Compressor, thermal management system, and vehicle

Abstract

This utility model discloses a compressor, a thermal management system, and a vehicle, belonging to the field of compressor technology. The compressor includes a housing assembly, a motor assembly, and a heater. At least a portion of the heater is disposed within the housing assembly. The heater and the motor assembly are distributed along the axis of the motor assembly. The heater includes a first heating tube and a second heating tube arranged side by side. The first heating tube includes a first tube body and a first heating part, and the second heating tube includes a second tube body and a second heating part. The outer diameter of the first heating tube is d1, the outer diameter of the second heating tube is d2, the length of the first heating part is L1, the length of the second heating part is L2, the total internal volume of the heater is V1, and the outer diameter of the stator core is Do. According to the compressor of this utility model embodiment, the heating power of the heater is matched with the volume, which can improve the space utilization of the compressor and optimize the performance of the compressor.

Description

Technical Field

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

[0002] With the development of the new energy vehicle industry and technological advancements, integrating compressors and heaters is an industry trend. The core challenge lies in balancing heater reliability with maximum heating power. On one hand, to prevent the heater from failing due to impact loads caused by boiling of the heat exchange medium, it is necessary to avoid rapid heating and boiling of the heat exchange medium within the heater. On the other hand, to meet the demand for rapid heating of the vehicle cabin, the compressor heater needs to have a large heating power output, which typically means increasing the heating area of ​​the heater and the size of the heat exchange medium flow pipes.

[0003] However, if the heater's flow channel size is too large, it will result in an oversized compressor, which is detrimental to the miniaturization requirements of the compressor. This is especially true when the vehicle assembly space is limited, where an excessively large compressor may even fail to meet the assembly space requirements. Therefore, miniaturizing the compressor while ensuring its reliability and heating needs remains a challenge for the industry. Utility Model Content

[0004] One objective of this invention is to provide a compressor, a thermal management system, and a vehicle that matches the heating power of the heater with its volume, and can miniaturize the compressor while ensuring its reliability and heating requirements.

[0005] A compressor according to an embodiment of the present invention includes: a housing assembly; a motor assembly disposed within the housing assembly, the motor assembly including a stator core; and a heater, at least a portion of which is disposed within the housing assembly. The heater and the motor assembly are distributed along the axis of the motor assembly. The heater includes a first heating tube and a second heating tube arranged side-by-side. 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 outer diameter of the first heating tube is d1, the outer diameter of the second heating tube is d2, the length of the first heating element along the axis of the first heating tube is L1, the length of the second heating element along the axis of the second heating tube is L2, the total internal volume of the heater is V1, and the outer diameter of the stator core is Do. .

[0006] According to the compressor of this utility model embodiment, the heating power of the heater is matched with the volume, which reduces the risk of boiling caused by heat exchange cutoff while ensuring that the heater has sufficient heating power, thereby improving the reliability of the compressor.

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

[0008] In some embodiments, in the orthographic projection along the axis of the motor stator, the outer circle of the stator core encloses a projection region X1, the first heating part, the second heating part, and the gap between the first heating part and the second heating part combine to form a projection region X2, and the overlapping portion of projection region X1 and projection region X2 forms a projection region X3, wherein the area size of projection region X1 is S1, the area size of projection region X2 is S2, the area size of projection region X3 is S3, and 0.05≤S3 / S1<1.

[0009] In some embodiments, 0.4 ≤ S3 / S1 ≤ 0.9.

[0010] In some embodiments, in the orthographic projection along the axis of the motor stator, the outer circle of the stator core encloses a projection region X1. The first heating element, the second heating element, and the gap between the first and second heating elements combine to form a projection region X2. The overlapping portion of projection region X1 and projection region X2 forms a projection region X3. The maximum dimension of projection region X3 along its length is L4. The tube spacing between the first heating tube and the second heating tube is w. The angle between the axis of the first heating tube and / or the axis of the second heating tube and the axis of the motor assembly is α. On a projection plane perpendicular to the rotation axis of the motor assembly, the extension direction of the orthographic projection of the first heating tube on the projection plane is the length direction. .

[0011] In some embodiments, ;0.4≤L4 / Do<1;0.4≤L4 / L1≤0.9.

[0012] In some embodiments, the distance between the first heating tube and the second heating tube is w, and the angle between the axis of the first heating tube and the axis of the motor assembly is α, where 0.2≤(w+d1+d2) / Do≤1.5. .

