Vehicle horizontal rotary compressor, air conditioning system and vehicle

Abstract

The invention discloses a horizontal rotary compressor for a vehicle, an air conditioning system and the vehicle, and relates to the field of compressors. The horizontal rotary compressor for the vehicle comprises a shell, a support and a compression mechanism part. The shell is provided with an accommodating cavity; the support is at least partially arranged in the shell so as to divide the containing cavity into two cavities, and a support suction inlet is formed in the support. The compression mechanism part is arranged in the second cavity and comprises a main bearing, an auxiliary bearing, an air cylinder and a crankshaft, the main bearing is arranged on the support, the air cylinder is arranged between the main bearing and the auxiliary bearing and provided with a compression cavity, and the crankshaft penetrates through the main bearing, the auxiliary bearing, the air cylinder and the support and then extends into the first cavity; the compression mechanism part is provided with a main channel; one end of the main channel is communicated with the bracket suction inlet; one end of the air cylinder channel is a channel inlet end and is communicated with the main channel, and the other end of the air cylinder channel is communicated with the compression cavity; the main channel is provided with a circulation section and a buffer section. The horizontal rotary compressor for the vehicle can reduce airflow disturbance and pulse vibration generated in the compression process.

Description

Technical Field

[0001] This invention relates to the field of compressors, and more particularly to a horizontal rotary compressor for vehicles, an air conditioning system, and a vehicle. Background Technology

[0002] During the compression process of an electric compressor, the situation inside the compression chamber becomes particularly complex. Specifically, when the compression process begins, the air inlet remains open, allowing external air or gas to be drawn into the compression chamber under the influence of pressure differential. This process continues until the amount of gas in the compression chamber reaches a preset value or meets specific conditions, at which point the air inlet closes rapidly.

[0003] At the moment the air inlet closes, due to the previously established pressure difference and the dynamic characteristics of gas flow, the gas that was flowing in at high speed through the inlet suddenly loses its passage into the compression chamber. This sudden change disrupts the gas flow, creating strong airflow pulsations. These pulsations can cause vibrations in the electric compressor, potentially affecting its performance and stability. They can also generate noise.

[0004] Therefore, there is room for improvement in electric compressors. Summary of the Invention

[0005] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, one aspect of the present invention aims to provide a horizontal rotary compressor for automobiles that can reduce airflow disturbances and pulse vibrations generated during the compression process.

[0006] Another objective of this invention is to provide an air conditioning system and a vehicle.

[0007] According to a first aspect of the present invention, a horizontal rotary compressor for vehicles includes: a housing, a bracket, and a compression mechanism. The housing has a receiving cavity; the bracket is at least partially disposed within the housing to divide the receiving cavity into a first chamber and a second chamber, and the bracket has a bracket inlet communicating with the first chamber; the compression mechanism is located within the second chamber, and the compression mechanism includes a main bearing, a secondary bearing, a cylinder, and a crankshaft. The main bearing is located on the bracket, the cylinder is sandwiched between the main bearing and the secondary bearing and has a compression cavity, and the crankshaft partially passes through the main bearing, the secondary bearing, and the cylinder, and partially extends through the bracket into the first chamber; wherein the compression mechanism... The cylinder has a main channel extending axially along the crankshaft, one end of which is connected to the bracket intake port; the cylinder has a cylinder channel, one end of which is the channel inlet and connected to the main channel, and the other end is the channel outlet and connected to the compression chamber. The cylinder channel extends obliquely toward the auxiliary bearing from the channel inlet to the channel outlet. The main channel includes a flow section and a buffer section. The flow section is the portion of the main channel from the bracket intake port to the farthest channel inlet, and the buffer section is the portion from the farthest channel inlet to the end of the main channel.

[0008] According to an embodiment of the present invention, the automotive horizontal rotary compressor, by providing an inclined cylinder passage, allows gas to flow smoothly along a path before entering the compression chamber, reducing energy loss and disturbance caused by gas turning or suddenly changing direction. A flow section is provided in the main passage to ensure that gas enters the cylinder passage smoothly and steadily. A buffer section is provided after the flow section to provide a buffer zone for gas that suddenly loses its flow direction at the moment the cylinder passage closes. This buffer section effectively absorbs and dissipates the kinetic energy of the gas, reducing pulse vibration and noise caused by sudden airflow obstruction. This, in turn, improves the operational stability and reliability of the automotive horizontal rotary compressor.

[0009] According to some embodiments of the present invention, in a horizontal rotary compressor for vehicles, the angle between the extending direction of the cylinder passage and the extending direction of the main passage is greater than or equal to 30 degrees and less than or equal to 60 degrees.

[0010] According to some embodiments of the present invention, the buffer section has an axial dimension of L1, and the adjacent cylinder passage has a radial dimension of L2, where L1 is greater than L2.

[0011] According to some embodiments of the present invention, in a horizontal rotary compressor for vehicles, the cylinder connected to the main bearing is a first cylinder, the cylinder passage on the first cylinder is a first cylinder passage, and the first cylinder passage is open on the side facing the main bearing.

[0012] In some embodiments, the main bearing is provided with a bearing channel, which is open in the direction toward the first cylinder, and the bearing channel cooperates with the first cylinder channel and extends in the same direction.

[0013] According to some embodiments of the present invention, the automotive horizontal rotary compressor includes at least two cylinders, and the compression mechanism further includes a partition plate sandwiched between each two adjacent cylinders; each cylinder is provided with a cylinder channel, and the axial distance from the inlet end of each cylinder channel to the bracket is less than the axial length of the main channel.

