Horizontal rotary compressor for vehicle and vehicle

Abstract

The horizontal rotary compressor comprises a shell and a compression mechanism, the compression mechanism comprises a bearing assembly and an air cylinder assembly, the air cylinder assembly is arranged on the bearing assembly and comprises at least one air cylinder, and each air cylinder is provided with an air cylinder cavity and a sliding piece groove; a piston rotating eccentrically is arranged in each air cylinder cavity, a sliding piece moving in a reciprocating mode is arranged in each sliding piece groove, one end of each sliding piece abuts against the peripheral wall of the corresponding piston, an air inlet noise reduction channel is formed in the shell or the compression mechanism, one axial end of the air inlet noise reduction channel is open, and the other axial end of the air inlet noise reduction channel is closed. A communication opening communicated with the air cylinder cavity is formed in the circumferential wall of the air inlet noise reduction channel, the distance between the communication opening and the closed end of the air inlet noise reduction channel in the axial direction of the air inlet noise reduction channel is X, X is larger than or equal to 0.1 * pi * (d1 + d2) and smaller than or equal to 0.2 * pi * (d1 + d2), d1 is the diameter of the air cylinder cavity, and d2 is the outer diameter of the piston. Therefore, the compression mechanism can reduce noise on the air suction side and has good sound quality.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of vehicle compressors, in particular to a horizontal rotary compressor for a vehicle and the vehicle. BACKGROUND

[0002] A compressor, for example, an electric compressor, is a core component of a refrigeration device for a vehicle, which generates vibration noise during operation, affecting the noise of the vehicle and easily causing auditory problems. For example, during operation of the compressor, refrigerant enters the compression mechanism from the suction port and is compressed by the change in the cavity volume to discharge high-pressure refrigerant; in this process, due to the change in the cavity volume of the compression mechanism, the fluid state of the refrigerant changes dramatically, causing high-frequency pulsation, which easily occurs during the suction and discharge processes, causing noise problems. SUMMARY

[0003] The present application aims to at least solve one of the technical problems existing in the prior art. To this end, the present application provides a horizontal rotary compressor for a vehicle and the vehicle, which can reduce the noise on the suction side and has good sound quality.

[0004] According to the horizontal rotary compressor for a vehicle according to the first aspect of the present application, the compressor mechanism includes a bearing assembly and a cylinder assembly, the bearing assembly is arranged in the housing, the cylinder assembly is arranged in the housing and on the bearing assembly, the cylinder assembly includes at least one cylinder, each cylinder is provided with a cylinder cavity and a slide groove, each cylinder cavity is provided with an eccentric rotating piston, each slide groove is provided with a reciprocating slide, one end of the slide abuts against the outer peripheral wall of the piston, wherein the housing or the compressor mechanism is formed with an intake silencing passage, one axial end of the intake silencing passage is open and the other axial end is closed, a communication port communicating with the cylinder cavity is formed on the peripheral wall of the intake silencing passage, the distance between the communication port and the closed end of the intake silencing passage in the axial direction of the intake silencing passage is X, 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2), d1 is the diameter of the cylinder cavity, and d2 is the outer diameter of the piston.

[0005] According to the compression mechanism of the embodiment of the present application, by setting an air intake sound-elimination passage with one end open and the other end closed and communicating with the upstream side of the cylinder cavity, a part of the air intake sound-elimination passage can be configured as a blind hole cavity, and 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2) is set, so that the 1 / 4 wavelength frequency corresponding to the above-mentioned blind hole cavity part corresponds to the cavity modal frequency of the suction side space (i.e. the suction cavity) in the cylinder cavity. The sound-elimination frequency of the air intake sound-elimination passage corresponds to the cavity modal frequency of the suction cavity, so as to achieve the purpose of reducing the fluid noise of the suction side and improving the sound quality of the product.

[0006] In some embodiments, the axial direction of the air intake sound-elimination passage is parallel to the axial direction of the compression mechanism; or, in the axial direction of the compression mechanism, the air intake sound-elimination passage extends obliquely from outside to inside and towards the cylinder assembly.

[0007] In some embodiments, the bearing assembly includes a main bearing and a secondary bearing, and the cylinder assembly is clamped between the main bearing and the secondary bearing. The compression mechanism is configured to satisfy any one of the following conditions: condition A1, the air intake sound-elimination passage penetrates the main bearing and extends to the cylinder assembly; condition A2, the air intake sound-elimination passage penetrates the main bearing and the cylinder assembly and extends to the secondary bearing; condition A3, the compression mechanism further includes a sound eliminator arranged on the side of the secondary bearing away from the cylinder assembly, and the air intake sound-elimination passage penetrates the main bearing, the cylinder assembly and the secondary bearing and extends to the sound eliminator; condition A4, the compression mechanism further includes a connecting pipe, a through hole is formed in the secondary bearing, the connecting pipe is fitted in the through hole and at least partially located on the side of the secondary bearing away from the cylinder assembly, one end of the connecting pipe adjacent to the main bearing is open and the other end away from the main bearing is closed, and the air intake sound-elimination passage penetrates the main bearing and the cylinder assembly and extends to the connecting pipe.

[0008] In some embodiments, the compression mechanism is configured to satisfy condition A4, and the compression mechanism further includes a sound eliminator arranged on the side of the secondary bearing away from the cylinder assembly, and the connecting pipe penetrates the sound eliminator and extends to the side of the sound eliminator away from the secondary bearing.

[0009] In some embodiments, the communication port and the suction port of the cylinder cavity are arranged in radial alignment or misalignment with respect to the compression mechanism.

[0010] In some embodiments, the cylinder is a plurality of cylinders, and the communication port is a plurality of communication ports and is arranged one-to-one corresponding to the plurality of cylinders.

[0011] In some embodiments, the plurality of cylinders includes a first cylinder and a second cylinder, the cylinder assembly further includes a partition plate arranged between the first cylinder and the second cylinder, the plurality of communication ports includes a first communication port communicated with the first cylinder and a second communication port communicated with the second cylinder, the first communication port and the second communication port are respectively located on opposite sides of the partition plate, and in the axial direction of the compression mechanism, the first communication port and the second communication port are both arranged adjacent to one end of the corresponding cylinder away from the closed end of the intake silencing passage.