[0013] In some embodiments, 1.0 ≤ L1 / Do ≤ 2.

[0014] In some embodiments, 10mm≤d1≤40mm; or, 10mm≤d2≤40mm; or, the tube spacing between the first heating tube and the second heating tube is w, 6mm≤w≤20mm; or, 80mm≤L1≤300mm; or, 80mm≤L2≤300mm.

[0015] According to an embodiment of the present invention, the thermal management system includes the aforementioned compressor.

[0016] According to an embodiment of the present invention, the vehicle includes the aforementioned thermal management system. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of a compressor according to one embodiment of the present invention.

[0018] Figure 2 This is a cross-sectional view of a compressor according to an embodiment of the present invention.

[0019] Figure 3 This is an exploded schematic diagram of a compressor according to one embodiment of the present invention.

[0020] Figure 4 This is a side view of a compressor according to an embodiment of the present invention.

[0021] Figure 5 This is another cross-sectional view of a compressor according to one embodiment of the present invention.

[0022] Figure 6 This is a schematic diagram of a motor assembly according to an embodiment of the present invention.

[0023] Figure 7 This is a cross-sectional view of a heater according to an embodiment of the present invention.

[0024] Figure 8 This is a schematic diagram of a heater according to one embodiment of the present invention.

[0025] Figure 9 This is a schematic diagram of a heater according to an embodiment of the present invention, showing the volume V1 of the heater.

[0026] Figure 10 This is a schematic diagram of a heater according to another embodiment of the present invention, showing the volume V1 of the heater.

[0027] Figure 11 This is a schematic diagram of a heater according to an embodiment of the present invention, showing the projected area X2.

[0028] Figure 12 This is a schematic diagram of a stator core according to an embodiment of the present invention, showing the projected area X1.

[0029] Figure 13 This is a schematic diagram of the projection area X3 of one embodiment of the present invention.

[0030] Figure 14 This is a schematic diagram comparing the heating power of X and the heater, and the risk factor of membrane rupture in a compressor according to one embodiment of this utility model.

[0031] Figure 15 This is a schematic diagram showing the comparison between the Di / Do ratio and the torque rating of the motor assembly in a compressor according to one embodiment of this utility model.

[0032] Figure 16 This is a schematic diagram showing the comparison between L1 / d1 and heat loss and flow resistance in a compressor according to one embodiment of this utility model.

[0033] Figure 17 This is a schematic diagram showing the comparison between the ratio (w+d1+d2) / Do and the cost and heater power rating of one embodiment of this utility model.

[0034] Figure 18 In a compressor according to one embodiment of this utility model A diagram showing the comparison between cost and heater power rating.

[0035] 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. Detailed Implementation

[0036] The main purpose of this utility model is to provide a compressor 10, which is designed to provide a compressor 10 with small size, high output power of heater 13 and high heat exchange efficiency, which can improve the space utilization and heating demand of vehicles when applied to vehicles.

[0037] 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.

[0038] like Figures 1 to 6 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 2 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 3 A partial exploded view of the compressor 10 is shown, illustrating the relative positions of components of the heater 13, including the first heating tube 131, the second heating tube 132, the lower flange 1331, and the water tank 1332. The lower flange 1331 and the water tank 1332 combine to form a connector 133. The lower flange 1331 is connected to the lower end of the first heating tube 131 and the lower end of the second heating tube 132. The water tank 1332 is connected to the lower flange 1331, forming a flow channel between them that connects the internal channels of the first heating tube 131 and the second heating tube 132. The heater 13 may include structurally identical first and second heating tubes 131, connected by the connector 133 to form a U-shape.

