Heater, compressor, thermal management system and vehicle

Abstract

This utility model discloses a heater, compressor, thermal management system, and vehicle, belonging to the field of heater technology. The heater includes a first heating tube and a second heating tube, with a minimum tube spacing of L between the first and second heating tubes. The first heating tube includes a first tube body and a first heating element, and the second heating tube includes a second tube body and a second heating element. The average of the maximum dimensions H1 of the first heating element and H2 of the second heating element is H, and the average of the outer diameters D1 and D2 of the first and second heating tubes is D, where 0.45 ≤ X ≤ 2.85. The heater according to this utility model embodiment reduces the impact of noise or heat radiation on the operational stability of the heater.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and in particular to a heater, compressor, thermal management system and vehicle. Background Technology

[0002] A compressor typically includes a compression mechanism and an electronic control unit. The compression mechanism compresses the refrigerant to create a pressure difference, compressing the low-pressure, low-temperature gaseous refrigerant drawn in through the intake port into a high-pressure, high-temperature gaseous refrigerant that is discharged from the exhaust port, thus forming a physical transformation and flow of the refrigerant. The electronic control unit controls the operation of the compression mechanism.

[0003] In related technologies, the compressor integrates a heater. The distance between different heating parts in the heater can affect the heater's noise or radiant heat, thus affecting the stability of the heater's operation. Utility Model Content

[0004] One objective of this invention is to provide a heater, compressor, thermal management system, and vehicle that reduces the impact of noise or thermal radiation on the operational stability of the heater.

[0005] The heater according to an embodiment of the present invention includes a first heating tube and a second heating tube, which are arranged side by side and spaced apart. The minimum distance between the first heating tube and the second heating tube is L. The first heating tube includes a first tube body and a first heating element disposed on the outer surface of the first tube body. The second heating tube includes a second tube body and a second heating element disposed on the outer surface of the second tube body. The average of the maximum dimension H1 of the first heating element along the axial direction of the first heating tube and the maximum dimension H2 of the second heating element along the axial direction of the second heating tube is H. The average of the outer diameter D1 of the first heating tube and the outer diameter D2 of the second heating tube is D. 0.45≤X≤2.85 , .

[0006] The heater according to the embodiments of this utility model reduces the impact of noise or heat radiation on the operational stability of the heater.

[0007] In addition, the heater according to the above embodiments of the present invention may also have the following additional technical features: In some embodiments, 0.53 ≤ X ≤ 1.75.

[0008] In some embodiments, 0.95 ≤ X ≤ 1.75.

[0009] In some embodiments, 0.77 ≤ D1 / D2 ≤ 1.3.

[0010] In some embodiments, 100mm≤H<116mm, 0.55≤X≤2.85; or, 116mm≤H<132mm, 0.50≤X≤2.50; or, 132mm≤H≤150mm, 0.45≤X≤2.15.

[0011] In some embodiments, 100mm≤H≤116mm, 0.65≤X≤2.35; or, 116mm≤H<132mm, 0.60≤X≤2.00; or, 132mm≤H≤150mm, 0.55≤X≤1.65.

[0012] In some embodiments, 100mm≤H≤116mm, 1.00≤X≤2.20; or, 116mm≤H<132mm, 0.95≤X≤1.85; or, 132mm≤H≤150mm, 0.90≤X≤1.50.

[0013] In some embodiments, 16mm≤D1≤35mm; or, 16mm≤D2≤35mm; or, 9mm≤L≤47mm; or, 100mm≤H1≤150mm; or, 100mm≤H2≤150mm.

[0014] In some embodiments, the heater further includes a connector that connects the first heating tube and the second heating tube, with the first heating tube and the second heating tube located on the same side of the connector.

[0015] The compressor according to an embodiment of the present invention includes: a housing assembly; a motor assembly disposed within the housing assembly; and the aforementioned heater, at least a portion of which is disposed within the housing assembly, wherein the heater and the motor assembly are distributed along the axis of the motor assembly.

[0016] In some embodiments, the first heating element and the second heating element are arranged side by side, the outer diameter of the motor assembly is W, and the angle between the axis of the first heating element and the axis of the motor assembly is γ. , .

[0017] According to the thermal management system of this utility model, the thermal management system includes the aforementioned compressor.

[0018] The vehicle according to this utility model includes the aforementioned thermal management system. Attached Figure Description

[0019] Figure 1 This is a cross-sectional view of a compressor according to an embodiment of the present invention.

[0020] Figure 2This is a partial explosion diagram of a compressor according to an embodiment of the present invention.

[0021] Figure 3 This is a schematic diagram of a heater according to one embodiment of the present invention.

[0022] Figure 4 This is a partial schematic diagram of a heater according to one embodiment of the present invention.

[0023] Figure 5 This is a cross-sectional view of a heater according to an embodiment of the present invention.

[0024] Figure 6 This is another cross-sectional view of a heater according to one embodiment of the present invention.

[0025] Figure 7 This is a schematic diagram of the inter-tube thermal radiation of a heater according to an embodiment of the present invention.

[0026] Figure 8 This is a schematic diagram of the inter-tube thermal radiation of a heater according to another embodiment of the present invention.

[0027] Figure 9 This is a schematic diagram comparing X with noise and radiant heat Q.

[0028] Figure 10 This is a schematic diagram showing the comparison between X, noise, and radiant heat Q under different ranges of H values.

[0029] Figure 11 This is a schematic diagram comparing X with noise and radiant heat Q when 100mm≤H<116mm.

[0030] Figure 12 This is a schematic diagram comparing X with noise and radiant heat Q when 116mm≤H<132mm.

[0031] Figure 13 This is a schematic diagram comparing X with noise and radiant heat Q when 132mm≤H≤150mm.

[0032] Figure 14 This is a schematic diagram illustrating how to determine the equivalent outer diameter of a heating tube with an elliptical cross-section.

[0033] Figure 15 This is a schematic diagram illustrating how to determine the equivalent outer diameter of a heating tube with a square cross-section.

[0034] Figure 16 This is a schematic diagram of a stator assembly according to an embodiment of the present invention.

[0035] Figure 17 This is a schematic diagram of a rotor assembly according to an embodiment of the present invention.

[0036] Figure 18 This is a schematic diagram showing the comparison between the ratio Di / W and the torque rating of the motor assembly in one embodiment of the present invention.

[0037] Figure 19 This is a schematic diagram showing the comparison between the ratio H / D and flow resistance and heat loss in one embodiment of the present invention.

[0038] Figure 20 This is a schematic diagram showing the comparison between the ratio (L+2×D) / W and cost and power rating of one embodiment of the present invention.

[0039] Figure 21 This is a schematic diagram showing the comparison between the ratio (H×sinγ) / W and cost and power rating of one embodiment of the present invention.