[0014] In some embodiments, the cylinder connected to the partition plate on the side facing the secondary bearing is a second cylinder, and the cylinder passage on the second cylinder is a second cylinder passage, which is open on the side facing the partition plate.

[0015] In some embodiments, the partition plate is provided with a partition channel, which is open in the direction toward the secondary bearing, and the partition channel cooperates with the second cylinder channel and extends in the same direction.

[0016] According to some embodiments of the present invention, in a horizontal rotary compressor for vehicles, the main channel extends to the secondary bearing, and a portion of the secondary bearing is a blind hole.

[0017] The air conditioning system according to a second aspect of the present invention includes the above-described automotive horizontal rotary compressor.

[0018] A vehicle according to a third aspect of the present invention includes a vehicle-mounted horizontal rotary compressor or air conditioning system as described in the second aspect of the present invention.

[0019] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0020] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0021] Figure 1 This is a schematic diagram of the structure of a vehicle-mounted horizontal rotary compressor according to some embodiments of the present invention;

[0022] Figure 2 This is a schematic diagram of the main channel structure according to some embodiments of the present invention;

[0023] Figure 3This is a schematic diagram of the cylinder passage structure in some embodiments of the present invention;

[0024] Figure 4 This is a schematic diagram of the cylinder passage structure in some embodiments of the present invention;

[0025] Figure 5 This is a schematic diagram of the cylinder passage structure in some embodiments three of the present invention;

[0026] Figure 6 This is a schematic diagram of the cylinder passage structure in some embodiments four of the present invention;

[0027] Figure 7 This is a schematic diagram of the cylinder passage structure in some embodiments five of the present invention;

[0028] Figure 8 The graph shows the relationship between the turning angle α between the extension direction of the cylinder passage and the extension direction of the main passage in a horizontal rotary compressor for vehicles according to some embodiments of the present invention, and the local loss coefficient ξ and the average noise reduction value ΔdB.

[0029] Figure 9 This is a schematic diagram of a vehicle according to some embodiments of the present invention.

[0030] Figure label:

[0031] Vehicles 1000, Air conditioning system 200

[0032] 100-type horizontal rotary compressor for vehicles

[0033] Shell 10, accommodating cavity 11, first chamber 111, second chamber 112

[0034] Stent 20, Stent suction port 21

[0035] Compression mechanism 30, main bearing 31, bearing channel 311, auxiliary bearing 32, cylinder 33, compression chamber 330, cylinder channel 3301, channel inlet 3301a, channel outlet 3301b, first cylinder 331, first cylinder channel 3311, second cylinder 332, second cylinder channel 3321, crankshaft 34.

[0036] Main channel 35, flow section 351, buffer section 352, middle partition 36, partition channel 361. Detailed Implementation

[0037] Embodiments of the present invention 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 the present invention, and should not be construed as limiting the present invention.

[0038] In the description of this invention, it should be understood that the terms "upper," "lower," "front," "rear," "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 as "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.

[0039] 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.

[0040] The following is for reference. Figure 1 - Figure 8 A vehicle-mounted horizontal rotary compressor 100 according to an embodiment of the first aspect of the present invention is described.

[0041] The vehicle-mounted horizontal rotary compressor 100 of the present invention can be a single-cylinder single-exhaust compressor, a single-cylinder double-exhaust compressor, a double-cylinder compressor, etc.

[0042] It is worth noting that the automotive horizontal rotary compressor 100 of this embodiment is used in vehicle 1000 to meet the high load requirements of vehicle 1000. The specific use of automotive horizontal rotary compressor 100 in vehicle 1000 is not limited. It can be applied to air conditioning system 200 to provide the compression power required for cooling or heating, and can also be flexibly configured in equipment such as refrigerators, heat pump water heaters, and thermal management systems for new energy vehicles.

[0043] In some embodiments, the refrigerant used in the automotive horizontal rotary compressor 100 is carbon dioxide, and the automotive horizontal rotary compressor 100 is a carbon dioxide compressor. Of course, the refrigerant used in the automotive horizontal rotary compressor 100 is not limited to this. The use of carbon dioxide as the refrigerant in the automotive horizontal rotary compressor 100 has many advantages.

[0044] Carbon dioxide, when used as a refrigerant, has a relatively high intake and exhaust pressure compared to traditional refrigerants. The automotive horizontal rotary compressor 100 of this invention can meet the sealing requirements when using carbon dioxide as a refrigerant. Furthermore, carbon dioxide has excellent thermodynamic properties; therefore, when the same cooling capacity is required, using carbon dioxide as a refrigerant reduces the volume of the compressor's compression chamber, thus decreasing the overall size and weight of the compressor. In addition, the compressor using carbon dioxide can operate over a wide pressure range, exhibiting stable performance whether performing initial compression under low pressure or deep compression under high pressure. Therefore, the automotive horizontal rotary compressor 100 of this application can achieve an optimized compression ratio, providing efficient cooling performance in refrigeration systems, thereby reducing energy consumption and improving energy utilization.

[0045] While achieving a high compression ratio using a carbon dioxide compressor, the compressor may experience abnormal phenomena such as surge and vibration, affecting the normal operation of the system. Furthermore, a high compression ratio can also lead to increased pressure fluctuations in the system, impacting the normal operation of other equipment. Therefore, this application improves the intake channel structure of the compression mechanism 30 to mitigate the vibration and noise problems caused by achieving a high compression ratio using carbon dioxide as the refrigerant. Of course, this application can solve the vibration and noise problems of automotive horizontal rotary compressors 100 using carbon dioxide as the refrigerant, and it can also solve the vibration and noise problems of automotive horizontal rotary compressors 100 using other refrigerants. Because carbon dioxide achieves a high compression ratio as the refrigerant, the noise reduction effect of this application will be more significant in automotive horizontal rotary compressors 100 using carbon dioxide.