[0012] In some embodiments, the horizontal rotary compressor adopts carbon dioxide as the refrigerant.

[0013] In some embodiments, the horizontal rotary compressor includes a bracket arranged in the shell and separating the internal space of the shell into a low-pressure cavity and a high-pressure cavity, a communication passage is formed in the bracket and communicates the low-pressure cavity and the intake silencing passage, and the compression mechanism is arranged in the high-pressure cavity.

[0014] In some embodiments, the low-pressure cavity is defined between the bracket and the low-pressure shell, the high-pressure cavity is defined between the bracket and the high-pressure shell, the horizontal rotary compressor further includes a cover plate arranged on the side of the low-pressure shell away from the high-pressure shell and defining a receiving cavity with the low-pressure shell, and an electric control structure is arranged in the receiving cavity and electrically connected with the motor.

[0015] The vehicle according to the second aspect of the embodiments of the present application includes the horizontal rotary compressor for vehicle according to the first aspect of the embodiments of the present application.

[0016] The vehicle according to the embodiments of the present application can improve the sound quality of the vehicle by using the horizontal rotary compressor described above.

[0017] Additional aspects and advantages of the present application will be given in part in the following description, become apparent from the following description, or be learned by practice of the present application. BRIEF DESCRIPTION OF DRAWINGS

[0018] The above and / or additional aspects and advantages of the present application will become apparent and be readily understood from the following description, taken in conjunction with the accompanying drawings, in which:

[0019] Figure 1 is a schematic view of a cylinder assembly shown in FIG. 1;

[0020] Figure 2 is a schematic view of a cylinder assembly shown in FIG. 1; Figure 1

[0021] ​Figure 3 is a schematic view of a compression mechanism according to some embodiments of the present application;

[0022] Figure 4 is a schematic view of a compression mechanism according to some embodiments of the present application;

[0023] Figure 5 is a schematic view of a compression mechanism according to some embodiments of the present application;

[0024] Figure 6 is a schematic view of a horizontal rotary compressor according to some embodiments of the present application;

[0025] Figure 7 is a schematic view of a compression mechanism and a bracket shown in Figure 6

[0026] Figure 8 is a schematic view of a compression mechanism according to some embodiments of the present application;

[0027] Figure 9 is a schematic view of a vehicle according to some embodiments of the present application.

[0028] Reference signs:

[0029] Vehicle 300, horizontal rotary compressor 200, housing 101, low-pressure shell 1011, high-pressure shell 1012, gas outlet 1012a, low-pressure cavity 101a, high-pressure cavity 101b, bracket 102, communication passage 102a, communication cavity 102b, motor 103, crankshaft 104, sealing member 105, cover plate 106, containing cavity 106a, electronic control structure 107,

[0030] Compression mechanism 100, intake silencing passage 100a, communication port 100b, first communication port 100c, second communication port 100d,

[0031] Bearing assembly 1, main bearing 11, auxiliary bearing 12, through hole 12a,

[0032] Cylinder assembly 2, cylinder 21, cylinder cavity 21a, suction cavity 21b, exhaust cavity 21c, sliding vane groove 21d, suction port 21e, exhaust port 21f,

[0033] First cylinder 211, second cylinder 212, piston 22, sliding vane 23, partition plate 24,

[0034] Silencer 3, silencing cavity 30, outlet 30a, connecting pipe 4. DETAILED DESCRIPTION

[0035] ​Embodiments of the present application are described below by reference to the accompanying drawings, in which like reference numerals refer to like elements or features in different views. The following detailed description is exemplary in nature and is not intended to limit the scope, applicability, or configuration of the application in any way. Rather, the following description provides a description on various examples of embodiments of the application along with the figures.

[0036] The following disclosure provides many different embodiments, or examples, for implementing different structures of the present application. For purposes of explanation and non- limitation, specific details of certain examples are described. Of course, many modifications can be made to the embodiments described herein, and the embodiments described herein are merely examples and are not intended to limit the present application. In addition, the present application can repeatedly refer to reference numerals and / or letters in different examples. Such repetition is for the purpose of simplification and clarity, and does not indicate a relationship between the various embodiments and / or arrangements being discussed. In addition, the present application provides various specific examples of processes and materials, but those of ordinary skill in the art can appreciate the applicability of other processes and / or the use of other materials.

[0037] In the description of the embodiments of the present application, the term "and / or" is merely an association relationship of the associated objects, which means that there can be three relationships, for example, A and / or B, which can represent the three cases of A alone, A and B together, and B alone. In addition, the character " / " herein generally represents an "or" relationship between the associated objects before and after it.

[0038] Hereinafter, with reference to the accompanying drawings, a horizontal rotary compressor 200 for a vehicle according to an embodiment of the present application is described. In the present embodiment, the horizontal rotary compressor 200 can be a single-cylinder single-discharge compressor, a single-cylinder double-discharge compressor, a double-cylinder compressor, etc.

[0039] As shown in FIG. 1, Figure 6 The horizontal rotary compressor 200 includes a housing 101 and a compression mechanism 100. As shown in FIG. 2, Figure 1 and Figure 2 The compression mechanism 100 includes a bearing assembly 1 and a cylinder assembly 2, the bearing assembly 1 is provided in the housing 101, the cylinder assembly 2 is provided in the housing 101 and on the bearing assembly 1, and the cylinder assembly 2 includes at least one cylinder 21, each cylinder 21 is provided with a cylinder cavity 21a and a vane groove 21d, each cylinder cavity 21a is provided with an eccentrically rotating piston 22, each vane groove 21d is provided with a reciprocating vane 23, one end of the vane 23 abuts against the outer peripheral wall of the piston 22. The vane 23 is movably provided in the vane groove 21d, and the leading end of the vane 23 (the end of the vane 23 closest to the center of the cylinder 21) abuts against the outer peripheral wall of the piston 22.

