scroll at a fixed orbital radius, thereby achieving compression of the fluid. The cooperation of the first scroll 11 and the second scroll 12 in the present application includes but is not limited to the following embodiments.

[0114] In one embodiment, in combination Figures 8 to 12 The first scroll 11 is configured as a fixed scroll, and the second scroll 12 is configured as a movable scroll. The second scroll 12 moves around the axis of the first scroll 11 at a fixed orbital radius.

[0115] For example, the first scroll plate 11 includes a first bottom plate 111 and a plurality of first scroll teeth 112, and the plurality of first scroll teeth 112 converge at the center of the first bottom plate 111 to form an integrated multi-tooth structure. In addition, the plurality of first scroll teeth 112 divide the space of the first bottom plate 111 into a plurality of independent compression channels 1001, and each compression channel 1001 is provided with an exhaust hole 1002 near the center of the first scroll plate 11. For example, the number of first scroll teeth 112 can be four, and the four first scroll teeth 112 will separate four independent compression channels 1001, and each compression channel 1001 is provided with an exhaust hole 1002 near the center of the scroll plate.

[0116] The second scroll 12 includes a second bottom plate 121 and a plurality of second scroll teeth 122. A bearing seat for mounting a bearing is generally provided on the back of the second scroll 12. The plurality of second scroll teeth 122 are separated and do not intersect each other. There may be four second scroll teeth 122.

[0117] The matching process of the first scroll 11 and the second scroll 12 is as follows: Figures 15 to 18 As shown, the second scroll 12 translates around the center of the first scroll 11 with a fixed orbital radius (counterclockwise on the paper). The multiple second scroll teeth 122 of the second scroll 12 form multiple matching points with the multiple first scroll teeth 112 of the first scroll 11. When the matching structures of the multiple first scroll teeth 112 and the multiple second scroll teeth 122 are exactly the same, the displacement of each compression channel 1001 is 1 / N of the total displacement of the compression unit 10 (N is the number of the first scroll teeth 112 or the second scroll teeth 122). Multiple matching points divide the multiple compression channels 1001 into multiple crescent-shaped cavities. As the translation continues, the matching points move, the volume of the crescent cavity gradually decreases, compressing the refrigerant and doing work on the refrigerant. As the volume of the refrigerant is compressed, its position gradually moves from the edge of the compression unit 10 to the center of the compression unit 10, close to the exhaust hole 1002.

[0118] like Fig.13 and Fig.14In another example, it includes a first scroll 11 and a second scroll 12, the second scroll 12 is a discrete multi-tooth movable scroll, and the first scroll 11 is an integrated multi-tooth static scroll. The discrete multi-tooth movable scroll includes a plurality of second scroll teeth 122, a second bottom plate 121, and a second bearing hole; the integrated multi-tooth static scroll includes a plurality of first scroll teeth 112, a plurality of exhaust holes 1002, and a first bottom plate 111. The plurality of second scroll teeth 122 divide the compression space of the scroll into a plurality of compression channels 1001. The integrated multi-tooth static scroll also includes a first bearing hole. The above structure adds a support point to the crankshaft, that is, the crankshaft is supported by the first bearing hole of the integrated multi-tooth static scroll. The integrated multi-tooth static scroll has a large rigidity. Using this structure as a fulcrum will further improve the stability of the shaft system. In addition, the crankshaft can pass through a scroll assembly composed of a separate multi-toothed vortex orbiting scroll and an integrated multi-toothed vortex stationary scroll, providing a structural basis for a single crankshaft to drive multiple similar scroll assemblies.

[0119] In another embodiment, if Figures 19 to 23 The first scroll 11 is configured as a movable scroll, and the second scroll 12 is configured as a stationary scroll. The first scroll 11 moves translationally around the axis of the second scroll 12 at a fixed orbital radius.

[0120] For example, the first scroll 11 includes a first bottom plate 111 and a plurality of first scroll teeth 112. The first scroll teeth 112 converge at the center of the first scroll 11 to form an integrated multi-scroll tooth structure. A bearing seat for bearing installation is disposed on the back of the first scroll 11.