[0046] like Figure 1 As shown, the vehicle-mounted horizontal rotary compressor 100 according to an embodiment of the present invention includes: a housing 10, a bracket 20, and a compression mechanism 30.

[0047] The housing 10, as the main external structure of the automotive horizontal rotary compressor 100, serves to provide a robust support frame to protect the complex and precise mechanical components inside the automotive horizontal rotary compressor 100 from interference and damage from the external environment. The housing 10 ensures the stability and durability of the overall structure of the automotive horizontal rotary compressor 100.

[0048] The housing 10 has a receiving cavity 11. The receiving cavity 11 provides space for the installation and operation of multiple mechanical components inside the vehicle horizontal rotary compressor 100, ensuring the stable and safe operation of the vehicle horizontal rotary compressor 100.

[0049] The support 20 is at least partially disposed within the housing 10 to divide the accommodating cavity 11 into a first chamber 111 and a second chamber 112. The support 20 is provided with a support suction port 21 that communicates with the first chamber 111.

[0050] The bracket 20 is installed on the housing 10. The bracket 20 can be completely located inside the housing 10 or partially located inside the housing 10. The connection between the bracket 20 and the housing 10 can enhance the overall rigidity and stability of the housing 10 and prevent the housing 10 from deforming or vibrating during operation.

[0051] The bracket 20 will also be equipped with various mounting interfaces and fixing holes to securely install other components (such as motors, compressor units 30, etc.) in designated positions.

[0052] The bracket 20 not only supports and fixes other components, but also divides the accommodating cavity 11 into a first chamber 111 and a second chamber 112. The first chamber 111 can be used as an independent cavity to absorb refrigerant gas and as an intake buffer chamber for the compression mechanism 30.

[0053] The spacing provided by the bracket 20 can also reduce heat transfer between the two chambers to a certain extent, ensuring that the refrigerant is in a low temperature and low pressure state before entering the compressor section 30, thus ensuring the compression efficiency of the automotive horizontal rotary compressor 100.

[0054] The bracket intake 21 is located on the bracket 20 and is responsible for introducing the low-pressure gas from the first chamber 111 into the second chamber for compression, providing the necessary raw material for the subsequent compression process. The bracket intake 21 ensures that the automotive horizontal rotary compressor 100 continuously and stably draws in low-pressure gas.

[0055] like Figure 1 As shown, the compression mechanism 30 is located in the second chamber 112. The compression mechanism 30 includes a main bearing 31, a secondary bearing 32, a cylinder 33, and a crankshaft 34. The main bearing 31 is located on the bracket 20. The cylinder 33 is sandwiched between the main bearing 31 and the secondary bearing 32 and has a compression chamber 330. The crankshaft 34 is partially inserted through the main bearing 31, the secondary bearing 32, and the cylinder 33, and partially extends through the bracket 20 into the first chamber 111.

[0056] The main bearing 31 is securely mounted on the bracket 20, serving as one of the support points for the entire compression mechanism 30. It bears the enormous radial force and part of the axial force generated by the rotation of the crankshaft 34. By supporting and guiding the rotational motion of the crankshaft 34 through the main bearing 31, the stable operation of the crankshaft 34 is ensured, and wear caused by friction is reduced accordingly.

[0057] The auxiliary bearing 32 is located on the other side of the cylinder 33, opposite the main bearing 31, and together they hold the cylinder 33. The auxiliary bearing 32 works in cooperation with the main bearing 31 to ensure that the cylinder 33 can maintain a stable position when subjected to compressive force, and also provides additional support and lubrication for the crankshaft 34 to ensure the smooth operation of the compression process.

[0058] The main function of cylinder 33 is to provide a closed space so that the gas entering it can be compressed under the push of the piston. As the crankshaft 34 rotates, the piston reciprocates within cylinder 33, thereby realizing the intake, compression, and exhaust of gas.

[0059] The crankshaft 34 serves as the core of the power transmission in the compression mechanism 30. It converts the rotational motion from the power source (such as an electric motor) into the reciprocating motion of the piston. During rotation, the crankshaft 34 pushes the piston to reciprocate within the cylinder 33 via the connecting rod, thereby compressing the gas.

[0060] The bracket 20 provides a stable support platform, ensuring that the compression mechanism 30 is not displaced due to vibration or external forces during operation. At the same time, it also provides necessary protection and support for other components (such as the portion of the crankshaft 34 that passes through the bracket 20).

[0061] like Figure 1 - Figure 5 As shown, the compression mechanism 30 is provided with a main channel 35 extending axially along the crankshaft 34, and one end of the main channel 35 is connected to the support suction port 21. In this way, when the medium to be compressed enters the first chamber 111 through the support suction port 21, it can quickly and smoothly enter the interior of the compression mechanism 30 through the main channel 35.

[0062] Therefore, the main channel 35 is not only a simple channel, but also serves to guide the flow of gas. Here, since the main channel 35 extends along the axial direction of the crankshaft 34, the axial direction of the entire automotive horizontal rotary compressor 100, the axial direction of the crankshaft 34, and the axial direction of the main channel 35 are in the same direction.