[0040] Figure label: Compressor 10, housing assembly 11, first chamber 11A, second chamber 11B, third chamber 11C, refrigerant intake port 11E, refrigerant exhaust port 11F, first housing 111, second housing 112, third housing 113, motor assembly 12, stator assembly 121, stator core 1211, stator winding 1212, rotor assembly 122, rotor core 1221, permanent magnet 1222, heater 13, inlet 13A, outlet 13B, first heating tube 131, first tube body 1311, first heating element 1312, second heating tube 132, second tube body 1321, second heating element 1322, connector 133, compression assembly 14, controller 15, motor assembly axis L12, heater axis L13. Detailed Implementation

[0041] In this invention, the heater 13 is integrated into the compressor 10, which improves the integration and space utilization of the compressor 10. The heater 13 typically includes a first heating element 131 and a second heating element 132. The heat radiation between the first heating element 131 and the second heating element 132 can affect each other. If the distance between the first heating element 131 and the second heating element 132 is too close, it may cause the temperature of the first heating element 131 and the second heating element 132 to become too high, which may easily trigger the temperature protection or even cause the heater 13 to overheat and burn out. If the distance between the first heating element 131 and the second heating element 132 is increased in order to reduce the heat radiation between them, it will not only increase the size and weight of the heater 13, but also increase the overall noise radiation area of ​​the compressor 10, resulting in increased noise from the compressor 10.

[0042] Therefore, this invention provides a heater 13, aiming to define the optimal solution range for balancing noise and heat radiation by defining the heater 13 and the relationship between various relevant parameters of the heater 13 and the motor assembly. This invention proposes a heater 13, a compressor 10, a thermal management system, and a vehicle. The compressor 10 has good environmental adaptability and occupies little space.

[0043] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain this utility model, and should not be construed as limiting this utility model.

[0044] like Figure 1 and Figure 2 The compressor 10 according to an embodiment of the present invention includes: a housing assembly 11, a motor assembly 12, and a heater 13. The motor assembly 12 is disposed within the housing assembly 11, and at least a portion of the heater 13 is disposed within the housing assembly 11. The heater 13 and the motor assembly 12 are distributed along the axis L12 of the motor assembly. The housing assembly 11 provides support and installation space for the motor assembly 12 and the heater 13. The compressor 10 may further include a compression assembly 14, and the motor assembly 12 may be connected to the compression assembly 14 to drive the compression assembly 14 to operate. For example, the housing assembly 11 may have a first chamber 11A and a second chamber 11B. The compression assembly 14 can drive refrigerant (which may include Freon, tetrafluoroethane, or tetrafluoropropylene, etc.) to flow from the first chamber 11A to the second chamber 11B. The refrigerant is output from the second chamber 11B, undergoes heat exchange through a heat exchanger or other structure, and then flows back to the first chamber 11A, forming a refrigerant cycle. The heater 13 is integrated into the compressor 10. The heater 13 can be used to heat the heat exchange medium (which may include water or other fluid media). It can also be connected to the heat exchanger through external pipelines to achieve the circulation of the heat exchange medium. Figure 1 A cross-sectional view of the compressor 10 is shown, illustrating the relative positions of the heater 13 and other components of the compressor 10. Figure 2 A partial exploded view of the compressor 10 is shown, illustrating the relative positions of components such as the first heating tube 131, the second heating tube 132, the lower flange 1331, and the water box 1332 of the heater 13.

[0045] like Figure 1As shown, the motor assembly 12 is disposed on the housing assembly 11, and the motor assembly 12 includes a stator assembly 121 and a rotor assembly 122. The stator assembly 121 can be stationary relative to the housing assembly 11, while the rotor assembly 122 is rotatably coupled to the stator assembly 121. The stator assembly 121 can drive the rotor assembly 122 to rotate via electromagnetic drive. The rotor assembly 122 can be connected to the compression assembly 14 of the compressor 10 to drive the compression assembly 14. Additionally, as... Figure 16 The stator assembly 121 includes a stator core 1211 and a stator winding 1212; such as Figure 17 The rotor assembly 122 includes a rotor core 1221 and a permanent magnet 1222. The stator core 1211 may have winding slots, and stator windings 1212 may be disposed in the winding slots. The rotor core 1221 may include magnet slots, and the permanent magnet 1222 may be disposed within these magnet slots. Of course, the motor assembly 12 in this invention can also take other forms, for example, by attaching the permanent magnet 1222 to the outer surface of the rotor core 1221. The motor assembly 12 in this invention can be disposed within the housing assembly 11. For example, the motor assembly 12 can be disposed within the first cavity 11A of the aforementioned housing assembly 11. The stator assembly 121 can be interference-fitted with the inner surface of the housing assembly 11 to achieve stable installation of the motor assembly 12. The rotor assembly 122 is rotatably disposed within the stator assembly 121, or the stator assembly 121 can be arranged around the rotor assembly 122.

[0046] like Figures 2 to 5 The heater 13 has an inlet 13A and an outlet 13B, which can be located on the same side of the heater 13. The heater 13 includes at least one heating tube (such as a first heating tube 131 and / or a second heating tube 132 described below) with an internal flow channel located between the inlet 13A and the outlet 13B. The heating tube is used to heat the heat exchange medium flowing through the flow channel, and the cross-section of the heating tube perpendicular to the flow channel axis is configured as a closed section surrounding the flow channel. The heater 13 can be located in the housing assembly 11. By installing the heater 13 in the housing assembly 11, the compressor 10 can meet both the heating requirements of the heater 13 and the user's heat exchange requirements through the high-pressure refrigerant discharged from the second chamber 11B, thus enabling the compressor 10 to perform multiple functions. This also improves the environmental adaptability of the compressor 10, resulting in a simple, efficient, compact, space-saving, and low-cost compressor 10. The closed section of the heating tube in the heater 13 surrounding the flow channel improves the sealing performance of the heater 13, making the compressor 10 safer to operate. Additionally, as... Figure 1 and Figure 2Alternatively, at least a portion of the heater 13 can be disposed within the housing assembly 11. For example, the housing assembly 11 may also include a third cavity 11C. The first cavity 11A, the second cavity 11B, and the third cavity 11C are distributed along the axis L12 of the motor assembly, and at least a portion of the heater 13 can be disposed within the third cavity 11C.

[0047] Optionally, such as Figure 1 and Figure 2 The housing assembly 11 may include a first housing 111, a second housing 112, and a third housing 113. The first housing 111, second housing 112, and third housing 113 may be arranged along the axis L12 of the motor assembly. The first housing 111 is located between the second housing 112 and the third housing 113. A first cavity 11A may be located between the first housing 111 and the second housing 112. The third cavity 11C may be at least partially located between the first housing 111 and the third housing 113 (or at least partially located within the third housing 113). Additionally, a mounting port may be provided at one end of the third cavity 11C in the vertical direction, and at least a portion of the heater 13 may be inserted into the third cavity 11C through the mounting port. The motor assembly 12 may be located within the first housing 111, and the compression assembly 14 may be located within the second housing 112 or between the first housing 111 and the second housing 112.

