High pressure housing assembly, electric compressor, air conditioning system and vehicle

Abstract

The application discloses a high-pressure shell assembly for an electric compressor, an electric compressor, an air conditioning system and a vehicle, and relates to the technical field of electric compressors. The high-pressure shell assembly comprises a high-pressure shell, a high-pressure cavity and a refrigerant discharge port are formed on the high-pressure shell, a compression component of the electric compressor is adapted to discharge compressed refrigerant to the high-pressure cavity, and the refrigerant discharge port is used for discharging refrigerant outside the high-pressure shell; a resonance cavity and an oil separation cavity which are in communication with each other are further formed on the high-pressure shell, the oil separation cavity is in communication with the high-pressure cavity to receive refrigerant flowing out of the high-pressure cavity, a sound attenuation nozzle is arranged in the resonance cavity, a flow-through channel is defined between the sound attenuation nozzle and the inner wall surface of the resonance cavity, one end of the cavity in the sound attenuation nozzle is in communication with the refrigerant discharge port, and the sound attenuation nozzle is provided with a sound attenuation hole which is in communication with the cavity and the flow-through channel. The high-pressure shell assembly for the electric compressor can eliminate noise and pressure pulsation accompanied by gaseous refrigerant, and has good sound attenuation effect.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of compressors, in particular to a high-pressure shell assembly, an electric compressor, an air conditioning system and a vehicle. BACKGROUND

[0002] The electric compressor is a core component of the refrigeration equipment for vehicles. The electric compressor works to generate vibration noise, which affects the noise of the vehicle and causes subjective hearing problems. In the related art, the high-pressure refrigerant discharged by the compression component of the electric compressor enters the high-pressure cavity and then directly leaves the compressor through the refrigerant discharge outlet. Along with the exhaust gas flow noise and pressure pulsation generated when the electric compressor operates, the resonance of each component in the thermal management system of the vehicle is easily excited, which causes the noise and vibration problems of the vehicle. SUMMARY

[0003] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, one object of the present application is to provide a high-pressure shell assembly that can improve the exhaust noise and pressure pulsation of an electric compressor.

[0004] The present application also provides an electric compressor having the above high-pressure shell assembly.

[0005] The present application also provides an air conditioning system having the above electric compressor.

[0006] The present application also provides a vehicle having the above air conditioning system.

[0007] The high-pressure shell assembly for an electric compressor according to an embodiment of the present application comprises: a high-pressure shell, a high-pressure cavity and a refrigerant discharge outlet are formed on the high-pressure shell, a compression component of the electric compressor is adapted to discharge compressed refrigerant into the high-pressure cavity, and the refrigerant discharge outlet is used to discharge refrigerant outside the high-pressure shell; a resonance cavity and an oil separation cavity that are in communication with each other are also formed on the high-pressure shell, the oil separation cavity is in communication with the high-pressure cavity to receive the refrigerant flowing out of the high-pressure cavity, and a sound-absorbing insert pipe is arranged in the resonance cavity, a flow-through passage is defined between the sound-absorbing insert pipe and the inner wall surface of the resonance cavity, one end of a pipe cavity in the sound-absorbing insert pipe is in communication with the refrigerant discharge outlet, the sound-absorbing insert pipe is provided with a sound-absorbing hole that communicates the pipe cavity with the flow-through passage, and the high-pressure shell is configured to discharge the refrigerant flowing into the flow-through passage from the oil separation cavity into the pipe cavity through the sound-absorbing hole.

[0008] According to the high-pressure shell assembly for the electric compressor in the embodiment of the present application, by arranging the resonance cavity on the high-pressure shell, and by connecting the flow passage between the resonance cavity and the sound-eliminating nozzle with the oil separation cavity, and by connecting the lumen of the sound-eliminating nozzle with the outlet of the refrigerant, the cavity structure satisfying the Helmholtz resonance principle is formed, so that the resonance cavity can not only eliminate the noise generated by the refrigerant acting on the high-pressure shell, but also eliminate the noise and pressure pulsation accompanied by the gaseous refrigerant, and by arranging the sound-eliminating nozzle, the sound-eliminating effect in the resonance cavity is greatly improved, thereby improving the airflow noise and pulsation at the exhaust side of the electric compressor, and further improving the noise and pulsation of the refrigerant discharged by the electric compressor, reducing or eliminating the resonance problem of each component in the vehicle thermal management system, and improving the safety of the electric compressor.

[0009] In some embodiments, one of the first end and the second end of the sound-eliminating nozzle is arranged as a fixed end for connecting and fixing the sound-eliminating nozzle, and the other of the first end and the second end of the sound-eliminating nozzle is arranged as a matching end which is arranged in a suspended manner.

[0010] In some embodiments, the mounting size of the matching end of the sound-eliminating nozzle satisfies: 0≤T≤0.2D; wherein T is the suspended height of the matching end, and D is the minimum inner diameter of the sound-eliminating nozzle.

[0011] In some embodiments, the sound-eliminating nozzle is a variable cross-section straight pipe, and the outer diameter of the fixed end of the sound-eliminating nozzle is greater than the outer diameter of the matching end of the sound-eliminating nozzle.

[0012] In some embodiments, a first opening for processing the resonance cavity is formed on the surface of the high-pressure shell, and a first end cover is arranged on the first opening.

[0013] In some embodiments, the first end of the resonance cavity is formed with the first opening, the second end of the resonance cavity is connected with the outlet of the refrigerant through a connecting passage, the flow area of the connecting passage is smaller than the flow area of the resonance cavity, and the sound-eliminating nozzle is fixed to the inner wall of the resonance cavity or the connecting passage.

[0014] In some embodiments, the center line of the connecting passage coincides with the center line of the resonance cavity, and the connecting passage and the resonance cavity are both adapted to be processed through the first opening.

[0015] In some embodiments, the first end cover is provided with a mounting groove which is open towards the resonance cavity; wherein the first end of the sound-eliminating nozzle is fixedly connected with the inner peripheral wall of the mounting groove, or the first end of the sound-eliminating nozzle is gap-fitted with the inner peripheral wall of the mounting groove.

[0016] In some embodiments, a plurality of turns of the sound attenuation holes are arranged along an axial direction of the sound attenuation cannula, each turn of the sound attenuation holes comprising a plurality of sound attenuation holes arranged at intervals along a circumferential direction of the sound attenuation cannula.

[0017] In some embodiments, a center distance t between adjacent sound attenuation holes satisfies: d≤t≤5d; wherein d is an equivalent diameter of a hole section of the sound attenuation hole, and when the hole section sizes of the plurality of sound attenuation holes are different, d is an equivalent diameter of the sound attenuation hole with the largest hole section size.

[0018] In some embodiments, a hole section of the sound attenuation hole satisfies: 0.05D≤d≤D; wherein d is an equivalent diameter of a hole section of the sound attenuation hole, D is an equivalent diameter of a cross section of the sound attenuation cannula, and when the sound attenuation cannula is of a variable cross section structure, D is an equivalent diameter of a smallest cross section of the sound attenuation cannula.

[0019] In some embodiments, the first oil return channel is further arranged at a bottom space of the resonance cavity in a direction of gravity.

[0020] In some embodiments, a position of the first oil return channel in the resonance cavity satisfies: h≤0.3H; wherein h is a vertical distance between a highest point of the first oil return channel and a lowest point of the resonance cavity in a direction of gravity, and H is a vertical distance between a highest point and a lowest point of the resonance cavity in the direction of gravity.

[0021] In some embodiments, the oil separation cavity is provided with an oil separation member for oil-gas separation, and the refrigerant entering the oil separation cavity is subjected to oil-gas separation by the oil separation member and then flows to the resonance cavity.

[0022] The electric compressor according to the second aspect of the embodiments of the present application comprises: a shell component, which comprises the high-pressure shell assembly for the electric compressor according to any one of the above embodiments; a compression component, whose exhaust port is in communication with the high-pressure cavity to discharge the compressed refrigerant to the high-pressure cavity; and a motor component, which comprises a motor body and a driving shaft, and the motor body drives the compression component to perform compression work through the driving shaft.

[0023] In some embodiments, the shell component further comprises: a middle partition plate, the compression component and the motor body are arranged on two sides of the middle partition plate, and the driving shaft is arranged through the middle partition plate to be connected with the compression component; and a low-pressure shell, which forms a low-pressure cavity accommodating the motor body with the middle partition plate, and the low-pressure shell is provided with a refrigerant suction port in communication with the low-pressure cavity, and the compression component suctions refrigerant from the low-pressure cavity.

[0024] An air conditioning system according to a third aspect of the present invention includes an electric compressor according to a second aspect of the present invention.

[0025] A vehicle according to a fourth aspect of the present invention includes a vehicle body and an air conditioning system mounted on the vehicle body, wherein the air conditioning system is an air conditioning system according to a third aspect of the present invention.

[0026] The vehicle, the air conditioning system, the electric compressor, and the high-pressure housing assembly for the electric compressor described above all have the same advantages over the prior art, and will not be repeated here.

[0027] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0028] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0029] Figure 1 This is a schematic diagram of the structure of an electric compressor according to an embodiment of the present invention;

[0030] Figure 2 This is a schematic diagram of the high-pressure housing according to Embodiment 1 of the present invention;

[0031] Figure 3 This is a schematic diagram of the high-pressure casing according to Embodiment 2 of the present invention;

[0032] Figure 4 This is a schematic diagram of the high-pressure housing according to Embodiment 3 of the present invention;

[0033] Figure 5 This is a schematic diagram of the high-pressure housing structure according to Embodiment 4 of the present invention;

[0034] Figure 6 This is a schematic diagram of the high-pressure housing according to Embodiment 5 of the present invention;

[0035] Figure 7 This is a schematic diagram of the high-pressure housing according to Embodiment Six of the present invention;

[0036] Figure 8 This is a partial enlarged view of the fixed end of the silencer cannula in Embodiments 2 and 3 of the present invention;

[0037] Figure 9 This is a partial enlarged view of the mating end of the silencer cannula in Embodiment Six of the present invention;

[0038] Figure 10is a partial enlarged view of the fitting end of the sound-attenuating insertion tube according to Embodiment Three of the present application;

[0039] Figure 11 is a partial enlarged view of the fitting end of the sound-attenuating insertion tube according to Embodiment Four of the present application;

[0040] Figure 12 is a structural schematic view of a vehicle according to an embodiment of the present application.

