CN116988975A

CN116988975A - High-pressure housing assembly, electric compressor, air conditioning system and vehicle

Info

Publication number: CN116988975A
Application number: CN202210451643.2A
Authority: CN
Inventors: 马宇山
Original assignee: Guangdong Welling Auto Parts Co Ltd; Anhui Welling Auto Parts Co Ltd
Current assignee: Guangdong Welling Auto Parts Co Ltd; Anhui Welling Auto Parts Co Ltd
Priority date: 2022-04-26
Filing date: 2022-04-26
Publication date: 2023-11-03

Abstract

The invention discloses a high-pressure shell component for an electric compressor, the electric compressor, an air conditioning system and a vehicle, wherein the high-pressure shell component comprises: the compression part of the electric compressor is suitable for discharging compressed refrigerant to the high-pressure cavity, and the refrigerant discharge port is used for discharging the refrigerant to the outside of the high-pressure shell; the high-pressure shell is also provided with a resonant cavity and an oil cavity which are mutually communicated, the oil cavity is communicated with the high-pressure cavity to receive the refrigerant flowing out of the high-pressure cavity, a silencing insertion pipe is arranged in the resonant cavity, a circulating channel is defined between the silencing insertion pipe and the inner wall surface of the resonant cavity, one end of a pipe cavity in the silencing insertion pipe is communicated with a refrigerant outlet, and a silencing hole which is used for communicating the pipe cavity with the circulating channel is formed in the silencing insertion pipe. The high-pressure shell component for the electric compressor can eliminate noise and pressure pulsation accompanying the gaseous refrigerant and has good silencing effect.

Description

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

Technical Field

The invention 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

The electric compressor is a core component of the refrigeration equipment for the vehicle, and the electric compressor can generate vibration noise when working, so that the vehicle noise is influenced and the subjective hearing problem is generated. In the related art, after a high-pressure refrigerant discharged from a compression component of an electric compressor enters a high-pressure cavity, the high-pressure refrigerant directly leaves the compressor through a refrigerant discharge port, and along with exhaust airflow noise and pressure pulsation generated during operation of the electric compressor, resonance of each component in a thermal management system on a vehicle is easily excited, so that the problems of vehicle noise and vibration are caused.

Disclosure of Invention

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

The invention also provides an electric compressor with the high-pressure shell assembly.

The invention also provides an air conditioning system with the electric compressor.

The invention further provides a vehicle with the air conditioning system.

A high pressure housing assembly for an electric compressor according to an embodiment of the present invention includes: the compression part of the electric compressor is suitable for discharging compressed refrigerant to the high-pressure cavity, and the refrigerant discharge port is used for discharging the refrigerant to the outside of the high-pressure shell; the high-pressure shell is further provided with a resonant cavity and an oil cavity which are mutually communicated, the oil cavity is communicated with the high-pressure cavity to receive the refrigerant flowing out of the high-pressure cavity, a silencing insertion pipe is arranged in the resonant cavity, a circulation channel is defined between the silencing insertion pipe and the inner wall surface of the resonant cavity, one end of a pipe cavity in the silencing insertion pipe is communicated with the refrigerant outlet, the silencing insertion pipe is provided with a silencing hole communicated with the circulation channel, and the high-pressure shell is configured to enable the refrigerant entering the circulation channel from the oil cavity to be discharged into the pipe cavity through the silencing hole.

According to the high-pressure shell assembly for the electric compressor, the resonant cavity is formed in the high-pressure shell, the circulating channel between the resonant cavity and the silencing insertion pipe is communicated with the oil cavity, the circulating channel is communicated with the pipe cavity of the silencing insertion pipe through the silencing hole, and the pipe cavity of the silencing insertion pipe is communicated with the refrigerant discharge port, so that a cavity structure meeting the Helmholtz resonance principle can be formed, the resonant cavity can eliminate noise generated by the refrigerant acting on the high-pressure shell, noise and pressure pulsation caused by the gaseous refrigerant can be eliminated, and the silencing effect in the resonant cavity is greatly improved by the arrangement of the silencing insertion pipe, so that air flow noise and pulsation on the exhaust side of the electric compressor are improved, noise and pulsation of the refrigerant discharged by the electric compressor are improved, resonance problems of various parts in a vehicle thermal management system are relieved or eliminated, and safety of the electric compressor is improved.

In some embodiments, one of the first end and the second end of the sound attenuating cannula is provided as a fixed end and is used for connection fixation of the sound attenuating cannula; the other of the first end and the second end of the silencing cannula is set to be a matching end, and the matching end is suspended.

In some embodiments, the mating end of the sound attenuating cannula is sized to: t is more than or equal to 0 and less than or equal to 0.2D; wherein T is the suspension height of the matched end, and D is the minimum inner diameter of the silencing cannula.

In some embodiments, the sound attenuating cannula is a variable cross-section straight tube and the outer diameter of the fixed end of the sound attenuating cannula is greater than the outer diameter of the mating end of the sound attenuating cannula.

In some embodiments, a first opening formed for machining the resonant cavity is formed on a surface of the high pressure housing, and the high pressure housing includes a first end cap covering the first opening.

In some embodiments, the first opening is formed at a first end of the resonant cavity, the second end of the resonant cavity is communicated with the refrigerant discharge port through a connecting channel, the overflow area of the connecting channel is smaller than that of the resonant cavity, and the silencing insertion tube is fixed in the resonant cavity or the inner wall of the connecting channel.

In some embodiments, a centerline of the connecting channel coincides with a centerline of the resonant cavity, and both the connecting channel and the resonant cavity are adapted to be machined through the first opening.

In some embodiments, the first end cap is provided with a mounting recess that opens into the resonant cavity; the first end of the silencing insertion tube is fixedly connected with the inner peripheral wall of the mounting groove, or is in clearance fit with the inner peripheral wall of the mounting groove.

In some embodiments, a plurality of turns of the sound deadening holes are provided along an axial direction of the sound deadening cannula, each turn of the sound deadening holes including a plurality of the sound deadening holes provided at intervals along a circumferential direction of the sound deadening cannula.

In some embodiments, the center-to-center distance t between adjacent ones of the sound attenuation holes satisfies: d is more than or equal to t and less than or equal to 5d; wherein d is the equivalent diameter of the hole section of the sound-deadening hole, and d is the equivalent diameter of the sound-deadening hole with the largest hole section when the hole sections of the plurality of sound-deadening holes are different in size.

In some embodiments, the sound deadening holes have a hole cross section that satisfies: d is more than or equal to 0.05 and less than or equal to D; wherein D is the equivalent diameter of the hole section of the silencing hole, D is the equivalent diameter of the cross section of the silencing cannula, and D is the equivalent diameter of the minimum cross section of the silencing cannula when the silencing cannula is of a variable cross section structure.

In some embodiments, the bottom space of the resonant cavity in the gravity direction is further provided with a first oil return channel.

In some embodiments, the position of the first oil return passage within the resonant cavity satisfies: h is less than or equal to 0.3H; and H is the vertical distance between the highest point of the first oil return channel and the lowest point of the resonant cavity in the gravity direction, and H is the vertical distance between the highest point and the lowest point of the resonant cavity in the gravity direction.

In some embodiments, an oil component for oil-gas separation is arranged in the oil component cavity, and the refrigerant entering the oil component cavity flows to the resonance cavity after oil-gas separation of the oil component.

An electric compressor according to an embodiment of a second aspect of the present invention includes: a housing component comprising the high pressure housing assembly for an electric compressor of any of the embodiments described above; the exhaust port of the compression part is communicated with the high-pressure cavity so as to discharge compressed refrigerant to the high-pressure cavity; and the motor component comprises a motor body and a driving shaft, and the motor body drives the compression component to execute compression work through the driving shaft.

In some embodiments, the housing component further comprises: the middle partition plate, the compression part and the motor body are respectively arranged at two sides of the middle partition plate, and the driving shaft penetrates through the middle partition plate to be connected with the compression part; the low-pressure shell is provided with a refrigerant suction inlet communicated with the low-pressure cavity, and the compression part sucks refrigerant from the low-pressure cavity.

An air conditioning system according to an embodiment of the third aspect of the present invention includes an electric compressor according to an embodiment of the second aspect of the present invention.

A vehicle according to an embodiment of a fourth aspect of the present invention includes a vehicle body and an air conditioning system mounted on the vehicle body, the air conditioning system being an air conditioning system according to an embodiment of a third aspect of the present invention.

The vehicle, the air conditioning system, the electric compressor and the high-pressure housing assembly for the electric compressor described above have the same advantages over the prior art, and are not described in detail herein.

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.

Drawings

The foregoing and/or additional aspects and advantages of the invention will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

fig. 1 is a schematic view of a structure of an electric compressor according to an embodiment of the present invention;

fig. 2 is a schematic structural view of a high-pressure casing according to a first embodiment of the present invention;

fig. 3 is a schematic structural view of a high-pressure casing according to a second embodiment of the present invention;

fig. 4 is a schematic structural view of a high-pressure casing according to a third embodiment of the present invention;

Fig. 5 is a schematic structural view of a high-pressure casing according to a fourth embodiment of the present invention;

fig. 6 is a schematic structural view of a high-pressure casing according to a fifth embodiment of the present invention;

fig. 7 is a schematic view of a structure of a high-pressure casing according to a sixth embodiment of the present invention;

FIG. 8 is an enlarged view of a portion of the fixed end of the sound deadening cannula according to the second and third embodiments of the present invention;

FIG. 9 is an enlarged partial view of the mating end of a sound attenuating cannula in accordance with a sixth embodiment of the invention;

FIG. 10 is an enlarged view of a portion of a mating end of a sound attenuating cannula in accordance with a third embodiment of the invention;

FIG. 11 is an enlarged view of a portion of a mating end of a sound attenuating cannula in accordance with a fourth embodiment of the invention;

fig. 12 is a schematic structural view of a vehicle according to an embodiment of the present invention.