[0048] Additionally, the compressor 10 also includes a controller 15, which is connected to the heater 13 and the motor assembly 12, and can supply power to the heater 13 and the motor assembly 12. Figure 1 The third housing 113 defines a third cavity 11C on one side of the first housing 111. The heater 13 and controller 15 are placed inside the third cavity 11C. A motor assembly 12 and a compression assembly 14 are disposed in the area between the other side of the first housing 111 and the second housing 112. The compressor 10 has a refrigerant exhaust port 11F and a refrigerant intake port 11E. The controller 15 can control the heating assembly and the motor assembly 12. The first housing 111 is sealed to the second housing 112, and the first housing 111 is sealed to the third housing 113. The controller 15 can simultaneously and independently control the heater 13 and the motor assembly 12, and can adjust the heating power of the heater 13 and the speed of the motor assembly 12. This compressor 10, through the integrated controller 15, can simultaneously perform refrigerant compression and heat exchange medium heating functions. This compressor 10 has advantages such as smaller overall size, lighter weight, and lower cost. The controller 15 can be positioned between the first housing 111 and the third housing 113.

[0049] like Figures 3 to 5As shown, heater 13 includes at least one heating tube (such as the first heating tube 131 and / or the second heating tube 132 described below). Heater 13 is disposed on housing assembly 11, and heater 13 and motor assembly 12 are distributed along the axis L12 of motor assembly 12. This avoids heater 13 occupying the radial space of compressor 10, improving the space utilization of compressor 10. The heating tube may include a tube body and a heating element. The heating element may be disposed on the outer surface of the tube body, and the heating element can heat the flow channel inside the tube body by heating. The tube body may be configured as a circular tube, a square tube, or other shaped tube, etc., and a flow channel with a closed cross-section (the cross-section is perpendicular to the axis of the tube body) is formed inside the tube body. The heating element may be disposed around the outer surface of the tube body, for example, the heating element may be stacked on the outer surface of the tube body, wherein the heating element may be a thick film heating structure, etc. Thick film heating technology is a highly efficient, fast, and compact heating method. Its core principle is to print different functional electronic pastes layer by layer onto a substrate material (tube body) through processes such as screen printing, and then sinter them at high temperatures (usually 800°C-900°C) to finally form an integrated heating element. It can include an insulating dielectric layer, a resistive heating layer, and a protective encapsulation layer.

[0050] The outer diameter of the heating tube can be the diameter of the outer surface of the tube body. The heating element can be disposed on the outer surface of the tube body, and its thickness is typically small; therefore, the diameter of the outer surface of the heating element can be approximated as the outer diameter of the heating tube. The heating tube in this invention can be either circular or non-circular. When the heating tube is circular, its outer diameter is the same as the outer diameter of the heating tube; when the heating tube is non-circular, the diameter of a circular tube with the same cross-sectional area as the non-circular tube is used as the outer diameter of the heating tube. For example, as... Figure 14 The heating element is an elliptical tube. The area enclosed by the outer edge of the cross-section of the elliptical tube in a plane perpendicular to the axis is elliptical. This ellipse can be equivalent to an equivalent circle with the same area. Therefore, the diameter of this equivalent circle is taken as the outer diameter of the elliptical tube. For example, such as... Figure 15 The heating element is a square tube. The area enclosed by the outer edge of the cross-section of the square tube in the plane perpendicular to the axis is square (it can be a rectangle or a square, with rounded corners). This square can be equivalent to an equivalent circle with the same area, and the diameter of this equivalent circle is the outer diameter of the square tube. Alternatively, the heating element can also be other regular or irregular shapes. The area enclosed by the outer edge of the cross-section of the heating element can be equivalent to a circle with the same area, and the diameter of this circle is the outer diameter of the heating element. That is, when the area enclosed by the outer edge of the cross-section of the heating element is S11, the outer diameter of the heating element is... The cross-section of the heating element is perpendicular to its axis.

[0051] The maximum dimension of the heating element along the axial direction of the heating tube can be the maximum value among the dimensions of the heating element at different positions along the axial direction of the heating tube. For example, the maximum value can be taken as the maximum dimension of the heating element along the axial direction of the heating tube by measuring the length of the heating element at different positions using a ruler. The heating element can be a thick-film heating structure. When the heating element is a thick-film heating structure, the maximum dimension of the heating element along the axial direction of the heating tube can be the maximum dimension of the thick-film heating structure along the axial direction of the heating tube. For example, the heating element may include an insulating dielectric layer, a resistance heating layer, an electrode layer, and a protective glaze layer sequentially formed on the surface of the heating tube using screen printing technology. Typically, the insulating dielectric layer and the protective glaze layer in the thick-film heating structure have the same length along the axial direction of the heating tube and are longer than the resistance heating layer and the electrode layer. Therefore, the maximum dimension of the insulating dielectric layer and the protective glaze layer along the axial direction of the heating tube can be taken as the maximum dimension of the heating element along the axial direction of the heating tube. When the lengths of the insulating dielectric layer and the protective glaze layer are different, the longer one of the insulating dielectric layer and the protective glaze layer is taken as the maximum dimension of the heating element along the axial direction of the heating tube. Of course, the heating element can also be stacked on the outer surface of the tube body, or in other forms. The maximum dimension of the heating element along the axial direction of the heating tube can be determined using corresponding measurement methods. Additionally, the heater 13 may include a mounting plate and a connector 133. The connector 133 is used to connect multiple heating tubes. For example, the heating tubes may include a first heating tube 131 and a second heating tube 132. The connector 133 connects the first heating tube 131 and the second heating tube 132, forming a U-shaped structure. At least a portion of the heater 13 can be installed inside the housing assembly 11. The mounting plate covers the housing assembly 11 to stably position the heating tubes within the housing assembly 11. The maximum length of the heating element along the axial direction of the heating tube is generally not greater than the distance between the mounting plate and the connector 133.

[0052] like Figure 1 The compressor 10 of this invention includes a heater 13, a compression assembly 14, and a motor assembly 12, etc. The motor assembly 12 can be placed inside the housing assembly 11. The motor assembly 12 can include a stator assembly 121 and a rotor assembly 122, with the axis of the rotor assembly 122 coinciding with the axis of the stator assembly 121. Figure 16 The stator assembly 121 includes a stator core 1211 and a stator winding 1212, the stator winding 1212 being wound on the stator core 1211, such as... Figure 17The rotor assembly 122 includes a rotor core 1221 and a permanent magnet 1222. The rotor core 1221 is provided with a magnet slot, and a permanent magnet 1222 (e.g., a magnet) is placed in the magnet slot. The heater 13 may include two heating tubes with the same structure (i.e., the first heating tube 131 and the second heating tube 132 described below) and are connected by a connector 133 to form a U-shape. An insulating layer is provided on the surface of the heating tube.