[0041] Reference Signs:

[0042] Electric compressor 100;

[0043] High-pressure housing 1;

[0044] High-pressure cavity 11; refrigerant discharge port 12;

[0045] Resonance cavity 13; first opening 131; first oil return passage 132;

[0046] Connection passage 14;

[0047] Oil separation cavity 15; oil separation inlet 151, oil separation outlet 152; second oil return passage 153; second opening 154;

[0048] First end cover 21; abutting portion 211; connecting portion 212; mounting groove 213; second end cover 22;

[0049] Oil separation member 3; sound-attenuating insertion tube 4; sound-attenuating hole 41; thin tube section 42; transition section 43; thick tube section 44;

[0050] Low-pressure housing 102; refrigerant suction port 1021; middle partition 103; cover plate 104; low-pressure cavity 105;

[0051] Compression member 20; exhaust port 201;

[0052] Motor member 30; motor body 301; drive shaft 302;

[0053] Electronic control member 40;

[0054] Vehicle body 200; air conditioning system 300; vehicle 1000. DETAILED DESCRIPTION

[0055] Embodiments of the present application are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals represent the same or similar elements or elements having the same or similar functions throughout. The embodiments described below by reference to the drawings are exemplary only, and are for the purpose of explanation only, and are not to be taken as limiting of the present application.

[0056] Reference is made below Figures 1-11A high-pressure housing assembly for an electric compressor according to an embodiment of the present invention is described. This high-pressure housing assembly, by providing a resonant cavity 13 and an oil separator 15, can greatly improve the exhaust noise and pressure pulsation of the electric compressor 100, thereby enhancing the user experience.

[0057] like Figures 1-7 As shown, the high-pressure housing assembly includes a high-pressure housing 1, on which a high-pressure chamber 11 and a refrigerant outlet 12 are formed. The compression component 20 of the electric compressor 100 is adapted to discharge compressed refrigerant into the high-pressure chamber 11, and the high-pressure chamber 11 is adapted to discharge refrigerant out of the high-pressure housing 1 through the refrigerant outlet 12. Thus, when the electric compressor 100 is powered on and operating normally, it can draw in low-pressure refrigerant, which is then compressed by the compression component 20 to form high-pressure refrigerant. This high-pressure refrigerant is discharged into the high-pressure chamber 11 through the exhaust port 201 of the compression component 20, and finally discharged out of the high-pressure housing 1 through the refrigerant outlet 12.

[0058] The high-pressure housing 1 also has a resonant cavity 13 and an oil separator 15, which are interconnected. The oil separator 15 is connected to the high-pressure cavity 11 to receive the refrigerant flowing out of the high-pressure cavity 11, and the resonant cavity 13 is connected to the refrigerant outlet 12. Thus, when the electric compressor 100 is actually running, the high-pressure refrigerant in the high-pressure cavity 11 enters the oil separator 15 from the oil separator inlet 151. After oil-gas separation in the oil separator 15, the gaseous refrigerant enters the resonant cavity 13 from the oil separator outlet 152, and after passing through the structure in the resonant cavity 13, flows out from the refrigerant outlet 12, thus discharging the refrigerant.

[0059] Among them, such as Figures 2-7 As shown, a silencing tube 4 is provided inside the resonant cavity 13. A flow channel is defined between the silencing tube 4 and the inner wall of the resonant cavity 13. That is, the outer diameter of the silencing tube 4 is smaller than the inner diameter of the resonant cavity 13. Thus, after the silencing tube 4 is located inside the resonant cavity 13, at least a portion of the outer peripheral wall of the silencing tube 4 defines a flow channel between the inner wall of the resonant cavity 13 and the outer wall of the resonant cavity 13. One end of the lumen inside the silencing tube 4 is connected to the refrigerant outlet 12. The silencing tube 4 is provided with a silencing hole 41 that connects the lumen to the flow channel. The refrigerant from the high-pressure housing 1 that enters the flow channel from the oil separator 15 is discharged into the lumen through the silencing hole 41.

[0060] In actual design, one end of the tube cavity in the sound attenuation insert pipe 4, i.e., the end close to the refrigerant discharge port 12, can be set as an open end to communicate with the refrigerant discharge port 12, while the other end of the tube cavity in the sound attenuation insert pipe 4, i.e., the end away from the refrigerant discharge port 12, can be set as a closed end and suspended into the resonance cavity 13, so that the tube cavity in the sound attenuation insert pipe 4 communicates with the flow passage through the sound attenuation hole 41. Alternatively, one end of the tube cavity in the sound attenuation insert pipe 4, i.e., the end close to the refrigerant discharge port 12, can be set as an open end to communicate with the refrigerant discharge port 12, while the other end of the tube cavity in the sound attenuation insert pipe 4, i.e., the end away from the refrigerant discharge port 12, can also be set as an open end, and the outer peripheral wall of the sound attenuation insert pipe 4 at the open end is in interference fit with the inner wall of the resonance cavity 13, so that the tube cavity in the sound attenuation insert pipe 4 also communicates with the flow passage through the sound attenuation hole 41. Of course, in actual design, the outer peripheral wall of the sound attenuation insert pipe 4 at the open end can be in clearance fit with the inner wall of the resonance cavity 13 for easy installation, and the clearance is small and has no obvious refrigerant flow, so that the tube cavity in the sound attenuation insert pipe 4 mainly communicates with the flow passage through the sound attenuation hole 41. Figure 10

[0061] That is, in the present application, the gaseous refrigerant separated in the oil separation cavity 15 can enter the resonance cavity 13 from the oil separation outlet 152 and flow in the flow passage before entering the tube cavity in the sound attenuation insert pipe 4 from the sound attenuation hole 41 of the sound attenuation insert pipe 4 and flowing in the tube cavity in the axial direction to the end of the tube cavity for discharge from the refrigerant discharge port 12. It should be noted that the resonance cavity 13 has a cavity structure meeting the principle of Helmholtz resonance and communicates with the oil separation cavity 15 and the refrigerant discharge port 12, so that the noise generated by the separated gaseous refrigerant in the oil separation cavity 15 during discharge to the refrigerant discharge port 12 can enter the resonance cavity 13 for elimination or weakening, thereby improving the flow noise and pulsation on the discharge side of the electric compressor 100 and further improving the noise and pulsation of the refrigerant discharged from the electric compressor 100. The sound attenuation insert pipe 4 arranged in the resonance cavity 13 can divide the cavity structure formed by the resonance cavity 13 into the flow passage between the outer peripheral wall of the sound attenuation insert pipe 4 and the inner wall of the resonance cavity 13 and the tube cavity in the sound attenuation insert pipe 4, i.e., the number of sound attenuation chambers in the resonance cavity 13 is increased by arranging the sound attenuation insert pipe 4, thereby facilitating the multiplication of the sound attenuation effect in the resonance cavity 13.

[0062] ​In other words, after the gaseous refrigerant enters the resonance cavity 13 from the oil outlet 152, the vibration noise and pressure pulsation in the gaseous refrigerant can be eliminated once in the flow passage, i.e., by the reflection of the outer peripheral wall of the sound attenuation nozzle 4 and the inner wall of the resonance cavity 13, and the vibration noise and pressure pulsation in the gaseous refrigerant can be eliminated again in the reflection of the inner wall of the lumen of the sound attenuation nozzle 4 when the gaseous refrigerant enters the sound attenuation nozzle 4 through the sound attenuation hole 41. Thus, the sound attenuation effect in the resonance cavity 13 is greatly improved by providing the sound attenuation nozzle 4. Thus, when the electric compressor 100 is used in the vehicle 1000, the resonance problem of each component in the thermal management system of the vehicle 1000 caused by the exhaust gas flow noise and pressure pulsation of the electric compressor 100 can be improved, and the noise and vibration caused to the vehicle 1000 can be improved.

[0063] It should be noted that the "Helmholtz resonance principle" is well known to those skilled in the art. Based on the disclosure that the resonance cavity 13 can be provided on the high-pressure shell 1, the flow passage between the resonance cavity 13 and the sound attenuation nozzle 4 is communicated with the oil separation cavity 15, the flow passage and the lumen of the sound attenuation nozzle 4 are communicated through the sound attenuation hole 41, and the lumen of the sound attenuation nozzle 4 is communicated with the refrigerant discharge port 12, those skilled in the art can match and calculate the specific dimensions required by the resonance cavity 13, the flow passage and the lumen of the sound attenuation nozzle 4 according to the specific requirements of different working conditions. Therefore, the specific dimensions are not limited in the present application.

[0064] According to the high-pressure shell assembly for the electric compressor in the embodiment of the present application, by providing the resonance cavity 13 on the high-pressure shell 1, communicating the flow passage between the resonance cavity 13 and the sound attenuation nozzle 4 with the oil separation cavity 15, communicating the flow passage and the lumen of the sound attenuation nozzle 4 through the sound attenuation hole 41, and communicating the lumen of the sound attenuation nozzle 4 with the refrigerant discharge port 12, a cavity structure satisfying the Helmholtz resonance principle is formed. The resonance cavity 13 can not only eliminate the noise generated by the refrigerant acting on the high-pressure shell 1, but also eliminate the noise and pressure pulsation in the gaseous refrigerant. By providing the sound attenuation nozzle 4, the sound attenuation effect in the resonance cavity 13 is greatly improved, thereby improving the gas flow noise and pulsation on the exhaust side of the electric compressor 100, further improving the noise and pulsation of the refrigerant discharged from the electric compressor 100, reducing or eliminating the resonance problem of each component in the thermal management system of the vehicle 1000, and improving the safety of the electric compressor 100.