Reference numerals:

an electric compressor 100;

a high-pressure housing 1;

a high pressure chamber 11; a refrigerant discharge port 12;

a resonant cavity 13; a first opening 131; a first oil return passage 132;

a connecting channel 14;

an oil chamber 15; an oil inlet 151 and an oil outlet 152; a second oil return passage 153; a second opening 154;

a first end cap 21; a pressing portion 211; a connection portion 212; a mounting groove 213; a second end cap 22;

an oil component 3; a sound deadening cannula 4; a sound deadening hole 41; a thin tube section 42; a transition section 43; a thick pipe section 44;

A low pressure housing 102; a refrigerant suction port 1021; a middle separator 103; a cover plate 104; a low pressure chamber 105;

a compression member 20; an exhaust port 201;

a motor part 30; a motor body 301; a drive shaft 302;

an electric control part 40;

a vehicle body 200; an air conditioning system 300; vehicle 1000.

Detailed Description

Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the invention.

A high-pressure housing assembly for an electric compressor according to an embodiment of the present invention, which can greatly improve exhaust noise and pressure pulsation of the electric compressor 100 by providing the resonance chamber 13 and the oil chamber 15, and enhance user experience, will be described with reference to fig. 1 to 11.

As shown in fig. 1 to 7, the high-pressure housing assembly includes a high-pressure housing 1, a high-pressure chamber 11 and a refrigerant discharge port 12 are formed in the high-pressure housing 1, a compression member 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 discharge port 12. Thus, when the motor-driven compressor 100 is powered on and normally operates, the low-pressure refrigerant is sucked in, compressed by the compression member 20 to form a high-pressure refrigerant, and the high-pressure refrigerant is discharged into the high-pressure chamber 11 through the exhaust port 201 of the compression member 20 and finally discharged out of the high-pressure casing 1 through the refrigerant discharge port 12.

The high-pressure housing 1 is further formed with a resonance chamber 13 and an oil chamber 15, the resonance chamber 13 and the oil chamber 15 are communicated with each other, the oil chamber 15 is communicated with the high-pressure chamber 11 to receive the refrigerant flowing out of the high-pressure chamber 11, and the resonance chamber 13 is communicated with the refrigerant discharge port 12. In this way, when the motor-driven compressor 100 is actually operated, the high-pressure refrigerant in the high-pressure chamber 11 enters the oil chamber 15 from the oil inlet 151, and after oil-gas separation in the oil chamber 15, the gaseous refrigerant enters the resonance chamber 13 from the oil outlet 152, passes through the structure in the resonance chamber 13, and then flows out from the refrigerant discharge port 12, thereby realizing discharge of the refrigerant.

Wherein, as shown in fig. 2-7, a silencing cannula 4 is arranged in the resonant cavity 13, a circulation channel is defined between the silencing cannula 4 and the inner wall of the resonant cavity 13, that is, the outer diameter of the silencing cannula 4 is smaller than the inner diameter of the resonant cavity 13, so that after the silencing cannula 4 is positioned in the resonant cavity 13, a circulation channel is defined between at least part of the peripheral wall of the silencing cannula 4 and the inner wall of the resonant cavity 13. And one end of the pipe cavity in the silencing insertion pipe 4 is communicated with the refrigerant discharge port 12, the silencing insertion pipe 4 is provided with a silencing hole 41 for communicating the pipe cavity with the circulation channel, and the refrigerant entering the circulation channel from the oil cavity 15 of the high-pressure shell 1 is discharged into the pipe cavity through the silencing hole 41.

In practical design, one end of the pipe cavity in the silencing insertion pipe 4, namely one end close to the refrigerant discharge port 12, can be set as an open end, so that the open end is communicated with the refrigerant discharge port 12; meanwhile, the other end of the pipe cavity in the silencing insertion pipe 4, such as one end deviating from the refrigerant discharge port 12, is set as a closed end, and the closed end is suspended and extends into the resonant cavity 13, so that the pipe cavity in the silencing insertion pipe 4 is communicated with the circulation channel through the silencing hole 41. Alternatively, one end of the lumen in the muffler pipe 4, that is, one end near the refrigerant discharge port 12 may be set as an open end so that the open end communicates with the refrigerant discharge port 12; meanwhile, the other end of the pipe cavity in the silencing insertion pipe 4 is also set as an open end, such as one end deviating from the refrigerant discharge port 12, and the outer peripheral wall of the silencing insertion pipe 4 at the open end is in interference fit with the inner wall of the resonant cavity 13, so that the pipe cavity in the silencing insertion pipe 4 is communicated with the circulation channel through the silencing hole 41, and of course, when in specific design, the outer peripheral wall of the silencing insertion pipe 4 at the open end can be in clearance fit with the inner wall of the resonant cavity 13 as shown in fig. 10 so as to be convenient for installation, and the clearance is small without obvious refrigerant circulation, so that the pipe cavity in the silencing insertion pipe 4 is mainly communicated with the circulation channel through the silencing hole 41.

That is, in the present invention, the gaseous refrigerant separated in the oil chamber 15 can enter the resonance chamber 13 from the oil outlet 152, circulate before the circulation passage after entering the resonance chamber 13, enter the pipe chamber of the muffler pipe 4 from the muffler hole 41 of the muffler pipe 4 after circulating for a certain stroke, and flow in the pipe chamber to one end of the pipe chamber in the axial direction to be discharged from the refrigerant discharge port 12. By arranging the resonant cavity 13, the resonant cavity 13 forms a cavity structure in the high-pressure housing 1 of the electric compressor, which meets the helmholtz resonance principle, and the resonant cavity 13 is communicated with the oil cavity 15 and the refrigerant discharge port 12, so that noise generated in the process of discharging the separated gaseous refrigerant in the oil cavity 15 to the refrigerant discharge port 12 can be eliminated or weakened in the resonant cavity 13, thereby improving air flow noise and pulsation on the exhaust side of the electric compressor 100, and further improving noise and pulsation of the refrigerant discharged by the electric compressor 100. And set up amortization intubate 4 in resonant cavity 13, can make amortization intubate 4 separate the cavity structure that resonant cavity 13 formed into the circulation passageway that is located between the outer peripheral wall of amortization intubate 4 and the inner wall of resonant cavity 13 and the lumen that is located amortization intubate 4, increased the quantity of the amortization cavity in resonant cavity 13 through setting up amortization intubate 4 promptly to do benefit to the amortization effect in the multiplication resonant cavity 13.

In other words, after the gaseous refrigerant enters the resonance chamber 13 from the oil outlet 152, the vibration noise and pressure pulsation accompanying the gaseous refrigerant can be eliminated once in the circulation passage, that is, under the reflection of the outer peripheral wall of the muffler pipe 4 and the inner wall of the resonance chamber 13, and the vibration noise and pressure pulsation accompanying the gaseous refrigerant entering the muffler pipe 4 from the muffler hole 41 can be eliminated again under the reflection of the inner wall of the pipe chamber of the muffler pipe 4, thereby greatly improving the effect of eliminating noise and pulsation in the resonance chamber 13 by providing the muffler pipe 4. Thus, when the motor-driven compressor 100 is used in the vehicle 1000, resonance problems of various components in the thermal management system of the vehicle 1000 due to exhaust gas flow noise and pressure pulsation of the motor-driven compressor 100 can be improved, and noise and vibration caused to the vehicle 1000 can be improved.

It should be noted that the "helmholtz resonance principle" is well known to those skilled in the art, and the present application proposes that "a resonant cavity 13 may be provided on the high pressure housing 1, and a flow channel between the resonant cavity 13 and the silencing cannula 4 is communicated with the oil cavity 15, and the flow channel is communicated with a lumen of the silencing cannula 4 through the silencing hole 41, so that a cavity structure satisfying the helmholtz resonance principle may be formed.

According to the high-pressure shell assembly for the electric compressor in the embodiment of the invention, by arranging the resonant cavity 13 on the high-pressure shell 1, communicating the communication channel between the resonant cavity 13 and the silencing insert pipe 4 with the oil cavity 15, communicating the communication channel with the pipe cavity of the silencing insert pipe 4 through the silencing hole 41, and communicating the pipe cavity of the silencing insert pipe 4 with the refrigerant discharge port 12, a cavity structure meeting the Helmholtz resonance principle can be formed, so that the resonant cavity 13 can eliminate noise generated by the refrigerant acting on the high-pressure shell 1, and can eliminate noise and pressure pulsation accompanying the gaseous refrigerant, and by arranging the silencing insert pipe 4, the silencing effect in the resonant cavity 13 is greatly improved, thereby improving the airflow noise and pulsation of the refrigerant discharged by the electric compressor 100, further improving the noise and pulsation of the refrigerant discharged by 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.