[0121] The second scroll 12 includes a second bottom plate 121 and a plurality of second scroll teeth 122 , and also includes a plurality of exhaust holes 1002 ; the plurality of second scroll teeth 122 divide the space of the second scroll 12 into a plurality of compression channels 1001 .

[0122] The matching process of the first scroll 11 and the second scroll 12 can be referred to Figures 15 to 18 The compression unit 10 of the present application will significantly reduce the vibration and noise of the compressor.

[0123] In some embodiments, a plurality of exhaust holes 1002 are provided on the static scroll for exhausting the plurality of compression passages 1001. The compression unit 10 also includes a crankshaft, which includes a main journal and a connecting rod journal. The main journal is rotatably connected to the static scroll, and the connecting rod journal is rotatably connected to the movable scroll, which is used to drive the movable scroll to translate around the axis of the static scroll with a fixed radius. The static scroll is provided with a central through hole, and a plurality of exhaust holes 1002 are distributed around the central through hole. The central through hole can be used for the crankshaft to pass through, and the static scroll can be used to provide support for the crankshaft. At the same time, the exhaust holes 1002 are arranged around the central through hole to facilitate the exhaust of the compression unit 10 and avoid the crankshaft passing through the central through hole affecting the exhaust of the compression unit 10.

[0124] In some embodiments of the present application, Fig.24 As shown, taking R134a refrigerant as an example, assuming that the compressor displacement is 34cc, the displacement of each compression channel 1001 is 8.5cc, the suction pressure is 0.3MPa, the exhaust pressure is 1.5MPa, the suction superheat is 10K, and the compressor speed is 3000rpm, then the gas torque pulsation value is 0.06N*m, and the traditional single-tooth scroll compressor is 1.26N*m, and the pulsation value is reduced by 95%. The obvious improvement of the gas torque pulsation value and the offset of the gas force will effectively improve the vibration and noise problems of the compressor.

[0125] In other embodiments of the present application, Fig.25 As shown, taking R134a refrigerant as an example, assuming that the compressor displacement is 34cc, the displacement of each compression channel 1001 is 8.5cc, the suction pressure is 0.3MPa, the exhaust pressure is 1.5MPa, the suction superheat is 10K, and the compressor speed is 3000rpm, then the exhaust mass flow pulsation value is 0.010kg / s, while that of the traditional single-tooth scroll compressor is 0.056kg / s, and the pulsation value is reduced by 82%.

[0126] Additionally, in some embodiments, a plurality of exhaust holes 1002 are arranged around the axis of the fixed scroll.

[0127] In combination with the foregoing, in some embodiments of the present application, the tooth head area of ​​multiple vortex teeth on the fixed scroll adopts an integral structural design, and the corresponding movable scroll adopts a discrete multi-vortex tooth structure, which can reduce the clearance volume and improve the compressor performance.

[0128] In addition, the first scroll plate 11 in the present application forms a plurality of compression channels 1001, each of which is equipped with an exhaust hole 1002 and an exhaust structure. Each compression channel 1001 forms an independent compression process, which will effectively reduce the gas exhaust mass flow pulsation, gas torque pulsation, and reduce the vibration of the compressor.

[0129] Of course, in some other embodiments of the present application, the tooth head area of ​​the movable scroll adopts an integral structural design, while the fixed scroll adopts a discrete multi-scroll tooth structure, which can also improve the performance of the compressor. In the present application, the tooth head area of ​​multiple vortex teeth on the movable scroll can be designed with an integral structural design, and the corresponding fixed scroll adopts a discrete multi-scroll tooth structure, which can reduce the clearance volume and improve the performance of the compressor. The tooth head area of ​​multiple vortex teeth on the movable scroll adopts an integral structural design, and the corresponding fixed scroll adopts a discrete multi-scroll tooth structure to form multiple compression channels 1001, and each compression channel 1001 is equipped with an exhaust hole 1002 and an exhaust structure. Each compression channel 1001 constitutes an independent compression process, which will effectively reduce the gas exhaust mass flow pulsation and gas torque pulsation, and reduce the vibration of the compressor.