[0065] In some embodiments, one of the first end and the second end of the sound attenuation nozzle 4 is provided as a fixed end, and the fixed end is used for the connection and fixation of the sound attenuation nozzle 4, i.e., the sound attenuation nozzle 4 can be fixedly installed in the high-pressure shell 1 through the fixed end. Meanwhile, the other of the first end and the second end of the sound attenuation nozzle 4 is provided as a matching end, and the matching end is provided in suspension in the high-pressure shell 1.Figures 2-7 As shown in FIG. 1, the resonant cavity 13 is inclinedly extended from the lower left to the upper right in the high-pressure shell 1, and the extension direction of the sound-attenuating insert pipe 4 is the same as that of the resonant cavity 13. The lower left end of the sound-attenuating insert pipe 4 can be set as a fixed end, and the upper right end can be set as a cooperating end, or the upper right end of the sound-attenuating insert pipe 4 can be set as a fixed end, and the lower left end can be set as a cooperating end. In the embodiment shown in FIG. 1, the lower left end of the sound-attenuating insert pipe 4 is suspended in the high-pressure shell 1, and the upper right end is fixed in the high-pressure shell 1. Figures 2-3 In the embodiment shown in FIG. 2, the lower left end of the sound-attenuating insert pipe 4 is fixed in the high-pressure shell 1, and the upper right end is suspended in the high-pressure shell 1. Figures 4-7 In the embodiment shown in FIG. 2, the lower left end of the sound-attenuating insert pipe 4 is fixed in the high-pressure shell 1, and the upper right end is suspended in the high-pressure shell 1.

[0066] It should be noted that the fixed end of the sound-attenuating insert pipe 4 is fixedly installed in the high-pressure shell 1, and can be matched with the high-pressure shell 1 in the form of interference fit, or in the form of welding fit, or in the form of threaded connection.

[0067] Therefore, one end of the sound-attenuating insert pipe 4 in the present application is fixed in the high-pressure shell 1, and the other end is suspended. In actual installation, one end of the sound-attenuating insert pipe 4 can be fixed, and the other end does not need to consider the problems of fixation and sealing and installation precision, which greatly reduces the installation requirements of the sound-attenuating insert pipe 4 in the resonant cavity 13, reduces the installation cost, and facilitates quick disassembly when the sound-attenuating insert pipe 4 is disassembled and replaced.

[0068] In some embodiments, the installation size of the cooperating end of the sound-attenuating insert pipe 4 satisfies: 0≤T≤0.2D; wherein, as shown in FIG. 1 and FIG. 2, T is the suspended height of the cooperating end, that is, the distance between the closest position of the cooperating end of the sound-attenuating insert pipe 4 in the high-pressure shell 1 to the inner wall surface of the high-pressure shell 1, as shown in FIG. 3, the distance between the end surface of the cooperating end of the sound-attenuating insert pipe 4 and the upper end surface of the resonant cavity 13 is T, or as shown in FIG. 4, the distance between the outer peripheral wall of the cooperating end of the sound-attenuating insert pipe 4 and the first end cover 21 of the resonant cavity 13 is T, and or as shown in FIG. 5, the distance between the outer peripheral wall of the cooperating end of the sound-attenuating insert pipe 4 and the inner peripheral wall of the connecting channel 14 is T. Figure 9 Figure 10 Figure 9 Figure 10 Figure 11

[0069] As shown in FIG. 1, the resonant cavity 13 is inclinedly extended from the lower left to the upper right in the high-pressure shell 1, and the extension direction of the sound-attenuating insert pipe 4 is the same as that of the resonant cavity 13. The lower left end of the sound-attenuating insert pipe 4 can be set as a fixed end, and the upper right end can be set as a cooperating end, or the upper right end of the sound-attenuating insert pipe 4 can be set as a fixed end, and the lower left end can be set as a cooperating end. In the embodiment shown in FIG. 1, the lower left end of the sound-attenuating insert pipe 4 is suspended in the high-pressure shell 1, and the upper right end is fixed in the high-pressure shell 1. Figure 8 ​​​​​As shown, D is the minimum inner diameter of the silencer tube 4. The silencer tube 4 in this invention can be set as a constant cross-section tube or a variable cross-section tube. When the silencer tube 4 is a constant cross-section tube, D is the inner diameter of the silencer tube 4. When the silencer tube 4 is a variable cross-section tube, D is the inner diameter of the smallest position among the different positions of the silencer tube 4.

[0070] In other words, the ratio between the distance between the mating end of the silencer tube 4 and the inner wall of the high-pressure housing 1 and the minimum inner diameter of the silencer tube 4 in this invention is greater than 0 and less than or equal to 0.2, such as 0.1 or 0.15, that is, the ratio of the two is within a small range. Therefore, it not only ensures that the mating end of the silencer tube 4 can be reasonably and quickly installed in the high-pressure housing 1, which is convenient for installation, but also that the distance between the mating end of the silencer tube 4 and the inner wall of the high-pressure housing 1 is not too large, reducing the opening amount of the resonance cavity 13, and ensuring the effectiveness of silencing in the resonance cavity 13 under the premise of effective exhaust.

[0071] In some embodiments, the silencing cannula 4 is a straight tube with a variable cross-section, meaning that the cross-sectional area of ​​the silencing cannula 4 is different at at least two locations, and the outer diameter of the fixed end of the silencing cannula 4 is larger than the outer diameter of the mating end of the silencing cannula 4. In actual design, the silencing cannula 4 is constructed to include a thin tube segment 42 with a larger length dimension, a thick tube segment 44 with a smaller length dimension, and a transition section 43 connecting the thin tube segment 42 and the thick tube segment 44. That is, the silencing cannula 4 includes a thin tube segment 42, a transition section 43, and a thick tube segment 44 connected sequentially along the length direction, with the outer diameters of the three increasing sequentially. The transition section 43 is constructed to gradually increase the outer diameter from the end connected to the thin tube segment 42 to the end connected to the thick tube segment 44, forming an inclined transition structure, so that the connection between the thin tube segment 42 and the thick tube segment 44 is relatively gentle.

[0072] like Figure 6 As shown, the outer diameter of the upper right end of the silencing cannula 4 is larger than that of the lower left end, meaning the upper right end of the silencing cannula 4 is a fixed end. The thin tube section 42, the transition section 43, and the thick tube section 44 are connected sequentially from the lower left to the upper right to form a complete silencing cannula 4. The end of the thick tube section 44 facing away from the transition section 43 is a fixed end, and the end of the thin tube section 42 facing away from the transition section 43 is a mating end. The lower end of the thin tube section 42 is clearance-fitted with the inner wall surface of the high-pressure housing 1, while the upper end of the thick tube section 44 is fixedly fitted with the inner wall surface of the high-pressure housing 1. Or as... Figure 7As shown, the outer diameter of the lower left end of the silencing cannula 4 is larger than that of the upper right end, that is, the lower left end of the silencing cannula 4 is constructed as a fixed end. The thin tube section 42, the transition section 43 and the thick tube section 44 are connected sequentially from the upper right to the lower left to form a complete silencing cannula 4. The end of the thick tube section 44 away from the transition section 43 is formed as a fixed end, and the end of the thin tube section 42 away from the transition section 43 is formed as a mating end. The upper end of the thin tube section 42 is clearance-fitted with the inner wall surface of the high-pressure housing 1, while the lower end of the thick tube section 44 is fixedly fitted with the inner wall surface of the high-pressure housing 1.

[0073] In some embodiments, such as Figures 2-7 As shown, a first opening 131 is formed on the surface of the high-pressure housing 1. The first opening 131 is used to process the resonant cavity 13. If the high-pressure housing 1 is formed by drilling, a drilling tool can be inserted from the first opening 131 to perform the drilling operation, and the drilling tool can be withdrawn from the first opening 131. Alternatively, if the high-pressure housing 1 is formed by casting, the processing mold of the resonant cavity 13 can be removed from the first opening 131. Thus, by designing the first opening 131, it is beneficial to realize the processing and forming of the resonant cavity 13, to realize the forming of the high-pressure housing 1 by various processing methods, to reduce the processing difficulty and processing cost of the high-pressure housing 1, and to realize the mass production and practical application of the high-pressure housing 1.

[0074] And such as Figures 2-7 As shown, the high-pressure housing 1 includes a first end cap 21 covering the first opening 131. That is, in this invention, the first opening 131 is designed to cooperate with the first end cap 21. After the high-pressure housing 1 is installed in the entire electric compressor 100, the high-pressure chamber 11 communicates with the oil separator chamber 15, and the resonance chamber 13 communicates with the oil separator chamber 15. The resonance chamber 13 is closed at the first opening 131 by the first end cap 21, thereby forming a cavity structure that satisfies the Helmholtz resonance principle. In this invention, the cover refers to at least a portion of the first end cap 21 extending into the first opening 131 and the remaining portion blocking the first opening 131, so that the first end cap 21 achieves connection and fixation at the first opening 131 and blocks and closes the first opening 131.

