Horizontal rotary compressor for a vehicle and vehicle

Abstract

The utility model discloses a horizontal rotary compressor and vehicle for vehicle, horizontal rotary compressor includes casing and compression mechanism, and compression mechanism includes bearing assembly and cylinder subassembly, and cylinder subassembly is established on bearing assembly and includes at least one cylinder, and each cylinder is equipped with cylinder cavity and slide slot, and each cylinder cavity is equipped with eccentrically rotating piston, and each slide slot is equipped with reciprocating slide, and one end of slide stops on the outer peripheral wall of piston, wherein, the casing or compression mechanism forms and is provided with the intake silencing passage, and the axial one end of intake silencing passage is open and is provided with the axial other end closed setting, and the peripheral wall of intake silencing passage forms and is provided with the communicating port of cylinder cavity, and in the axial direction of intake silencing passage, the distance between communicating port and the closed end of intake silencing passage is X, 0.1*PI*(d1+d2)X0.2*PI*(d1+d2), and d1 is the diameter of cylinder cavity, and d2 is the outer diameter of piston. Therefore, the compression mechanism can reduce the noise of the suction side, and has good sound quality.

Description

Technical Field

[0001] This utility model relates to the field of automotive compressor technology, and in particular to a horizontal rotary compressor for vehicles and a vehicle. Background Technology

[0002] Compressors, such as electric compressors, are core components of vehicle refrigeration equipment. Their operation generates vibration and noise, affecting vehicle noise levels and potentially causing auditory problems. For example, when a compressor is working, refrigerant enters the compression mechanism from the intake port and is compressed through changes in cavity volume to expel high-pressure refrigerant. During this process, the constantly changing volume of the compression mechanism causes drastic changes in the fluid state of the refrigerant, resulting in high-frequency pulsations. These high-frequency fluid pulsations are prone to occur during both intake and exhaust processes, leading to noise problems. Summary of the Invention

[0003] This invention aims to solve at least one of the technical problems existing in the prior art. To this end, this invention proposes a horizontal rotary compressor for vehicles and a vehicle, wherein the horizontal rotary compressor can reduce intake-side noise and has good sound quality.

[0004] A horizontal rotary compressor for a vehicle according to a first aspect of the present invention includes: a housing; a compression mechanism, the compression mechanism including a bearing assembly and a cylinder assembly, the bearing assembly being disposed within the housing, the cylinder assembly being disposed within the housing and mounted on the bearing assembly, the cylinder assembly including at least one cylinder, each cylinder having a cylinder chamber and a vane groove, each cylinder chamber having an eccentrically rotating piston, each vane groove having a reciprocating vane, one end of the vane abutting against the piston. An intake muffler channel is formed on the outer peripheral wall of the housing or the compression mechanism. One axial end of the intake muffler channel is open and the other axial end is closed. A communication port connecting the cylinder cavity is formed on the peripheral wall of the intake muffler channel. The distance between the communication port and the closed end of the intake muffler channel in the axial direction is X, where 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 this utility model embodiment, by setting an intake silencer channel with one end open and the other end closed on the compression mechanism and connected to the upstream side of the cylinder cavity, a part of the intake silencer channel can be constructed as a blind 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 cavity part corresponds to the cavity modal frequency of the intake side space (i.e., intake cavity) in the cylinder cavity. Then the silencer frequency of the intake silencer channel corresponds to the cavity modal frequency of the intake cavity, thereby achieving the purpose of reducing fluid noise on the intake side and improving the sound quality of the product.

[0006] In some embodiments, the axial direction of the intake muffler channel is parallel to the axial direction of the compression mechanism; or, in the axial direction of the compression mechanism, the intake muffler channel extends obliquely from the outside to the inside toward the cylinder assembly.