In some embodiments, one of the first end and the second end of the sound-deadening cannula 4 is provided as a fixed end, and the fixed end is used for connection fixation of the sound-deadening cannula 4, i.e. the sound-deadening cannula 4 is fixedly mounted in the high-pressure casing 1 through the fixed end, while the other of the first end and the second end of the sound-deadening cannula 4 is provided as a mating end, which is suspended in the high-pressure casing 1. As shown in fig. 2 to 7, the resonant cavity 13 extends obliquely from bottom left to top right in the high-pressure housing 1, the extending direction of the silencing cannula 4 is the same as that of the resonant cavity 13, the bottom left end of the silencing cannula 4 may be set as a fixed end, the top right end may be set as a mating end, or the top right end of the silencing cannula 4 may be set as a fixed end, and the bottom left end may be set as a mating end; as shown in fig. 2-3, the left lower end of the silencing cannula 4 is suspended in the high-pressure shell 1, and the right upper end of the silencing cannula 4 is fixed in the high-pressure shell 1; or as shown in fig. 4-7, the left lower end of the silencing cannula 4 is fixed in the high-pressure shell 1, and the right upper end of the silencing cannula 4 is suspended in the high-pressure shell 1, so that the silencing cannula 4 can be installed and fixed in the resonant cavity 13.

It should be noted that, the fixed end of the silencing cannula 4 is fixedly installed in the high-pressure housing 1, and can be matched with the high-pressure housing 1 in an interference fit manner, or in a welding fit manner, or in a threaded connection manner.

Therefore, one end of the silencing cannula 4 is fixed in the high-pressure shell 1, the other end of the silencing cannula is suspended, one end of the silencing cannula 4 can be fixed in the actual installation, the other end of the silencing cannula does not need to consider the problems of fixed sealing and installation precision, the installation requirement of the silencing cannula 4 in the resonant cavity 13 is greatly reduced, the installation rejection rate is reduced, and the installation cost is reduced. And facilitates quick disassembly when the sound-absorbing cannula 4 is removed and replaced.

In some embodiments, the mating end of the sound attenuating cannula 4 is sized to: t is more than or equal to 0 and less than or equal to 0.2D; wherein T is the flying height of the mating end, i.e., the distance of T between the location of the mating end of the sound-deadening cannula 4 closest to the inner wall surface of the high-pressure housing 1 within the high-pressure housing 1, as shown in fig. 9, the interval between the end surface of the mating end of the sound-deadening cannula 4 and the upper end surface of the resonance chamber 13 is T, as shown in fig. 9, or the lower end of the resonance chamber 13 is provided with the first end cap 21, the interval between the outer peripheral wall of the mating end of the sound-deadening cannula 4 and the first end cap 21 is T, and, as shown in fig. 10, the interval between the upper end of the resonance chamber 13 and the inner peripheral wall of the connection passage 14 is T, as shown in fig. 11, communicating between the upper end of the resonance chamber 13 and the refrigerant discharge port 12 through the connection passage 14.

As shown in fig. 8, D is the minimum inner diameter of the silencer cannula 4, wherein the silencer cannula 4 in the present invention may be provided as a constant cross-section tube or a variable cross-section tube, for example, when the silencer cannula 4 is a constant cross-section tube, D is the inner diameter of the silencer cannula 4, and when the silencer cannula 4 is a variable cross-section tube, D is the inner diameter at the smallest position among the inner diameters at different positions of the silencer cannula 4.

That is, in the present invention, the ratio between the space between the mating end of the silencer cannula 4 and the inner wall surface of the high-pressure casing 1 and the minimum inner diameter of the silencer cannula 4 is greater than 0 and equal to or less than 0.2, such as the ratio of 0.1 and 0.15, i.e., the ratio of the two is in a smaller range, thereby not only ensuring that the mating end of the silencer cannula 4 can be reasonably and rapidly installed in the high-pressure casing 1 and being convenient for installation, but also the space between the mating end of the silencer cannula 4 and the inner wall surface of the high-pressure casing 1 is not excessively large, reducing the opening amount of the resonant cavity 13 and ensuring the silencing effectiveness in the resonant cavity 13 on the premise of effective exhaust.

In some embodiments, the sound attenuating cannula 4 is a variable cross-section straight tube, i.e., the cross-sectional areas at least two locations of the sound attenuating cannula 4 are different, and the outer diameter of the fixed end of the sound attenuating cannula 4 is greater than the outer diameter of the mating end of the sound attenuating cannula 4. As in practical design, the silencer cannula 4 is constructed to include a thin pipe section 42 with a large length and a thick pipe section 44 with a small length and a transition section 43 connected between the thin pipe section 42 and the thick pipe section 44, i.e., the silencer cannula 4 includes the thin pipe section 42, the transition section 43 and the thick pipe section 44 connected in sequence in the length direction, the outer diameters of the three are increased in sequence, and the transition section 43 is constructed to gradually increase from the outer diameter of the end connected with the thin pipe section 42 to the outer diameter of the end connected with the thick pipe section 44, so that an inclined transition structure is formed, and the connection between the thin pipe section 42 and the thick pipe section 44 is relatively gentle.

As shown in fig. 6, the outer diameter of the right upper end of the sound-deadening cannula 4 is larger than the outer diameter of the left lower end, that is, the right upper end of the sound-deadening cannula 4 is configured as a fixed end, the thin pipe section 42, the transition section 43 and the thick pipe section 44 are sequentially connected from bottom left to top right to form the complete sound-deadening cannula 4, one end of the thick pipe section 44, which is away from the transition section 43, is formed as a fixed end, one end of the thin pipe section 42, which is away from the transition section 43, is formed as a matched end, the lower end of the thin pipe section 42 is in clearance fit with the inner wall surface of the high-pressure casing 1, and meanwhile, the upper end of the thick pipe section 44 is in fixed fit with the inner wall surface of the high-pressure casing 1. Or as shown in fig. 7, the outer diameter of the left lower end of the silencing insert tube 4 is larger than the outer diameter of the right upper end, namely, the left lower end of the silencing insert tube 4 is configured as a fixed end, the thin pipe section 42, the transition section 43 and the thick pipe section 44 are sequentially connected from the right upper end to the left lower end to form the complete silencing insert tube 4, one end of the thick pipe section 44, which is away from the transition section 43, is formed as a fixed end, one end of the thin pipe section 42, which is away from the transition section 43, is formed as a matched end, and the upper end of the thin pipe section 42 is in clearance fit with the inner wall surface of the high-pressure shell 1, and meanwhile, the lower end of the thick pipe section 44 is in fixed fit with the inner wall surface of the high-pressure shell 1.

In some embodiments, as shown in fig. 2-7, a first opening 131 is formed on the surface of the high-pressure housing 1, where the first opening 131 is used for machining the resonant cavity 13, for example, when the high-pressure housing 1 is formed by punching, a punching tool can be inserted into the first opening 131 to perform punching operation, and the punching tool can be withdrawn from the first opening 131, or when the high-pressure housing 1 is formed by casting, a machining mold of the resonant cavity 13 can be withdrawn from the first opening 131, thereby, by designing the first opening 131, the machining forming of the resonant cavity 13 is facilitated, the forming of various machining modes of the high-pressure housing 1 is facilitated, the machining difficulty and the machining cost of the high-pressure housing 1 are reduced, and the mass production and the practical application of the high-pressure housing 1 are facilitated.

And as shown in fig. 2-7, the high-pressure casing 1 includes a first end cap 21 covering the first opening 131, that is, in the present invention, the first opening 131 is designed to cooperate with the first end cap 21, and after the high-pressure casing 1 is mounted on the whole electric compressor 100, the high-pressure chamber 11 communicates with the oil chamber 15, the resonance chamber 13 communicates with the oil chamber 15, and the resonance chamber 13 is closed at the first opening 131 by the first end cap 21, so that the resonance chamber 13 forms a cavity structure satisfying the helmholtz resonance principle. The cover in the present invention is configured such that at least a portion of the first end cover 21 extends into the first opening 131 and is partially shielded from the first opening 131, so that the first end cover 21 is fixed to the first opening 131 and is shielded from the first opening 131.

In a specific design, the resonant cavity 13 may be configured into a hole shape, and the first opening 131 is formed at least one side hole end of the resonant cavity 13 (it may 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 in a hole shape" means that: a three-dimensional hole shape having a certain depth, not a planar hole shape, is formed such that both ends in the direction in which the center line of the hole extends are both ends in the longitudinal direction of the resonant cavity 13. Therefore, the resonant cavity 13 has the advantages of simple structure, convenience in processing, flexible setting position, smaller occupied space, capability of reducing the whole volume and saving the occupied space in a vehicle on the premise of meeting noise reduction, and capability of being processed in various modes such as punching or casting.