[0075] In the specific design, the resonant cavity 13 can be configured as a hole shape, the first opening 131 is formed at at least one side hole end of the resonant cavity 13 (it can be understood that the hole shape has two side end holes, and one side end hole of the resonant cavity 13 is communicated with the refrigerant discharge port 12, and the other side end hole is formed with the first opening 131); wherein, the resonant cavity 13 is a hole shape, which means that it has a certain depth of three-dimensional hole shape, rather than a planar hole shape, and the two ends in the center line extension direction of the hole are the two ends of the resonant cavity 13 in the length direction. Therefore, the resonant cavity 13 in the application has a simple structure, is easy to process, can be processed by punching or casting and other ways, has flexible setting position, meets the design requirements of different models, occupies smaller space, can reduce the overall volume under the premise of meeting the noise reduction, and saves the occupation of the space in the vehicle.

[0076] Wherein, the first machining end face is formed on the outside of the high-pressure shell 1, and the first opening 131 is open at the first machining end face, as shown in Figures 2-7 The first machining end face is configured as a machining plane arranged on the outside of the high-pressure shell 1, and the surface is regular and smooth, which is not easy to interfere with the punching tool or the mold, and is beneficial to realize the disengagement of the user's operation of the punching tool or the mold. The first end cover 21 comprises a pressing part 211 and a connecting part 212, the pressing part 211 and the connecting part 212 are integrally formed, and the pressing part 211 is configured as a disc, the connecting part 212 is configured as a column, and the end face of the pressing part 211 is fixedly connected with the end face of the connecting part 212, wherein, the outer diameter size of the pressing part 211 is greater than the outer diameter size of the connecting part 212 to form a limiting surface at the position connected with the connecting part 212. And in the assembly, the connecting part 212 can be stretched into the first opening 131, and the connecting part 212 is fixedly connected with the inner wall of the first opening 131, and the pressing part 211 is located outside the first opening 131 and is pressed on the first machining end face.

[0077] In the specific design, the connecting portion 212 can be threadedly connected with the inner circumferential wall of the first opening 131, so that the connecting portion 212 can be rotatably detached from or installed in the first opening 131, or the connecting portion 212 can be in interference fit with the inner circumferential wall of the first opening 131, that is, the connecting portion 212 can be pressed into the first opening 131 to be tightly pressed with the inner circumferential wall of the first opening 131, so as to ensure the connection stability of the first end cover 21 at the first opening 131. Wherein, the abutting portion 211 is designed to abut against the first machined end face through the limiting surface, so as to limit the relative position between the first end cover 21 and the high-pressure shell 1, that is, when the connecting portion 212 is fitted to the maximum position in the first opening 131, the abutting portion 211 abuts against the first machined end face, preventing the first end cover 21 from being excessively or completely inserted into the first opening 131, so that the part of the abutting portion 211 of the first end cover 21 is effectively kept outside the first opening 131, ensuring the relative position between the first end cover 21 and the high-pressure shell 1, and facilitating the user to operate the abutting portion 211 to install and detach the first end cover 21, improving the rationality of the structural design.

[0078] In some embodiments, a first opening 131 is formed at a first end of the resonance cavity 13, and a second end of the resonance cavity 13 is communicated with the refrigerant discharge outlet 12 through a connecting channel 14, as shown in Figures 2-5 , Figure 7 The first opening 131 is formed at the lower left end of the resonance cavity 13, and the connecting channel 14 is located at the upper right end of the resonance cavity 13, and the connecting channel 14 is used to communicate the upper right end of the resonance cavity 13 with the refrigerant discharge outlet 12, so that the gaseous refrigerant flowing into the resonance cavity 13 can flow from the connecting channel 14 to the refrigerant discharge outlet 12.

[0079] The flow area of the connecting channel 14 is smaller than the flow area of the resonance cavity 13, so that the first end of the resonance cavity 13, such as the lower end in Figure 2 , is formed by the first end cover 21 to form an inner end face of the resonance cavity 13, and the second end of the resonance cavity 13, such as the upper end in Figure 2 , forms a stepped surface at the connection with the connecting channel 14, which can be used as another inner end face of the resonance cavity 13.

[0080] Therefore, the first end of the resonance cavity 13 is fitted with the first end cover 21, and the second end of the resonance cavity 13 is fitted with the stepped surface formed between the connecting channel 14, so that the resonance cavity 13 forms a cavity structure that satisfies the Helmholtz resonance principle, thereby improving the airflow noise and pulsation of the electric compressor 100 on the discharge side, and further improving the noise and pulsation of the refrigerant discharged by the electric compressor 100.

[0081] And in actual installation, the sound attenuation insert tube 4 can be fixed to the inner wall of the resonance cavity 13 or the connecting channel 14, that is, the fixed end of the sound attenuation insert tube 4 can be fixedly connected with the inner wall of the resonance cavity 13, as shown in Figs. 2 and Figure 3 The fixed end of the sound attenuation insert tube 4 is the upper right end thereof, and the fixed end of the sound attenuation insert tube 4 extends into the connecting channel 14 to be fixedly connected with the inner circumferential wall of the connecting channel 14, as shown in Fig. 2. Figure 7 The fixed end of the sound attenuation insert tube 4 is the lower left end thereof, and the fixed end of the sound attenuation insert tube 4 is fixedly connected with the lower end region of the inner circumferential wall of the resonance cavity 13 in the resonance cavity 13.

[0082] In some embodiments, the center line of the connecting channel 14 coincides with the center line of the resonance cavity 13, and the connecting channel 14 and the resonance cavity 13 are both adapted to be processed by the first opening 131. It should be noted that the resonance cavity 13 is configured as a channel structure with a circular cross section, the connecting channel 14 is also configured as a channel structure with a circular cross section, and the center line of the resonance cavity 13 and the center line of the connecting channel 14 are the respective corresponding axes, that is, the axis of the resonance cavity 13 coincides with the axis of the connecting channel 14.

[0083] As shown in Fig. 2, the first opening 131 is provided at the lower left end of the resonance cavity 13, and the connecting channel 14 is formed at the upper right end of the resonance cavity 13, so that the resonance cavity 13 and the connecting channel 14 can be co-formed when co-processed. Figures 2-7

[0084] Specifically, when the high-pressure shell 1 is punch-formed, the punch tool can be inserted from the first opening 131 to perform the punching operation, and the punch tool first processes the resonance cavity 13 on the high-pressure shell 1, and as the punch tool is inserted and the punching radius is reduced, the connecting channel 14 can be processed, and the axis of the connecting channel 14 coincides with the axis of the resonance cavity 13, so that the punch tool can be operated in a single processing direction or a tool withdrawal direction, reducing the forming difficulty. Alternatively, when the high-pressure shell 1 is cast-formed, the processing die of the resonance cavity 13 can be withdrawn from the first opening 131, and in actual design, the resonance cavity 13 and the connecting channel 14 are processed by the same die, for example, the processing die includes two parts, one part with a smaller diameter for forming the connecting channel 14, and the other part with a larger diameter for forming the resonance cavity 13, and the first opening 131 is larger than the outer diameter of the processing die, facilitating rapid demolding. Thus, the resonance cavity 13 and the connecting channel 14 can be demolded by the same die, improving processing efficiency, reducing the number of dies, and reducing processing costs.

[0085] In actual processing, the punch tool can be withdrawn along the axis of the resonance cavity 13, or the processing die can be withdrawn along the axis of the resonance cavity 13, to avoid damage to the formed high-pressure shell 1 by the punch tool or the processing die. ​

[0086] In some embodiments, the first end cover 21 is provided with a mounting groove 213 which is open towards the resonance cavity 13, that is, the mounting groove 213 is recessed on the end face of the first end cover 21, and after the first end cover 21 is installed in the high-pressure shell 1, the mounting groove 213 is located in the resonance cavity 13 and is open towards the resonance cavity 13. In actual installation, one end of the sound-attenuating insert pipe 4 can be fixedly connected with the inner peripheral wall of the mounting groove 213, or the one end of the sound-attenuating insert pipe 4 can be clearance-fitted with the inner peripheral wall of the mounting groove 213.

[0087] That is, the inner diameter of the mounting groove 213 is greater than the outer diameter of the end portion of the sound-attenuating insert pipe 4, so that the one end of the sound-attenuating insert pipe 4 can extend into the mounting groove 213 and be mounted and fitted with the first end cover 21, such as clearance-fitted with the inner wall of the mounting groove 213, or the inner peripheral wall of the mounting groove 213 is provided with internal threads, and the end portion of the sound-attenuating insert pipe 4 is provided with external threads, the sound-attenuating insert pipe 4 extends into the mounting groove 213 to be screwed with the first end cover 21; or the inner diameter of the mounting groove 213 is close to the outer diameter of the end portion of the sound-attenuating insert pipe 4, so that the sound-attenuating insert pipe 4 is installed in the mounting groove 213 to be interference-fitted with the first end cover 21, to realize connection and fixation.

[0088] As shown in FIG. 5, the lower left end of the sound-attenuating insert pipe 4 extends into the mounting groove 213 and is spaced apart from the inner wall of the mounting groove 213, as shown in FIG. 6, the lower left end of the sound-attenuating insert pipe 4 extends into the mounting groove 213 and is fixed with the inner wall of the mounting groove 213, such as interference-fitted. Figure 3 Figures 4-6 In some embodiments of the application, the mounting groove 213 is provided, so that at least part of the end portion of the sound-attenuating insert pipe 4 is located in the mounting groove 213 for limiting and fitting, and the first end cover 21 and the sound-attenuating insert pipe 4 can share part of the space in the axial direction, which is beneficial to improve the fitting depth of the sound-attenuating insert pipe 4 with the first end cover 21 and beneficial to increase the length of the sound-attenuating insert pipe 4.