[0007] In some embodiments, the bearing assembly includes a main bearing and a secondary bearing, the cylinder assembly is sandwiched between the main bearing and the secondary bearing, and the compression mechanism is configured to satisfy any one of the following conditions: Condition A1, the intake muffler passage passes through the main bearing and extends to the cylinder assembly; Condition A2, the intake muffler passage passes through the main bearing and the cylinder assembly and extends to the secondary bearing; Condition A3, the compression mechanism further includes a muffler disposed on the side of the secondary bearing away from the cylinder assembly, the intake muffler passage passes through the main bearing, the cylinder assembly and the secondary bearing, and extends to the muffler; Condition A4, the compression mechanism further includes a connecting pipe, a through hole is formed on the secondary bearing, the connecting pipe is fitted into the through hole and is 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, the intake muffler passage passes through 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 muffler disposed on the side of the auxiliary bearing opposite to the cylinder assembly, the connecting pipe passing through the muffler and extending to the side of the muffler opposite to the auxiliary bearing.

[0009] In some embodiments, the communication port and the intake port of the cylinder cavity are arranged either directly opposite or offset along the radial direction of the compression mechanism.

[0010] In some embodiments, there are multiple cylinders and multiple communication ports, each corresponding to one of the multiple 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 disposed between the first cylinder and the second cylinder, and the plurality of communication ports include a first communication port communicating with the first cylinder and a second communication port communicating with the second cylinder. 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 both disposed adjacent to the end of the corresponding cylinder that is away from the closed end of the intake muffler channel.

[0012] In some embodiments, the refrigerant used in the horizontal rotary compressor is carbon dioxide.

[0013] In some embodiments, the horizontal rotary compressor includes: a support bracket disposed on the housing and dividing the internal space of the housing into a low-pressure chamber and a high-pressure chamber, the support bracket having a connecting channel connecting the low-pressure chamber and the intake silencer channel, the compression mechanism being disposed in the high-pressure chamber; and a motor being disposed in the low-pressure chamber.

[0014] In some embodiments, the low-pressure cavity is defined between the support and the low-pressure housing, and the high-pressure cavity is defined between the support and the high-pressure housing. The horizontal rotary compressor further includes: a cover plate disposed on the side of the low-pressure housing away from the high-pressure housing, and defining a receiving cavity between the cover plate and the low-pressure housing; and an electrical control structure disposed in the receiving cavity and electrically connected to the motor.

[0015] A vehicle according to a second aspect of the present invention includes a horizontal rotary compressor for a vehicle according to the first aspect of the present invention described above.

[0016] According to the embodiments of the present invention, the vehicle's sound quality can be improved by employing the aforementioned horizontal rotary compressor.

[0017] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0018] The above and / or additional aspects and advantages of this utility model will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0019] Figure 1 This is a schematic diagram of a compression mechanism according to some embodiments of the present invention;

[0020] Figure 2 yes Figure 1 A schematic diagram of the cylinder assembly shown;

[0021] Figure 3 This is a schematic diagram of a compression mechanism according to other embodiments of the present invention;

[0022] Figure 4 This is a schematic diagram of a compression mechanism according to some embodiments of the present invention;

[0023] Figure 5 This is a schematic diagram of a compression mechanism according to some embodiments of the present invention;

[0024] Figure 6 This is a schematic diagram of a horizontal rotary compressor according to some embodiments of the present invention;

[0025] Figure 7 yes Figure 6 A schematic diagram of the compression mechanism and support shown;

[0026] Figure 8 These are the noise reduction performance test results of the compression mechanism according to some embodiments of this utility model;

[0027] Figure 9 This is a schematic diagram of a vehicle according to some embodiments of the present invention.

[0028] Figure label:

[0029] Vehicle 300, horizontal rotary compressor 200, housing 101, low-pressure housing 1011, high-pressure housing 1012, air outlet 1012a, low-pressure chamber 101a, high-pressure chamber 101b, bracket 102, connecting channel 102a, connecting chamber 102b, motor 103, crankshaft 104, seal 105, cover plate 106, receiving cavity 106a, electrical control structure 107.

[0030] Compression mechanism 100, intake silencer channel 100a, connecting port 100b, first connecting port 100c, second connecting port 100d,

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

[0032] Cylinder assembly 2, cylinder 21, cylinder chamber 21a, intake chamber 21b, exhaust chamber 21c, vane groove 21d, intake port 21e, exhaust port 21f.