[0063] like Figure 1 , Figure 3 - Figure 7 As shown, the cylinder 33 is provided with a cylinder channel 3301. One end of the cylinder channel 3301 is the channel inlet 3301a and is connected to the main channel 35, and the other end is the channel outlet 3301b and is connected to the compression chamber 330. The cylinder channel 3301 extends obliquely toward the auxiliary bearing 32 from the channel inlet 3301a to the channel outlet 3301b.

[0064] The cylinder passage 3301 acts as a bridge in the cylinder 33. It passes through the cylinder 33 wall and connects the main passage 35 outside the cylinder 33 and the compression chamber 330 inside the cylinder 33, so as to realize the function of drawing gas from the outside of the cylinder 33 into the inside of the cylinder 33.

[0065] Optionally, the cross-sectional shape of the cylinder passage 3301 can be circular, square, or any other arbitrary shape. The cross-sectional shape of the cylinder passage 3301 only needs to ensure that gas can smoothly enter the compression chamber 330 inside the cylinder 33.

[0066] In some embodiments, the cylinder passage 3301 is designed with a circular cross-sectional shape. Firstly, this circular design ensures high smoothness of gas flow through the cylinder passage 3301, reducing obstruction. The circular cross-section provides a continuous and smooth flow path for the gas, reducing eddies and resistance caused by abrupt changes or irregularities in shape, thereby improving gas flow efficiency.

[0067] Secondly, the machining of the circular cross-section cylinder channel 3301 is relatively simple. Circles have wide applications and mature machining technologies in the field of mechanical processing. Therefore, using a circular cross-section cylinder channel 3301 makes it easier to achieve high-precision machining, ensuring that the dimensional accuracy and surface quality of the channel meet design requirements.

[0068] The two ends of the cylinder passage 3301 are the passage inlet 3301a and the passage outlet 3301b, respectively.

[0069] The inlet end 3301a is directly connected to the main channel 35. When external gas enters the compression mechanism 30 through the main channel 35, it first reaches the inlet end 3301a and is ready to enter the cylinder channel 3301 for further transmission.

[0070] The other end of the cylinder passage 3301, the outlet 3301b, is directly connected to the compression chamber 330. After the gas is transmitted through the cylinder passage 3301, it enters the compression chamber 330 from the outlet 3301b, ready to be compressed.

[0071] The cylinder passage 3301 extends obliquely toward the auxiliary bearing 32 from the passage inlet 3301a to the passage outlet 3301b. This design can improve gas flow efficiency and reduce energy loss.

[0072] First, the inclined cylinder passage 3301 means that the gas flow direction can more naturally match the direction of the subsequent compression chamber 330 as it flows through the passage. Compared to the traditional vertical arrangement, the inclined cylinder passage 3301 reduces abrupt changes in gas flow, thereby reducing resistance and energy loss caused by sudden changes in airflow direction. This helps maintain high gas velocity and stability, improving the compression efficiency of the automotive horizontal rotary compressor 100.

[0073] Secondly, the inclined cylinder passage 3301 can reduce the impact of gas on the inner wall of the cylinder 33, piston, and other components when entering the compression chamber 330. Since the gas flow direction is more consistent with the piston movement direction, it can reduce the vibration and noise caused by gas impact, and also help extend the service life of the cylinder 33 and piston, thereby reducing noise.

[0074] As is well known to those skilled in the art, during the operation of the automotive horizontal rotary compressor 100, the periodic opening and closing of the compression chamber 330 generates pulse vibrations to a certain extent. When the air inlet of the compression chamber 330 is closed instantaneously, the rapidly flowing gas is suddenly cut off. Due to inertia and the large pressure difference inside and outside the compression chamber 330, this gas attempts to continue moving forward along the main channel 35, thus forming a strong shock wave within the main channel 35. This shock wave directly contacts the end of the main channel 35 and immediately changes direction, encountering the subsequently entering airflow, thereby generating severe disturbances, i.e., pulse vibrations. This vibration not only increases the wear of mechanical parts but also causes a certain degree of noise pollution.

[0075] To solve the above problems, combined with Figure 2 In some embodiments of the present invention, the main channel 35 includes a flow section 351 and a buffer section 352.

[0076] The main channel 35 has a flow section 351 extending from the support inlet 21 to the furthest channel inlet 3301a. The flow section 351 guides external gas smoothly into the main channel 35, thus enabling gas introduction. Here, the end of the main channel 35 near the secondary bearing 32 is its end point.

[0077] The section between the farthest channel inlet 3301a and the end of the main channel 35 is the buffer section 352. In other words, the section between the end of the main channel 35 and the nearest channel inlet 3301a is the buffer section 352.

[0078] The design of buffer section 352 is to provide a buffer zone for gas that has nowhere to go when the inlet is suddenly closed. When the inlet is closed, the airflow that was originally flowing towards the compression chamber 330 is guided into buffer section 352. Within buffer section 352, the airflow has some space to flow, thus slowing down its velocity and gradually releasing pressure. This process of slowing down velocity and releasing pressure effectively reduces the kinetic energy of the airflow, causing it to gradually stabilize within buffer section 352. The possibility of it hitting the bottom and forming a reverse shock wave is also greatly reduced. Even if some airflow still bounces back, its kinetic energy has been reduced, so the intensity of the resulting reverse shock wave will be correspondingly weakened. This avoids the risk of violent collision with the subsequently entering airflow. Consequently, the vibration generated within the main channel 35 is also reduced. This not only improves the operational stability of the automotive horizontal rotary compressor 100 but also extends the service life of the equipment.