The first processing end surface may be formed on the outer side of the high-pressure housing 1, and the first opening 131 is formed by opening the first processing end surface, as shown in fig. 2-7, where the first processing end surface is configured as a processing plane disposed on the outer side of the high-pressure housing 1, and the surface is regular and smooth, and is not easy to interfere with the punching tool or the die, so that the punching tool or the die is easy to be separated by a user. The first end cover 21 includes a pressing portion 211 and a connecting portion 212, the pressing portion 211 and the connecting portion 212 are integrally formed, the pressing portion 211 is in a disc shape, the connecting portion 212 is in a column shape, an end face of the pressing portion 211 is fixedly connected with an end face of the connecting portion 212, and an outer diameter size of the pressing portion 211 is larger than an outer diameter size of the connecting portion 212 to form a limiting surface at a position connected with the connecting portion 212. And when in assembly, the connecting part 212 can extend into the first opening 131, the connecting part 212 is fixedly connected with the inner peripheral wall of the first opening 131, and the pressing part 211 is positioned outside the first opening 131 and is pressed against the first processing end surface.

In a specific design, the connecting portion 212 may be in threaded engagement with the inner peripheral wall of the first opening 131, so that the connecting portion 212 may be detached from or installed into the first opening 131 in a rotatable manner, or the connecting portion 212 may be in interference engagement with the inner peripheral wall of the first opening 131, i.e. the connecting portion 212 may be pressed into the first opening 131 to tightly press against the inner peripheral wall of the first opening 131, thereby ensuring connection stability of the first end cap 21 at the first opening 131. The limiting surface of the pressing portion 211 is designed to be in pressing fit with the first processing end surface, so that the first end cover 21 and the high-pressure shell 1 can have a limiting effect, namely, when the connecting portion 212 is matched to the maximum position in the first opening 131, the pressing portion 211 is pressed against the first processing end surface, so that the first end cover 21 is prevented from excessively and even completely extending into the first opening 131, the part of the pressing portion 211 of the first end cover 21 is effectively kept outside the first opening 131, the relative position of the first end cover 21 and the high-pressure shell 1 is ensured to be fixed, and a user can operate the pressing portion 211 to load and disassemble the first end cover 21, so that the rationality of structural design is improved.

In some embodiments, a first opening 131 is formed at a first end of the resonant cavity 13, a second end of the resonant cavity 13 is in communication with the refrigerant discharge port 12 through a connection channel 14, as shown in fig. 2-5 and 7, the first opening 131 is formed at a left lower end of the resonant cavity 13, meanwhile, the connection channel 14 is located at a right upper end of the resonant cavity 13, and the connection channel 14 is used for communicating the right upper end of the resonant cavity 13 with the refrigerant discharge port 12, and the gaseous refrigerant entering into the resonant cavity 13 can flow from the connection channel 14 to the refrigerant discharge port 12.

Wherein the overflow area of the connecting channel 14 is smaller than that of the resonant cavity 13, by the arrangement, the first end of the resonant cavity 13, such as the lower end in fig. 2, forms one inner end surface of the resonant cavity 13 by the first end cover 21, and the second end of the resonant cavity 13, such as the upper end in fig. 2, forms a step surface at the connection with the connecting channel 14, and the step surface can serve as the other inner end surface of the resonant cavity 13.

Therefore, the first end of the resonant cavity 13 is matched with the first end cover 21, and the step surface formed between the second end of the resonant cavity 13 and the connecting channel 14 can enable the resonant cavity 13 to form a cavity structure meeting the helmholtz resonance principle, so that the air flow noise and pulsation of the exhaust side of the electric compressor 100 are improved, and the noise and pulsation of the refrigerant discharged by the electric compressor 100 are further improved.

And at the time of actual installation, the silencer cannula 4 may be fixed to the inside of the resonance chamber 13 or the inner wall of the connection passage 14, that is, the fixed end of the silencer cannula 4 may be fixedly connected to the inner wall of the resonance chamber 13, as shown in fig. 2 and 3, the fixed end of the silencer cannula 4 is the upper right end thereof, and the fixed end of the silencer cannula 4 extends into the connection passage 14 to be fixedly connected to the inner peripheral wall of the connection passage 14, as shown in fig. 7, the fixed end of the silencer cannula 4 is the lower left end thereof, and the fixed end of the silencer cannula 4 is fixedly connected to the lower end region of the inner peripheral wall of the resonance chamber 13 in the resonance chamber 13.

In some embodiments, 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 adapted to be machined through the first opening 131. It should be noted that the resonant cavity 13 is configured as a channel structure having a circular cross section, the connection channel 14 is also configured as a channel structure having a circular cross section, and the center line of the resonant cavity 13 and the center line of the connection channel 14 are respective corresponding axes, that is, the axis of the resonant cavity 13 coincides with the axis of the connection channel 14.

As shown in fig. 2 to 7, the first opening 131 is opened at the left lower end of the resonant cavity 13, and the connection channel 14 is formed at the right upper end of the resonant cavity 13, whereby the resonant cavity 13 and the connection channel 14 can be co-molded at the time of co-molding.

Specifically, when the high-pressure housing 1 is formed by punching, the punching tool can be inserted into the first opening 131 to perform punching operation, and the resonant cavity 13 is machined on the high-pressure housing 1 by the punching tool, and the connecting channel 14 can be machined along with the insertion of the punching tool and the reduction of the punching radius, and the axis of the connecting channel 14 is coincident with the axis of the resonant cavity 13, so that the punching tool can be operated in a single machining direction or tool withdrawal direction, and the forming difficulty is reduced. Or, when the high-pressure shell 1 is formed by casting, the processing mold of the resonant cavity 13 can be separated from the first opening 131, and in actual design, the resonant cavity 13 and the connecting channel 14 are formed by processing the same mold, for example, the processing mold comprises two parts, one part of the processing mold is smaller in diameter and used for forming the connecting channel 14, the other part of the processing mold is larger in diameter and used for forming the resonant cavity 13, and the first opening 131 is larger than the outer diameter of the processing mold, so that quick demolding is facilitated, and therefore, the resonant cavity 13 and the connecting channel 14 can be formed by demolding the same mold, the processing efficiency is improved, the number of the molds is reduced, and the processing cost is reduced.

During actual processing, the punching tool can withdraw along the axis of the resonant cavity 13, or the processing die can withdraw along the axis of the resonant cavity 13, so that the punching tool or the processing die is prevented from damaging the molded high-pressure shell 1.

In some embodiments, the first end cover 21 is provided with a mounting groove 213 that is open toward the inside of the resonant cavity 13, that is, the mounting groove 213 is concavely formed on the end surface of the first end cover 21, and after the first end cover 21 is mounted on the high-pressure housing 1, the mounting groove 213 is located in the resonant cavity 13 and open toward the inside of the resonant cavity 13, and in actual mounting, one end of the sound-deadening cannula 4 may be fixedly connected to the inner peripheral wall of the mounting groove 213, or one end of the sound-deadening cannula 4 may be clearance-fitted to the inner peripheral wall of the mounting groove 213.

That is, the inside diameter dimension of the installation groove 213 is larger than the outside diameter dimension of the end of the sound-deadening cannula 4, so that one end of the sound-deadening cannula 4 can extend into the installation groove 213 to be in installation engagement with the first end cap 21, for example, the sound-deadening cannula 4 is in clearance engagement with the inner wall of the installation groove 213, or the inner peripheral wall of the installation groove 213 is provided with internal threads, while the end of the sound-deadening cannula 4 is provided with external threads, and the sound-deadening cannula 4 extends into the installation groove 213 to be in threaded connection with the first end cap 21; alternatively, the inner diameter dimension of the mounting groove 213 is close to the outer diameter dimension of the end portion of the sound-deadening cannula 4, so that the sound-deadening cannula 4 is mounted in the mounting groove 213 to be interference fit with the first end cap 21, and connection fixation is achieved.

Wherein, as shown in fig. 3, the left lower end of the sound-deadening cannula 4 extends into the mounting groove 213 and is spaced apart from the inner wall of the mounting groove 213, and as shown in fig. 4-6, the left lower end of the sound-deadening cannula 4 extends into the mounting groove 213 and is fixed with the inner wall of the mounting groove 213, such as an interference fit. In some embodiments of the invention, the mounting groove 213 is provided, so that at least part of the end portion of the silencing cannula 4 is located in the mounting groove 213 for limit fit, and the first end cover 21 and the silencing cannula 4 can share a part of space in the axial direction, which is beneficial to improving the fit depth of the silencing cannula 4 and the first end cover 21 and increasing the length of the silencing cannula 4.

In some embodiments, a plurality of rings of the sound deadening holes 41 are provided in the axial direction of the sound deadening cannula 4, that is, the outer peripheral wall of the sound deadening cannula 4 is provided with a plurality of rings of the sound deadening holes 41, and the plurality of rings of the sound deadening holes 41 are distributed at intervals in the axial direction of the sound deadening cannula 4. So as to increase the flow cross section between the pipe cavity of the silencing insertion pipe 4 and the flow channel and ensure the flow efficiency of the gaseous refrigerant. In practical design, the plurality of rings of silencing holes 41 can be uniformly spaced along the axial direction of the silencing cannula 4, so that the uniformity of the air flow at each position of the silencing cannula 4 in the axial direction is ensured, and the silencing effect at each position of the silencing cannula 4 is relatively uniform.

Each turn of the sound deadening hole 41 includes a plurality of sound deadening holes 41, and the plurality of sound deadening holes 41 of each turn are arranged at intervals in the circumferential direction of the sound deadening cannula 4. From this, can make the axial and the different positions in circumference of amortization intubate 4 department, all can carry out the air current circulation, and through setting up the axial and the circumference of amortization intubate 4 of great quantity of amortization hole 41 distribution, increase gaseous refrigerant from the circulation passageway to the circulation of the interior circulation of amortization intubate 4, realize quick exhaust.