[0053] like Figures 3 to 5 The heater 13 according to an embodiment of the present invention includes a first heating tube 131 and a second heating tube 132, which are arranged side by side and spaced apart. The minimum distance between the first heating tube 131 and the second heating tube 132 is L. The minimum distance between the first heating tube 131 and the second heating tube 132 can be measured by inserting calipers between them. Figures 3 to 8 The first heating element 131 includes a first tube body 1311 and a first heating element 1312. The first heating element 1312 is disposed on the outer surface of the first tube body 1311. The maximum dimension of the first heating element 1312 along the axial direction of the first heating element 131 is H1, and the outer diameter of the first heating element 131 is D1. The second heating element 132 may include a second tube body 1321 and a second heating element 1322. The second heating element 1322 is disposed on the outer surface of the second tube body 1321. The maximum dimension of the second heating element 1322 along the axial direction of the second heating element 132 is H2, and the outer diameter of the second heating element 132 is D2. H1 and H2 can be determined with reference to the aforementioned maximum dimension of the heating element along the axial direction of the heating element, and D1 and D2 can be determined with reference to the aforementioned outer diameter of the heating element.

[0054] In addition, the average of the maximum dimension H1 of the first heating element 1312 along the axial direction of the first heating tube 131 and the maximum dimension H2 of the second heating element 1322 along the axial direction of the second heating tube 132 is H, that is, H = (H1 + H2) / 2. The average of the outer diameter dimension D1 of the first heating tube 131 and the outer diameter dimension D2 of the second heating tube 132 is D, that is, D = (D1 + D2) / 2.

[0055] in, 0.45≤X≤2.85 , .

[0056] In a cross-section perpendicular to the axis of the first heating tube 131 or the axis of the second heating tube 132, It is the average of the circumference of the outer side of the first heating tube 131 and the circumference of the outer side of the second heating tube 132. It is the average of the arc length of the central angle α on the outer side of the first heating tube 131 and the arc length of the central angle α on the outer side of the second heating tube 132; It can be approximated as the area between the arc of the central angle α on the outer surface of the first heating tube 131 and the arc of the central angle α on the outer surface of the second heating tube 132, as shown in the attached figure. Figure 7 and Figure 8 The area marked is 70% of the total area.

[0057] The total arc length of the arc after subtracting the arc of the central angle α from the arc of the central angle β on the outer surface of the first heating tube 131 and the total arc length of the arc after subtracting the arc of the central angle α from the arc of the central angle β on the outer surface of the second heating tube 132 are averaged. It can be approximated as the distance between the arc of the central angle β on the outer surface of the first heating tube 131 after removing the arc of the central angle α and the arc of the central angle β on the outer surface of the second heating tube 132 after removing the arc of the central angle α. It can be approximated as the area between the arc of the central angle β on the outer surface of the first heating tube 131 minus the arc of the central angle α, and the arc of the central angle β on the outer surface of the second heating tube 132 minus the arc of the central angle α. (Refer to Appendix) Figure 7 and Figure 8 The sum of the areas marked as 15% in the middle. Among them, It can be approximated as Figure 7 and Figure 8 The length dimensions of the 15% area are marked in the middle. It can be approximated as Figure 7 and Figure 8 The total width of the area marked as 15% is specified.

[0058] Wherein, the arc of the central angle β on the outer side of the first heating tube 131 is directly opposite to the arc of the central angle β on the outer side of the second heating tube 132; the arc of the central angle α on the outer side of the first heating tube 131 is directly opposite to the arc of the central angle α on the outer side of the second heating tube 132.

[0059] Furthermore, the mutual thermal radiation between the first heating tube 131 and the second heating tube 132 decreases as the distance gradually increases. The distance between the arc of the central angle α on the outer surface of the first heating tube 131 and the arc of the central angle α on the outer surface of the second heating tube 132 is the closest. The distance between the arc of the central angle β on the outer surface of the first heating tube 131 minus the arc of the central angle α and the arc of the central angle β on the outer surface of the second heating tube 132 minus the arc of the central angle α is slightly farther. The distance between other areas on the outer surface of the first heating tube 131 and the outer surface of the second heating tube 132 is even farther, and the mutual thermal radiation between them can be ignored.

[0060] 0.7 is the thermal radiation coefficient between the arc of the central angle α on the outer surface of the first heating tube 131 and the arc of the central angle α on the outer surface of the second heating tube 132. Therefore, It can be approximated as the product of the area between the arc of the central angle α on the outer surface of the first heating tube 131 and the arc of the central angle α on the outer surface of the second heating tube 132 and the thermal radiation coefficient. 0.3 is the thermal radiation coefficient between the arc of the outer surface of the first heating tube 131 after subtracting the arc of the central angle α from the arc of the central angle β in the outer surface of the second heating tube 132, and the arc of the outer surface of the second heating tube 132 after subtracting the arc of the central angle α from the arc of the central angle β. Therefore, It can be approximated as the product of the area between the arc of the central angle β on the outer surface of the first heating tube 131 minus the arc of the central angle α and the arc of the central angle β on the outer surface of the second heating tube 132 minus the arc of the central angle α, and the thermal radiation coefficient.

[0061] therefore, It can reflect the thermal radiation between the first heating tube 131 and the second heating tube 132.

[0062] α and β are determined empirically and experimentally, reflecting the regions with different radiation levels between the first heating tube 131 and the second heating tube 132. Specifically, as shown in the attached... Figure 7 and Figure 8 As shown, when the spacing or outer diameter of the first heating tube 131 and the second heating tube 132 are different, the high radiation area (see attached diagram) Figure 7 and Figure 8 (70% of the area is marked) and low-radiation areas (attached) Figure 7 and Figure 8 The values ​​of the central angles α and β (indicated by the 15% area) will change. For example, when the distance between the first heating tube 131 and the second heating tube 132 is small, or when the outer diameter of the first heating tube 131 and the second heating tube 132 is large, the central angles α and β of the arcs corresponding to the high-radiation and low-radiation regions are larger; conversely, when the distance between the first heating tube 131 and the second heating tube 132 is large, or when the outer diameter of the first heating tube 131 and the second heating tube 132 is small, the central angles α and β of the arcs corresponding to the high-radiation and low-radiation regions are smaller. Experiments have shown that the values ​​of the central angles α and β are related to... Proportional.

[0063] In addition, combined with such Figure 7 and Figure 8 70% of the heat radiated from the first heating tube 131 to the second heating tube 132 is concentrated in Figure 7 and Figure 8 In the region corresponding to the central angle α, 30% of the heat radiated from the first heating tube 131 to the second heating tube 132 is concentrated in... Figure 7and Figure 8 The region corresponding to the central angle β-α; the heat radiated from other regions of the first heating tube 131 to the second heating tube 132 is low and negligible. The heat radiation from the second heating tube 132 to the first heating tube 131 is similar.