[0079] In some alternative embodiments, the cylinder passage 3301 is at least one.

[0080] When there is only one cylinder passage 3301, the flow section 351 refers to the area from the bracket intake port 21 to the inlet end 3301a of the single cylinder passage 3301. The main function of this area is to guide the external gas smoothly and steadily into the cylinder passage 3301. The remaining part is the buffer section 352.

[0081] When there are two or more cylinder passages 3301, the flow section 351 is defined as the area extending from the intake port of the bracket 20 to the inlet end 3301a of the cylinder passage 3301 furthest from the bracket 20. This ensures that regardless of the distribution of the cylinder passages 3301, the main passage 35 provides a sufficiently long and smooth intake path for all cylinder passages 3301. The remaining portion is the buffer section 352.

[0082] In some optional embodiments, the buffer section 352 is provided with a buffer element. The buffer element includes, but is not limited to, porous dielectric material elements, rubber material elements, silicone material elements, etc. In this way, the kinetic energy and impact energy of the gas flowing through the buffer section 352 will be reduced to a certain extent.

[0083] According to some embodiments of the present invention, a horizontal rotary compressor 100 for vehicles, such as Figure 2 As shown, the angle between the extending direction of the cylinder passage 3301 and the extending direction of the main passage 35 is greater than or equal to 30 degrees and less than or equal to 60 degrees. Here, we call the angle between the extending direction of the cylinder passage 3301 and the extending direction of the main passage 35 the turning angle α.

[0084] When there is an angle between the cylinder passage 3301 and the main passage 35, the gas can form a relatively uniform and stable flow field before entering the cylinder passage 3301, reducing eddies and turbulence, thereby reducing energy loss and improving compression efficiency.

[0085] Combination Figure 2 The angle between the extending direction of the cylinder passage 3301 and the extending direction of the main passage 35 is α, which satisfies 30°≤α≤60°. Optionally, α can be 30°, 40°, 45°, 50°, 55°, 60°, etc.

[0086] When the angle is too large or too small, it may lead to poor gas flow or a large pressure drop, affecting the overall performance of the automotive horizontal rotary compressor 100. Here, α is controlled within the range of 30°-60°, which can ensure smooth gas flow while maintaining a small pressure loss.

[0087] Specifically, according to the formula: It can be seen that the key to the pressure loss in the compressor lies in the local loss coefficient ξ.

[0088] It is understandable that a large local loss coefficient ξ in a compressor indicates significant energy loss in localized areas within the compressor. This energy loss primarily manifests as a decrease in fluid pressure and a change in velocity, reducing the effective power output of the compressor. To compensate for this local loss, the compressor requires more energy to maintain normal operation. This leads to increased energy consumption and higher operating costs. The airflow from the main channel 35 to the cylinder channel 3301 involves a bend; therefore, the magnitude of the bend angle α at this point affects the local loss coefficient ξ.

[0089] The airflow turning and flowing will generate greater friction, which also affects how the airflow bounces back from the buffer section 352 and the cylinder passage 3301 and then converges in the main passage 35, especially how the sound waves are superimposed when they bounce back. Therefore, the size of the turning angle α will also affect the noise of the compressor. Thus, a reasonable average noise reduction value ΔdB can be obtained by setting the turning angle α appropriately.

[0090] Reference Figure 8 It can be seen that as the turning angle α increases, the local loss coefficient ξ also gradually increases, while the average noise reduction value ΔdB shows a trend of first increasing and then decreasing.

[0091] Referring to Table 1 below, Table 1 lists the specific values ​​of the local loss coefficient ξ and the average noise reduction value ΔdB when the turning angle α takes different values.

[0092] Table 1. Correspondence between the turning angle α of a vehicle-mounted horizontal carbon dioxide compressor and the local loss coefficient ξ and average noise reduction value ΔdB.

[0093] α 10 30 50 70 90 ξ 0.1 0.2 0.4 0.7 1.1 ΔdB(A) 2 2.7 2.5 1.5 0

[0094] Combination Figure 8 As shown in Table 1 above, in order to obtain a smaller local loss coefficient ξ, the scheme with better noise reduction effect is selected in this application. After comprehensive consideration, the turning angle α is controlled within the range of 30°-60°.

[0095] In some such Figure 7 In the illustrated embodiment, there are two cylinders 33, namely a first cylinder 331 and a second cylinder 332. The first cylinder 331 includes a first cylinder passage 3311; the second cylinder 332 includes a second cylinder passage 3321. At this time, the vehicle-mounted horizontal rotary compressor 100 has two turning angles α.

[0096] One of the turning angles α is the angle α1 between the extending direction of the first cylinder passage 3311 and the extending direction of the main passage 35, which satisfies 30°≤α1≤60°. The other turning angle α is the angle α2 between the extending direction of the second cylinder passage 3321 and the extending direction of the main passage 35, which satisfies 30°≤α2≤60°.

[0097] It is worth noting that the values ​​of α1 and α2 can be the same or different, as long as they are both within the range of 30°-60°.

[0098] According to some embodiments of the present invention, a horizontal rotary compressor 100 for vehicles, such as Figure 2 As shown, the buffer section 352 has an axial dimension of L1, and the adjacent cylinder passage 3301 has a radial dimension of L2, where L1 is greater than L2. By appropriately setting the length of the buffer section 352, it can be configured as a silencer in the airflow. It is understandable that frictional noise and vibration noise are generated during airflow. When the cylinder passage 3301 is closed by the piston, not only will the airflow flowing into the cylinder passage 3301 flow backward, but the sound waves will also be reflected by the piston. Similarly, the airflow flowing into the buffer section 352 will flow backward, and the sound waves will also be reflected by the end of the main passage 35. By setting the axial dimension L1 of the buffer section 352 to be greater than the radial dimension L2 of the cylinder passage 3301, the reflected sound waves from both locations will collide and cancel each other out, thus helping to reduce noise.