[0040] For example, the piston 22 can roll along the inner wall of the corresponding cylinder chamber 21a. Under the action of spring force or gas force, the tip of the slide 23 can always abut against the outer peripheral wall of the piston 22. When the piston 22 rotates in the cylinder chamber 21a, the slide 23 moves accordingly in the slide groove 21d, so that the piston 22 and the slide 23 cooperate to divide the cylinder chamber 21a into an intake chamber 21b and an exhaust chamber 21c. The cylinder 21 has an intake port 21e communicating with the intake chamber 21b and an exhaust port 21f communicating with the exhaust chamber 21c; compression When mechanism 100 is used in a compressor, each piston 22 can be fitted onto the eccentric part of the crankshaft 104 of the compressor. The motor 103 drives the crankshaft 104 to rotate, and the piston 22, driven by the crankshaft 104, closely adheres to the inner wall of the cylinder chamber 21a and rolls along the inner wall of the cylinder chamber 21a to compress the refrigerant, so that the refrigerant enters the intake chamber 21b through the intake port. The piston 22 rolls along the inner wall of the cylinder chamber 21a to compress the refrigerant, and the refrigerant continuously heats up and pressurizes, and enters the exhaust chamber 21c, and then is discharged from the cylinder assembly 2 through the exhaust port.

[0041] An intake muffler channel 100a is formed on the housing 101 or the compression mechanism 100. One axial end of the intake muffler channel 100a is open, and the other axial end of the intake muffler channel 100a is closed. A connecting port 100b is formed on the peripheral wall of the intake muffler channel 100a, which connects to the cylinder cavity 21a. The intake muffler channel 100a is connected to the upstream side of the cylinder cavity 21a. Low-pressure refrigerant can flow through the aforementioned axial end of the intake muffler channel 100a to the intake muffler channel 100a, and then flow through the connecting port 100b to the cylinder cavity 21a for compression. In the axial direction of the intake muffler channel 100a, the distance between the connecting port 100b and the closed end of the intake muffler channel 100a (i.e., the other end of the intake muffler channel 100a in the aforementioned axial direction) is X, 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2), where d1 is the diameter of the cylinder chamber 21a, d2 is the outer diameter of the piston 22, and π is pi.

[0042] For example, in Figure 1 In the example, on the axial direction of the intake muffler channel 100a (which can be simply understood as the approximate flow direction of the airflow in the intake muffler channel 100a), the distance between the center of the connecting port 100b and the closed end of the intake muffler channel 100a is X, X=k*π*(d1+d2), k is a design parameter, and 0.1≤k≤0.2.

[0043] It is understandable that when the intake muffler channel 100a is formed on the compression mechanism 100, a part of the intake muffler channel 100a can be formed on the bearing assembly 1, and another part of the intake muffler channel 100a can be formed on the cylinder assembly 2.

[0044] It is found through research that the continuously changing volume of the compression mechanism cavity will be accompanied by a dramatic change in the fluid state of the refrigerant, causing high-frequency pulsation. Such high-frequency pulsation is prone to resonance with the cavity mode of the space in which it is located, thereby causing noise problems. Therefore, in the embodiments of the present application, the intake sound-attenuating channel 100a, which is open at one end and closed at the other end and is connected to the upstream side of the cylinder cavity 21a, is provided so that part of the intake sound-attenuating channel 100a can be configured as a blind hole cavity. Such a one-sided closed blind hole cavity can reflect sound waves, and the reflected sound waves can superimpose with the noise source to achieve noise reduction, thereby having a sound-attenuating effect for a specific frequency in terms of the transmission and reverse characteristics of sound waves. The condition 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2) is set to make the 1 / 4 wavelength frequency corresponding to the above-mentioned blind hole cavity part correspond to the cavity mode frequency of the suction side space (i.e., the suction cavity 21b) in the cylinder cavity 21a. Therefore, the sound-attenuating frequency of the intake sound-attenuating channel 100a corresponds to the cavity mode frequency of the suction cavity 21b, thereby achieving the purpose of reducing the fluid noise on the suction side.

[0045] The noise reduction performance test is performed with X=k*π*(d1+d2), and the results are shown in Figure 8 The horizontal axis is the parameter k, and the vertical axis is the noise reduction sound pressure in dB. It can be seen from Figure 8 that when k is between 0.1 and 0.2, the intake sound-attenuating channel 100a has good noise reduction effect, and can basically achieve a noise reduction of more than 10 dB. When k is 0.15, the noise reduction is more than 50 dB. Of course, k can also be 0.1, 0.11, 0.12, 0.13, 0.14, 0.155, 0.16, 0.174, 0.18, 0.192, or 0.2, etc.

[0046] It can be understood that when the communication port 100b is one, the position of the communication port 100b in the axial direction of the intake silencing passage 100a satisfies 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2), and when the communication port 100b is multiple, the position of each communication port 100b in the axial direction of the intake silencing passage 100a satisfies 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2) respectively, for example, the multiple communication ports 100b can be arranged at intervals along the axial direction of the intake silencing passage 100a, and the multiple communication ports 100b are respectively a first communication port 100c, a second communication port 100d, …, and an n-th communication port, the distance between the first communication port 100c and the closed end of the intake silencing passage 100a in the axial direction of the intake silencing passage 100a is X1, the distance between the second communication port 100d and the closed end of the intake silencing passage 100a in the axial direction of the intake silencing passage 100a is X2, …, and the distance between the n-th communication port and the closed end of the intake silencing passage 100a in the axial direction of the intake silencing passage 100a is Xn, X1, X2, …, Xn are all located in the range of 0.1*π*(d1+d2)~0.2*π*(d1+d2).

[0047] According to the horizontal rotary compressor 200 for a vehicle in the embodiment of the present application, by arranging an intake silencing passage 100a which is open at one end and closed at the other end and communicates with the upstream side of the cylinder cavity 21a on the shell 101 or the compression mechanism 100, a part of the intake silencing passage 100a can be configured as a blind hole cavity, and 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2) is arranged, so that the 1 / 4 wavelength frequency corresponding to the above-mentioned blind hole cavity part corresponds to the cavity modal frequency of the suction side space (i.e. the suction cavity 21b) in the cylinder cavity 21a, then the silencing frequency of the intake silencing passage 100a corresponds to the cavity modal frequency of the suction cavity 21b, so as to achieve the purpose of reducing the fluid noise on the suction side and improving the sound quality of the product.