[0039] like Figures 1 to 3The motor assembly 12 is located on the housing assembly 11, and includes a stator assembly 121 and a rotor assembly 122. The stator assembly 121 can be stationary relative to the housing assembly 11, and the rotor assembly 122 is rotatably engaged with the stator assembly 121. The stator assembly 121 can drive the rotor assembly 122 to rotate by electromagnetic drive. The rotor assembly 122 can be connected to the compression assembly 14 of the compressor 10 to drive the compression assembly 14. In addition, the stator assembly 121 includes a stator core 1211 and a stator winding 1212, and the rotor assembly 122 includes a rotor core 1221 and a permanent magnet 1222 (e.g., a magnet). The stator core 1211 may be provided with a winding slot, and the stator winding 1212 may be provided with a winding slot. The rotor core 1221 may include a magnet slot, and the permanent magnet 1222 may be provided in the magnet slot. Of course, the motor assembly 12 in this utility model may also be in other forms, for example, the permanent magnet 1222 may be attached to the outer surface of the rotor core 1221. The motor assembly 12 in this utility model can be disposed inside the housing assembly 11. For example, the motor assembly 12 can be disposed inside the first cavity 11A of the aforementioned housing assembly 11. The stator assembly 121 can be interference-fitted with the inner side of the housing assembly 11 to achieve stable installation of the motor assembly 12. The rotor assembly 122 can be rotatably disposed inside the stator assembly 121, or the stator assembly 121 can be arranged around the rotor assembly 122.

[0040] like Figure 7 and Figure 8 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 4 and Figure 5Alternatively, 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 12, and at least a portion of the heater 13 can be disposed within the third cavity 11C.

[0041] 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.

[0042] Additionally, the compressor 10 includes a controller 15, which connects to the heater 13 and the motor assembly 12, and can supply power to the heater 13 and the motor assembly 12. The controller 15 can be positioned between the first housing 111 and the third housing 113. Figure 2 The third housing 113 defines a third cavity 11C on one side of the first housing 111. The heater 13 and controller 15 are housed inside the third cavity 11C. The third cavity 11C has a water interface and an electrical interface with the outside. A motor assembly 12 and a compression assembly 14 are located 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 controls the heater 13 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.

[0043] like Figures 4 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 can be disposed on housing assembly 11, and heater 13 and motor assembly 12 are distributed along the axis L12 of motor assembly. This avoids heater 13 occupying the radial space of compressor 10, improving the space utilization of compressor 10. The heating tube includes a tube body and a heating element. The heating element can 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 can be configured as a circular tube, 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 can be disposed around the outer surface of the tube body, for example, the heating element can be stacked on the outer surface of the tube body, wherein the heating element can 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 use processes such as screen printing to print different functional electronic pastes layer by layer onto a substrate material (tube body), 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 glaze layer, etc.

[0044] 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 the thickness of the heating element is usually 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 a circular tube or a non-circular tube. When the heating tube is a circular tube, the outer diameter of the circular tube is the outer diameter of the heating tube; when the heating tube is a non-circular tube, 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, if the heating tube is an elliptical tube, and the area enclosed by the outer edge of the cross-section obtained in the plane perpendicular to the axis of the elliptical tube is elliptical, this ellipse can be equivalent to an equivalent circle with the same area. Then, the diameter of this equivalent circle is used as the outer diameter of the elliptical tube. For example, the heating element can also be other regular or irregular shapes. The area enclosed by the outer edge of the heating element's cross-section can be considered equivalent to a circle with the same area, and the diameter of this circle can be taken as the outer diameter of the heating element. In other words, when the area enclosed by the outer edge of the heating element's cross-section is S11, the outer diameter of the heating element is... The cross-section of the heating element is perpendicular to its axis.

[0045] 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 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 can be installed inside the housing assembly. The mounting plate covers the housing assembly to stably position the heating tubes within the housing assembly. 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.

[0046] like Figures 7 to 10 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. The minimum distance between the first heating tube 131 and the second heating tube 132 is w. The minimum distance w can be the minimum distance between the first heating tube 131 and the second heating tube 132, which can be measured by inserting calipers between them.

[0047] like Figure 8The 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 L1, 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 L2, and the outer diameter of the second heating element 132 is d2. L1 and L2 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.

[0048] like Figure 9 The total internal volume of heater 13 is V1, where V1 can be the volume of heat exchange medium that heater 13 can hold. For example, when heater 13 has a spiral section, a boss structure, a groove structure, etc., the total volume of heat exchange medium that heater 13 can hold can be used as the total internal volume of heater 13. The total internal volume V1 of heater 13 can be determined by filling the heater with liquid and then pouring the liquid into a measuring cup to measure the internal volume. Figure 9 The total volume V1 is shown when the spiral section 136 is not installed inside the heating tube, as follows: Figure 10 The total volume V1 is shown when the spiral section 136 is provided inside the heating tube. Additionally, the total volume V1 inside the heater 13 includes the volume inside the connector, which is a structure for connecting the heater 13 to an external pipeline. The heater may include an inlet connector and an outlet connector. Optionally, the inlet connector connects to the first heating tube 131, and the outlet connector includes the second heating tube 132. The heater 13 also includes a connector 133. The total internal volume V1 of the heater can be calculated by subtracting the volume of the spiral section 136 and other structures inside the heater 13 from the sum of the volumes inside the inlet connector 134, the outlet connector 135, the first heating tube 131, the second heating tube 132, and the connector 133. This can be measured by injecting water into the heater 13 as described above.