In some embodiments, in the plurality of circles of sound deadening holes 41, as shown in fig. 8, the center-to-center distance t between adjacent sound deadening holes 41 satisfies: d is more than or equal to t and less than or equal to 5d; as shown in fig. 8, d is the equivalent diameter of the hole cross section of the sound deadening hole 41. That is, the ratio of the center distance between two adjacent sound deadening holes 41 to the equivalent diameter of the hole cross section of the sound deadening hole 41 is in the interval 1 to 5, and t is set to 2d or 3d.

It can be understood that the silencing hole 41 is hollowed out and formed on the outer peripheral wall of the silencing cannula 4, and by arranging the silencing hole 41, the gaseous refrigerant can circulate between the circulation channel and the lumen of the silencing cannula 4, and the weight of the silencing cannula 4 can be reduced, so that the design of light weight can be realized. Wherein, set up the centre-to-centre spacing of amortization hole 41 to above-mentioned within range, not only do benefit to the air input of guaranteeing amortization intubate 4, and avoid amortization hole 41 to set up too many the structure intensity that causes amortization intubate 4 to be too low, prevent to appear amortization intubate 4 to receive the too big problem that leads to the structure to break of vibration in electric compressor 100 operation in-process.

When the hole cross-section sizes of the plurality of sound deadening holes 41 are different, d is the equivalent diameter of the sound deadening hole 41 having the largest hole cross-section. That is, in the actual design, the diameters of the plurality of sound deadening holes 41 may be set to be the same when the inner diameters of the different sound deadening holes 41 are the same, d is the equivalent diameter of any one sound deadening hole 41, and d is the equivalent diameter of the hole section maximum sound deadening hole 41 when the diameters of at least two of the plurality of sound deadening holes 41 are different, whereby the design of the center distance and the hole diameter of the sound deadening holes 41 can be compared. Here, the sound deadening hole 41 in the present invention may be configured as a circular hole, or may be configured as a square hole or other irregularly shaped hole, and the equivalent diameter is the diameter of the square hole or other irregularly shaped hole corresponding to the diameter under the circular hole of the same cross-sectional area.

In some embodiments, the hole section of the sound deadening hole 41 satisfies: d is more than or equal to 0.05 and less than or equal to D; wherein D is the equivalent diameter of the hole section of the sound deadening hole 41, D is the equivalent diameter of the cross section of the sound deadening cannula 4, i.e., the ratio between the equivalent diameter of the hole section of the sound deadening hole 41 and the equivalent diameter of the cross section of the sound deadening cannula 4 is 0.05 to 1, and D is set to 0.1D, 0.2D, as shown in fig. 8.

Wherein, setting the size of the hole cross section of the sound deadening hole 41 within the above range makes it possible to make the equivalent diameter of the hole cross section of the sound deadening hole 41 more reasonable with respect to the equivalent diameter of the cross section of the sound deadening cannula 4. That is, the problem that the flow of the gaseous refrigerant flowing through the silencing hole 41 is larger than the flow of the second end of the pipe cavity due to the fact that the silencing hole 41 is too small is avoided, and the gaseous refrigerant can be reasonably discharged from the oil outlet 152, the flowing channel, the silencing hole 41, the pipe cavity and the refrigerant discharge port 12 in sequence; and also can not appear the amortization hole 41 too big, lead to the too little problem of structural strength of amortization intubate 4, avoid appearing in motor compressor 100 operation in-process amortization intubate 4 receive the too big problem that leads to the structure to break of vibration, improve the security of amortization intubate 4.

And D is the equivalent diameter of the smallest cross section of the sound deadening cannula 4 when the sound deadening cannula 4 is of variable cross section structure. That is, the sound-deadening-cannula 4 in the present invention may be constructed as a constant-section pipe, and in the case of a constant-section pipe, the equivalent diameter at the cross section at any position of the sound-deadening-cannula 4 is D; the sound-deadening cannula 4 may also be constructed as a variable-cross-section tube, and in the case of a variable-cross-section tube, the diameter at the smallest cross-section of the sound-deadening cannula 4 is D. The cross section of the sound-deadening cannula 4 in the present invention may be a circular cross section, or may be a square cross section or another irregular cross section, and the equivalent diameter is a diameter of the square cross section or the other irregular cross section corresponding to the circular cross section of the same cross section.

In some embodiments, a first oil return channel 132 is disposed in a bottom space of the resonant cavity 13 in the gravity direction, as shown in fig. 7, the first oil return channel 132 is disposed at a lower end of the resonant cavity 13, that is, an inlet end of the first oil return channel 132 is disposed at an inner peripheral wall of the resonant cavity 13 and is open toward the interior of the resonant cavity 13, so that oil deposited in the resonant cavity 13 can flow out through the first oil return channel 132 and flow back to a space where the compression part 20 is located.

The first oil return channel 132 extends in a bottom space of the resonant cavity 13 towards a direction close to the compression part 20, an axis of the first oil return channel 132 forms a certain included angle with an axis of the resonant cavity 13, and the first oil return channel 132 extends towards a direction away from the resonant cavity 13 and is inclined downward relative to the resonant cavity 13, it can be understood that the resonant cavity 13 is also configured such that a lower end is opened to form the first opening 131, and thus, the first oil return channel 132 and the resonant cavity 13 can be processed from the same side of the high pressure housing 1, for example, the first oil return channel 132 and the resonant cavity 13 can be processed from different positions of the lower side of the high pressure housing 1 respectively, thereby reducing processing difficulty.

In practical design, the first oil return channel 132 is lower than the oil outlet 152, that is, in the design that the oil outlet 152 is disposed on the inner peripheral wall of the connecting channel 14 or in the design that the oil outlet 152 is disposed on the inner peripheral wall of the resonant cavity 13, the oil outlet 152 is higher than the first oil return channel 132, so that after the oil entering the resonant cavity 13 at the oil outlet 152 is deposited in the resonant cavity 13, the oil can effectively flow back into the space where the compression part 20 is located from the first oil return channel 132, and the inlet end of the first oil return channel 132 is spaced from the lower end surface of the resonant cavity 13 by a certain distance, so that after the first end cover 21 is mounted on the first opening 131, the first end cover 21 is spaced from the first oil return channel 132 to avoid the first end cover 21 from being mounted too deeply to cause blockage of the first oil return channel 132.

In some embodiments, the position of the first oil return passage 132 within the resonance chamber 13 satisfies: h is less than or equal to 0.3H; as shown in fig. 7, H is a vertical distance between the highest point of the first oil return passage 132 and the lowest point of the resonance chamber 13 in the gravity direction, and H is a vertical distance between the highest point and the lowest point of the resonance chamber 13 in the gravity direction. As shown in fig. 3, the first oil return passage 132 is located in the bottom space inside the resonance chamber 13, that is, the first oil return passage 132 is spaced apart from the upper end of the resonance chamber 13 and from the lower end of the resonance chamber 13, and the ratio of the vertical distance between the first oil return passage 132 and the lowest point of the resonance chamber 13 to the vertical distance between the highest point and the lowest point of the resonance chamber 13 is less than 0.3, such as 0.28, 0.25, or 0.2.

Therefore, the position of the first oil return channel 132 in the resonant cavity 13 is set within the above range, so that the position of the inlet end of the first oil return channel 132 in the resonant cavity 13 is lower, the deposited oil in the resonant cavity 13 can be ensured to be in the first oil return channel 132, the phenomenon that the pressure of the first end cover 21 is larger due to excessive deposited oil in the resonant cavity 13 is avoided, and the effectiveness of oil return is ensured.

In practical design, the first oil return channel 132 may be set to at least one, that is, one first oil return channel 132 may be set on the outer peripheral wall of the resonant cavity 13, or two, three or more first oil return channels 132 may be set, so as to ensure oil return, prevent that a single first oil return channel 132 is blocked to cause abnormal oil return, and improve oil return reliability.

In the present 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 at the inner peripheral wall of the connecting channel 14, the height of the oil outlet 152 is higher, the oil entering the resonant cavity 13 is less, and the height of the first oil return channel 132 is higher; or if the oil outlet 152 is located at the inner peripheral wall of the resonant cavity 13, the height of the oil outlet 152 is lower, so that more oil enters the resonant cavity 13, and the height of the first oil return channel 132 is lower, so as to ensure timely oil return. Wherein the higher and lower are not absolutely higher or lower than the two arrangements.

In some embodiments, as shown in fig. 2-7, the bottom of the oil cavity 15 in the gravity direction is provided with a second oil return channel 153, it is understood that the oil cavity 15 is communicated with the high pressure cavity 11, so that the high pressure refrigerant can enter the oil cavity 15 for oil-gas separation, the separated gaseous refrigerant flows from the oil outlet 152 to the connecting channel 14 or the resonant cavity 13, the separated oil liquid is converged downward at the bottom of the oil cavity 15 under the action of gravity, and flows back from the second oil return channel to the space where the compression part 20 is located.