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

[0034] Silencer 3, Silence chamber 30, Outlet 30a, Connecting pipe 4. Detailed Implementation

[0035] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.

[0036] The following disclosure provides numerous different embodiments or examples for implementing various structures of the present invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. In addition, examples of various specific processes and materials are provided in this invention; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0037] In the description of the embodiments in this application, the term "and / or" is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.

[0038] Hereinafter, with reference to the accompanying drawings, a horizontal rotary compressor 200 for a vehicle according to an embodiment of the present invention will be described. In the embodiments of this application, the horizontal rotary compressor 200 may be a single-cylinder single-exhaust compressor, a single-cylinder double-exhaust compressor, a twin-cylinder compressor, etc.

[0039] like Figure 6 As shown, the horizontal rotary compressor 200 includes a housing 101 and a compression mechanism 100. (As indicated...) Figure 1 and Figure 2 As shown, the compression mechanism 100 includes a bearing assembly 1 and a cylinder assembly 2. The bearing assembly 1 is disposed within the housing 101, and the cylinder assembly 2 is disposed within the housing 101 and mounted on the bearing assembly 1. The cylinder assembly 2 includes at least one cylinder 21. Each cylinder 21 has a cylinder chamber 21a and a vane groove 21d. Each cylinder chamber 21a contains an eccentrically rotating piston 22, and each vane groove 21d contains 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 disposed in the vane groove 21d, and the tip 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] Research has shown that the constantly changing volume of the compressor cavity causes drastic changes in the refrigerant's fluid state, resulting in high-frequency pulsations. These high-frequency pulsations easily resonate with the cavity modes of the space they occupy, leading to noise problems. Therefore, in this embodiment, an intake muffler channel 100a, open at one end and closed at the other, connected to the upstream side of the cylinder cavity 21a, is provided. A portion of the intake muffler channel 100a can be constructed as a blind cavity. This type of single-sided closed blind cavity can reflect sound waves. It can be superimposed on the noise source to achieve noise reduction, thus having a noise reduction effect on a specific frequency in the transmission and reverse characteristics of sound waves. By setting 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2), the 1 / 4 wavelength frequency corresponding to the above-mentioned blind hole cavity part corresponds to the cavity mode frequency of the intake side space (i.e., intake cavity 21b) in the cylinder cavity 21a. Then the noise reduction frequency of the intake noise reduction channel 100a corresponds to the cavity mode frequency of the intake cavity 21b, thereby achieving the purpose of reducing the fluid noise on the intake side.

[0045] The noise reduction performance was tested using X = k * π * (d1 + d2), and the results are as follows: Figure 8 As shown, the horizontal axis represents the parameter k, and the vertical axis represents the noise reduction voltage in dB. Figure 8 As can be seen, when the value of k is between 0.1 and 0.2, the intake muffler channel 100a has a good noise reduction effect, basically achieving a noise reduction of nearly 10dB or more; when k is 0.15, the noise reduction is more than 50dB. 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 there is only one connecting port 100b, its position along the axial direction of the intake muffler channel 100a satisfies 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2). When there are multiple connecting ports 100b, the position of each connecting port 100b along the axial direction of the intake muffler channel 100a satisfies 0.1*π*(d1+d2)≤X≤0.2*π*(d1+d2). For example, multiple connecting ports 100b can be spaced apart along the axial direction of the intake muffler channel 100a, and the multiple connecting ports 100b can be the first connecting port 100c, the second connecting port 100b, the third connecting port 100b, the fourth connecting port 100b, the fifth connecting port 100b, the sixth connecting port 100b, the seventh connecting port 100b, the eleventh ... The first connecting port 100c is located at a distance of X1 between the first connecting port 100c and the closed end of the intake muffler channel 100a along the axial direction. The second connecting port 100d is located at a distance of X2 between the second connecting port 100d and the closed end of the intake muffler channel 100a along the axial direction. The distances between the second connecting port 100d and the closed end of the intake muffler channel 100a along the axial direction are X2, X2, X2, X2, Xn, Xn, all of which are within the range of 0.1*π*(d1+d2)~0.2*π*(d1+d2).