[0048] It can be understood that in the embodiment of the present application, the intake silencing passage 100a can extend along a straight line and / or a curve, for example, the intake silencing passage 100a includes multiple straight passage segments which are sequentially communicated.

[0049] Further, in the embodiments of the present application, when the air intake muffling passage 100a is formed on the housing 101, the communication port 100b can be formed on the inner circumferential wall of the housing 101. When the air intake muffling passage 100a is formed on the compression mechanism 100, the communication port 100b can be formed on the corresponding cylinder 21; or the communication port 100b can be formed on the cylinder 21 and the bearing assembly 1, for example, the cylinder assembly 2 includes the first cylinder 211 and the main bearing 11 and the auxiliary bearing 12 arranged on both sides of the first cylinder 211, the first communication port 100c corresponding to the first cylinder 211 is formed on the first cylinder 211 and the main bearing 11, at this time, a part of the first communication port 100c is formed on the first cylinder 211 and the other part of the first communication port 100c is formed on the main bearing 11; or the communication port 100b can be formed on the cylinder 21 and the partition plate 24, for example, the cylinder assembly 2 includes the first cylinder 211, the second cylinder 212 and the partition plate 24, the partition plate 24 is arranged between the first cylinder 211 and the second cylinder 212, the second communication port 100d corresponding to the second cylinder 212 is formed on the second cylinder 212 and the partition plate 24, at this time, a part of the second communication port 100d is formed on the second cylinder 212 and the other part of the second communication port 100d is formed on the partition plate 24.

[0050] In some embodiments, as shown in Figure 1 , Figures 3-5 the axial direction of the air intake passage is parallel to the axial direction of the compression mechanism 100, the central axis L1 of the air intake muffling passage 100a is parallel to the central axis L2 of the compression mechanism 100, the air intake muffling passage 100a can extend along a straight line, which is convenient for simplifying the structure of the air intake muffling passage 100a and facilitating molding; or in the axial direction of the compression mechanism 100, the air intake muffling passage 100a extends obliquely from outside to inside and towards the cylinder assembly 2, so that the distance between the air intake muffling passage 100a and the cylinder assembly 2 in the radial direction of the compression mechanism 100 can be reduced along the airflow direction, which is convenient for adapting to the scene where the axial direction of the air intake hole of the cylinder cavity 21a is inclined relative to the radial direction of the compression mechanism 100.

[0051] Of course, whether the axial direction of the air intake passage is parallel to the axial direction of the compression mechanism 100 or not, it can be applied to the scene where the axial direction of the air intake hole is parallel or not parallel to the radial direction of the compression mechanism 100.

[0052] It can be understood that in the description of the present application, the axial direction of the compression mechanism 100 is the extension direction of the central axis L2 of the compression mechanism 100, the circumferential direction of the compression mechanism 100 is the direction around the central axis L2, and the radial direction of the compression mechanism 100 is the direction in the radial plane perpendicular to the central axis L2 and passing through the central axis L2.

[0053] In some embodiments, as shown in Figure 1 ,Figures 3-5 As shown, the bearing assembly 1 includes a main bearing 11 and a sub bearing 12, and the cylinder assembly 2 is sandwiched between the main bearing 11 and the sub bearing 12, and the main bearing 11 and the sub bearing 12 can stably support the cylinder assembly 2. The compression mechanism 100 is configured to satisfy any one of the following conditions: condition A1, the intake silencing passage 100a penetrates the main bearing 11 and extends to the cylinder assembly 2; condition A2, the intake silencing passage 100a penetrates the main bearing 11 and the cylinder assembly 2 and extends to the sub bearing 12; condition A3, the compression mechanism 100 further includes a silencer 3 arranged on the side of the sub bearing 12 away from the cylinder assembly 2, and the intake silencing passage 100a penetrates the main bearing 11, the cylinder assembly 2 and the sub bearing 12 and extends to the silencer 3; condition A4, the compression mechanism 100 further includes a connecting pipe 4, and the sub bearing 12 is formed with a through hole 12a, the connecting pipe 4 is arranged in the through hole 12a and at least partially located on the side of the sub bearing 12 away from the cylinder assembly 2, one end of the connecting pipe 4 adjacent to the main bearing 11 is open and the other end away from the main bearing 11 is closed, and the intake silencing passage 100a penetrates the main bearing 11 and the cylinder assembly 2 and extends to the connecting pipe 4.

[0054] As shown, the compression mechanism 100 satisfies the condition A1, the intake silencing passage 100a does not penetrate the cylinder assembly 2, and the closed end of the intake silencing passage 100a is formed in the cylinder assembly 2; as shown, the compression mechanism 100 satisfies the condition A2, the intake silencing passage 100a does not penetrate the sub bearing 12, and the closed end of the intake silencing passage 100a is formed in the sub bearing 12; as shown, the compression mechanism 100 satisfies the condition A3, the intake silencing passage 100a does not penetrate the silencer 3, and the closed end of the intake silencing passage 100a is formed in the silencer 3; as shown, the compression mechanism 100 satisfies the condition A4, the intake passage does not penetrate the connecting pipe 4, and the closed end of the intake silencing passage 100a is formed in the connecting pipe 4. Figure 1 Figure 2 Figure 4 Figure 5

[0055] Therefore, the closed end of the intake silencing passage 100a is more flexible to set, so as to make the closed end of the intake silencing passage 100a have different setting positions relative to the cylinder assembly 2, so as to flexibly adjust the distance X between the communication port 100b and the closed end, so that X can better match different specifications of the compression mechanism 100 under the premise of satisfying the above conditions, and improve the structural flexibility and applicability of the compression mechanism 100.

[0056] It can be understood that when the compression mechanism 100 satisfies the condition A4, the connecting pipe 4 cooperates with the through hole 12a, which can include the following multiple examples: 1, the connecting pipe 4 can be arranged in the entire through hole 12a (as shown in Figure 5 ​​​​3、the connecting pipe 4 extends through the through hole 12a and protrudes from the main bearing 11, and the other part of the circumferential wall of the through hole 12a can be used to define the intake silencing passage 100a; 4、the entire connecting pipe 4 is arranged on the side of the auxiliary bearing 12 away from the main bearing 11, and the connecting pipe 4 is arranged opposite to the through hole 12a. The connecting mode between the connecting pipe 4 and the auxiliary bearing 12 is not specifically limited in the embodiments of the present application. For example, the connecting pipe 4 can be interference-fitted in the through hole 12a, or the connecting pipe 4 can be welded to the auxiliary bearing 12.