[0130] In addition, in the above description, the example in which the number of first vortex teeth 112 is four and the number of second vortex teeth 122 is four is mainly used for illustration. This is not a limitation on the protection scope of the present application. The number of first vortex teeth 112 in the present application is not necessarily four, and may be greater than or equal to two. It should also be emphasized that the distribution of the plurality of first vortex teeth 112 along the circumference of the first scroll disk 11 in the present application may be uniform or uneven. In addition, the tooth width and length of the plurality of first vortex teeth 112 and the plurality of second vortex teeth 122 are not necessarily the same.

[0131] Among them, the scroll teeth in this application refer to: the structure formed by the scroll profile, and the scroll profile includes the tooth head correction curve, the involute and the tooth tail connection curve. The clearance volume in this application refers to: the volume that does not participate in the compression in the compression structure is the clearance volume. The clearance volume will reduce the isentropic efficiency and volumetric efficiency of the compressor, thereby reducing the performance of the compressor.

[0132] The single-tooth scroll compression structure of an embodiment of the present application is described below with reference to the accompanying drawings.

[0133] like Fig.26 and Fig. 27 In some embodiments, the single-tooth scroll compression structure includes a third scroll plate 13 and a fourth scroll plate 14, the third scroll plate 13 includes a third bottom plate 131 and a third scroll tooth 132 arranged on the third bottom plate 131, the fourth scroll plate 14 includes a fourth bottom plate 141 and a fourth scroll tooth 142 arranged on the fourth bottom plate 141, the fourth scroll tooth 142 cooperates with the third scroll tooth 141, wherein one of the third scroll plate 13 and the fourth scroll plate 14 is a movable scroll and the other is a fixed scroll.

[0134] Combination Figure 29 to Figure 30 In some embodiments, as Fig.30 The compression unit 10 further includes an anti-self-rotation structure (not shown in the figure), the anti-self-rotation structure is relatively stationary with the fixed scroll 101, one of the movable scroll 102 and the anti-self-rotation structure is provided with at least one anti-self-rotation ring 1021, and the other is provided with a positioning portion, which can be positioned at the anti-self-rotation ring in a translational manner around a fixed radius. Optionally, a plurality of anti-self-rotation rings are processed on the back of the bottom plate of the movable scroll, and the anti-self-rotation function can be realized by cooperating with a plurality of pins fixed at other positions.

[0135] In addition, if Fig.28 and Fig.29The fixed scroll 101 is provided with an exhaust hole 1002 and an exhaust structure 1006, and the exhaust structure 1006 may include a reed valve plate 10061, a lift limiter 10062 and a fastener 10063. The reed valve plate can only be opened in one direction, and the lift is limited by the lift limiter. The above structure is a possible form of the exhaust structure.

[0136] A specific implementation of the present application is described below with reference to the accompanying drawings.

[0137] Combination Figures 1 to 30 The compressor may include a first compression unit and a second compression unit, the first compression unit is a four-tooth scroll assembly, and the second compression unit is a four-tooth scroll assembly, wherein the four-tooth scroll assembly may include the aforementioned multi-tooth scroll assembly, wherein the number of first scroll teeth and the number of second scroll teeth are four. The compressor also includes a crankshaft, which transmits torque to the first compression unit and the second compression unit. The exhaust position of the first compression unit includes an exhaust chamber, and the exhaust chamber includes an exhaust hole. The exhaust position of the second compression unit includes an exhaust chamber, and the exhaust chamber includes an exhaust hole.