[0049] The outer diameter of the stator core 1211 is Do, which can be the diameter of the largest outer circle of the stator core 1211. Optionally, half of the outer diameter Do can be the maximum distance from the axis of the stator core 1211 to its outer edge. The outer diameter Do can be measured perpendicular to the axis at different positions on the stator core 1211 using calipers, and the maximum measured value is taken as the outer diameter Do of the stator core 1211.

[0050] Compressor 10 meets Where S4 = , which is the total heating area of ​​the first heating element 1312 and the second heating element 1322. This illustrates the relationship between the volume V1 of heater 13, the total heating area of ​​heater 13, and the outer diameter Do of stator core 1211.

[0051] like Figure 14 When X is small, for example, X < 0.01, heater 13 has a large heating power, and the heat exchange medium heats up very quickly. When the temperature reaches the boiling point of the heat exchange medium, the heat exchange medium inside heater 13 boils. At this time, the insulation layer on the outer wall of the first heating part 1312 and the second heating part 1322 will burst due to the impact stress generated by boiling, resulting in heater failure due to membrane bursting. In other words, when X is small, although heater 13 has a large heating power, the risk of membrane bursting of the first heating part 1312 and the second heating part 1322 increases, leading to a reduction in the service life of heater 13. When X is large, for example, X > 0.5, heater 13 has a small heating power, and the heat exchange medium heats up very slowly when flowing through the heating tube. At this time, the heat output of heater 13 is small, which is insufficient to meet the needs of rapid heating of the entire vehicle cabin. Therefore, in this invention, the ratio X is set in the range of 0.01 to 0.5, which not only ensures that the heater 13 has sufficient heating power, but also reduces the risk factor of the heater 13 bursting and improves the service life of the heater 13. The value of X can be set to 0.01, 0.05, 0.1, 0.15, 0.2, 0.23, 0.28, 0.30, 0.34, 0.35, 0.4, 0.45, or 0.5, etc.

[0052] According to the compressor 10 of this utility model embodiment, the value of X is set between 0.01 and 0.5, which can limit the heating power of the heater 13 and the ratio of the volume of the heater 13 to the outer diameter Do of the stator core 1211 within an appropriate range, matching the heating power and volume of the heater 13. This allows the heater 13 to have a large output power to meet the rapid heating requirements of the cabin, while also preventing the heat exchange medium from boiling due to rapid heating, which could cause the insulation layer of the heater 13 to fail due to boiling impact.

[0053] like Figure 14 In some embodiments, When the value of X is set to be greater than or equal to 0.02, the risk coefficient of the rupture of the heater 13 will tend to level off as the value of X increases, which can keep the risk coefficient of the rupture at a low level. Moreover, the value of X being less than or equal to 0.3 can ensure that the heater 13 has sufficient heating power and improve the heating power of the heater 13.

[0054] like Figures 11 to 13 In some embodiments, in the orthographic projection along the axis of the motor assembly 12, the outer circle of the stator core 1211 encloses the projection area X1 (e.g., Figure 12 As shown), the first heating element 1312, the second heating element 1322, and the gap between the first heating element 1312 and the second heating element 1322 form a projection area X2 (as shown). Figure 11 As shown), the projection area X2 may include: the projection area of ​​the first heating element 1312; the projection area of ​​the second heating element 1322; and the projection area between the lines connecting the two ends of the first heating element 1312 and the two ends of the second heating element 1322. The overlapping portion of the projection area X1 and the projection area X2 forms the projection area X3 (as shown). Figure 13 As shown in the figure, the area of ​​the projection region X1 is S1, the area of ​​the projection region X2 is S2, the area of ​​the projection region X3 is S3, and 0.05≤S3 / S1<1.