[0099] like Figure 3 - Figure 7 As shown, in some embodiments of the present invention, the automotive horizontal rotary compressor 100 has a cylinder 33 connected to the main bearing 31 as a first cylinder 331, and a cylinder passage 3301 on the first cylinder 331 is a first cylinder passage 3311, which is open on the side facing the main bearing 31.

[0100] It is known that the first cylinder 331 is directly connected to the main bearing 31. This connection method helps to ensure the stability and sealing of the cylinder 33.

[0101] Specifically, the open first cylinder passage 3311 allows gas to flow in efficiently and smoothly directly from near the main bearing 31, shortening the gas flow path and reducing flow resistance. This design ensures that gas can enter the first cylinder 331 quickly and efficiently for compression, thereby effectively reducing the time required for gas to flow in the main passage 35 and the associated energy loss.

[0102] In some embodiments, such as Figure 3 , Figure 5 and Figure 7 As shown, the main bearing 31 is provided with a bearing channel 311, which is open in the direction toward the first cylinder 331. The bearing channel 311 and the first cylinder channel 3311 are matched and extend in the same direction, so that the bearing channel 311 and the first cylinder channel 3311 are combined into one channel.

[0103] On the one hand, the bearing channel 311 and the first cylinder channel 3311 are not only spatially connected, but their extension directions are also completely consistent. This consistency can reduce obstruction and turbulence in the gas flow process. When the gas enters the first cylinder channel 3311 from the main channel 35, it flows along a continuous path without the need for a sharp change in direction at the intersection of the bearing channel 311 and the cylinder channel 3301. This continuity not only reduces energy loss caused by abrupt changes in airflow direction, but also improves the efficiency of gas entering the first cylinder 331, enabling the first cylinder 331 to perform compression work more effectively.

[0104] On the other hand, the alignment of the bearing passage 311 and the cylinder passage 3301 helps reduce wear on the main bearing 31 and the internal components of the first cylinder 331 caused by airflow impact or sudden changes in direction. In an airflow environment, if the gas direction changes constantly at a certain location, this sudden change will exacerbate the erosion and wear on the surfaces of the contact parts. A uniform airflow direction can minimize these impact effects, thereby protecting the main bearing 31 and the internal components of the first cylinder 331, and thus extending the service life of the entire automotive horizontal rotary compressor 100.

[0105] Furthermore, this open layout allows for further optimization of the main channel 35. By placing the first cylinder channel 3311 at the bearing channel 311 position, the axial length of the main channel 35 occupied by the first cylinder channel 3311 can be reduced. This adjustment not only allows the main channel 35 itself to be shortened accordingly, thereby reducing the overall axial dimension of the automotive horizontal rotary compressor 100, but also helps to achieve a compact layout of the internal structure of the automotive horizontal rotary compressor 100.

[0106] like Figure 3 - Figure 7 As shown, in some embodiments of the present invention, the automotive horizontal rotary compressor 100 includes at least two cylinders 33, and the compression mechanism 30 further includes a partition plate 36 sandwiched between each two adjacent cylinders 33.

[0107] When there are two or more cylinders 33, the multiple cylinders 33 are arranged along the axial direction of the vehicle horizontal rotary compressor 100 to form a compact compression unit. Each cylinder 33 can independently perform the processes of gas intake, compression and discharge. Accordingly, the parallel operation of multiple cylinders 33 effectively improves the processing capacity and efficiency of the entire vehicle horizontal rotary compressor 100.

[0108] The partition plate 36 is disposed between each pair of adjacent cylinders 33, which can enhance the structural strength of the compression mechanism 30 to a certain extent and prevent mutual interference between cylinders 33, thus preventing deformation. The partition plate 36 is in close contact with the adjacent cylinders 33, which also ensures the independence and sealing of the gas in the corresponding cylinder 33.

[0109] Each cylinder 33 is provided with a cylinder channel 3301. The axial distance from the channel inlet 3301a of each cylinder channel 3301 to the bracket 20 is less than the axial length of the main channel 35.

[0110] Combination Figure 3 - Figure 7 In some embodiments, there are two cylinders 33, namely a first cylinder 331 and a second cylinder 332. The axial distance from the inlet 3301a of the cylinder channel 3301 of the first cylinder 331 to the bracket 20 is greater than the axial length of the main channel 35, and the axial distance from the inlet 3301a of the cylinder channel 3301 of the second cylinder 332 to the bracket 20 is greater than the axial length of the main channel 35.

[0111] This design ensures that the main channel 35 has sufficient extra space in its axial length to accommodate the buffer section 352, thereby allowing the gas in the main channel 35 to be buffered and adjusted when the cylinder channel 3301 is closed.

[0112] In some embodiments, such as Figure 3 - Figure 7 As shown, the cylinder 33 connected to the partition plate 36 on the side facing the secondary bearing 32 is the second cylinder 332, and the cylinder passage 3301 on the second cylinder 332 is the second cylinder passage 3321. The second cylinder passage 3321 is open on the side facing the partition plate 36.