[0047] According to an embodiment of the present invention, a horizontal rotary compressor 200 for vehicles is provided on the housing 101 or the compression mechanism 100, with one end open and the other closed, and connected to the upstream side of the cylinder cavity 21a. A portion of the intake silencer channel 100a can be constructed as a blind 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 blind cavity portion corresponds to the cavity modal frequency of the intake side space (i.e., intake cavity 21b) in the cylinder cavity 21a. Thus, the noise reduction frequency of the intake silencer channel 100a corresponds to the cavity modal frequency of the intake cavity 21b, thereby reducing the fluid noise on the intake side and improving the sound quality of the product.

[0048] It is understood that in the embodiments of this application, the intake muffler channel 100a may extend along a straight line and / or a curve. For example, the intake muffler channel 100a includes multiple sequentially connected straight channel segments.

[0049] Furthermore, in this embodiment, when the intake muffler channel 100a is formed on the housing 101, the connecting port 100b can be formed on the inner peripheral wall of the housing 101. When the intake muffler channel 100a is formed on the compression mechanism 100, the connecting port 100b can be formed on the corresponding cylinder 21; or, the connecting port 100b can be formed on the cylinder 21 and the bearing assembly 1. For example, the cylinder assembly 2 includes a first cylinder 211 and a main bearing 11 and a secondary bearing 12 disposed on both sides of the first cylinder 211. The first connecting port 100c corresponding to the first cylinder 211 can be formed on the first cylinder 211 and the main bearing 11. In this case, a part of the first connecting port 100c is formed on the first cylinder 211 and a part of the main bearing 11 is formed on the main bearing 11. Another part of the first connecting port 100c is formed; or, the connecting port 100b can be formed on the cylinder 21 and the partition plate 24. For example, the cylinder assembly 2 includes a first cylinder 211, a second cylinder 212 and a partition plate 24. The partition plate 24 is located between the first cylinder 211 and the second cylinder 212. The second connecting 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 connecting port 100d is formed on the second cylinder 212 and the other part of the second connecting port 100d is formed on the partition plate 24.

[0050] In some embodiments, such as Figure 1 , Figures 3-5 As shown, the axial direction of the intake muffler channel 100a is parallel to the axial direction of the compression mechanism 100. Therefore, the central axis L1 of the intake muffler channel 100a is parallel to the central axis L2 of the compression mechanism 100. The intake muffler channel 100a can extend in a straight line, which simplifies the structure of the intake muffler channel 100a and facilitates molding. Alternatively, in the axial direction of the compression mechanism 100, the intake muffler channel 100a extends obliquely from the outside to the inside towards the cylinder assembly 2, so that the distance between the intake muffler channel 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 to adapt to the scenario where the axial direction of the intake port of the cylinder cavity 21a is set obliquely relative to the radial direction of the compression mechanism 100.

[0051] Of course, regardless of whether the axial direction of the intake channel is parallel to the axial direction of the compression mechanism 100, it can be applied to scenarios where the axial direction of the intake port is parallel or not parallel to the radial direction of the compression mechanism 100.

[0052] It is understood that in the description of this 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 passing through the central axis L2 in the radial plane perpendicular to the central axis L2.

[0053] In some embodiments, such as Figure 1 , Figures 3-5 As shown, the bearing assembly 1 includes a main bearing 11 and a secondary bearing 12. The cylinder assembly 2 is sandwiched between the main bearing 11 and the secondary bearing 12. The main bearing 11 and the secondary bearing 12 can provide stable support for the cylinder assembly 2. The compression mechanism 100 is configured to satisfy any one of the following conditions: Condition A1, the intake muffler channel 100a passes through the main bearing 11 and extends to the cylinder assembly 2; Condition A2, the intake muffler channel 100a passes through the main bearing 11 and the cylinder assembly 2 and extends to the auxiliary bearing 12; Condition A3, the compression mechanism 100 further includes a muffler 3 located on the side of the auxiliary bearing 12 away from the cylinder assembly 2, 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; Condition A4, the compression mechanism 100 further includes a connecting pipe 4, a through hole 12a is formed on the auxiliary bearing 12, the connecting pipe 4 passes through the through hole 12a and is at least partially located on the side of the auxiliary 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, the intake muffler channel 100a passes through the main bearing 11 and the cylinder assembly 2, and extends to the connecting pipe 4.