The second oil return channel 153 extends in a direction approaching the compression member 20 in a bottom space of the oil cavity 15, an axis of the second oil return channel 153 forms a certain included angle with an axis of the oil cavity 15, and the second oil return channel 153 extends in a direction departing from the oil cavity 15 and is inclined downward relative to the oil cavity 15. In this way, both the second oil return passage 153 and the oil chamber 15 may be machined from the same side of the high pressure housing 1, for example, the second oil return passage 153 and the oil chamber 15 may be machined from different positions on the lower side of the high pressure housing 1, respectively, so as to reduce machining difficulty. In practical design, the second oil return channel 153 is lower than the oil outlet 152 and is also lower than the oil inlet 151 of the oil cavity 15, so that after the high-pressure refrigerant enters the oil cavity 15 from the oil inlet 151 for separation, the oil can be deposited in the bottom space of the oil cavity 15 under the action of gravity so as to return from the second oil return channel 153, and reasonable oil return of the oil in the oil cavity 15 is ensured.

In some embodiments, the surface of the high pressure housing 1 is formed with the second opening 154 for forming the oil cavity 15, for example, when the high pressure housing 1 is formed by punching, the punching tool may be inserted into the second opening 154 for punching, and the punching tool may be withdrawn from the second opening 154, or when the high pressure housing 1 is formed by casting, the processing mold of the oil cavity 15 may be withdrawn from the second opening 154, thereby, by designing the second opening 154, the processing forming of the oil cavity 15 is facilitated, the forming of various processing modes of the high pressure housing 1 is facilitated, the processing difficulty and the processing cost of the high pressure housing 1 are reduced, and the mass production and the practical application of the high pressure housing 1 are facilitated.

As shown in fig. 2-7, the high-pressure housing 1 includes a second end cap 22 covering the second opening 154, that is, in the present invention, the second opening 154 is designed to cooperate with the second end cap 22, and after the high-pressure housing 1 is installed in the whole electric compressor 100, the high-pressure chamber 11 is communicated with the oil inlet 151 of the oil chamber 15, and the resonant chamber 13 is communicated with the oil inlet 151 of the oil chamber 15, and the second opening 154 is closed by the second end cap 22, so that the oil chamber 15 has a stable sealing state at positions other than the oil inlet 151 and the oil inlet 151, thereby ensuring the reliability of oil effect. The cover arrangement of the second end cover 22 at the second opening 154 is the same as the cover arrangement of the first end cover 21 at the first opening 131, and will not be described herein.

And, the outside of high-pressure housing 1 is formed with the second processing terminal surface, and second opening 154 is opened at the second processing terminal surface and is formed, and as shown in fig. 2-7, the second processing terminal surface is structured to locate the processing plane of the outside of high-pressure housing 1, and the surface is regular smooth, is difficult for producing the interference with punching cutter or mould, does benefit to the realization user and operates the deviate from of punching cutter or mould. The second end cap 22 may be configured in the same structural shape as the first end cap 21, and the matching manner of the second end cap 22 and the second opening 154 is the same as the matching manner of the first end cap 21 and the first opening 131, which is not described herein.

The center line of the oil outlet 152 coincides with the center line of the oil chamber 15, and both the oil outlet 152 and the oil chamber 15 are adapted to be formed by the second opening 154. The oil chamber 15 is configured as a channel structure having a circular cross section, the oil outlet 152 is also configured as a channel structure having a circular cross section, and the center line of the oil chamber 15 and the center line of the oil outlet 152 are axes corresponding to each other, that is, the axis of the oil chamber 15 coincides with the axis of the oil outlet 152. As shown in fig. 2 to 4, the second opening 154 is opened at the right lower end of the oil chamber 15, and the oil outlet 152 is formed at the left upper end of the oil chamber 15, whereby the oil chamber 15 and the oil outlet 152 can be molded together at the time of co-molding.

Specifically, when the high-pressure housing 1 is formed by punching, the punching tool can be inserted into the second opening 154 to perform punching operation, and the oil cavity 15 is processed by the punching tool on the high-pressure housing 1, and the oil outlet 152 can be processed along with the insertion of the punching tool and the reduction of the punching radius, and the axis of the oil outlet 152 and the axis of the oil cavity 15 are coincident, so that the punching tool can be operated in a single processing direction or retracting direction, and the forming difficulty is reduced. Or, when the high-pressure housing 1 is formed by casting, the processing mold of the oil cavity 15 can be separated from the second opening 154, and in practical design, the oil cavity 15 and the oil outlet 152 are formed by processing the same mold, for example, the processing mold comprises two parts, one part of the processing mold has a smaller diameter for forming the oil outlet 152, the other part of the processing mold has a larger diameter for forming the oil cavity 15, and the second opening 154 is larger than the outer diameter of the processing mold, so that quick demolding is facilitated, and therefore, the oil cavity 15 and the oil outlet 152 can be formed by demolding the same mold, so that the processing efficiency is improved, the number of the molds is reduced, and the processing cost is reduced.

During actual processing, the punching tool can withdraw along the axis of the oil cavity 15, or the processing die can withdraw along the axis of the oil cavity 15, so that the high-pressure shell 1 after being molded is prevented from being damaged by the punching tool or the processing die.

In some embodiments, as shown in fig. 2-7, the oil chamber 15 is provided with an oil component 3 for oil-gas separation, the oil component 3 is used for improving the oil effect in the oil chamber 15, and the refrigerant in the oil chamber 15 can be discharged from the oil outlet 152 after oil-gas separation by the oil component 3. That is, after the high-pressure refrigerant in the high-pressure chamber 11 enters the oil chamber 15, the separated oil is deposited downward in the bottom space of the oil chamber 15 by the separation action of the oil component 3, and flows back from the second oil return passage 153 toward the space where the compression member 20 is located, and the separated gaseous refrigerant is discharged upward toward the oil outlet 152.

And, further, the oil member 3 is constructed in a hollow tubular structure, such as the oil member 3 is constructed as an oil insertion tube, the axial direction of the oil member 3 is parallel to the length direction of the oil chamber 15, that is, the axis of the lumen of the oil insertion tube is parallel to the axis of the oil chamber 15, and the oil inlet 151 is located outside the peripheral wall of the oil member 3, that is, the oil inlet 151 is provided at the outer peripheral wall of the oil chamber 15 and located radially outside the oil insertion tube.

After the oil cannula is mounted in the oil chamber 15, the oil cannula is positioned in the upper space of the oil chamber 15, the upper end of the oil cannula is fixedly connected to the upper end of the oil chamber 15, the lower end of the oil cannula is suspended in the oil chamber 15, both ends of the oil cannula are opened, the upper end of the oil cannula is communicated with the oil outlet 152, the lower end of the oil cannula is communicated with the oil chamber 15, and the height of the oil inlet 151 is positioned between the upper end and the lower end of the oil cannula, as shown in fig. 2 to 7.

Thus, after the high-pressure refrigerant in the high-pressure chamber 11 enters the oil chamber 15, the high-pressure refrigerant acts on the outer peripheral wall of the oil insertion pipe at a high flow rate, and moves downward and into a space lower than the lower end of the oil insertion pipe due to the gravity of the high-pressure refrigerant itself guided by the outer peripheral wall of the oil insertion pipe, and the separated gaseous refrigerant enters the lumen of the oil insertion pipe and is discharged upward from the oil outlet 152 under the action of the internal pressure of the oil chamber 15; the oil separated from the high-pressure refrigerant is deposited downward in the bottom space of the oil cavity 15 along the outer peripheral wall of the oil insertion pipe or the inner peripheral wall of the oil cavity 15, and flows back into the space where the compression member 20 is located from the second oil return passage 153, thereby realizing oil-gas separation.

It can be understood that the oil inlet 151 and the outer circumferential wall of the oil insertion pipe are arranged opposite to each other in the radial direction, so that the high-pressure refrigerant entering the oil cavity 15 from the oil inlet 151 directly acts on the outer circumferential wall of the oil insertion pipe, flows towards the inner circumferential wall of the oil cavity 15 under the guiding action of the oil insertion pipe, and forms a circumferential swirl along the inner circumferential wall of the oil cavity 15, thereby enabling oil gas to be separated at a high speed in the circumferential swirl process, and being beneficial to enhancing the oil-gas separation effect.

In practical design, as shown in fig. 2-7, the axial length of the oil insertion tube is set to be not less than half of the axial length of the oil cavity 15, so that after the high-pressure refrigerant enters the oil cavity 15, the high-pressure refrigerant can have enough flow stroke to realize oil-gas separation, and the amount of oil in the gaseous refrigerant is reduced, namely, the oil entering the resonant cavity 13 or the connecting channel 14 is reduced.

Next, referring to fig. 1, an electric compressor 100 according to a second aspect of the present invention will be described.

As shown in fig. 1, the motor-driven compressor 100 may include: the motor assembly includes a housing part including the high-pressure housing assembly for the electric compressor according to any one of the above-described first aspect, the compression part 20 having the discharge port 201 communicating with the high-pressure chamber 11 to discharge the compressed refrigerant to the high-pressure chamber 11, and a motor part 30 including a motor body 301 and a driving shaft 302, the motor body 301 driving the compression part 20 through the driving shaft 302 to perform a compression operation. Thus, by providing the high-pressure housing assembly, exhaust gas flow noise and pressure pulsation generated when the motor-driven compressor 100 is operated can be effectively improved.