[0057] In some embodiments, as shown in Figure 5 , the compression mechanism 100 is configured to meet the condition A4, and the compression mechanism 100 further comprises a silencer 3 arranged on the side of the auxiliary bearing 12 away from the cylinder assembly 2, a connecting pipe 4 penetrating the silencer 3, and the connecting pipe 4 extending to the side of the silencer 3 away from the auxiliary bearing 12. At this time, since the closed end of the intake silencing passage 100a is formed in the connecting pipe 4, the axial position restriction of the closed end of the intake silencing passage 100a by the silencer 3 can be broken, so that the axial position of the closed end of the intake silencing passage 100a can be flexibly set, and it is convenient to avoid excessive adjustment of the structure of the silencer 3, which is conducive to reducing the cost.

[0058] In some embodiments, as shown in Figure 1 , Figures 3-5 , the communication port 100b and the suction port 21e of the cylinder cavity 21a are arranged opposite along the radial direction of the compression mechanism 100, so that the flow channel 21g between the communication port 100b and the suction port 21e can extend along the radial direction of the compression mechanism 100, which is convenient for reducing the machining difficulty of the flow channel 21g. Of course, in other embodiments of the present application, the communication port 100b and the suction port 21e can also be arranged in a radial direction offset manner along the compression mechanism 100, so that the center of the communication port 100b and the center of the suction port 21e are arranged in an axial direction interval manner along the compression mechanism 100, and at this time, the flow channel 21g between the communication port 100b and the suction port 21e can extend in an inclined manner relative to the axial direction of the compression mechanism 100, which is conducive to reducing the change amount of the flow direction of the gas flow at the communication port 100b, and is conducive to reducing the pressure loss.

[0059] In some embodiments, as shown in Figure 1 , Figures 3-5As shown, there are multiple cylinders 21 and multiple connecting ports 100b, with each connecting port 100b corresponding to one of the multiple cylinders 21. It is evident that the intake silencing channel 100a allows air intake for multiple cylinders 21, which is beneficial for improving the output capacity of the compression mechanism 100 and reducing the intake noise of the multiple cylinders 21. Optionally, if the multiple cylinders 21 have the same specifications, then the diameter of the cylinder chamber 21b is the same, and the outer diameter of the piston 22 located in the cylinder chamber 21b is the same.

[0060] Of course, in other embodiments of this application, there may be only one cylinder 21.

[0061] In some embodiments, such as Figure 1 , Figures 3-5 As shown, the plurality of cylinders 21 include a first cylinder 211 and a second cylinder 212. The cylinder assembly 2 also includes a partition 24 disposed between the first cylinder 211 and the second cylinder 212 to separate the cylinder chamber 21a of the first cylinder 211 and the cylinder chamber 21a of the second cylinder 212. The plurality of connecting ports 100b include a first connecting port 100c connected to the first cylinder 211 and a second connecting port 100d connected to the second cylinder 212. The first connecting port 100c and the second connecting port 100d are respectively located on opposite sides of the partition 24. In the axial direction of the compression mechanism 100, the first connecting port 100c and the second connecting port 100d are both located near the end of the corresponding cylinder 21 that is away from the closed end of the intake muffler channel 100a. This allows for a reasonable setting of the positions of the first connecting port 100c and the second connecting port 100d, which helps to appropriately reduce the distance between the closed end of the intake muffler channel 100a and the main bearing 11 to a certain extent, thereby saving space occupied by the compression mechanism 100.

[0062] Of course, if the compression mechanism 100 has sufficient arrangement space, the positions of the first connecting port 100c and the second connecting port 100d are not limited to being located at the end of the corresponding cylinder 21 away from the closed end of the intake muffler channel 100a. For example, the first connecting port 100c and the second connecting port 100d can be located in the middle of the corresponding cylinder 21 or at the end of the corresponding cylinder 21 adjacent to the closed end of the intake muffler channel 100a in the axial direction of the compression mechanism 100.

[0063] In other embodiments of this application, if there is only one cylinder 21, the communication port 100b corresponding to the cylinder 21 can be located near the end of the cylinder 21 away from the closed end of the intake muffler channel 100a, or near the end of the cylinder 21 close to the closed end of the intake muffler channel 100a, or located in the middle position of the cylinder 21 in the axial direction.

[0064] In some embodiments, the horizontal rotary compressor 200 uses carbon dioxide as the refrigerant, thus the horizontal rotary compressor 200 can be a carbon dioxide compressor. For example, carbon dioxide has relatively high suction and discharge pressures when used as a refrigerant, and it also has good thermodynamic properties. Therefore, when the same cooling capacity is required, using carbon dioxide as the refrigerant reduces the volume required for the compressor's compression chamber, allowing for a smaller volume and thus reducing the overall size and weight of the compressor. Furthermore, compressors using carbon dioxide can operate over a wider pressure range, exhibiting stable performance whether performing initial compression under low pressure or deep compression under high pressure. Therefore, the horizontal rotary compressor 200 of this application embodiment facilitates obtaining an optimized compression ratio, provides efficient cooling performance when used in a refrigeration system, and can reduce energy consumption and improve energy utilization.

[0065] While achieving a high compression ratio using a carbon dioxide compressor can lead to abnormal phenomena such as surge and vibration, affecting the normal operation of the system, this high compression ratio can also cause increased pressure fluctuations, impacting the normal operation of other equipment. Therefore, this application proposes an improvement to the horizontal rotary compressor to mitigate the vibration and noise issues arising from using carbon dioxide as the refrigerant to achieve a high compression ratio.