[0113] It is known that when the compression mechanism 30 in the automotive horizontal rotary compressor 100 adopts a dual-cylinder 33 design, the main bearing 31, the cylinder 33, and the auxiliary bearing 32 will be arranged sequentially along the axial direction of the automotive horizontal rotary compressor 100.

[0114] like Figure 1 - Figure 7 As shown, when cylinder 33 includes first cylinder 331 and second cylinder 332, first cylinder 331 and second cylinder 332 are also arranged sequentially along the circumference of vehicle horizontal rotary compressor 100.

[0115] The main bearing 31 is located at the input end of the compression mechanism 30. One side of the first cylinder 331 is adjacent to the main bearing 31, and a partition plate 36 is provided on the other side of the first cylinder 331. At the end of the partition plate 36 away from the first cylinder 331, a second cylinder 332 is provided, and the end of the second cylinder 332 away from the partition plate 36 is close to the auxiliary bearing 32. At the same time, the auxiliary bearing 32 is also located at the output end of the compression mechanism 30.

[0116] At this time, a second cylinder passage 3321 is formed on the second cylinder 332 to connect the main passage 35 and the second cylinder 332.

[0117] By opening the second cylinder passage 3321 on the side facing the partition plate 36, the path of gas entering the second cylinder passage 3321 can be shortened to some extent, as the second cylinder passage 3321 is closer to the input end of the compression mechanism 30. Shortening the gas flow path also reduces the resistance encountered by the gas during flow. The closer the second cylinder passage 3321 is to the input end of the compression mechanism 30 (i.e., the closer the second cylinder passage 3321 is to the air intake), the less energy is lost during gas flow, thereby improving intake efficiency. Simultaneously, shortening the gas flow path also helps reduce eddies and turbulence that may occur due to an excessively long path.

[0118] In some such Figure 3 , Figure 6 and Figure 7 In the embodiment shown, the partition plate 36 is provided with a partition channel 361, which is open in the direction toward the secondary bearing 32. The partition channel 361 cooperates with the second cylinder channel 3321 and extends in the same direction, so that the partition channel 361 and the second cylinder channel 3321 are combined into one channel.

[0119] The partition channel 361 is open in the direction of the secondary bearing 32, so that when the gas enters the second cylinder 332 through the partition 36, it will not encounter the obstruction from the partition 36 and cause a sudden change in direction, thus ensuring smooth airflow and reducing energy loss.

[0120] The partition channel 361 and the second cylinder channel 3321 are not only spatially connected, but their extension directions are also completely consistent. This consistency ensures that when gas enters the second cylinder 332 from the partition channel 361, it can flow along a continuous and smooth path without complex turning at the junction. This further reduces energy loss caused by abrupt changes in airflow direction, improves the efficiency of gas entering the second cylinder 332, and thus enhances the compression performance of the second cylinder 332.

[0121] Similar to the relationship between the bearing channel 311 and the first cylinder channel 3311, the alignment of the partition channel 361 and the second cylinder channel 3321 also helps reduce wear on the internal components of the second cylinder 332 caused by airflow impact or abrupt changes in direction. During the gas flow through the partition channel 361 into the second cylinder 332, the continuity of the airflow direction reduces the scouring and wear effects on the contact surfaces. This not only protects the integrity of the partition 36 itself but also extends the service life of the second cylinder 332 and its internal components.

[0122] The design of the partition channel 361 further optimizes the internal structural layout of the compression mechanism 30. By combining the second cylinder channel 3321 with the partition channel 361 and aligning their extension directions, a portion of the second cylinder channel 3321 is formed using the space of the middle partition 36. This helps to achieve a compact layout of the second cylinder channel 3321, making the entire compression mechanism 30 more compact. This compact layout helps to reduce the overall size and weight of the automotive horizontal rotary compressor 100.

[0123] According to some embodiments of the present invention (not shown in the figures), the main channel 35 extends to the secondary bearing 32, and a portion of the secondary bearing 32 is a blind hole (not shown in the figures).

[0124] First, the blind hole structure formed in the section extending from the main channel 35 to the secondary bearing 32 naturally becomes an effective buffer section 352. This results in a corresponding increase in the length of the buffer section 352. The increased length of the buffer section 352 allows the gas more time and space to regulate its velocity, thereby reducing the impact energy of the gas flow.

[0125] Secondly, the blind hole structure on the secondary bearing 32 not only serves as a buffer section 352, but also ensures the sealing of its connection with the corresponding cylinder 33, avoiding the possibility of gas leakage, thereby ensuring the operational stability of the automotive horizontal rotary compressor 100.

[0126] In some alternative embodiments, a filter is provided within the main channel 35. The filter is located near the support inlet 21.

[0127] The quality of the gas entering the main channel 35 is ensured by installing a filtration device. The filtration device can intercept and remove harmful substances such as impurities, particles, and dust from the gas to the greatest extent possible, reducing or avoiding wear and damage to key components inside the compression mechanism 30 caused by impurities. At the same time, it ensures the gas compression effect and improves the reliability of the automotive horizontal rotary compressor 100.

[0128] Furthermore, the longer main channel 35 provides more space for installing a filter, thus better protecting the automotive horizontal rotary compressor 100 from impurities.

[0129] According to an embodiment of the second aspect of the present invention, an air conditioning system 200 is described, with reference to... Figure 9 This includes the vehicle-mounted horizontal rotary compressor 100 according to the first aspect embodiment of the present invention. This is beneficial for reducing the operating noise of the air conditioning system 200.