[0089] In some embodiments, a plurality of sound-attenuating holes 41 are arranged in the axial direction of the sound-attenuating insert pipe 4, that is, the outer peripheral wall of the sound-attenuating insert pipe 4 is provided with a plurality of sound-attenuating holes 41 which are spaced apart in the axial direction of the sound-attenuating insert pipe 4. This is to increase the flow section between the pipe cavity of the sound-attenuating insert pipe 4 and the flow passage, to ensure the flow efficiency of the gaseous refrigerant. In actual design, the plurality of sound-attenuating holes 41 can be uniformly spaced apart in the axial direction of the sound-attenuating insert pipe 4, to ensure the uniformity of the gas flow at each position of the sound-attenuating insert pipe 4, and to make the sound-attenuating effect at each position of the sound-attenuating insert pipe 4 more uniform.

[0090] ​Each ring of silencer holes 41 includes multiple silencer holes 41, and the multiple silencer holes 41 in each ring are spaced apart along the circumference of the silencer tube 4. This allows airflow to occur at different positions along both the axial and circumferential directions of the silencer tube 4. Furthermore, by distributing a large number of silencer holes 41 along the axial and circumferential directions of the silencer tube 4, the flow rate of gaseous refrigerant from the flow channel to the silencer tube 4 is increased, achieving rapid exhaust.

[0091] In some embodiments, in the multi-turn silencer hole 41, such as Figure 8 As shown, the center distance t between adjacent silencing holes 41 satisfies: d ≤ t ≤ 5d; where, as Figure 8 As shown, d is the equivalent diameter of the cross-section of the silencing hole 41. That is, the ratio of the center distance between two adjacent silencing holes 41 to the equivalent diameter of the cross-section of the silencing hole 41 is in the range of 1 to 5, such as setting t to 2d or 3d.

[0092] Understandably, the silencing holes 41 are formed by hollowing out the outer peripheral wall of the silencing tube 4. By setting the silencing holes 41, it is not only beneficial to allow the gaseous refrigerant to flow between the flow channel and the cavity of the silencing tube 4, but also to reduce the weight of the silencing tube 4, achieving a lightweight design. Setting the center distance of the silencing holes 41 within the aforementioned range not only ensures the air intake of the silencing tube 4, but also avoids the structural strength of the silencing tube 4 being too low due to an excessive number of silencing holes 41, preventing the silencing tube 4 from breaking due to excessive vibration during the operation of the electric compressor 100.

[0093] Furthermore, when the cross-sectional sizes of multiple silencing holes 41 are different, d is the equivalent diameter of the silencing hole 41 with the largest cross-sectional area. That is, in actual design, when the inner diameters of different silencing holes 41 are the same, the diameters of multiple silencing holes 41 can be set to be the same, and d is the equivalent diameter of any one of the silencing holes 41. However, when at least two of the multiple silencing holes 41 have different diameters, d is the equivalent diameter of the silencing hole 41 with the largest cross-sectional area. Thus, a comparative design of the center distance and hole diameter of the silencing holes 41 can be achieved. It should be noted that the silencing holes 41 in this invention can be constructed as circular holes, square holes, or other irregularly shaped holes. The equivalent diameter is the diameter of a circular hole with the same cross-sectional area corresponding to a square hole or other irregularly shaped hole.

[0094] In some embodiments, the cross-sectional area of ​​the silencing hole 41 satisfies: 0.05D ≤ d ≤ D; where, as Figure 8 As shown, d is the equivalent diameter of the cross-section of the silencing hole 41, and D is the equivalent diameter of the cross-section of the silencing tube 4. That is, the ratio between the equivalent diameter of the cross-section of the silencing hole 41 and the equivalent diameter of the cross-section of the silencing tube 4 is 0.05 to 1, such as d being set to 0.1D or 0.2D.

[0095] The size of the hole section of the sound attenuation hole 41 is set within the above range, so that the equivalent diameter of the hole section of the sound attenuation hole 41 is more reasonable relative to the equivalent diameter of the cross section of the sound attenuation nozzle 4. That is, the sound attenuation hole 41 is not too small, which causes the flow rate of the gaseous refrigerant flowing through the sound attenuation hole 41 to be greatly different from the flow rate of the second end of the lumen, ensuring that the gaseous refrigerant can be reasonably discharged from the oil outlet 152, the flow-through passage, the sound attenuation hole 41, the lumen, and the refrigerant discharge port 12 in sequence; and the sound attenuation hole 41 is not too large, which causes the structural strength of the sound attenuation nozzle 4 to be too small, avoiding the problem of structural rupture of the sound attenuation nozzle 4 caused by excessive vibration during operation of the electric compressor 100, thereby improving the safety of the sound attenuation nozzle 4.

[0096] And when the sound attenuation nozzle 4 is a variable cross-section structure, D is the equivalent diameter of the smallest cross section of the sound attenuation nozzle 4. That is, the sound attenuation nozzle 4 in the present application can be configured as a constant cross-section tube, and when it is a constant cross-section tube, the equivalent diameter of the cross section at any position of the sound attenuation nozzle 4 is D; the sound attenuation nozzle 4 can also be configured as a variable cross-section tube, and when it is a variable cross-section tube, the diameter of the smallest cross section of the sound attenuation nozzle 4 is D. It should be noted that the cross section of the sound attenuation nozzle 4 in the present application can be configured as a circular cross section, or a square cross section or other irregular shape cross section, and the equivalent diameter is the diameter of the circular cross section corresponding to the same cross-sectional area of the square cross section or other irregular shape cross section.

[0097] In some embodiments, a first oil return passage 132 is arranged at the bottom space of the resonance cavity 13 in the direction of gravity, as shown in Figure 7 The first oil return passage 132 is arranged at the lower end of the resonance cavity 13, that is, the inlet end of the first oil return passage 132 is arranged at the inner circumferential wall of the resonance cavity 13 and opens towards the inside of the resonance cavity 13, so that the oil deposited in the resonance cavity 13 can flow out through the first oil return passage 132 and return to the space where the compression component 20 is located.

[0098] The first oil return passage 132 extends towards the compression component 20 at the bottom space of the resonance cavity 13, and the axis of the first oil return passage 132 forms an angle with the axis of the resonance cavity 13, and the first oil return passage 132 extends away from the resonance cavity 13 and is inclined downward relative to the resonance cavity 13. It can be understood that the resonance cavity 13 is also configured to have a first opening 131 formed at the open lower end, so that the first oil return passage 132 and the resonance cavity 13 can be machined from the same side of the high-pressure shell 1, for example, the first oil return passage 132 and the resonance cavity 13 can be machined from different positions on the lower side of the high-pressure shell 1, thereby reducing the machining difficulty.

[0099] In actual design, the first oil return channel 132 is lower than the oil outlet 152. That is, in the design where the oil outlet 152 is located on the inner peripheral wall of the connecting channel 14 or the inner peripheral wall of the resonant cavity 13, the oil outlet 152 is higher than the first oil return channel 132. This design allows the oil entering the resonant cavity 13 at the oil outlet 152 to be deposited in the resonant cavity 13 and then effectively flow back to the space where the compression component 20 is located through the first oil return channel 132. In addition, the inlet end of the first oil return channel 132 is spaced apart from the lower end face of the resonant cavity 13 by a certain distance, so that after the first end cap 21 is installed on the first opening 131, the first end cap 21 is spaced apart from the first oil return channel 132 to avoid the first end cap 21 being installed too deeply and causing blockage of the first oil return channel 132.

[0100] In some embodiments, the position of the first oil return channel 132 within the resonant cavity 13 satisfies: h ≤ 0.3H; wherein, as shown in the figure... Figure 7 As shown, h is the vertical distance between the highest point of the first oil return channel 132 and the lowest point of the resonant cavity 13 in the direction of gravity, and H is the vertical distance between the highest and lowest points of the resonant cavity 13 in the direction of gravity. Figure 3 As shown, the first oil return channel 132 is located in the bottom space inside the resonant cavity 13, that is, the first oil return channel 132 is spaced apart from the upper end of the resonant cavity 13 and from the lower end of the resonant cavity 13, and the ratio of the vertical distance between the first oil return channel 132 and the lowest point of the resonant cavity 13 to the vertical distance between the highest point and the lowest point of the resonant cavity 13 is less than 0.3, such as 0.28, 0.25 or 0.2.

[0101] Therefore, by setting the position of the first oil return channel 132 within the resonant cavity 13 within the aforementioned range, the inlet end of the first oil return channel 132 can be positioned relatively low within the resonant cavity 13, ensuring that the oil deposited within the resonant cavity 13 can flow out through the first oil return channel 132, thus avoiding excessive oil deposits within the resonant cavity 13 that could cause excessive pressure on the first end cap 21, and ensuring the effectiveness of oil return.

[0102] In actual design, at least one first oil return channel 132 can be set, that is, one first oil return channel 132 can be set on the outer peripheral wall of the resonant cavity 13, or two, three or even more first oil return channels 132 can be set to ensure the oil return volume, prevent the blockage of a single first oil return channel 132 from causing the inability to return oil normally, and improve the reliability of oil return.

[0103] In this invention, the height of the first oil return channel 132 can be flexibly set according to the position of the oil outlet 152. For example, when the oil outlet 152 is located on the inner peripheral wall of the connecting channel 14, the oil outlet 152 is at a higher height, resulting in less oil entering the resonance cavity 13, and the height of the first oil return channel 132 is higher. Alternatively, if the oil outlet 152 is located on the inner peripheral wall of the resonance cavity 13, the oil outlet 152 is at a lower height, resulting in more oil entering the resonance cavity 13, and the height of the first oil return channel 132 is lower, to ensure timely oil return. Here, "higher" and "lower" refer to a comparison between two different settings, not necessarily an absolute higher or lower.

[0104] In some embodiments, such as Figures 2-7 As shown, the oil separator 15 has a second oil return channel 153 at the bottom in the direction of gravity. It can be understood that the oil separator 15 is connected to the high pressure chamber 11, so that the high pressure refrigerant can enter the oil separator 15 for oil-gas separation. The separated gaseous refrigerant flows from the oil separator outlet 152 to the connecting channel 14 or the resonant chamber 13. The separated oil flows downward under the action of gravity and gathers at the bottom of the oil separator 15, and flows back from the second oil return channel to the space where the compression component 20 is located.