[0066] In some embodiments, such as Figure 6 As shown, the system includes a housing 101, a bracket 102, and a motor 103. The bracket 102 is located on the housing 101 and divides the internal space of the housing 101 into a low-pressure chamber 101a and a high-pressure chamber 101b. The compression mechanism 100 is located in the high-pressure chamber 101b, and the intake silencer channel 100a is connected to the low-pressure chamber 101a. The motor 103 is located in the low-pressure chamber 101a. The structure of the motor 103 can be used to drive the compression mechanism 100 to compress the refrigerant. At this time, the low-pressure chamber 101a provides space for the motor 103. In this way, the bracket 102 can isolate the high-temperature and high-pressure gas inside the housing 101 from the thermal impact on the motor 103, reduce the risk of performance degradation or even damage to the motor 103 due to overheating, thereby helping to reduce the operating temperature of the motor 103, reduce the heat dissipation burden, extend the service life of the motor 103, improve the working stability and reliability of the horizontal rotary compressor 200, and reduce the risk of shutdown of the horizontal rotary compressor 200 caused by motor 103 failure.

[0067] It is understood that an air inlet and an air outlet 1012a are formed on the housing 101. The air inlet is connected to the low-pressure chamber 101a, and the air outlet 1012a is connected to the high-pressure chamber 101b. The refrigerant flows from the air inlet to the low-pressure chamber 101a and flows through the air intake silencer channel 100a to the cylinder chamber 21a for compression. After compression, the refrigerant is finally discharged from the housing 101 through the air outlet. The crankshaft 104 passes through the bearing assembly 1 and the cylinder assembly 2, and the crankshaft 104 passes through the bracket 102 and extends into the low-pressure chamber 101a to be connected to the motor 103 for transmission.

[0068] In some embodiments, such as Figure 6 and Figure 7 As shown, a connecting channel 102a is formed on the bracket 102, which connects the low-pressure chamber 101a and the intake silencer channel 100a. For example, the connecting channel 102a can extend through opposite sides of the bracket 102 along the axial direction of the compression mechanism 100. Therefore, the connection channel 102a allows for reliable intake of the horizontal rotary compressor 200, and the refrigerant flowing into the low-pressure chamber 101a does not need to flow through the external space of the housing 101, simplifying the sealing configuration of the horizontal rotary compressor 200.

[0069] In some embodiments, such as Figure 6 As shown, the housing 101 includes a low-pressure housing 1011 and a high-pressure housing 1012 respectively disposed on opposite sides of the support 102. A low-pressure chamber 101a is defined between the support 102 and the low-pressure housing 1011, and a high-pressure chamber 101b is defined between the support 102 and the high-pressure housing 1012. The horizontal rotary compressor 200 also includes a cover plate 106 and an electrical control structure 107. The cover plate 106 is disposed on the side of the low-pressure housing 1011 away from the high-pressure housing 1012, and a receiving cavity 106a is defined between the cover plate 106 and the low-pressure housing 1011. The electrical control structure 107 is disposed in the receiving cavity 106a and is electrically connected to the motor 103. Therefore, under the premise of achieving a reliable connection between the electronic control structure 107 and the motor 103 so as to achieve reliable control of the motor 103, the distance between the electronic control structure 107 and the motor 103 is relatively close, which facilitates the electrical connection between the two. In addition, when the refrigerant flows through the low-pressure shell 1011, the temperature of the low-pressure shell 1011 is relatively low, and the temperature of the receiving cavity 106a is also relatively low, which facilitates a certain degree of cooling of the electronic control structure 107 and is beneficial to the heat dissipation of the electronic control structure 107. Furthermore, the refrigerant is separated from the electronic control structure 107 and does not come into contact with it, so it is not easy to affect the operation of the electronic control structure 107.

[0070] For example, a connecting channel 102a is formed on the bracket 102, the connecting channel 102a connects to the low-pressure chamber 101a, the housing 101 includes a low-pressure housing 1011 and a high-pressure housing 1012, the low-pressure housing 1011 and the bracket 102 define a low-pressure chamber 101a, the high-pressure housing 1012 and the bracket 102 define a high-pressure chamber 101b, an intake silencer channel 100a is formed on the high-pressure housing 1012 and connected to the end of the connecting channel 102a away from the low-pressure chamber 101a, the refrigerant in the low-pressure chamber 101a can flow to the intake silencer channel 100a through the connecting channel 102a.

[0071] In some embodiments, the housing 101 includes a low-pressure housing 1011 and a high-pressure housing 1012, with a bracket 102 sandwiched between the low-pressure housing 1011 and the high-pressure housing 1012. A low-pressure cavity 101a is defined between the bracket 102 and the low-pressure housing 1011, and a high-pressure cavity 101b is defined between the bracket 102 and the high-pressure housing 1012. A sealing element 105 is provided between the bracket 102 and the low-pressure housing 1011, and / or between the bracket 102 and the high-pressure housing 1012. Optionally, the sealing element 105 is a gasket.

[0072] According to a second aspect embodiment of the present invention, a vehicle 300 includes the horizontal rotary compressor 200 for a vehicle described in the first aspect embodiment of this application. This improves the sound quality of the vehicle 300. It is worth noting that the specific type of vehicle 300 referred to in this application is not limited. For example, the vehicle 300 can be a gasoline-powered vehicle, a natural gas-powered vehicle, or a new energy vehicle. New energy vehicles can be pure electric vehicles, hybrid electric vehicles, fuel cell electric vehicles, range-extended electric vehicles, solar-powered electric vehicles, gas fuel vehicles (e.g., hydrogen engine vehicles), or biofuel vehicles (e.g., vehicles powered by ethanol, biodiesel, etc.).

[0073] Other configurations and operations of the vehicle 300 according to embodiments of the present invention are known to those skilled in the art and will not be described in detail here.

[0074] The following is for reference. Figures 1-7 A horizontal rotary compressor 200 according to an embodiment of the present invention is described in detail with reference to four specific embodiments. It is to be understood that the following description is merely illustrative and not intended to limit the invention in any specific way.

[0075] Example 1

[0076] In this embodiment, as Figure 1 , Figure 2 , Figure 6 and Figure 7As shown, the horizontal rotary compressor 200 includes a housing 101, a support 102, a motor 103, a compression mechanism 100, and a crankshaft 104. The support 102 is disposed on the housing 101 and divides the internal space of the housing 101 into a low-pressure chamber 101a and a high-pressure chamber 101b. The motor 103 is disposed in the low-pressure chamber 101a, and the compression mechanism 100 is disposed in the high-pressure chamber 101b. The crankshaft 104 passes through the compression mechanism 100 and the support 102 and extends into the low-pressure chamber 101a to be connected to the motor 103.