[0064] set up After conducting numerous experiments with different values ​​of α, it was found that the values ​​of α basically conform to the curve with a slope of 44.56. The value of β basically conforms to the curve with a slope of 54.84. .

[0065] As attached Figure 7 and Figure 8 As shown, within the arc length range corresponding to the circular angle α, the radiated heat from the first heating tube 131 to the second heating tube 132 is relatively high; within the arc length range corresponding to the circular angle β-α, the radiated heat from the first heating tube 131 to the second heating tube 132 is relatively low. This reflects the overall level of radiated heat from the first heating tube 131 to the second heating tube 132.

[0066] This can reflect the area of ​​the heating structure of the first heating tube 131 and the second heating tube 132 in the cross-section passing through the axis of the first heating tube 131 and the axis of the second heating tube 132, as shown in the attached figure. Figure 5 Therefore, X can reflect the heat radiation, noise level, and space occupied by heater 13 to a certain extent. The value of X can be set to 0.45, 0.50, 0.52, 0.55, 0.8, 1.0, 1.5, 2.0, 2.5, 2.8, or 2.85, etc.

[0067] In addition, due to The ratio is too small to be easily measured, so the parameter 0.01 was introduced.

[0068] like Figure 9 The diagram illustrates the relationship between X and noise and radiant heat Q, showing the correspondence between different values ​​of X and noise / radiant heat Q. The left axis represents the noise power coordinate value, and the right axis represents the radiant heat Q resulting from the interaction between the first heating tube 131 and the second heating tube 132. The dashed line represents the relationship curve between X and noise; the solid line represents the relationship curve between X and radiant heat Q.

[0069] Studies have found that as the number X increases, the radiant area between the first heating tube 131 and the second heating tube 132 increases, the radiant heat Q increases, and the mutual influence of the radiant heat of the first heating tube 131 and the second heating tube 132 also increases. In severe cases, this can affect the normal operation of the heater 13 and even lead to a decrease in its lifespan, thus affecting the service life of the heater 13. As the number X decreases, the area of ​​external noise radiated by the entire heater 13 increases, resulting in noise degradation.

[0070] In summary, considering both noise and radiant heat, X should be controlled within a relatively reasonable range to achieve a balance between the reliability and noise performance of the compressor 10 and the heater 13.

[0071] From the appendix Figure 9 As can be seen, when X is relatively small, for example, X < 0.45, although the radiant heat of heater 13 is at a low level, the noise during the operation of heater 13 is relatively large, leading to increased compressor noise. When X is relatively large, for example, X > 2.85, although the noise during the operation of heater 13 is low, the radiant heat of heater 13 is at a high level, affecting the normal operation and service life of heater 13. Therefore, in this invention, X is limited to the range of 0.45 to 2.85, controlling the noise level and radiant heat within an appropriate range, which can reduce the noise and radiant heat during the operation of heater 13, thereby improving the stability and service life of heater 13.

[0072] According to the embodiment of the present invention, by limiting the range of values ​​for X, the heater 13 can reduce the impact of noise or radiant heat on the operational stability of the heater 13, thereby improving the stability and service life of the heater 13.

[0073] In addition, from the appendix Figure 9 As can be seen, when 0.95≤X≤1.75, the noise level and thermal radiation level of heater 13 can be within a better range, which has a greater effect on improving the stability and service life of heater 13.

[0074] Furthermore, it should be noted that X in this invention is influenced by D1, D2, L, H1, and H2. To obtain a more optimal X region, in addition to considering the balance between D1, D2, L, H1, and H2, the impact of H on the overall manufacturing difficulty of the heater 13 and the overall volume of the compressor 10 must also be considered. If H is too large, it will obviously lead to increased cost and volume. Moreover, the compressor 10 of this invention needs to be installed within the automotive air conditioning system; if its volume is too large, it will cause installation difficulties or even make installation impossible. Conversely, if H is too small, it will also affect the heating effect and prevent it from serving the automotive air conditioning system.

[0075] Therefore, in this invention, the range of X is further limited for different values ​​of H, in order to optimize the performance of heater 13 according to different values ​​of H. For example... Figure 10 In some embodiments, as the value of H gradually increases, the value of X can be appropriately reduced to improve the performance of heater 13, which can greatly optimize the performance of heater 13. Therefore, this invention limits the range of X values ​​for different ranges of H values.

[0076] like Figure 11 The diagram shows the changes in radiant heat Q and noise of heater 13 when 100mm ≤ H < 116mm. It can be seen that when 0.55 ≤ X ≤ 2.85, the radiant heat Q and noise of heater 13 are at a good level. Therefore, in this invention, when 100mm ≤ H < 116mm, the value of X is set within the range of 0.55 to 2.86. For example, H can be 100mm, 105mm, 110mm, 113mm, or 115mm, and the value of X can be set to 0.55, 0.8, 1.0, 1.5, 2.0, 2.5, 2.8, or 2.85. Furthermore, when 100mm ≤ H ≤ 116mm, setting the value of X to 0.65 ≤ X ≤ 2.35 can further reduce the radiant heat between the first heating tube 131 and the second heating tube 132, and reduce the noise during the operation of compressor 10. When 100mm≤H≤116mm, the value of X is set to 1.00≤X≤2.20, and the heater 13 and the compressor 10 with the heater 13 have better performance.

[0077] like Figure 12 The diagram shows the changes in radiant heat Q and noise of heater 13 when 116mm ≤ H < 132mm. It can be seen that when 0.50 ≤ X ≤ 2.50, the radiant heat Q and noise of heater 13 are at a good level. Therefore, in this invention, when 116mm ≤ H < 132mm, the value of X is set within the range of 0.50 to 2.5. For example, when H is 116mm, 120mm, 125mm, 130mm, or 131mm, the value of X is set to 0.50, 0.52, 0.55, 0.8, 1.0, 1.5, 2.0, or 2.50, respectively. Furthermore, when 116mm ≤ H < 132mm, setting the value of X to 0.60 ≤ X ≤ 2.00 can further reduce the radiant heat between the first heating tube 131 and the second heating tube 132, and reduce the noise during the operation of compressor 10. When 116mm≤H<132mm, the value of X is set to 0.95≤X≤1.85, and the heater 13 and the compressor 10 with the heater 13 have better performance.