[0138] according to Figure 1 In the structure, the first compression unit and the second compression unit can have the same displacement. When the first compression unit and the second compression unit have a phase difference of 180° on the crankshaft, the gas forces of the two units are in opposite directions and cancel each other out, thus reducing vibration. On the other hand, the multi-tooth vortex structure with the opposed arrangement can significantly reduce gas torque pulsation. Specifically:

[0139] like Figure 6 As shown, taking R134a refrigerant as an example, assuming that the compressor displacement is 34cc, the compression unit displacement is 17cc, the displacement of each compression channel is 4.25cc, the suction pressure is 0.3MPa, the exhaust pressure is 1.5MPa, the suction superheat is 10K, and the compressor speed is 3000rpm, then the gas torque pulsation value is 0.03N*m, and the traditional single-tooth scroll compressor is 1.26N*m, and the pulsation value is reduced by 98%. The obvious improvement of the gas torque pulsation value and the offset of the gas force will effectively improve the vibration and noise problems of the compressor.

[0140] like Figure 7 As shown, taking R134a refrigerant as an example, assuming that the compressor displacement is 34cc, the displacement of a single compression unit is 17cc, the displacement of each compression channel is 4.25cc, the suction pressure is 0.3MPa, the exhaust pressure is 1.5MPa, the suction superheat is 10K, and the compressor speed is 3000rpm, then the exhaust mass flow pulsation value is 0.010kg / s, and the traditional single-tooth scroll compressor is 0.056kg / s, and the pulsation value is reduced by 82%. Figure 1The structure in the exhaust gas compressor will effectively reduce the pulsation of the exhaust mass flow and reduce the gas noise.

[0141] In the present application, the number of the first volutes or the second volutes can be set to be greater than 2, for example, the number of the first volutes is set to 2, 3, 5 or 6, etc. The shapes and sizes of the multiple first volutes may also be different, and the shapes and sizes of the multiple second volutes may also be different. However, for performance, vibration and noise considerations, there is generally no special requirement to design multiple first volutes or multiple second volutes of different shapes and sizes. After the multiple first volutes or multiple second volutes have different sizes, the displacement of the independent compression channels formed is also different.

[0142] According to the thermal management system of the embodiment of the present application, it includes the aforementioned compressor. According to the vehicle of the embodiment of the present application, it includes the aforementioned compressor; or includes the aforementioned thermal management system. The thermal management system and vehicle provided by the present application are provided with a plurality of compression units, and the plurality of compression units are transmission-connected. By setting the rotation angle of at least two movable scrolls to have a phase difference, the gas force of the plurality of compression units can be weakened or offset, thereby effectively reducing the pulsation of the gas exhaust quality, flow rate, gas torque, etc., reducing the vibration of the compressor, improving the stability of the compressor operation, and also achieving the noise reduction of the compressor.

[0143] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present application.

[0144] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include at least one of the features. In the description of this application, the meaning of "plurality" is at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0145] In this application, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0146] In the present application, unless otherwise clearly specified and limited, a first feature being “above” or “below” a second feature may mean that the first and second features are in direct contact, or the first and second features are in indirect contact through an intermediate medium. Moreover, a first feature being “above”, “above”, and “above” a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature. A first feature being “below”, “below”, and “below” a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.

[0147] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of the different embodiments or examples, without contradiction.

[0148] Although the embodiments of the present application have been shown and described above, it can be understood that the above embodiments are exemplary and cannot be understood as limitations on the present application. Ordinary technicians in this field can change, modify, replace and modify the above embodiments within the scope of the present application.

Claims

1. A compressor (100), characterized in that: It comprises a plurality of compression units, wherein the compression units comprise a fixed scroll and a movable scroll which cooperate with each other, the movable scrolls of the plurality of compression units are transmission-connected, and the rotation angles of the movable scrolls of at least two of the compression units have a phase difference.

2. The compressor (100) according to claim 1, characterized in that: The plurality of compression units include a first compression unit (10a) and a second compression unit (10b), and the rotation angles of the movable scroll of the first compression unit (10a) and the movable scroll of the second compression unit (10b) have a phase difference.

3. The compressor (100) according to claim 2, characterized in that: The phase difference between the rotation angles of the movable scroll of the first compression unit (10a) and the movable scroll of the second compression unit (10b) is 180°.