[0077] The compression mechanism 100 includes a bearing assembly 1 and a cylinder assembly 2. The bearing assembly 1 includes a main bearing 11 and a secondary bearing 12 located on opposite sides of the cylinder assembly 2. The cylinder assembly 2 includes two cylinders 21 and a partition plate 24. Each cylinder 21 has a cylinder chamber 21a and a vane groove 21d. Each cylinder chamber 21a contains an eccentrically rotating piston 22, which is fitted onto the eccentric portion of the crankshaft 104. Each vane groove 21d contains a reciprocating vane 23, one end of which abuts against the outer peripheral wall of the piston 22, thereby dividing the cylinder chamber 21a into an intake chamber 21b and an exhaust chamber 21c. The intake chamber 21b has an intake port 21e, and the exhaust chamber 21c has an exhaust port 21f.

[0078] An intake silencer channel 100a is formed on the compression mechanism 100. One axial end of the intake silencer channel 100a is open and is connected to the low-pressure chamber 101a through the connecting channel 102 on the bracket 102. The other axial end of the intake silencer channel 100a is closed. A connecting port 100b is formed on the peripheral wall of the intake silencer channel 100a, which connects to the intake chamber 21b (or the intake port 21e). There are two connecting ports 100b, which correspond one-to-one with the two cylinders 21.

[0079] The two cylinders 21 are the first cylinder 211 and the second cylinder 212, respectively. The first cylinder 211 is set with the main bearing 11 and the second cylinder 212 is set with the auxiliary bearing 12. The two connecting ports 100b are the first connecting port 100c and the second connecting port 100d, respectively. The first connecting port 100c is connected to the intake chamber 21b of the first cylinder 211 and the second connecting port 100d is connected to the intake chamber 21b of the second cylinder 212.

[0080] The compression mechanism 100 also includes a muffler 3, which is located on the side of the auxiliary bearing 12 away from the cylinder assembly 2 and defines a muffler cavity 30 between the muffler 3 and the auxiliary bearing 12. The muffler cavity 30 is connected to the exhaust cavity 21c of the second cylinder 212. The muffler cavity 30 has an outlet 30a, which is connected to the exhaust port 1012a through the high pressure cavity 101b.

[0081] A connecting cavity 102b is defined between the bracket 102 and the main bearing 11. The connecting cavity 102b is connected to the exhaust cavity 21c of the first cylinder 211. The compression mechanism 100 also has a channel (not shown in the figure) connecting the connecting cavity 102b and the muffler cavity 30. The refrigerant compressed by the first cylinder 211 can flow to the muffler cavity 30 through the connecting channel 102a and the aforementioned channel. The refrigerant compressed by the second cylinder 212 can flow to the muffler cavity 30, and after converging, it is discharged to the outlet 1012a through the outlet 30a.

[0082] It is understood that the natural frequency of the cavity is usually related to the piston rotation angle, the cylinder cavity diameter, and the piston outer diameter. The piston rotation angle usually changes with the working conditions of the compression mechanism. In this embodiment, the common working conditions of the compression mechanism are selected, and the piston rotation angle is selected as the rotation angle at the moment the valve plate opens. It is set on the axial direction of the intake muffler channel 100a. The distance between the first connecting port 100c and the closed end of the intake muffler channel 100a is X1, and the distance between the second connecting port (100d) and the closed end of the intake muffler channel 100a is X2. 0.1*π*(d1+d2)≤X1≤0.2*π*(d1+d2), 0.1*π*(d1+d2)≤X2≤0.2*π*(d1+d2), where X1>X2, d1 is the diameter of the cylinder cavity 21a, d2 is the outer diameter of the piston 22, and the two cylinders 21 have the same specifications.

[0083] The intake muffler channel 100a passes through the main bearing 11 and extends to the cylinder assembly 2. The main bearing 11 forms a first channel section, the first cylinder 211 forms a second channel section, the middle partition 24 forms a third channel section, and the second cylinder 212 forms a fourth channel section. The intake muffler channel 100a includes the first channel section, the second channel section, the third channel section, and the fourth channel section. The fourth channel section is roughly a blind hole cavity, so that the closed end of the intake muffler channel 100a is formed in the second cylinder 212.

[0084] Example 2

[0085] like Figure 3 As shown, the structure of this embodiment is roughly the same as that of Embodiment 1, with the same reference numerals used for the same components. The difference is that the intake muffler channel 100a passes through the main bearing 11 and the cylinder assembly 2 and extends to the auxiliary bearing 12. The main bearing 11 forms a first channel section, the first cylinder 211 forms a second channel section, the middle partition 24 forms a third channel section, the second cylinder 212 forms a fourth channel section, and the auxiliary bearing 12 forms a fifth channel section. The intake muffler channel 100a includes the first channel section to the fifth channel section. The fifth channel section is roughly a blind cavity, so that the closed end of the intake muffler channel 100a is formed at the auxiliary bearing 12.

[0086] Example 3

[0087] like Figure 4 As shown, the structure of this embodiment is roughly the same as that of Embodiment 1, with the same reference numerals used for the same components. The difference is that the intake muffler channel 100a passes through the main bearing 11, the cylinder assembly 2 and the auxiliary bearing 12, and extends to the muffler 3. The main bearing 11 forms a first channel section, the first cylinder 211 forms a second channel section, the middle partition 24 forms a third channel section, the second cylinder 212 forms a fourth channel section, the auxiliary bearing 12 forms a fifth channel section, and the muffler 3 forms a sixth channel section. The intake muffler channel 100a includes the first channel section to the sixth channel section. The sixth channel section is roughly a blind cavity, so that the closed end of the intake muffler channel 100a is formed in the muffler 3.