The specific type of the motor-driven compressor 100 is not limited, and may be, for example, a horizontal compressor having a central axis extending in a lateral direction or slightly inclined to a horizontal line, a vertical compressor having a central axis extending in a vertical direction or slightly inclined to a vertical line, or the like.

It should be noted that the specific type of the electric compressor 100 is not limited, and may be, for example, a rotary compressor or a scroll compressor, etc., when the electric compressor 100 is a rotary compressor (this example is not shown in the drawings), the compression member 20 may include a cylinder, a piston, a slide vane, etc., the drive shaft 302 drives the piston to roll in the cylinder, and when the electric compressor 100 is a scroll compressor (for example, the example shown in fig. 1), the compression member 20 may include a fixed scroll, a movable scroll, the drive shaft 302 drives the movable scroll to rotate, etc.

It should be noted that, the relative positional relationship between the high-pressure housing 1 and the compression member 20 is not limited, for example, the compression member 20 may be completely located outside the high-pressure housing 1, or the compression member 20 may be at least partially located outside the high-pressure housing 1, so as to meet different design requirements of different models.

In some embodiments, as shown in fig. 1, the housing component further comprises: a middle partition plate 103 and a low pressure housing 102, a compression member 20 and a motor body 301 are disposed on both sides of the middle partition plate 103, and a driving shaft 302 is provided to penetrate the middle partition plate 103 to be connected with the compression member 20; a low-pressure chamber 105 accommodating the motor body 301 is formed between the low-pressure casing 102 and the intermediate partition 103, a refrigerant suction port 1021 communicating with the low-pressure chamber 105 is formed in the low-pressure casing 102, and the compression element 20 sucks in refrigerant from the low-pressure chamber 105. The low-pressure housing 102 is further connected with a cover plate 104, an installation space is defined between the cover plate 104 and the low-pressure housing 102, and the electric control component 40 is disposed in the installation space.

Thus, the electric compressor 100 may be a low back pressure compressor, which is advantageous for applications of new energy vehicles 1000 such as electric vehicles, hybrid vehicles, etc., and when used in these vehicles 1000, it is possible to improve noise and pressure pulsation of exhaust air flow due to the electric compressor 100, improve resonance problems of a thermal management system of the vehicle 1000, and improve noise and vibration caused to the vehicle 1000.

In some embodiments, as shown in fig. 1, the middle partition 103 is sandwiched between the low pressure casing 102 and the compression member 20, and the high pressure casing 1 is provided on the side of the compression member 20 facing away from the middle partition 103. Therefore, the structure can be simplified, the assembly is simplified, the volume is reduced, the production efficiency is improved, and the connection reliability is improved. For example, such a structure may be applied to a scroll compressor, but the structure of the scroll compressor is not limited thereto.

Further, as shown in fig. 1, the high-pressure casing 1 has a casing end face on which a high-pressure chamber 11 is formed, the high-pressure chamber 11 being open toward the compression member 20, the compression member 20 being in sealing engagement with the casing end face, and the exhaust port 201 of the compression member 20 being open toward the high-pressure chamber 11, whereby communication between the exhaust port 201 and the high-pressure chamber 11 can be achieved.

Next, an air conditioning system 300 according to an embodiment of the third aspect of the present invention is described with reference to the accompanying drawings.

Wherein the air conditioning system 300 may comprise the electric compressor 100 according to any of the embodiments of the second aspect of the present invention. Since the exhaust noise and pulsation of the electric compressor 100 according to any one of the embodiments 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 problem caused to the air conditioning system 300 due to the exhaust air flow noise and pressure pulsation of the electric compressor 100 can be improved.

It should be noted that, the specific application scenario of the air conditioning system 300 according to the embodiment of the present invention is not limited, for example, an indoor air conditioner, an indoor refrigerator, a vehicle-mounted air conditioner, etc., and when the application scenario is determined, a person skilled in the art can know other components of the air conditioning system 300, for example, when the air conditioning system is used in an indoor air conditioner or an indoor refrigerator, an evaporator, a condenser, a throttling element, etc., and, for example, when the air conditioning system is used in a vehicle-mounted air conditioner, at least one of an in-vehicle condenser, an in-vehicle evaporator, an out-vehicle condenser, an out-vehicle evaporator, a throttling assembly, etc., which are not described herein.

Next, a vehicle 1000 according to a fourth aspect of the invention is described with reference to the accompanying drawings.

As shown in fig. 12, a vehicle 1000 may include a vehicle body 200 and an air conditioning system 300 mounted on the vehicle body 200, the air conditioning system 300 including the air conditioning system 300 according to any of the embodiments of the third aspect of the present invention. Since the air conditioning system 300 according to any of the embodiments of the present invention can improve the exhaust noise and pulsation of the electric compressor 100, when the air conditioning system 300 is used for the vehicle 1000, the resonance problem of each component in the thermal management system of the vehicle 1000 due to the exhaust air 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. Optionally, the electric compressor 100 is configured to compress at least one refrigerant of R134a, R744, R290, and R1234yf, so as to meet the vehicle-mounted usage requirement.

It should be noted that, the specific type of the vehicle 1000 according to the embodiment of the present invention is not limited, and may be, for example, a new energy vehicle, which may include a pure electric vehicle, a hybrid vehicle, and the like, and will be described herein. In addition, when the type of the vehicle 1000 is specifically determined, those skilled in the art can know other components of the vehicle 1000, and detailed description thereof will be omitted herein.

Next, a high-pressure housing 1 for an electric compressor of a vehicle 1000 according to some embodiments of the present invention will be described with reference to fig. 2 to 7.

Example 1

As shown in fig. 2, the high-pressure casing 1 is formed with a high-pressure chamber 11 and a refrigerant discharge port 12, the high-pressure chamber 11 is located in a lower region of the high-pressure casing 1, the refrigerant discharge port 12 is located in an upper region of the high-pressure casing 1, the high-pressure casing 1 is further formed with a resonance chamber 13 and an oil chamber 15, and the high-pressure chamber 11 is located between the resonance chamber 13 and the oil chamber 15. Wherein, resonant cavity 13 forms in the left side of high-pressure housing 1, and resonant cavity 13 extends towards upper right slope along the lower left of high-pressure housing 1, simultaneously, oil cavity 15 forms in the right side of high-pressure housing 1, and oil cavity 15 extends towards upper left slope along the lower right of high-pressure housing 1, the periphery wall of oil cavity 15 is equipped with oil inlet 151, oil inlet 151 communicates high-pressure cavity 11 and oil cavity 15, and be equipped with oil outlet 152 in the upper end of oil cavity 15, oil outlet 152 communicates oil cavity 15 and resonant cavity 13's upper end, resonant cavity 13's upper end is equipped with connecting channel 14, connecting channel 14 communicates resonant cavity 13 and refrigerant discharge port 12.

As shown in fig. 2, the lower end of the resonant cavity 13 is open, and a first opening 131 is formed, the first opening 131 is open at the lower left of the high-pressure housing 1, the first opening 131 is used for processing the resonant cavity 13, a first end cover 21 is disposed at the first opening 131, and the first end cover 21 is used for closing the lower end of the resonant cavity 13. The resonance cavity 13 is internally provided with the silencing insertion pipe 4, the upper end of the silencing insertion pipe 4 extends into the connecting channel 14, the upper end of the silencing insertion pipe 4 is fixedly connected with the inner wall of the connecting channel 14, and the silencing insertion pipe 4 and the connecting channel are in interference fit, meanwhile, the lower end of the silencing insertion pipe 4 extends to a position close to the first end cover 21, the outer peripheral wall of the end part of the silencing insertion pipe 4 is spaced from the inner peripheral wall of the resonance cavity 13, and the end face of the lower end of the silencing insertion pipe 4 is in clearance fit with the end face of the first end cover 21. The first end cover 21 includes a pressing portion 211 and a connecting portion 212, the pressing portion 211 forms a limiting surface at a position connected with the connecting portion 212, the connecting portion 212 is in interference fit with the inner peripheral wall of the first opening 131, and the limiting surface of the pressing portion 211 is in pressing fit with the first processing end surface.

The second oil return passage 153 is disposed in the oil chamber 15, and the second oil return passage 153 communicates the oil chamber 15 with the space where the compression element 20 is located, so that the oil deposited in the second oil return passage 153 can return from the second oil return passage 153 to the space where the compression element 20 is located. Meanwhile, the lower end of the oil chamber 15 is opened, and a second opening 154 is formed, the second opening 154 is opened at the lower right of the high pressure housing 1, the second opening 154 is used for processing the oil chamber 15, a second end cover 22 is provided at the second opening 154, the second end cover 22 is used for closing the lower end of the oil chamber 15, and the second end cover 22 and the first end cover 21 are identical in construction.

Example two

As shown in fig. 3, the second embodiment differs from the first embodiment in that it includes: the end face of the first end cover 21 facing the inside of 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 silencing insertion tube 4, the lower end of the silencing insertion tube 4 extends into the mounting groove 213, and the lower end of the silencing insertion tube 4 is in clearance fit with the inner peripheral wall of the mounting groove 213.