[0078] like Figure 13 The diagram shows the changes in radiant heat Q and noise of heater 13 when 132mm≤H≤150mm. It can be seen that when 0.45≤X≤2.15, the radiant heat Q and noise of heater 13 are at a good level. Therefore, in this invention, when 132mm≤H≤150mm, the value of X is set within the range of 0.45 to 2.15. For example, when H is 132mm, 135mm, 140mm, 145mm, or 150mm, the value of X is set to 0.45, 0.50, 0.52, 0.55, 0.8, 1.0, 1.5, 2.0, or 2.15, etc. Furthermore, when 132mm≤H≤150mm, setting the value of X to 0.55≤X≤1.65 can further reduce the radiant heat between the first heating tube 131 and the second heating tube 132, and reduce the noise during the operation of compressor 10. When 132mm≤H≤150mm, the value of X is set to 0.90≤X≤1.50, and the heater 13 and the compressor 10 with the heater 13 have better performance.

[0079] By setting the above parameters, the range of X is limited for different ranges of H, so that when H has different values, the corresponding X value can be set, which can further improve the stability of heater 13 and improve the space utilization of heater 13. This is beneficial to improving the stability of compressor 10 with heater 13 and facilitates the high integration and miniaturization of compressor 10.

[0080] In some embodiments, 16mm ≤ D1 ≤ 35mm, for example, D1 can be set to 16mm, 18mm, 20mm, 25mm, 26.5mm, 30mm, 32mm, or 35mm, etc. Optionally, 16mm ≤ D2 ≤ 35mm, for example, D2 can be set to 16mm, 18mm, 20mm, 25mm, 26.5mm, 30mm, 32mm, or 35mm, etc. Optionally, 9mm ≤ L ≤ 47mm, for example, L can be set to 9mm, 12mm, 16mm, 20mm, 25mm, 30mm, 35mm, 40mm, or 47mm, etc. Optionally, 100mm ≤ H1 ≤ 150mm, for example, H1 can be set to 100mm, 110mm, 120mm, 125mm, 130mm, 135mm, 140mm, or 150mm, etc. Optionally, 100mm ≤ H2 ≤ 150mm, for example, H2 can be set to 100mm, 110mm, 120mm, 125mm, 130mm, 135mm, 140mm, or 150mm, etc. By limiting the size of heater 13 within an appropriate range, the problem of heater 13 being too large and occupying too much space is avoided, thus improving the space utilization of compressor 10. It also avoids the problem of heater 13 being too small and unable to meet the required heating power. Therefore, by limiting the size of heater 13, the space utilization of compressor 10 can be improved while ensuring the heater power requirements.

[0081] In some embodiments, 0.77 ≤ D1 / D2 ≤ 1.3, meaning the diameter ratio of the outer diameter D1 of the first heating tube 131 and the outer diameter D2 of the second heating tube 132 is set within a range not exceeding 1.3. This avoids the large difference in diameter between the first heating tube 131 and the second heating tube 132 affecting the stable operation of the heater 13, maintaining better space utilization and flow resistance of the heater 13. Furthermore, when the difference in outer diameter D1 of the first heating tube 131 and the outer diameter D2 of the second heating tube 132 is maintained within a range not exceeding 1.3, combined with the aforementioned range of X values, the impact of noise or radiant heat on the operational stability of the heater 13 can be further reduced, improving the stability and service life of the heater 13. D1 / D2 can be set to 0.77, 0.78, 0.85, 0.90, 0.98, 1, 1.1, 1.2, 1.25, or 1.3, etc.

[0082] like Figure 3 In some embodiments, the heater 13 further includes a connector 133, which connects a first heating tube 131 and a second heating tube 132, with the first heating tube 131 and the second heating tube 132 located on the same side of the connector 133. For example... Figure 3 and Figure 4The first heating tube 131 has a first flow channel inside. The second heating tube 132 has a second flow channel inside. Both the first heating tube 131 and the second heating tube 132 are configured to heat the heat exchange medium flowing through their respective flow channels, which can further extend the heating time and heating path of the heat exchange medium, resulting in higher heating efficiency. The heating power of the first heating tube 131 and the second heating tube 132 can also be adjusted separately to control the heating temperature of the heat exchange medium at different parts of the heater 13, making the heating effect of the heat exchange medium more controllable. The first heating tube 131 and the second heating tube 132 are connected in series, so that the first flow channel and the second flow channel form a sequentially connected flow channel. The heat exchange medium is heated by passing through the first flow channel and the second flow channel sequentially, which can superimpose the heating effect of the first heating tube 131 and the second heating tube 132 on the heat exchange medium, improving the heating efficiency of the heater 13. The heater 13 also includes a connector 133, which connects the first flow channel and the second flow channel. The first heating tube 131, connector 133, and second heating tube 132 can form sequentially connected flow channels. The first heating tube 131 and second heating tube 132 can be connected to the same side of connector 133, and the first heating tube 131 and second heating tube 132 are distributed side by side. This allows the heat exchange medium to flow rapidly between the first and second flow channels, enabling the heater 13 to heat more heat exchange medium in a short time, thus improving the heating efficiency of the heater 13. Connector 133, first heating tube 131, and second heating tube 132 are connected in a U-shape, that is, the first heating tube 131 and second heating tube 132 are located on the same side of connector 133 and both extend away from connector 133. The U-shaped pipe can achieve stable reversal of the internal heat exchange medium, allowing the heat exchange medium to flow more smoothly between the first heating tube 131, connector 133, and second heating tube 132, which helps reduce the risk of blockage of the heat exchange medium in the heater 13 and improves the reliability of the heater 13 in heating the heat exchange medium.

[0083] In some embodiments, the outer diameter of the stator core 1211 is W (or the outer diameter of the motor assembly 12 is W), and the outer diameter W of the stator core 1211 can be the diameter of the largest outer circle of the stator core 1211. Optionally, half of the outer diameter W of the stator core 1211 can be the maximum distance from the axis of the stator core 1211 to the outer edge of the stator core 1211. The dimensions perpendicular to the axis at different positions of the stator core 1211 can be measured by clamping calipers against the outer surface of the stator core 1211, and the maximum measured value is taken as the outer diameter W of the stator core 1211.

[0084] Where 1.0 ≤ H / W ≤ 1.5. When H / W < 1.0, the length of the first heating element 1312 or the second heating element 1322 is smaller than the outer diameter of the motor assembly 12, resulting in wasted space along the axial direction of the first heating tube 131 in the compressor 10, affecting the heating efficiency of the heater 13. When H / W > 1.5, the length of the first heating element 1312 or the second heating element 1322 is too large, extending too far from the outer side of the compressor 10. This not only increases the size of the compressor 10 but also causes the first heating element 1312 or the second heating element 1322 to radiate excessive heat outwards, affecting the surrounding environment and hindering stable operation. In this invention, 1.0 ≤ H / W ≤ 1.5 comprehensively considers the impact of the heater 13's size on the volume of the compressor 10, improving the space utilization of the compressor 10 and allowing the heater 13 to have a larger size, thus improving its heating efficiency and stability. H / W can be set to 1.0, 1.1, 1.2, 1.3, 1.45, or 1.5, etc.