[0105] The second oil return channel 153 extends from the bottom space of the oil separator chamber 15 towards the compression component 20, and the axis of the second oil return channel 153 forms a certain angle with the axis of the oil separator chamber 15. The second oil return channel 153 extends away from the oil separator chamber 15 and is inclined downwards. Thus, both the second oil return channel 153 and the oil separator chamber 15 can be machined from the same side of the high-pressure housing 1. For example, the second oil return channel 153 and the oil separator chamber 15 can be machined from different positions on the lower side of the high-pressure housing 1, thereby reducing machining difficulty. In actual design, the second oil return channel 153 is lower than the oil separator outlet 152 and also lower than the oil separator inlet 151 of the oil separator chamber 15. This allows the high-pressure refrigerant to enter the oil separator chamber 15 from the oil separator inlet 151 for separation, and the oil can then be deposited at the bottom space of the oil separator chamber 15 under gravity, thus returning through the second oil return channel 153, ensuring reasonable oil return within the oil separator chamber 15.

[0106] In some embodiments, a second opening 154 is formed on the surface of the high-pressure housing 1 for machining the oil separator 15. When the high-pressure housing 1 is formed by drilling, a drilling tool can be inserted into the second opening 154 to perform drilling operations, and the drilling tool can be withdrawn from the second opening 154. Alternatively, when the high-pressure housing 1 is formed by casting, the machining mold for the oil separator 15 can be removed from the second opening 154. Thus, by designing the second opening 154, it is beneficial to realize the machining and forming of the oil separator 15, to realize the forming of the high-pressure housing 1 in various processing methods, to reduce the processing difficulty and processing cost of the high-pressure housing 1, and to realize the mass production and practical application of the high-pressure housing 1.

[0107] Among them, such as Figures 2-7 As shown, the high-pressure housing 1 includes a second end cap 22 covering the second opening 154. In this invention, the second opening 154 is designed to cooperate with the second end cap 22. After the high-pressure housing 1 is installed in the entire electric compressor 100, the high-pressure chamber 11 communicates with the oil inlet 151 of the oil separator chamber 15, and the resonant chamber 13 communicates with the oil inlet 151 of the oil separator chamber 15. The second end cap 22 seals the second opening 154, ensuring a stable seal in the oil separator chamber 15 at all locations except for the oil inlet 151, thereby ensuring the reliability of the oil separation effect. The way the second end cap 22 covers the second opening 154 is the same as the way the first end cap 21 covers the first opening 131, and will not be described again here.

[0108] Furthermore, a second machined end face is formed on the outer side of the high-pressure housing 1, and a second opening 154 is formed open on the second machined end face, such as... Figures 2-7 As shown, the second machining end face is a machining plane located on the outer side of the high-pressure housing 1. Its surface is smooth and regular, making it less likely to interfere with the drilling tool or mold, thus facilitating the user's removal of the drilling tool or mold. The second end cap 22 can be constructed with the same structural shape as the first end cap 21, and the fitting method between the second end cap 22 and the second opening 154 is the same as the fitting method between the first end cap 21 and the first opening 131, which will not be described further here.

[0109] The centerline of the oil separator outlet 152 coincides with the centerline of the oil separator cavity 15, and both the oil separator outlet 152 and the oil separator cavity 15 are suitable for processing and shaping through the second opening 154. It should be noted that the oil separator cavity 15 is constructed as a channel structure with a circular cross-section, and the oil separator outlet 152 is also constructed as a channel structure with a circular cross-section. Furthermore, the centerlines of the oil separator cavity 15 and the oil separator outlet 152 are their respective axes, meaning the axis of the oil separator cavity 15 coincides with the axis of the oil separator outlet 152. Figures 2-4As shown, the second opening 154 is formed at the lower right end of the oil separation cavity 15, and the oil separation outlet 152 is formed at the upper left end of the oil separation cavity 15, so that the oil separation cavity 15 and the oil separation outlet 152 can be formed together when co-molded.

[0110] Specifically, when the high-pressure shell 1 is punch-formed, the punch tool can be inserted into the second opening 154 to punch the high-pressure shell 1, and the punch tool first processes the oil separation cavity 15 on the high-pressure shell 1, and then processes the oil separation outlet 152 as the punch tool is inserted and the punch radius is reduced. The axis of the oil separation outlet 152 coincides with the axis of the oil separation cavity 15, so that the punch tool can be operated in a single processing direction or a tool withdrawal direction, reducing the difficulty of forming. Alternatively, when the high-pressure shell 1 is cast-formed, the processing mold of the oil separation cavity 15 can be withdrawn from the second opening 154, and in actual design, the oil separation cavity 15 and the oil separation outlet 152 are processed and formed by the same mold. For example, the processing mold includes two parts, one part has a smaller diameter for forming the oil separation outlet 152, and the other part has a larger diameter for forming the oil separation cavity 15. The second opening 154 is larger than the outer diameter of the processing mold, which facilitates rapid demolding. Thus, the oil separation cavity 15 and the oil separation outlet 152 can be demolded and formed by the same mold, improving processing efficiency, reducing the number of molds, and reducing processing costs.

[0111] In actual processing, the punch tool can be withdrawn along the axis of the oil separation cavity 15, or the processing mold can be withdrawn along the axis of the oil separation cavity 15, to avoid damage to the formed high-pressure shell 1 by the punch tool or the processing mold.

[0112] In some embodiments, as shown, Figures 2-7 As shown, the oil separation cavity 15 is provided with an oil separation member 3 for oil-gas separation. The oil separation member 3 is used to improve the oil separation effect in the oil separation cavity 15. The refrigerant in the oil separation cavity 15 can be separated by the oil separation member 3 before being discharged from the oil separation outlet 152. That is, after the high-pressure refrigerant in the high-pressure cavity 11 enters the oil separation cavity 15, the separated oil flows back to the space where the compression component 20 is located through the second oil return passage 153 under the separation action of the oil separation member 3, and the separated gaseous refrigerant is discharged upward to the oil separation outlet 152.

[0113] Further, the oil separation member 3 is configured as a hollow tubular structure, such as an oil separation insert pipe. The axial direction of the oil separation member 3 is parallel to the length direction of the oil separation cavity 15, that is, the axis of the lumen of the oil separation insert pipe is parallel to the axis of the oil separation cavity 15. The oil inlet 151 is located outside the peripheral wall of the oil separation member 3, that is, the oil inlet 151 is arranged on the outer peripheral wall of the oil separation cavity 15 and located radially outside the oil separation insert pipe.

[0114] It should be noted that, as shown, Figures 2-7As shown, after the oil separation nozzle is installed in the oil separation chamber 15, the oil separation nozzle is located in the upper space of the oil separation chamber 15, the upper end of the oil separation nozzle is fixedly connected with the upper end of the oil separation chamber 15, the lower end of the oil separation nozzle is suspended in the oil separation chamber 15, and both ends of the oil separation nozzle are open, the upper end of the oil separation nozzle is in communication with the oil separation outlet 152, and the lower end of the oil separation nozzle is in communication with the oil separation chamber 15, as shown in Figures 2-7 As shown, the height of the oil separation inlet 151 is located between the upper end and the lower end of the oil separation nozzle.

[0115] In this way, after the high-pressure refrigerant in the high-pressure chamber 11 enters the oil separation chamber 15, the high-pressure refrigerant acts on the outer peripheral wall of the oil separation nozzle at a high flow rate, and under the guidance of the outer peripheral wall of the oil separation nozzle and the gravity of the high-pressure refrigerant, the high-pressure refrigerant moves downward and moves to a space below the lower end of the oil separation nozzle, and then under the action of the internal pressure of the oil separation chamber 15, the separated gaseous refrigerant enters the lumen of the oil separation nozzle and is discharged upward from the oil separation outlet 152; the oil separated from the high-pressure refrigerant deposits on the outer peripheral wall of the oil separation nozzle or the inner peripheral wall of the oil separation chamber 15 and flows into the space where the compression component 20 is located from the second oil return passage 153, thereby realizing oil-gas separation.

[0116] It can be understood that the oil separation inlet 151 is arranged in radial opposition to the outer peripheral wall of the oil separation nozzle, so that the high-pressure refrigerant entering the oil separation chamber 15 from the oil separation inlet 151 directly acts on the outer peripheral wall of the oil separation nozzle, and flows along the inner peripheral wall of the oil separation chamber 15 under the guidance of the oil separation nozzle, and forms a circumferential rotational flow along the inner peripheral wall of the oil separation chamber 15, thereby accelerating the separation of oil and gas during the circumferential rotational flow, and facilitating the enhancement of the oil-gas separation effect.

[0117] In actual design, as shown in Figure 1 The axial length of the oil separation nozzle is not less than half of the axial length of the oil separation chamber 15, so that the high-pressure refrigerant has sufficient flow distance to realize oil-gas separation after entering the oil separation chamber 15, and the amount of oil accompanying the gaseous refrigerant is reduced, that is, the amount of oil entering the resonance chamber 13 or the connecting passage 14 is reduced.

[0118] Next, with reference to the accompanying Figure 1 , the electric compressor 100 according to the second aspect of the present application is described.

[0119] As shown in Figure 1As shown, the electric compressor 100 can include: a shell component, a compression component 20, and a motor component 30, the shell component includes the high-pressure shell assembly for the electric compressor according to any one of the above first aspect embodiments, the exhaust port 201 of the compression component 20 communicates with the high-pressure cavity 11 to discharge the compressed refrigerant to the high-pressure cavity 11, the motor component 30 includes a motor body 301 and a drive shaft 302, the motor body 301 drives the compression component 20 to perform compression work through the drive shaft 302. Thus, by providing the high-pressure shell assembly, the exhaust gas flow noise and pressure pulsation generated during the operation of the electric compressor 100 can be effectively improved.