Example III

As shown in fig. 4, the third embodiment is different from the second embodiment in that it includes: the upper end of the silencing cannula 4 is positioned in the upper space of the resonant cavity 13, namely the upper end of the silencing cannula 4 does not extend into the connecting channel 14, and the upper end of the silencing cannula 4 is in clearance fit with the upper end face of the resonant cavity 13; and, the lower end of the sound deadening cannula 4 extends into the mounting groove 213, and the outer peripheral wall of the lower end of the sound deadening cannula 4 is interference fit with the inner peripheral wall of the mounting groove 213.

Example IV

As shown in fig. 5, the fourth embodiment differs from the third embodiment in that it includes: the upper end of amortization intubate 4 is the stiff end and the lower extreme is the mating end, and in the upper end of amortization intubate 4 stretched to connecting channel 14, and the outer peripheral wall of the upper end of amortization intubate 4 and the interior perisporium clearance fit of connecting channel 14, in the lower extreme of amortization intubate 4 stretched to mounting groove 213, and the outer peripheral wall of the lower extreme of amortization intubate 4 and the interior perisporium clearance fit of mounting groove 213.

Example five

As shown in fig. 6, the fifth embodiment differs from the fourth embodiment in that it includes: the upper end of the resonant cavity 13 is directly communicated with the refrigerant discharge port 12, i.e. no connecting channel 14 is provided. And the upper end of amortization intubate 4 sets up to the cooperation end, and the lower extreme sets up to the stiff end, and wherein, the external diameter of the upper right end of amortization intubate 4 is greater than the external diameter of left lower extreme, and includes from left lower to upper right consecutive tubule section 42, changeover portion 43 and thick pipe section 44, and the one end that tubule section 42 deviate from changeover portion 43 forms to the cooperation end, and the lower extreme of tubule section 42 and the interior wall clearance fit of high-pressure housing 1, simultaneously, the upper end of thick pipe section 44 and the upper end interior wall fixed fit of resonant cavity 13.

Example six

As shown in fig. 7, the sixth embodiment is different from the third embodiment in that it includes: the external diameter of the left lower extreme of amortization intubate 4 is greater than the external diameter of upper right end, and the left lower extreme of amortization intubate 4 constructs to the stiff end promptly, and tubule section 42, changeover portion 43 and thick pipe section 44 link to each other in proper order from upper right to lower left and form complete amortization intubate 4, and the one end that thick pipe section 44 deviates from changeover portion 43 forms to the stiff end, and the one end that tubule section 42 deviates from changeover portion 43 forms to the mating end, and the up end of tubule section 42 and the up end clearance fit of resonant cavity 13, simultaneously, the outer peripheral wall of the lower extreme of thick pipe section 44 and the inner wall fixed fit of the lower extreme of resonant cavity 13. And a first oil return channel 132 is arranged in the bottom space of the resonant cavity 13, and the first oil return channel 132 is used for returning the oil in the resonant cavity 13 to the space where the compression part 20 is located, so that recycling is realized.

In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present invention.

In the description of the invention, a "first feature" or "second feature" may include one or more of such features.

In the description of the present invention, "plurality" means two or more.

In the description of the invention, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, and may also include the first and second features not being in direct contact but being in contact with each other by another feature therebetween.

In the description of the invention, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature.

In the description of the present specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

While embodiments of the present invention have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A high pressure housing assembly for an electric compressor, comprising:

a high-pressure housing (1), wherein a high-pressure chamber (11) and a refrigerant discharge port (12) are formed on the high-pressure housing (1), a compression component (20) of the electric compressor (100) is suitable for discharging compressed refrigerant to the high-pressure chamber (11), and the refrigerant discharge port (12) is used for discharging refrigerant to the outside of the high-pressure housing (1);

the high-pressure shell (1) is further provided with a resonant cavity (13) and an oil cavity (15) which are communicated with each other, the oil cavity (15) is communicated with the high-pressure cavity (11) to receive the refrigerant flowing out of the high-pressure cavity (11), a silencing insertion pipe (4) is arranged in the resonant cavity (13), a circulation channel is defined between the silencing insertion pipe (4) and the inner wall surface of the resonant cavity (13), one end of a pipe cavity in the silencing insertion pipe (4) is communicated with the refrigerant discharge port (12), the silencing insertion pipe (4) is provided with a silencing hole (41) which is used for communicating the pipe cavity with the circulation channel, and the high-pressure shell (1) is configured to discharge the refrigerant entering the circulation channel from the oil cavity (15) into the pipe cavity through the silencing hole (41).

2. A high-pressure housing assembly for an electric compressor as set forth in claim 1, wherein,

One of the first end and the second end of the silencing insertion tube (4) is set as a fixed end and is used for connecting and fixing the silencing insertion tube (4);

the other of the first end and the second end of the silencing insertion tube (4) is set to be a matching end, and the matching end is arranged in a hanging mode.

3. The high-pressure housing assembly for an electric compressor according to claim 2, characterized in that the fitting end of the sound-deadening cannula (4) is mounted in a size such that: t is more than or equal to 0 and less than or equal to 0.2D; wherein T is the suspension height of the matched end, and D is the minimum inner diameter of the silencing insertion tube (4).

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

5. The high-pressure housing assembly for an electric compressor according to claim 1, wherein a first opening (131) for machining the resonance chamber (13) is formed on a surface of the high-pressure housing (1), 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, wherein the first end of the resonance chamber (13) is formed with the first opening (131), the second end of the resonance chamber (13) communicates with the refrigerant discharge port (12) through a connection passage (14), an overflow area of the connection passage (14) is smaller than that of the resonance chamber (13), and the sound-deadening cannula (4) is fixed to an inside wall of the resonance chamber (13) or the connection passage (14).

7. The high-pressure housing assembly for an electric compressor according to claim 6, characterized in that the centre line of the connecting channel (14) coincides with the centre line of the resonance chamber (13), and that both the connecting channel (14) and the resonance chamber (13) are adapted to be shaped by 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) open into the resonance chamber (13); wherein,,

the first end of the silencing insertion tube (4) is fixedly connected with the inner peripheral wall of the mounting groove (213), or the first end of the silencing insertion tube (4) is in clearance fit with the inner peripheral wall of the mounting groove (213).

9. High-pressure housing assembly for an electric compressor according to claim 1, characterized in that a plurality of turns of the sound deadening holes (41) are provided in the axial direction of the sound deadening cannula (4), each turn of the sound deadening holes (41) comprising a plurality of the sound deadening holes (41) provided at intervals in the circumferential direction of the sound deadening cannula (4).

10. A high-pressure housing assembly for an electric compressor as set forth in claim 9, wherein,

the center distance t between the adjacent sound attenuation holes (41) satisfies the following conditions: d is more than or equal to t and less than or equal to 5d;

Wherein d is the equivalent diameter of the hole cross section of the sound deadening holes (41), and d is the equivalent diameter of the sound deadening holes (41) with the largest hole cross section when the hole cross sections of the plurality of sound deadening holes (41) are different in size.

11. The high-pressure housing assembly for an electric compressor according to claim 9, characterized in that the hole section of the sound deadening hole (41) satisfies: d is more than or equal to 0.05 and less than or equal to D; wherein D is the equivalent diameter of the hole section of the sound-deadening hole (41), D is the equivalent diameter of the cross section of the sound-deadening cannula (4), and D is the equivalent diameter of the smallest cross section of the sound-deadening cannula (4) when the sound-deadening cannula (4) is of a variable cross section structure.

12. A high-pressure housing assembly for an electric compressor according to claim 1, characterized in that the resonance chamber (13) is further provided with a first oil return channel (132) in the bottom space in the direction of gravity.

13. The high-pressure housing assembly for an electric compressor according to claim 12, characterized in that the position of the first oil return channel (132) within the resonant cavity (13) satisfies: h is less than or equal to 0.3H; wherein 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 gravity direction, and H is the vertical distance between the highest point and the lowest point of the resonant cavity (13) in the gravity direction.

14. A high-pressure housing assembly for an electric compressor according to claim 1, characterized in that an oil component (3) for oil-gas separation is provided in the oil component chamber (15), and that the refrigerant entering the oil component chamber (15) flows to the resonance chamber (13) after oil-gas separation by the oil component (3).

15. An electric compressor (100), characterized by comprising:

a housing part comprising a high pressure housing assembly for an electric compressor according to any one of claims 1-14;

a compression member (20), wherein an exhaust port (201) of the compression member (20) communicates with the high-pressure chamber (11) to discharge compressed refrigerant into the high-pressure chamber (11);

-a motor part (30), the motor part (30) comprising a motor body (301) and a drive shaft (302), the motor body (301) driving the compression part (20) via the drive shaft (302) to perform a compression operation.

16. The electric compressor (100) of claim 15, wherein the housing member further comprises:

a middle partition plate (103), wherein the compression component (20) and the motor body (301) are respectively arranged at two sides of the middle partition plate (103), and the driving shaft (302) penetrates through the middle partition plate (103) to be connected with the compression component (20);

A low-pressure housing (102), a low-pressure chamber (105) for accommodating the motor body (301) is formed between the low-pressure housing (102) and the middle partition plate (103), a refrigerant suction port (1021) communicating with the low-pressure chamber (105) is formed in the low-pressure housing (102), and the compression member (20) sucks in refrigerant from the low-pressure chamber (105).

17. An air conditioning system (300) characterized by comprising an electric compressor (100) according to any one of claims 15-16.

18. A vehicle (1000) characterized by comprising an air conditioning system (300) according to claim 17.