4. The compressor (100) according to claim 2, characterized in that: The displacement of the first compression unit (10a) and the second compression unit (10b) are the same; or the displacement of the first compression unit (10a) and the second compression unit (10b) are different.

5. The compressor (100) according to claim 2, characterized in that: The plurality of compression units further includes a third compression unit (10c).

6. The compressor (100) according to claim 5, characterized in that The rotating angles of the movable scroll of the third compression unit (10c) and the movable scroll of the second compression unit (10b) have a phase difference; or, the rotating angle phase difference between the movable scroll of the first compression unit (10a) and the movable scroll of the second compression unit (10b) is 120°, the rotating angle phase difference between the movable scroll of the second compression unit (10b) and the movable scroll of the third compression unit (10c) is 120°, and the rotating angle phase difference between the movable scroll of the first compression unit (10a) and the movable scroll of the third compression unit (10c) is 120°; or, the rotating angle phase difference between the movable scroll of the first compression unit (10a) and the movable scroll of the second compression unit (10b) is 180°, and the rotating angle phase difference between the movable scroll of the second compression unit (10b) and the movable scroll of the third compression unit (10c) is 180°.

7. The compressor (100) according to claim 5, characterized in that The first compression unit (10a), the second compression unit (10b) and the third compression unit (10c) are distributed at equal intervals; or, the interval between the first compression unit (10a) and the second compression unit (10b) is different from the interval between the second compression unit (10b) and the third compression unit (10c).

8. The compressor (100) according to claim 5, characterized in that The displacements of the first compression unit (10a), the second compression unit (10b) and the third compression unit (10c) are the same; or the displacements of at least two of the first compression unit (10a), the second compression unit (10b) and the third compression unit (10c) are different.

9. The compressor (100) according to claim 2, characterized in that: The plurality of compression units further include a fourth compression unit (10d) and a fifth compression unit (10e).

10. The compressor (100) according to claim 9, characterized in that The movable scroll of the fourth compression unit (10d) has a phase difference with the movable scroll of the fifth compression unit (10e); or, the rotating angle phase difference between the movable scroll of the first compression unit (10a) and the movable scroll of the second compression unit (10b) is 90°, the rotating angle phase difference between the movable scroll of the second compression unit (10b) and the movable scroll of the fourth compression unit (10d) is 90°, the rotating angle phase difference between the movable scroll of the fourth compression unit (10d) and the movable scroll of the fifth compression unit (10e) is 90°, and the rotating angle phase difference between the movable scroll of the fourth compression unit (10d) and the movable scroll of the fifth compression unit (10e) is 90°. The rotation angle phase difference between the movable scroll of the first compression unit (10a) and the movable scroll of the fifth compression unit (10e) is 90°; or the rotation angle phase difference between the movable scroll of the first compression unit (10a) and the movable scroll of the second compression unit (10b) is 180°, the rotation angle phase difference between the movable scroll of the second compression unit (10b) and the movable scroll of the fourth compression unit (10d) is 0, and the rotation angle phase difference between the movable scroll of the fourth compression unit (10d) and the movable scroll of the fifth compression unit (10e) is 180°.

11. The compressor (100) according to claim 9, characterized in that: The first compression unit (10a), the second compression unit (10b), the fourth compression unit (10d) and the fifth compression unit (10e) are distributed at equal intervals; or at least one of the first compression unit (10a), the second compression unit (10b), the fourth compression unit (10d) and the fifth compression unit (10e) has a different interval from the other intervals.

12. The compressor (100) according to claim 9, characterized in that The displacements of the first compression unit (10a), the second compression unit (10b), the fourth compression unit (10d) and the fifth compression unit (10e) are the same; or the displacements of at least two of the first compression unit (10a), the second compression unit (10b), the fourth compression unit (10d) and the fifth compression unit (10e) are different.

13. The compressor (100) according to any one of claims 1 to 12, characterized in that: The plurality of compression units are configured such that gas forces of the stationary scroll cancel each other out; or, the plurality of compression units are configured such that torques caused by gas forces of the stationary scroll cancel each other out.