[0088] Example 4

[0089] like Figure 5 As shown, the structure of this embodiment is roughly the same as that of Embodiment 1, with the same reference numerals used for the same components. The difference is that the intake muffler channel 100a passes through the main bearing 11 and the cylinder assembly 2 and extends to the connecting pipe 4. The connecting pipe 4 passes through the through hole 12a on the secondary bearing 12 and covers the entire wall of the through hole 12a, and passes through the muffler 3 and even the side of the muffler 3 away from the secondary bearing 12. Thus, the main bearing 11 forms a first channel section, the first cylinder 211 forms a second channel section, the middle partition 24 forms a third channel section, the second cylinder 212 forms a fourth channel section, and the connecting pipe 4 forms a fifth channel section. The intake muffler channel 100a includes the first channel section to the fifth channel section. The fifth channel section is roughly a blind cavity, so that the closed end of the intake muffler channel 100a is formed in the connecting pipe 4.

[0090] Furthermore, it should be noted that the various specific technical features described in the above specific embodiments can be combined in any suitable manner without contradiction. To avoid unnecessary repetition, this application will not describe the various possible combinations separately. In addition, various different embodiments of this application can also be arbitrarily combined, as long as they do not violate the spirit of this application, they should also be regarded as the content disclosed in this application.

[0091] In the description of this invention, it should be understood that the terms "center," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0092] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0093] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0094] Although embodiments of the invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A horizontal rotary compressor for a vehicle, characterized by, The utility model relates to a horizontal rotary compressor for vehicle, which comprises a housing, a compression mechanism, and an intake muffling passage. The compression mechanism comprises a bearing assembly and a cylinder assembly, the bearing assembly is arranged in the housing, the cylinder assembly is arranged in the housing and on the bearing assembly, the cylinder assembly comprises at least one cylinder, each cylinder is provided with a cylinder cavity and a sliding vane slot, each cylinder cavity is provided with an eccentric rotating piston, each sliding vane slot is provided with a reciprocating sliding vane, one end of the sliding vane abuts against the outer peripheral wall of the piston, Wherein, the housing or the compression mechanism is formed with an intake muffling passage, one axial end of the intake muffling passage is open and the other axial end is closed, a communication port communicating with the cylinder cavity is formed on the peripheral wall of the intake muffling passage, the distance between the communication port and the closed end of the intake muffling passage in the axial direction of the intake muffling passage is X, 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2), d1 is the diameter of the cylinder cavity, and d2 is the outer diameter of the piston.

2. The horizontal rotary compressor for vehicle according to claim 1, wherein The axial direction of the intake muffling passage is parallel to the axial direction of the compression mechanism; or In the axial direction of the compression mechanism, the intake muffling passage extends obliquely from outside to inside and towards the cylinder assembly. The bearing assembly comprises a main bearing and a secondary bearing, the cylinder assembly is clamped between the main bearing and the secondary bearing, and the compression mechanism is configured to satisfy any one of the following conditions:

3. The horizontal rotary compressor for a vehicle according to claim 1, characterized by, Condition A1, the intake muffling passage penetrates through the main bearing and extends to the cylinder assembly; Condition A2, the intake muffling passage penetrates through the main bearing and the cylinder assembly and extends to the secondary bearing; Condition A3, the compression mechanism further comprises a muffler arranged on the side of the secondary bearing away from the cylinder assembly, the intake muffling passage penetrates through the main bearing, the cylinder assembly and the secondary bearing and extends to the muffler; Condition A4, the compression mechanism further comprises a connecting pipe, the secondary bearing is formed with a through hole, the connecting pipe is fitted in the through hole and at least partially located on the side of the secondary bearing away from the cylinder assembly, one end of the connecting pipe adjacent to the main bearing is open and the other end away from the main bearing is closed, and the intake muffling passage penetrates through the main bearing and the cylinder assembly and extends to the connecting pipe. The compression mechanism is configured to satisfy condition A4, the compression mechanism further comprises a muffler arranged on the side of the secondary bearing away from the cylinder assembly, and the connecting pipe penetrates through the muffler and extends to the side of the muffler away from the secondary bearing.

4. The horizontal rotary compressor for a vehicle according to claim 3, characterized by, The communication port and the suction port of the cylinder cavity are arranged in radial alignment or misalignment with respect to the compression mechanism.

5. The horizontal rotary compressor for a vehicle according to claim 1, characterized by, The cylinder is a plurality of cylinders, the communication port is a plurality of communication ports and is arranged in one-to-one correspondence with the plurality of cylinders.

6. The horizontal rotary compressor for a vehicle according to claim 1, characterized by, ​ 7. The horizontal rotary compressor for a vehicle according to claim 6, characterized by, The plurality of cylinders includes a first cylinder and a second cylinder, and the cylinder assembly further includes a partition plate arranged between the first cylinder and the second cylinder, and the plurality of communication ports includes a first communication port communicated with the first cylinder and a second communication port communicated with the second cylinder, and the first communication port and the second communication port are respectively located on opposite sides of the partition plate, In the axial direction of the compression mechanism, the first communication port and the second communication port are respectively arranged adjacent to one end of the corresponding cylinder away from the closed end of the intake silencing channel.

8. The horizontal rotary compressor for a vehicle according to claim 1, characterized by, The horizontal rotary compressor adopts carbon dioxide as the refrigerant.

9. The horizontal rotary compressor for a vehicle according to any one of claims 1-8, characterized by, The horizontal rotary compressor comprises: a bracket arranged in the shell and separating the internal space of the shell into a low-pressure cavity and a high-pressure cavity, a communication channel being formed in the bracket and communicating the low-pressure cavity and the intake silencing channel, and the compression mechanism being arranged in the high-pressure cavity; a motor arranged in the low-pressure cavity.

10. The horizontal rotary compressor for a vehicle according to claim 9, characterized by, The shell comprises a low-pressure shell and a high-pressure shell respectively arranged on opposite sides of the bracket, and the low-pressure cavity is defined between the bracket and the low-pressure shell, and the high-pressure cavity is defined between the bracket and the high-pressure shell, The horizontal rotary compressor further comprises: a cover plate arranged on the side of the low-pressure shell away from the high-pressure shell and defining a receiving cavity together with the low-pressure shell; an electric control structure arranged in the receiving cavity and electrically connected with the motor.

11. A vehicle characterized by comprising: The horizontal rotary compressor for a vehicle according to any one of claims 1-10.

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