[0085] The inner diameter of the stator core 1211 is Di. The stator core 1211 can be a hollow structure. The inner diameter of the stator core 1211 can be the diameter of the largest inner circle of the stator core 1211. The stator core 1211 can include multiple teeth distributed circumferentially. Winding slots can be formed between adjacent teeth. Half of the inner diameter Di of the stator core 1211 can be the minimum distance from the axis of the stator core 1211 to the teeth.

[0086] in, .like Figure 18 The required torque of the motor assembly is shown. Torque levels at different values ​​are presented, where there is a correspondence between torque level (dimensionless) and torque. Higher torque levels correspond to higher torque than lower torque levels. For compressors of different power ratings, the torque of the motor assembly varies. This invention illustrates the relationship between different values ​​of Di / W and torque level through the correspondence between torque level and required torque. It can be seen that as the ratio... The torque rating first increases and then decreases, at the ratio Smaller, for example At that time, the torque rating of motor assembly 12 is relatively small, less than the required torque of the motor assembly; in the ratio Larger, for example At that time, the torque rating of motor assembly 12 is relatively small, less than the required torque of the motor assembly. Therefore, in this utility model... The torque rating of the motor assembly is greater than the required torque, which can maintain the stable operation of the motor assembly 12 and improve the operational stability of the motor assembly 12. For example, the ratio can be... The values ​​are set to 0.45, 0.5, 0.51, 0.53, 0.55, 0.6, 0.62, 0.65, 0.68, 0.7, 0.71, 0.73, 0.74, and 0.75, etc.

[0087] In some embodiments, .from Figure 18 It can be seen from this that when the ratio When the torque is in the range of 0.55 to 0.65, the torque level of the motor assembly is at a high level, and the motor assembly 12 can operate at a higher power, which can improve the performance of the compressor 10.

[0088] like Figure 18 The figure shows the torque level variation curve. The larger the value on the vertical axis, the stronger the torque output capability, provided that the torque level meets the following conditions. At this point, the torque level is relatively high, meeting the requirements. When W is fixed and Di increases, under the same conditions, motor design theory shows that the air gap cross-sectional area through which the rotor magnetic field passes increases, meaning the motor magnetic flux increases, and the torque increases accordingly. However, if Di is too large, it will reduce the stator slot area and decrease the stator slot fill factor, thus reducing the motor torque. Therefore... There is a reasonable range that ensures the motor torque capacity meets the requirements. Since motor power is proportional to the product of torque and speed, with the speed remaining constant, increasing the torque can further increase the motor power, thus increasing the power of motor assembly 12.

[0089] For example, Di=62mm, W=101mm, .

[0090] like Figure 19 In some embodiments, 2 ≤ H / D ≤ 9. An excessively large H / D will result in an elongated shape for the first heating tube 131 or the second heating tube 132, leading to excessive flow resistance. An excessively small H / D will result in a short and thick shape for the first heating tube 131 or the second heating tube 132, resulting in poor heat exchange and excessive heat loss. This invention, by ensuring 2 ≤ H / D ≤ 9, can control the H / D within a suitable range to reduce flow resistance and heat loss in the first heating tube 131 or the second heating tube 132, thereby improving the heating effect of the heater 13. For example, H / D can be 2, 2.5, 3, 3.5, 4, 4.5, 5, 5.6, 6, 6.5, 7, 7.5, 8, 8.5, 8.8, or 9, etc.

[0091] like Figure 1 In some embodiments, the first heating tube 131 and the second heating tube 132 are arranged side by side. The outer diameter of the stator core 1211 is W, and the angle between the axis of the first heating tube 131 or the axis of the second heating tube 132 and the axis of the motor assembly 12 is γ.

[0092] like Figure 20 and Figure 21 In some embodiments, the first heating element 131 and the second heating element 132 are arranged side by side, the outer diameter of the motor assembly 12 is W, and the angle between the axis of the first heating element 131 and the axis of the motor assembly 12 is γ. , .

[0093] in, , .in, The total width of the first heating tube 131 and the second heating tube 132 is the maximum distance between the side of the first heating tube 131 away from the second heating tube 132 and the side of the second heating tube 132 away from the first heating tube 131. This can be the maximum length of the first heating element 1312 of the first heating tube 131 projected along the axis of the motor assembly 12 in the vertical direction, or the maximum length of the second heating element 1322 of the second heating tube 132 projected along the axis of the motor assembly 12 in the vertical direction. It can be set to 0.2, 0.25, 0.3, 0.4, 0.5, 0.6, or 0.7, etc. It can be set to 1, 1.1, 1.15, 1.2, 1.25, 1.5, 1.6 or 1.7, etc.

[0094] Optionally, such as Figure 3 As shown, the first heating tube 131 and the second heating tube 132 can be arranged side by side along the front-back direction. The upper end of the first heating part 1312 of the first heating tube 131 and the upper end of the second heating part 1322 of the second heating tube 132 are flush with each other in the front-back direction. The lower end of the first heating part 1312 of the first heating tube 131 and the lower end of the second heating part 1322 of the second heating tube 132 are flush with each other in the front-back direction. The upper end of the first heating tube 131 and the upper end of the second heating tube 132 are flush with each other in the front-back direction. The lower end of the first heating tube 131 and the lower end of the second heating tube 132 are flush with each other in the front-back direction.

[0095] The space occupied by the first heating element 131 and the second heating element 132 can be projected onto the axis of the motor assembly 12 in a rectangular shape, and the projection of the motor assembly 12 onto its axis L12 is approximately circular. , In the projection of the axis of the motor assembly 12, the space occupied by the first heating tube 131 and the second heating tube 132 has a large overlap with the space occupied by the motor assembly 12, which can improve the space utilization of the compressor 10 and ensure that the heater 13 has a large heating efficiency.

[0096] When satisfied , At this time, the power requirements of the heater can be met, and the overall volume of the compressor 10 is small, achieving the goal of lightweight design. When the stator outer diameter W is constant, and The smaller the size, the lower the power of heater 13. and The larger the heater, the higher its power, but the larger its size, which is not conducive to miniaturization and increases costs. , This design ensures that the heating power of heater 13 meets the requirements, and that heater 13 is small in size, achieving lightweight and miniaturization while keeping the cost within a reasonable range. There is a correspondence between heater power rating (dimensionless) and heating power; a higher heater power rating corresponds to a higher heating power than a lower heater power rating. For compressors of different power ratings, the heating power of the motor assembly varies. This invention demonstrates the correspondence between heater power rating and heater power requirement. The relationship between different values ​​of and heater power requirements. Cost is a development indicator formulated based on the actual product, expressed dimensionlessly; the larger the value, the higher the product cost and the lower the cost-effectiveness.

[0097] For example, when L=9.2mm, D=23.8mm, D2=23.8mm, W=101mm, and γ=93.5° = It meets the range of greater than 0.2 and less than 0.7. It satisfies the range of greater than 1 and less than 1.7.