[0120] It should be noted that the specific type of the electric compressor 100 is not limited, for example, it can be a horizontal compressor with the central axis extending along the transverse direction or slightly inclined to the horizontal line, for example, it can also be a vertical compressor with the central axis extending along the vertical direction or slightly inclined to the vertical line, and the like.

[0121] It should be noted that the specific type of the electric compressor 100 is not limited, for example, it can be a rotary compressor or a scroll compressor, and the like, when the electric compressor 100 is a rotary compressor (not shown in the example), the compression component 20 can include a cylinder, a piston, a sliding vane, and the like, the drive shaft 302 drives the piston to roll in the cylinder, when the electric compressor 100 is a scroll compressor (for example Figure 1 , the compression component 20 can include a static scroll, a dynamic scroll, the drive shaft 302 drives the dynamic scroll to rotate, and the like.

[0122] It should be noted that the relative position relationship between the high-pressure shell 1 and the compression component 20 is not limited, for example, the compression component 20 can be completely located outside the high-pressure shell 1, or the compression component 20 can also be at least partially located outside the high-pressure shell 1, and the like, so as to meet different design requirements of different models.

[0123] In some embodiments, as shown in Figure 1 , the shell component further includes: a partition plate 103 and a low-pressure shell 102, the compression component 20 and the motor body 301 are located on two sides of the partition plate 103, the drive shaft 302 penetrates the partition plate 103 to connect with the compression component 20; the low-pressure shell 102 and the partition plate 103 form a low-pressure cavity 105 accommodating the motor body 301, the low-pressure shell 102 is formed with a refrigerant suction port 1021 communicating with the low-pressure cavity 105, and the compression component 20 sucks in refrigerant from the low-pressure cavity 105. Wherein, the cover plate 104 is further connected on the low-pressure shell 102, and the cover plate 104 and the low-pressure shell 102 define a mounting space, and the electric control component 40 is arranged in the mounting space.

[0124] Therefore, the electric compressor 100 can be a low back pressure compressor. This type of compressor is beneficial for the application of new energy vehicles 1000 such as pure electric vehicles and hybrid vehicles. When used in these vehicles 1000, it can improve the exhaust airflow noise and pressure pulsation caused by the electric compressor 100, improve the resonance problem of the vehicle 1000's thermal management system, and improve the noise and vibration caused to the vehicle 1000.

[0125] In some embodiments, such as Figure 1 As shown, the partition 103 is sandwiched between the low-pressure housing 102 and the compression component 20, while the high-pressure housing 1 is located on the side of the compression component 20 opposite to the partition 103. This simplifies the structure, simplifies assembly, reduces size, improves production efficiency, and enhances connection reliability. For example, this structure can be applied to scroll compressors, but the structure of scroll compressors is not limited to this.

[0126] Furthermore, such as Figure 12 As shown, the high-pressure housing 1 has a housing end face, on which a high-pressure cavity 11 is formed. The high-pressure cavity 11 is open to the compression component 20. The compression component 20 is sealed to the housing end face. The exhaust port 201 of the compression component 20 is open to the high-pressure cavity 11, thereby enabling communication between the exhaust port 201 and the high-pressure cavity 11.

[0127] Hereinafter, with reference to the accompanying drawings, an air conditioning system 300 according to a third aspect embodiment of the present invention will be described.

[0128] The air conditioning system 300 may include an electric compressor 100 according to any embodiment of the second aspect of the present invention. Since the exhaust noise and pulsation of the electric compressor 100 according to any embodiment of the second aspect of the present invention can be improved, when the electric compressor 100 is used in the air conditioning system 300, the pressure pulsation and noise problems caused to the air conditioning system 300 due to the exhaust airflow noise and pressure pulsation of the electric compressor 100 can be improved.

[0129] It should be noted that the specific application scenarios of the air conditioning system 300 according to the embodiments of the present invention are not limited, such as indoor air conditioning, indoor refrigerator, vehicle air conditioning, etc. Once the application scenario is determined, those skilled in the art can know other components of the air conditioning system 300. For example, when used for indoor air conditioning or indoor refrigerator, it may also include an evaporator, a condenser, a throttling element, etc. For example, when used for vehicle air conditioning, it may also include at least one of an in-vehicle condenser, an in-vehicle evaporator, an external condenser, an external evaporator, a throttling component, etc., which will not be elaborated here.

[0130] Hereinafter, a vehicle 1000 according to a fourth aspect embodiment of the present invention will be described with reference to the accompanying drawings.

[0131] like Figures 2-7As shown, vehicle 1000 may include vehicle body 200 and air conditioning system 300 mounted on vehicle body 200. Air conditioning system 300 includes an air conditioning system 300 according to any embodiment of the third aspect of the present invention. Since the exhaust noise and pulsation of the electric compressor 100 included in the air conditioning system 300 according to any embodiment of the third aspect of the present invention can be improved, when the air conditioning system 300 is used in vehicle 1000, the resonance problem of various components in the thermal management system of vehicle 1000 caused by the exhaust airflow noise and pressure pulsation of electric compressor 100 can be improved, thereby reducing the noise and vibration caused to vehicle 1000. Optionally, electric compressor 100 is used to compress at least one refrigerant selected from R134a, R744, R290 and R1234yf, thereby meeting the requirements for vehicle use.

[0132] It should be noted that the specific type of vehicle 1000 according to the embodiments of the present invention is not limited. For example, it can be a new energy vehicle, which may include pure electric vehicles, hybrid vehicles, etc., which will not be elaborated here. In addition, once the type of vehicle 1000 is specifically determined, those skilled in the art will know the other components of vehicle 1000, which will not be elaborated here.

[0133] Below, in conjunction with the appendix Figure 2 The high-pressure housing 1 of an electric compressor for a vehicle 1000 is described in some specific embodiments of the present invention.

[0134] Example 1

[0135] like Figure 2 As shown, a high-pressure chamber 11 and a refrigerant outlet 12 are formed on the high-pressure housing 1. The high-pressure chamber 11 is located in the lower region of the high-pressure housing 1, and the refrigerant outlet 12 is located in the upper region of the high-pressure housing 1. A resonant chamber 13 and an oil separator 15 are also formed on the high-pressure housing 1. The high-pressure chamber 11 is located between the resonant chamber 13 and the oil separator 15. The resonant cavity 13 is formed on the left side of the high-pressure housing 1 and extends obliquely from the lower left to the upper right along the high-pressure housing 1. At the same time, the oil separator 15 is formed on the right side of the high-pressure housing 1 and extends obliquely from the lower right to the upper left along the high-pressure housing 1. The outer peripheral wall of the oil separator 15 is provided with an oil separator inlet 151, which connects the high-pressure housing 11 and the oil separator 15. An oil separator outlet 152 is provided at the upper end of the oil separator 15, which connects the oil separator 15 to the upper end of the resonant cavity 13. A connecting channel 14 is provided at the upper end of the resonant cavity 13, which connects the resonant cavity 13 to the refrigerant outlet 12.

[0136] Among them, such as Figure 3As shown, the lower end of the resonant cavity 13 is open, forming a first opening 131. The first opening 131 is located at the lower left of the high-pressure housing 1 and is used for machining the resonant cavity 13. A first end cap 21 is provided at the first opening 131 to close the lower end of the resonant cavity 13. A silencing tube 4 is provided inside the resonant cavity 13. The upper end of the silencing tube 4 extends into the connecting channel 14 and is fixedly connected to the inner wall of the connecting channel 14, such as by interference fit. At the same time, the lower end of the silencing tube 4 extends to a position close to the first end cap 21. The outer peripheral wall of the end of the silencing tube 4 is spaced apart from the inner peripheral wall of the resonant cavity 13, and the end face of the lower end of the silencing tube 4 is in clearance fit with the end face of the first end cap 21. The first end cap 21 includes a pressing part 211 and a connecting part 212. The pressing part 211 forms a limiting surface at the position where it is connected to the connecting part 212. The connecting part 212 is interference-fitted with the inner peripheral wall of the first opening 131. The limiting surface of the pressing part 211 is in a pressing fit with the first machined end face.

[0137] A second oil return channel 153 is provided in the oil separator chamber 15, which connects the oil separator chamber 15 with the space where the compression component 20 is located, so that the oil deposited in the second oil return channel 153 can return to the space where the compression component 20 is located. At the same time, the lower end of the oil separator chamber 15 is open, forming a second opening 154. The second opening 154 is located at the lower right of the high-pressure housing 1 and is used to process the oil separator chamber 15. A second end cap 22 is provided at the second opening 154 to close the lower end of the oil separator chamber 15. The second end cap 22 has the same structure as the first end cap 21.

[0138] Example 2

[0139] like Figure 4 As shown, the difference between this embodiment 2 and the above embodiment 1 includes: the end face of the first end cap 21 facing the resonant cavity 13 is provided with a mounting groove 213, the inner diameter of the mounting groove 213 is larger than the outer diameter of the silencer tube 4, and the lower end of the silencer tube 4 extends into the mounting groove 213, and the lower end of the silencer tube 4 is in clearance fit with the inner peripheral wall of the mounting groove 213.

[0140] Example 3

[0141] like Figure 5 As shown, the differences between this embodiment three and the above embodiment two include: the upper end of the silencing tube 4 is a mating end and the lower end is a fixed end; the upper end of the silencing tube 4 is located in the upper space of the resonant cavity 13, that is, the upper end of the silencing tube 4 does not extend into the connecting channel 14, and the upper end of the silencing tube 4 is clearance-fitted with the upper end face of the resonant cavity 13; and the lower end of the silencing tube 4 extends into the mounting groove 213, and the outer peripheral wall of the lower end of the silencing tube 4 is interference-fitted with the inner peripheral wall of the mounting groove 213.