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

[0055] Therefore, the closed end of the intake muffler channel 100a is set more flexibly, which makes it easier for the closed end of the intake muffler channel 100a to have different setting positions relative to the cylinder assembly 2, so as to flexibly adjust the distance X between the connecting port 100b and the closed end, so that X can better match the compression mechanism 100 of different specifications under the premise of meeting the above conditions, thereby improving the structural flexibility and applicability of the compression mechanism 100.

[0056] It is understood that when the compression mechanism 100 meets condition A4, the connecting pipe 4 fits into the through hole 12a, which can include the following examples: 1. The connecting pipe 4 can pass through the entire through hole 12a (e.g., Figure 5As shown, the connecting pipe 4 extends out of the through hole 12a at the end furthest from the main bearing 11; 2. The connecting pipe 4 can be fitted to a portion of the peripheral wall of the through hole 12a, with the connecting pipe 4 extending out of the through hole 12a at the end furthest from the main bearing 11. At this time, the other portion of the peripheral wall of the through hole 12a can help define the intake silencing channel 100a; 3. The entire connecting pipe 4 is located on the side of the secondary bearing 12 away from the main bearing 11, with the connecting pipe 4 and the through hole 12a facing each other. The connection method between the connecting pipe 4 and the secondary bearing 12 is not specifically limited in this embodiment. For example, the connecting pipe 4 can be interference-fitted into the through hole 12a, or the connecting pipe 4 can be welded to the secondary bearing 12.

[0057] In some embodiments, such as Figure 5 As shown, the compression mechanism 100 is configured to satisfy condition A4. The compression mechanism 100 also includes a muffler 3 located on the side of the auxiliary bearing 12 away from the cylinder assembly 2. A connecting pipe 4 passes through the muffler 3 and extends to the side of the muffler 3 away from the auxiliary bearing 12. At this time, since the closed end of the intake muffler channel 100a is formed in the connecting pipe 4, the axial position restriction of the closed end of the intake muffler channel 100a by the muffler 3 can be broken, allowing the axial position of the closed end of the intake muffler channel 100a to be flexibly set. Moreover, it is convenient to reduce costs without making too many structural adjustments to the muffler 3.

[0058] In some embodiments, such as Figure 1 , Figures 3-5 As shown, the connecting port 100b and the intake port 21e of the cylinder cavity 21a are arranged directly opposite each other along the radial direction of the compression mechanism 100. Therefore, the flow channel 21g between the connecting port 100b and the intake port 21e can extend radially along the compression mechanism 100, which helps reduce the processing difficulty of the flow channel 21g. Of course, in other embodiments of this application, the connecting port 100b and the intake port 21e can also be arranged radially offset along the compression mechanism 100. In this case, the center of the connecting port 100b and the center of the intake port 21e are spaced apart along the axial direction of the compression mechanism 100. In this case, the flow channel 21g between the connecting port 100b and the intake port 21e can extend at an angle relative to the axial direction of the compression mechanism 100, which helps reduce the change in the flow direction of the airflow at the connecting port 100b and helps reduce pressure loss.

[0059] In some embodiments, such as 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] The vehicle 300 according to the second aspect embodiment of the present invention includes the horizontal rotary compressor 200 for vehicles described in the first aspect embodiment of the present 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 The horizontal rotary compressor 200 according to an embodiment of the present invention is described in detail with four specific examples. 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 utility model, 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 this utility model 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 this utility model. Furthermore, features defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, unless otherwise stated, "a plurality of" means two or more.