[0098] According to an embodiment of the present invention, the thermal management system includes the aforementioned compressor 10.

[0099] According to an embodiment of the present invention, the thermal management system includes the aforementioned compressor 10. Optionally, the thermal management system may include the aforementioned compressor 10, evaporator (not shown in the figure), and condenser (not shown in the figure). The compressor 10, evaporator, and condenser are connected to form a refrigerant circuit. The refrigerant circuit is used to cool the refrigerant flowing through the evaporator and to heat the refrigerant flowing through the condenser using the refrigerant phase change. The refrigerant cooled or heated through the refrigerant circuit can flow to the vehicle's cabin, battery module, etc., for heat exchange to meet the user's heat exchange needs.

[0100] By incorporating a heater 13 into the housing assembly 11 of the compressor 10, the compressor 10 can meet both heating requirements through the heater 13 and user heat exchange requirements through the refrigerant circuit formed by the compressor 10, evaporator, and condenser, thus enabling the compressor 10 to perform multiple functions. Furthermore, this design improves the environmental adaptability of the compressor 10, resulting in a simple, efficient, compact, space-saving, and low-cost compressor 10. Additionally, it allows for a rational power distribution between the compressor 10 and the heater 13, satisfying both the cooling and heating requirements of the compressor 10 and the heater 13, while also achieving lightweight and miniaturization.

[0101] According to an embodiment of the present invention, the vehicle includes the aforementioned thermal management system. Optionally, the vehicle may include the aforementioned thermal management system and an in-vehicle heat exchange device, wherein the in-vehicle heat exchange device is connected to the thermal management system, and the in-vehicle heat exchange device and the thermal management system exchange heat using a refrigerant and a heat exchange medium.

[0102] The refrigerant cooled by the refrigerant circuit of the thermal management system can flow through the vehicle's heat exchange device, allowing the refrigerant to absorb heat from the heat exchange device and lower its temperature. The refrigerant in the refrigerant circuit of the thermal management system, along with the heat exchange medium heated by the heater 13 in the compressor 10, can flow through the vehicle's heat exchange device, allowing the heat exchange medium to dissipate heat to the heat exchange device and raise its temperature, thereby enabling temperature control of the vehicle's heat exchange device.

[0103] For example, the in-vehicle heat exchange device can be an onboard air conditioner. By working in conjunction with the thermal management system, the in-vehicle temperature can be regulated to improve passenger comfort. Alternatively, the in-vehicle heat exchange device can be a battery pack. This, in conjunction with the thermal management system, can regulate the battery pack's temperature to ensure normal operation and improve its safety. It prevents overheating due to excessive power output and reduces power output due to low ambient temperatures, allowing the vehicle to perform at its best and enhancing driving safety.

[0104] Here, the vehicle can be a new energy vehicle. In some embodiments, the new energy vehicle can be a pure electric vehicle with the motor assembly 12 as the main driving force. In other embodiments, the new energy vehicle can also be a hybrid vehicle with both an internal combustion engine and the motor assembly 12 as the main driving force. Regarding the internal combustion engine and motor assembly 12 mentioned in the above embodiments that provide driving power for the new energy vehicle, the internal combustion engine can use gasoline, diesel, hydrogen, etc. as fuel, and the way to provide electrical energy to the motor assembly 12 can be a power battery, hydrogen fuel cell, etc., without special limitation. It should be noted that this is merely an exemplary description of the structure of new energy vehicles, etc., and is not intended to limit the protection scope of this utility model.

[0105] By installing a heater 13 at the housing assembly 11 of the compressor 10, the compressor 10 can meet both heating requirements through the heater 13 and user heat exchange requirements through the refrigerant circuit formed by the compressor 10, evaporator, and condenser, thus enabling the compressor 10 to perform multiple functions. Furthermore, this improves the environmental adaptability of the compressor 10, resulting in a simple, efficient, compact, space-saving, and low-cost compressor 10.

[0106] The compressor 10, thermal management system, and other components and operations of the vehicle according to embodiments of the present invention are known to those skilled in the art and will not be described in detail here.

[0107] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0108] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this utility model, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0109] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0110] In this utility model, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0111] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0112] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A heater, characterized in that, include: A first heating element and a second heating element are arranged side-by-side and spaced apart, with a minimum distance L between them. The first heating tube includes a first tube body and a first heating element disposed on the outer surface of the first tube body. The second heating tube includes a second tube body and a second heating element disposed on the outer surface of the second tube body. The average of the maximum dimension H1 of the first heating element along the axial direction of the first heating tube and the maximum dimension H2 of the second heating element along the axial direction of the second heating tube is H. The average of the outer diameter D1 of the first heating tube and the outer diameter D2 of the second heating tube is D. in, , 0.45≤X≤2.85, , .

2. The heater according to claim 1, characterized in that, 0.95≤X≤1.75。 3. The heater according to claim 1, characterized in that, 0.77≤D1 / D2≤1.

3.

4. The heater according to claim 1, characterized in that, 100mm≤H<116mm, 0.55≤X≤2.85; or, 116mm≤H<132mm, 0.50≤X≤2.50; or, 132mm≤H≤150mm, 0.45≤X≤2.

15.

5. The heater according to claim 4, characterized in that, 100mm≤H≤116mm, 0.65≤X≤2.35; or, 116mm≤H<132mm, 0.60≤X≤2.00; or, 132mm≤H≤150mm, 0.55≤X≤1.

65.

6. The heater according to claim 5, characterized in that, 100mm≤H≤116mm, 1.00≤X≤2.20; or, 116mm≤H<132mm, 0.95≤X≤1.85; or, 132mm≤H≤150mm, 0.90≤X≤1.

50.

7. The heater according to claim 1, characterized in that, 16mm≤D1≤35mm; or, 16mm≤D2≤35mm; or, 9mm≤L≤47mm; or, 100mm≤H1≤150mm; or, 100mm≤H2≤150mm.

8. The heater according to claim 1, characterized in that, The heater also includes a connector that connects the first heating tube and the second heating tube, with the first heating tube and the second heating tube located on the same side of the connector.

9. A compressor, characterized in that, include: Housing assembly; A motor assembly, wherein the motor assembly is disposed within the housing assembly; The heater according to any one of claims 1-8, wherein at least a portion of the heater is disposed within the housing assembly, and the heater and the motor assembly are distributed along the axis of the motor assembly.

10. The compressor according to claim 9, characterized in that, The first heating element and the second heating element are arranged side by side. The outer diameter of the motor assembly is W. The angle between the axis of the first heating element and the axis of the motor assembly is γ. , .

11. A thermal management system, characterized in that, The thermal management system includes the compressor as described in claim 9 or 10.

12. A vehicle, characterized in that, The vehicle includes the thermal management system as described in claim 11.

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