[0055] When the ratio S3 / S1 is small, for example, S3 / S1 < 0.05, the proportion of the projected area X3 relative to the projected area X1 is small, causing the heater 13 to deviate from the axis of the motor assembly 12, and the overall size of the compressor 10 to increase, which is not conducive to the miniaturization of the compressor 10. Therefore, in this invention, the ratio S3 / S1 is set in the range of 0.05 to 1, which allows the heater 13 to be closer to the central axis of the motor assembly 12, thereby minimizing the overall size of the compressor 10. For example, S3 / S1 can be set to 0.05, 0.08, 0.1, 0.15, 0.20, 0.30, 0.35, 0.4, 0.5, 0.6, 0.64, 0.7, 0.75, 0.8, 0.85, 0.9, or 0.95, etc.

[0056] In some embodiments, 0.4 ≤ S3 / S1 ≤ 0.9. Limiting the ratio S3 / S1 to a more optimal range satisfies the heater power requirements and improves the space utilization of the compressor 10. Furthermore, in this invention, the heater 13 can include a first heating tube 131 and a second heating tube 132, facilitating the flow of the heat exchange medium within the heater 13. Moreover, an appropriate distance can be set between the first heating tube 131 and the second heating tube 132 to reduce the influence between the first heating element 1312 and the second heating element 1322, thereby improving the reliability and service life of the heater 13.

[0057] In addition, such as Figure 11 The projection area X2 can be formed as a rectangle with a maximum width of Wmax and a maximum length of Lmax, where S2 = Wmax × Lmax. The first heating element 131 and the second heating element 132 can be arranged along the front-back direction. The upper ends of the first heating element 1312 and the second heating element 1322 are aligned along the front-back direction, and the lower ends of the first heating element 1312 and the second heating element 1322 are aligned along the front-back direction. The projection area X2 can be a square area formed between the side of the first heating element 1312 away from the second heating element 1322 and the side of the second heating element 1322 away from the first heating element 1312.

[0058] like Figure 13 In some embodiments, the maximum dimension of the projection area X3 along its length is L4, and the tube spacing between the first heating tube 131 and the second heating tube 132 is w; the angle between the axis L13 of the first heating tube and the axis L12 of the motor assembly is α, and / or the angle between the axis L13 of the second heating tube and the axis L12 of the motor assembly 12 is α. On the projection plane perpendicular to the rotation axis of the motor assembly 12, the extension direction of the orthographic projection of the first heating tube 131 on the projection plane is the length direction.

[0059] 0.3 0.9. Among them, It can be approximated as the area of ​​the projected region X3. This can be approximated as the area of ​​the projected region X2. The performance of compressor 10 is optimized by limiting the comparison values ​​S31 / S21. Among these, The value can be 0.3, 0.4, 0.45, 0.5, 0.6, 0.7, 0.8 or 0.9, etc.

[0060] , This can be approximated by the area of ​​the projected region X1. By limiting the comparison value S31 / S11, the power requirements of the heater are met and the space utilization of the compressor 10 is improved. In addition, in this invention, the heater 13 can include a first heating tube 131 and a second heating tube 132, which facilitates the flow of the heat exchange medium in the heater 13. Moreover, an appropriate distance can be set between the first heating tube 131 and the second heating tube 132 to reduce the influence between the first heating part 1312 and the second heating part 1322, thereby improving the stability and service life of the heater 13.

[0061] Where 0.4 ≤ L4 / Do < 1, when L4 / Do is small, for example, L4 / Do < 0.4, the overlap area of ​​the heater 13 and the motor assembly 12 projected along the axis L12 of the motor assembly is small. If the required heating power is to be achieved, the projection of the heater 13 needs to extend a larger dimension beyond the outline of the motor assembly 12, affecting the volume of the compressor 10. Therefore, the present invention limits 0.4 ≤ L4 / Do < 1, which allows the power of the heater 13 to be adjusted to an appropriate range, thereby improving heating efficiency and space utilization. L4 / Do can be 0.4, 0.45, 0.5, 0.6, 0.65, 0.7, 0.8, 0.85, 0.9, or 0.95, etc.