[0092] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" 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 utility model 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 present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0094] Although embodiments of the present 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 present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A horizontal rotary compressor for vehicles, characterized in that, include: case; A compression mechanism includes a bearing assembly and a cylinder assembly. The bearing assembly is disposed within a housing, and the cylinder assembly is disposed within the housing and mounted on the bearing assembly. Each cylinder assembly includes at least one cylinder, each cylinder having a cylinder chamber and a vane groove. Each cylinder chamber contains an eccentrically rotating piston, and each vane groove contains a reciprocating vane. One end of the vane abuts against the outer peripheral wall of the piston. The housing or the compression mechanism has an intake muffler channel, which is open at one end and closed at the other end. The peripheral wall of the intake muffler channel has a connecting port that connects to the cylinder cavity. The distance between the connecting port and the closed end of the intake muffler channel in the axial direction is X, where 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 vehicles according to claim 1, characterized in that, The axial direction of the intake muffler channel is parallel to the axial direction of the compression mechanism; or, In the axial direction of the compression mechanism, the intake muffler channel extends obliquely from the outside to the inside toward the cylinder assembly.

3. The horizontal rotary compressor for vehicles according to claim 1, characterized in that, The bearing assembly includes a main bearing and a secondary bearing, the cylinder assembly is sandwiched between the main bearing and the secondary bearing, and the compression mechanism is configured to satisfy any one of the following conditions: Condition A1: The intake muffler channel passes through the main bearing and extends to the cylinder assembly; Condition A2: The intake muffler channel passes through the main bearing and the cylinder assembly, and extends to the auxiliary bearing; Condition A3: The compression mechanism further includes a muffler located on the side of the auxiliary bearing opposite to the cylinder assembly, and the intake muffler passage passes through the main bearing, the cylinder assembly and the auxiliary bearing, and extends to the muffler; Condition A4: The compression mechanism further includes a connecting pipe, a through hole is formed on the secondary bearing, the connecting pipe is fitted to the through hole and is 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, the intake muffler channel passes through the main bearing and the cylinder assembly and extends to the connecting pipe.

4. The horizontal rotary compressor for vehicles according to claim 3, characterized in that, The compression mechanism is configured to satisfy condition A4, and the compression mechanism further includes a muffler located on the side of the auxiliary bearing away from the cylinder assembly, and the connecting pipe passes through the muffler and extends to the side of the muffler away from the auxiliary bearing.

5. The horizontal rotary compressor for vehicles according to claim 1, characterized in that, The connecting port and the air intake port of the cylinder cavity are either directly opposite or offset along the radial direction of the compression mechanism.

6. The horizontal rotary compressor for vehicles according to claim 1, characterized in that, There are multiple cylinders, and there are multiple communication ports, each corresponding to one of the multiple cylinders.

7. The horizontal rotary compressor for vehicles according to claim 6, characterized in that, The plurality of cylinders includes a first cylinder and a second cylinder. The cylinder assembly further includes a partition plate disposed between the first cylinder and the second cylinder. The plurality of communication ports include a first communication port communicating with the first cylinder and a second communication port communicating with the second cylinder. 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, both the first and second connecting ports are located adjacent to the end of the cylinder that is away from the closed end of the intake muffler channel.

8. The horizontal rotary compressor for vehicles according to claim 1, characterized in that, The horizontal rotary compressor uses carbon dioxide as the refrigerant.

9. The horizontal rotary compressor for a vehicle according to any one of claims 1-8, characterized in that, include: A bracket is provided on the housing and divides the internal space of the housing into a low-pressure chamber and a high-pressure chamber. A connecting channel is formed on the bracket, which connects the low-pressure chamber and the air intake silencer channel. The compression mechanism is provided in the high-pressure chamber. An electric motor is located in the low-pressure chamber.

10. The horizontal rotary compressor for a vehicle according to claim 9, characterized in that, The housing includes a low-pressure housing and a high-pressure housing respectively disposed on opposite sides of the support. The low-pressure cavity is defined between the support and the low-pressure housing, and the high-pressure cavity is defined between the support and the high-pressure housing. The horizontal rotary compressor also includes: A cover plate is disposed on the side of the low-pressure shell opposite to the high-pressure shell, and defines a receiving cavity between the cover plate and the low-pressure shell; An electrical control structure is disposed in the receiving cavity and electrically connected to the motor.

11. A vehicle, characterized in that, Includes a horizontal rotary compressor for vehicles according to any one of claims 1-10.

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