14. The compressor (100) according to any one of claims 1 to 12, characterized in that: The compressor (100) further includes a crankshaft (30), wherein the crankshaft (30) is connected to the movable scrolls of the plurality of compression units; and / or the plurality of compression units are distributed along the axial direction; and / or the exhaust side of the stationary scroll is provided with an exhaust chamber (1007), and the wall of the exhaust chamber (1007) is provided with an exhaust hole (1008); and / or the plurality of compression units are configured to be connected in parallel with each other.

15. The compressor (100) according to claim 1, characterized in that At least one of the plurality of compression units is configured as a multi-tooth scroll compression structure.

16. The compressor (100) according to claim 15, characterized in that The multi-tooth scroll compression structure comprises a first scroll plate (11) and a second scroll plate (12), wherein the first scroll plate (11) comprises a first bottom plate (111) and a plurality of first scroll teeth (112) arranged on the first bottom plate (111), and the second scroll plate (12) comprises a second bottom plate (121) and a plurality of second scroll teeth (122) arranged on the second bottom plate (121), wherein the plurality of first scroll teeth (112) form a plurality of compression passages (1001), and the first bottom plate (111) or the second scroll teeth (122) form a plurality of compression passages (1001). The second bottom plate (121) is provided with a plurality of exhaust holes (1002) respectively connected to the plurality of compression channels (1001); the plurality of second scroll teeth (122) are respectively provided in the plurality of compression channels (1001) and respectively cooperate with the plurality of first scroll teeth (112) to drive the fluid along the compression channels (1001) to the corresponding exhaust holes (1002); wherein one of the first scroll plate (11) and the second scroll plate (12) is a movable scroll and the other is a stationary scroll.

17. The compressor (100) according to claim 16, characterized in that The fixed scroll is provided with a first central through hole (1004), the plurality of exhaust holes (1002) are provided on the fixed scroll and distributed around the first central through hole (1004), the movable scroll is provided with a second central through hole (1005), and the compressor (100) further includes a crankshaft (30), the crankshaft (30) includes a main journal and a connecting rod journal, the main journal is passed through the first central through hole (1004), and the connecting rod journal is passed through the second central through hole (1005).

18. The compressor (100) according to claim 1, characterized in that At least one of the plurality of compression units is configured as a single-tooth scroll compression structure.

19. The compressor (100) according to claim 18, characterized in that The single-tooth scroll compression structure comprises a third scroll (13) and a fourth scroll (14), wherein the third scroll (13) comprises a third bottom plate (131) and a third scroll tooth (132) arranged on the third bottom plate (131), and the fourth scroll (14) comprises a fourth bottom plate (141) and a fourth scroll tooth (142) arranged on the fourth bottom plate (141), and the fourth scroll tooth (142) cooperates with the third scroll tooth (132), wherein one of the third scroll (13) and the fourth scroll (14) is a movable scroll and the other is a stationary scroll.

20. The compressor (100) according to any one of claims 1, 15-19, characterized in that: The compression unit also includes a crankshaft (30), the compression units are distributed along the crankshaft (30) and are drivingly connected to the crankshaft (30), the crankshaft (30) has a driving end and a free end, the driving end is used to connect a driving member, the compression unit connected to the free end is configured as a single-tooth scroll compression structure, and the other compression units are configured as multi-tooth scroll compression structures.

21. The compressor (100) according to claim 1, characterized in that The compression unit also includes an anti-self-rotation structure, which is relatively stationary with the fixed scroll. One of the movable scroll and the anti-self-rotation structure is provided with at least one anti-self-rotation ring, and the other is provided with a positioning portion, which can be positioned translationally around a fixed radius on the anti-self-rotation ring.

22. A thermal management system, characterized in that: Comprising the compressor (100) according to any one of claims 1-21.

23. A vehicle, characterized in that: A compressor (100) comprising any one of claims 1 to 21; or a thermal management system according to claim 22.

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