[0062] Where 0.4 ≤ L4 / L1 ≤ 0.9, when L4 / L1 is small, for example, when L4 / L1 < 0.4, the overlap area of ​​the heater 13 and the motor assembly 12 projected along the axis L12 of the motor assembly 12 is small, requiring a larger projected extension of the heater 13, which affects the volume of the compressor 10; when L4 / L1 > 0.9, the overlap area of ​​the heater 13 and the motor assembly 12 projected along the axis L12 of the motor assembly is large, which will lead to a complex structure of the heater 13 or difficulty in achieving the set power. Therefore, the present invention limits 0.4 ≤ L4 / L1 ≤ 0.9, which can adjust the power of the heater 13 to an appropriate range, thereby improving heating efficiency and space utilization. Wherein, L4 / L1 can be 0.4, 0.45, 0.5, 0.6, 0.65, 0.7, 0.8, 0.85, or 0.9, etc.

[0063] Optionally, 0.4 ≤ L4 / L2 ≤ 0.9. Wherein, L4 / L2 can be 0.4, 0.45, 0.5, 0.6, 0.65, 0.7, 0.8, 0.85 or 0.9, etc.

[0064] Additionally, 0.2 ≤ (w + d1 + d2) / Do ≤ 1.5, where, The total width dimension of the first heating tube 131 and the second heating tube 132 is the maximum dimension 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.

[0065] An excessively large (w+d1+d2) / Do ratio may result in an overly large width of heater 13, leading to an excessively large heater 13 volume, increasing its footprint, and consequently increasing the size and cost of compressor 10. Conversely, an excessively small (w+d1+d2) / Do ratio may reduce the flow area of ​​the heater 13 used for heating the heat exchange medium, resulting in decreased heating efficiency. This invention achieves a ratio of 0.2 ≤ (w+d1+d2) / Do ≤ 1.5, keeping it within a suitable range. This reduces the space occupied by heater 13, thereby decreasing the size and cost of compressor 10, and also improves the operational safety of heater 13. Maintaining (w+d1+d2) / Do within a suitable range also improves the heating efficiency and uniformity of heater 13, and reduces flow losses. For example, (w+d1+d2) / Do can be 0.2, 0.25, 0.3, 0.4, 0.45, 0.5, 0.55, 0.6, 0.7, 0.9, 1.1, 1.3, 1.4, or 1.5, etc. Cost is a development indicator determined based on the actual product, expressed dimensionlessly. The larger the value, the higher the product cost and the lower the cost-effectiveness.

[0066] In some embodiments, 1.0 ≤ L1 / Do ≤ 2. When L1 / Do < 1.0, the length of the first heating element 1312 is smaller than the outer diameter of the motor assembly 12, and a portion of the compressor 10 along the axial direction of the first heating tube 131 is wasted, affecting the heating efficiency of the heater 13. When L1 / Do > 2, the length of the first heating element 1312 is too large, and the extension from the outer side of the compressor 10 is too large. This not only increases the size of the compressor 10, but also causes the heating element to radiate excessive heat outwards, affecting the surrounding environment of the compressor 10 and hindering its stable operation. In this invention, 1.0 ≤ L1 / Do ≤ 2 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, which can improve the heating efficiency and stability of the heater 13. L1 / Do can be set to 1.0, 1.1, 1.2, 1.3, 1.45, 1.5, 1.6, 1.7, 1.8, 1.9, 1.95 or 2, etc.

[0067] Optionally, 1.0 ≤ L2 / Do ≤ 2. Wherein, L2 / Do can be set to 1.0, 1.1, 1.2, 1.3, 1.45, 1.5, 1.6, 1.7, 1.8, 1.9, 1.95 or 2, etc.

[0068] like Figure 6 and Figure 11In some embodiments, the outer diameter of the stator core 1211 is Do, which can be the diameter of the largest outer circle of the stator core 1211. Half of the outer diameter Do can be the maximum distance from the axis of the stator core 1211 to its outer edge. The inner diameter of the stator core 1211 is Di, and the stator core 1211 can be a hollow structure. The inner diameter can be the diameter of the largest inner circle of the stator core 1211. The stator core 1211 can include multiple teeth distributed circumferentially, and winding slots can be formed between adjacent teeth. Half of the inner diameter Di can be the minimum distance from the axis of the stator core 1211 to the teeth.

[0069] in, .like Figure 15 The torque requirements of motor assembly 12 are shown. Torque levels with different values ​​are shown, where there is a correspondence between torque level (dimensionless) and torque. Higher torque levels correspond to higher torque than lower torque levels. For compressors 10 with different power ratings, the torque of the motor assembly 12 is different. This invention illustrates the relationship between different values ​​of Di / Do and torque level through the correspondence between torque level and torque requirement. 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 torque requirement of motor assembly 12; in the ratio Larger, for example At that time, the torque rating of motor assembly 12 is relatively small, less than the torque requirement of motor assembly 12. Therefore, in this utility model... The torque rating of motor assembly 12 is greater than the torque requirement, which can maintain the stable operation of motor assembly 12 and improve the operational stability of 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.