[0142] Example 4

[0143] like Figure 6 As shown, the differences between this embodiment four and the above embodiment three include: the upper end of the silencing tube 4 is a fixed end and the lower end is a mating end; the upper end of the silencing tube 4 extends into the connecting channel 14, and the outer peripheral wall of the upper end of the silencing tube 4 is in clearance fit with the inner peripheral wall of the connecting channel 14; the lower end of the silencing tube 4 extends into the mounting groove 213, and the outer peripheral wall of the lower end of the silencing tube 4 is in clearance fit with the inner peripheral wall of the mounting groove 213.

[0144] Example 5

[0145] like Figure 7 As shown, the differences between this fifth embodiment and the fourth embodiment mentioned above include: the upper end of the resonant cavity 13 is directly connected to the refrigerant outlet 12, i.e., no connecting channel 14 is provided. Furthermore, the upper end of the silencer tube 4 is configured as a mating end, and the lower end as a fixed end. The outer diameter of the upper right end of the silencer tube 4 is larger than the outer diameter of the lower left end, and it includes a thin tube section 42, a transition section 43, and a thick tube section 44 connected sequentially from the lower left to the upper right. The end of the thin tube section 42 facing away from the transition section 43 forms a mating end. The lower end of the thin tube section 42 is clearance-fitted with the inner wall surface of the high-pressure housing 1, while the upper end of the thick tube section 44 is fixedly fitted with the upper inner wall surface of the resonant cavity 13.

[0146] Example 6

[0147] like ​ As shown, the differences between this sixth embodiment and the third embodiment mentioned above include: the outer diameter of the lower left end of the silencing tube 4 is larger than the outer diameter of the upper right end, that is, the lower left end of the silencing tube 4 is constructed as a fixed end. The thin tube section 42, the transition section 43, and the thick tube section 44 are connected sequentially from the upper right to the lower left to form a complete silencing tube 4. The end of the thick tube section 44 facing away from the transition section 43 is formed as a fixed end, and the end of the thin tube section 42 facing away from the transition section 43 is formed as a mating end. The upper end of the thin tube section 42 is clearance-fitted with the upper end face of the resonant cavity 13. At the same time, the outer peripheral wall of the lower end of the thick tube section 44 is fixedly fitted with the inner wall surface of the lower end of the resonant cavity 13. In addition, a first oil return channel 132 is provided in the bottom space of the resonant cavity 13. The first oil return channel 132 is used to return the oil in the resonant cavity 13 to the space where the compression component 20 is located, so as to realize recycling.

[0148] In the description of the application, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only used to facilitate the description of the application and simplify the description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the application.

[0149] In the description of the application, "first feature" and "second feature" can include one or more of the features.

[0150] In the description of the application, "a plurality of" means two or more.

[0151] In the description of the application, "above" or "below" the first feature of the second feature can include that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact through another feature between them.

[0152] In the description of the application, "above", "over" and "on" the first feature of the second feature includes that the first feature is directly above and obliquely above the second feature, or only means that the first feature is higher than the second feature in height.

[0153] In the description of the application, the description of the terms "one embodiment", "some embodiments", "illustrative embodiment", "example", "specific example", or "some examples" and the like means that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the application. In this specification, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0154] Although embodiments of the application have been shown and described, those skilled in the art can understand that various changes, modifications, replacements and variations can be made to the embodiments without departing from the principles and spirit of the application, and the scope of the application is defined by the claims and their equivalents.

Claims

1. A high-pressure housing assembly for an electric compressor, characterized in that, include: A high-pressure housing (1) is provided, on which a high-pressure chamber (11) and a refrigerant outlet (12) are formed. The compression component (20) of the electric compressor (100) is adapted to discharge compressed refrigerant into the high-pressure chamber (11), and the refrigerant outlet (12) is used to discharge refrigerant out of the high-pressure housing (1). The high-pressure housing (1) is also formed with a resonant cavity (13) and an oil separator (15) that are interconnected. The oil separator (15) is connected to the high-pressure cavity (11) to receive the refrigerant flowing out of the high-pressure cavity (11). The resonant cavity (13) is provided with a silencer tube (4). The silencer tube (4) and the inner wall of the resonant cavity (13) define a flow channel. One end of the tube cavity in the silencer tube (4) is connected to the refrigerant outlet (12). The silencer tube (4) is provided with a silencer hole (41) that connects the tube cavity and the flow channel. The high-pressure housing (1) is configured such that the refrigerant entering the flow channel from the oil separator (15) is discharged into the tube cavity through the silencer hole (41). Multiple rings of the silencing holes (41) are provided along the axial direction of the silencing tube (4), and each ring of the silencing holes (41) includes multiple silencing holes (41) arranged circumferentially along the silencing tube (4); The center distance t between adjacent silencing holes (41) satisfies: d≤t≤5d; Wherein, d is the equivalent diameter of the cross-section of the silencing hole (41), and the cross-sections of the multiple silencing holes (41) are different, with d being the equivalent diameter of the silencing hole (41) with the largest cross-section; The cross-section of the silencing hole (41) satisfies: 0.05D≤d≤D; where d is the equivalent diameter of the cross-section of the silencing hole (41), D is the equivalent diameter of the cross-section of the silencing tube (4), the silencing tube (4) is a variable cross-section structure, and D is the equivalent diameter of the minimum cross-section of the silencing tube (4).

2. The high-pressure housing assembly for an electric compressor according to claim 1, characterized in that, One of the first end and the second end of the silencer cannula (4) is set as a fixed end and is used for connecting and fixing the silencer cannula (4); The other of the first and second ends of the silencing cannula (4) is configured as a mating end, which is suspended in the air.

3. The high-pressure housing assembly for an electric compressor according to claim 2, characterized in that, The installation dimensions of the mating end of the silencing cannula (4) satisfy: 0≤T≤0.2D; where T is the suspension height of the mating end and D is the minimum inner diameter of the silencing cannula (4).

4. The high-pressure housing assembly for an electric compressor according to claim 2, characterized in that, The silencing cannula (4) is a straight tube with a variable cross-section, and the outer diameter of the fixed end of the silencing cannula (4) is larger than the outer diameter of the mating end of the silencing cannula (4).

5. The high-pressure housing assembly for an electric compressor according to claim 1, characterized in that, The high-pressure housing (1) has a first opening (131) formed on its surface for processing the resonant cavity (13), and the high-pressure housing (1) includes a first end cap (21) covering the first opening (131).

6. The high-pressure housing assembly for an electric compressor according to claim 5, characterized in that, The first end of the resonant cavity (13) has the first opening (131), and the second end of the resonant cavity (13) is connected to the refrigerant outlet (12) through the connecting channel (14). The flow area of ​​the connecting channel (14) is smaller than the flow area of ​​the resonant cavity (13). The silencer tube (4) is fixed to the resonant cavity (13) or the inner wall of the connecting channel (14).

7. The high-pressure housing assembly for an electric compressor according to claim 6, characterized in that, The centerline of the connecting channel (14) coincides with the centerline of the resonant cavity (13), and both the connecting channel (14) and the resonant cavity (13) are suitable for processing and forming through the first opening (131).

8. The high-pressure housing assembly for an electric compressor according to claim 5, characterized in that, The first end cap (21) is provided with a mounting groove (213) that opens toward the resonant cavity (13); wherein, The first end of the silencing tube (4) is fixedly connected to the inner peripheral wall of the mounting groove (213), or the first end of the silencing tube (4) is clearance-fitted with the inner peripheral wall of the mounting groove (213).

9. The high-pressure housing assembly for an electric compressor according to claim 1, characterized in that, The resonant cavity (13) is also provided with a first oil return channel (132) in the bottom space in the direction of gravity.

10. The high-pressure housing assembly for an electric compressor according to claim 9, characterized in that, The position of the first oil return channel (132) in the resonant cavity (13) satisfies: h≤0.3H; where h is the vertical distance between the highest point of the first oil return channel (132) and the lowest point of the resonant cavity (13) in the direction of gravity, and H is the vertical distance between the highest point and the lowest point of the resonant cavity (13) in the direction of gravity.

11. The high-pressure housing assembly for an electric compressor according to claim 1, characterized in that, The oil separator (15) is provided with an oil separator (3) for oil-gas separation. The refrigerant entering the oil separator (15) flows to the resonant cavity (13) after being separated by the oil separator (3).

12. An electric compressor (100), characterized in that, include: A housing component, the housing component comprising a high-pressure housing assembly for an electric compressor according to any one of claims 1-11; A compression component (20) has an exhaust port (201) connected to the high-pressure chamber (11) to discharge compressed refrigerant into the high-pressure chamber (11); The motor component (30) includes a motor body (301) and a drive shaft (302). The motor body (301) drives the compression component (20) to perform compression work through the drive shaft (302).

13. The electric compressor (100) according to claim 12, characterized in that, The housing component also includes: A partition plate (103) is provided, the compression component (20) and the motor body (301) are respectively placed on both sides of the partition plate (103), and the drive shaft (302) passes through the partition plate (103) to connect with the compression component (20); A low-pressure housing (102) is formed between the low-pressure housing (102) and the middle partition (103) to form a low-pressure cavity (105) for accommodating the motor body (301). A refrigerant inlet (1021) communicating with the low-pressure cavity (105) is formed on the low-pressure housing (102). The compression component (20) draws in refrigerant from the low-pressure cavity (105).

14. An air conditioning system (300), characterized in that, Includes the electric compressor (100) according to any one of claims 12-13.

15. A vehicle (1000), characterized in that, Includes the air conditioning system (300) according to claim 14.

Images