[0070] In some embodiments, .from Figure 15 It can be seen from this that when the ratio Within the range of 0.55 to 0.65, the torque level of the motor assembly 12 is at a high level, enabling the motor assembly 12 to operate at higher power and improve the performance of the compressor 10.

[0071] like Figure 15The figure shows the torque level variation curve of motor assembly 12. The larger the value on the vertical axis, the stronger the torque output capability, while meeting the requirements... At this time, the torque level of motor assembly 12 is at a high level, meeting the torque requirements. When Do 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, that is, the motor magnetic flux increases, and the torque increases accordingly. However, if Di is too large, it will reduce the stator slot area and 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.

[0072] For example, Di=62mm, Do=101mm, .

[0073] like Figure 16 In some embodiments, 2 ≤ L1 / d1 ≤ 9. If L1 / d1 is too large, the first heating tube 131 will be elongated and have excessive flow resistance. If L1 / d1 is too small, the first heating tube 131 will be short and thick, resulting in poor heat exchange and excessive heat loss. This invention, by setting 2 ≤ L1 / d1 ≤ 9, controls L1 / d1 within a suitable range, thereby reducing flow resistance and heat loss in the first heating tube 131 and improving the heating effect of the heater 13. For example, L1 / d1 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.

[0074] Alternatively, 2 ≤ L2 / d2 ≤ 9.

[0075] In some embodiments, the first heating element 131 and the second heating element 132 are arranged side by side. The axis L12 of the motor assembly can be configured to extend in a left-right direction. The angle between the axis L13 of the first heating element and the axis L12 of the motor assembly is α. in, . It can be the maximum length dimension of the first heating part 1312 of the first heating tube 131 along the length direction of the orthogonal projection of the motor assembly 12 axis. It can be set to 1, 1.1, 1.15, 1.2, 1.25, 1.5, 1.6 or 1.7, etc.

[0076] In addition, combined Figure 17 and Figure 18 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 outer diameter Do of the stator core 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.

[0077] For example, when w=9.2mm, d1=23.8mm, d2=23.8mm, Do=101mm, α=93.5°, and L1=137mm, It meets the range of greater than 0.2 and less than or equal to 1.5. It satisfies the range of greater than or equal to 1 and less than or equal to 1.7.

[0078] Furthermore, , This can further improve the space utilization of the compressor 10. At the same time, it can avoid the first heating tube 131 and / or the second heating tube 132 being too thick or too thin, thus reducing the flow resistance of the heater 13.

[0079] Optionally, . It can be set to 1, 1.1, 1.15, 1.2, 1.25, 1.5, 1.6 or 1.7, etc.

[0080] Optionally, such as Figure 7As 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.

[0081] The space occupied by the first heating element 131 and the second heating element 132 is roughly rectangular in projection along the axis of the motor assembly 12, and the projection of the motor assembly 12 along its axis is roughly 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.

[0082] In some embodiments, 10mm ≤ d1 ≤ 40mm, for example, d1 can be set to 10mm, 15mm, 22mm, 23mm, 24mm, 25mm, 25.5mm, 26mm, 27.5mm, 30mm, 35.5mm, or 40mm, etc. Optionally, 10mm ≤ d2 ≤ 40mm, for example, d2 can be set to 10mm, 15mm, 22mm, 23mm, 24mm, 25mm, 25.5mm, 26mm, 27.5mm, 30mm, 35.5mm, or 40mm, etc. Optionally, 6mm ≤ w ≤ 20mm, for example, w can be set to 6mm, 8mm, 9.5mm, 10mm, 12mm, 12.5mm, 14mm, 15mm, 17.5mm, 18mm, 19mm, or 20mm, etc. Optionally, 80mm ≤ L1 ≤ 300mm, for example, L1 can be set to 80mm, 100mm, 122mm, 150mm, 160mm, 190mm, 200mm, 210mm, 240mm, 250mm, 280mm, or 300mm, etc. Optionally, 80mm ≤ L2 ≤ 300mm, for example, L2 can be set to 80mm, 100mm, 122mm, 150mm, 160mm, 190mm, 200mm, 210mm, 240mm, 250mm, 280mm, or 300mm, 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, 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.

[0083] like Figure 10 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 10 and Figure 11The heater 131 has a first flow channel, and the second heating tube 132 has a second flow channel. Both the first heating tube 131 and the second heating tube 132 are configured to heat the heat exchange medium flowing through their inner flow channels, which can further extend the heating time and heating path of the heat exchange medium, resulting in higher heating efficiency. The heater 132 can also be configured to adjust the heating power of the first heating tube 131 and the second heating tube 132 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.

[0084] 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.

[0085] 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 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, meeting the cooling requirements of the compressor 10 and the heating requirements of the heater 13, while also enhancing lightweight and miniaturization capabilities.

[0086] 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.

[0087] The refrigerant cooled by the refrigerant circuit of the thermal management system can flow through the vehicle's heat exchange device, allowing it to absorb heat from the device and lower its temperature. The heat exchange medium heated by the refrigerant circuit of the thermal management system and the heater 13 in the compressor 10 can also flow through the vehicle's heat exchange device, dissipating heat to it and raising its temperature. This allows for temperature control of the vehicle's heat exchange device.

[0088] 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.

[0089] 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.

[0090] 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.

[0091] 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.

[0092] 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.

[0093] 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.

[0094] 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.

[0095] 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.

[0096] 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 compressor, characterized in that, include: Housing assembly; A motor assembly, wherein the motor assembly is disposed within the housing assembly, the motor assembly including a stator core; A 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, the heater comprising a first heating tube and a second heating tube arranged side by side, the first heating tube comprising a first tube body portion and a first heating portion disposed on the outer surface of the first tube body portion, and the second heating tube comprising a second tube body portion and a second heating portion disposed on the outer surface of the second tube body portion; The outer diameter of the first heating tube is d1, the outer diameter of the second heating tube is d2, the length of the first heating element along the axis of the first heating tube is L1, the length of the second heating element along the axis of the second heating tube is L2, the total internal volume of the heater is V1, and the outer diameter of the stator core is Do. in, .

2. The compressor according to claim 1, characterized in that, 。 3. The compressor according to claim 1, characterized in that, In the orthographic projection along the axis of the motor assembly, the outer circle of the stator core encloses the projection area X1. The first heating part, the second heating part, and the gap between the first heating part and the second heating part combine to form the projection area X2. The overlapping part of the projection area X1 and the projection area X2 forms the projection area X3. The area size of the projection area X1 is S1, the area size of the projection area X2 is S2, the area size of the projection area X3 is S3, and 0.05 ≤ S3 / S1 < 1.

4. The compressor according to claim 3, characterized in that, 0.4≤S3 / S1≤0.

9.

5. The compressor according to claim 1, characterized in that, In the orthographic projection along the axis of the motor assembly, the outer circle of the stator core encloses a projection region X1. The first heating element, the second heating element, and the gap between the first and second heating elements combine to form a projection region X2. The overlapping portion of projection regions X1 and X2 forms a projection region X3. The maximum dimension of projection region X3 along its length is L4. The tube spacing between the first and second heating elements is w. The angle between the axis of the first heating element and / or the axis of the second heating element and the axis of the motor assembly is α. On a projection plane perpendicular to the rotation axis of the motor assembly, the extension direction of the orthographic projection of the first heating element on the projection plane is the length direction. .

6. The compressor according to claim 5, characterized in that, ； 0.4 ≤ L4 / Do < 1; 0.4≤L4 / L1≤0.

9.

7. The compressor according to claim 1, characterized in that, The distance between the first heating tube and the second heating tube is w, and the angle between the axis of the first heating tube and the axis of the motor assembly is α, where 0.2≤(w+d1+d2) / Do≤1.

5. .

8. The compressor according to claim 1, characterized in that, 1.0≤L1 / Do≤2.

9. The compressor according to claim 1, characterized in that, 10mm≤d1≤40mm; or, 10mm≤d2≤40mm; or, the tube spacing between the first heating tube and the second heating tube is w, 6mm≤w≤20mm; or, 80mm≤L1≤300mm; or, 80mm≤L2≤300mm.

10. A thermal management system, characterized in that, The thermal management system includes the compressor according to any one of claims 1-9.

11. A vehicle, characterized in that, The vehicle includes the thermal management system of claim 10.

Images