[0130] It is worth noting that the type of air conditioning system 200 in this application embodiment is not limited, and it can be an integrated air conditioning unit or a split air conditioning unit.

[0131] According to a third aspect embodiment of the vehicle 1000, referring to Figure 9 This includes the air conditioning system 200 of the second aspect embodiment of this application or the vehicle horizontal rotary compressor 100 of the first aspect embodiment. The structures of the vehicle horizontal rotary compressor 100 and the air conditioning system 200 will not be described in detail here. It is worth noting that the specific type of vehicle referred to in this invention is not limited. For example, the vehicle can be a fuel vehicle, a natural gas 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 electric vehicles, gas fuel vehicles such as hydrogen engine vehicles, or biofuel vehicles such as vehicles powered by ethanol, biodiesel, etc.

[0132] The vehicle described in this embodiment of the invention utilizes an improved automotive horizontal rotary compressor 100, which facilitates the rapid attainment and maintenance of a comfortable temperature environment by the vehicle's internal air conditioning system 200, providing passengers with a comfortable riding experience. Simultaneously, the automotive horizontal rotary compressor 100 has a low noise level, creating a quieter riding environment inside the vehicle and further enhancing the passenger experience.

[0133] The following describes in detail, with specific embodiments, a vehicle-mounted horizontal rotary compressor 100 according to an embodiment of the present invention. It is to be understood that the following description is merely illustrative and not intended to limit the scope of the invention.

[0134] Example 1

[0135] Reference Figure 1 - Figure 3The automotive horizontal rotary compressor 100 includes: a housing 10, a bracket 20, and a compression mechanism 30.

[0136] The housing 10 includes a receiving cavity 11.

[0137] The bracket 20 is installed inside the housing 10 and divides the accommodating cavity 11 into a first chamber 111 and a second chamber 112.

[0138] Reference Figure 2 The stent 20 includes a stent inlet 21. One end of the stent inlet 21 is connected to the first chamber 111.

[0139] The compression mechanism 30 is located in the second chamber 112, and the compression mechanism 30 includes: a main bearing 31, a secondary bearing 32, a cylinder 33, a crankshaft 34, a main channel 35, and a partition plate 36.

[0140] The main bearing 31 is located on the bracket 20, the cylinder 33 is sandwiched between the main bearing 31 and the auxiliary bearing 32 and has a compression chamber 330, and the crankshaft 34 is partially inserted through the main bearing 31, the auxiliary bearing 32 and the cylinder 33, and partially extends through the bracket 20 into the first chamber 111.

[0141] The compression mechanism 30 is provided with a main channel 35 extending axially along the crankshaft 34. One end of the main channel 35 is connected to the other end of the bracket intake port 21. The other end of the main channel 35 extends to the auxiliary bearing 32, and the portion on the auxiliary bearing 32 is a blind hole.

[0142] Reference Figure 3 The cylinder 33 includes a first cylinder 331 and a second cylinder 332 arranged axially along the vehicle horizontal rotary compressor 100.

[0143] The partition 36 is located between the first cylinder 331 and the second cylinder 332.

[0144] Each cylinder 33 is provided with a cylinder passage 3301. The cylinder passage 3301 on the first cylinder 331 is the first cylinder passage 3311; the cylinder passage 3301 on the second cylinder 332 is the second cylinder passage 3321.

[0145] Each cylinder passage 3301 includes a passage inlet 3301a and a passage outlet 3301b located at both ends.

[0146] The inlet end 3301a of the channel is connected to the main channel 35, and the outlet end 3301b is connected to the compression chamber 330. The cylinder channel 3301 extends obliquely toward the auxiliary bearing 32 from the inlet end 3301a to the outlet end 3301b.

[0147] The first cylinder passage 3311 is open on the side facing the main bearing 31.

[0148] The main bearing 31 is provided with a bearing channel 311, which is open in the direction toward the first cylinder 331. The bearing channel 311 cooperates with the first cylinder channel 3311 and extends in the same direction, so that the bearing channel 311 and the first cylinder channel 3311 form a channel.

[0149] Reference Figure 2 The extension direction of the first cylinder channel 3311 has an angle α with the extension direction of the main channel 35, satisfying 30°≤α≤60°.

[0150] The second cylinder 332 is connected to the side of the partition plate 36 facing the auxiliary bearing 32. The second cylinder passage 3321 is open on the side facing the partition plate 36.

[0151] The partition plate 36 is provided with a partition channel 361, which is open in the direction toward the secondary bearing 32. The partition channel 361 cooperates with the second cylinder channel 3321 and extends in the same direction, so that the partition channel 361 and the second cylinder channel 3321 are combined into one channel.

[0152] Reference Figure 2 The extension direction of the second cylinder channel 3321 has an angle α with the extension direction of the main channel 35, satisfying 30°≤α≤60°.

[0153] The main channel 35 includes a flow section 351 and a buffer section 352.

[0154] The flow section 351 is the section between the support suction port 21 and the channel inlet 3301a of the second cylinder channel 3321.

[0155] The section between the inlet end 3301a of the second cylinder passage 3321 and the bottom wall of the blind hole of the auxiliary bearing 32 is the buffer section 352.

[0156] Example 2

[0157] In this embodiment, the basic structure of the vehicle horizontal rotary compressor 100 is the same as that in Embodiment 1, the difference being that, referring to... Figure 4 The first cylinder passage 3311 is open on the side facing the main bearing 31; the second cylinder passage 3321 is open on the side facing the partition plate 36.

[0158] The automotive horizontal rotary compressor 100 in this second embodiment saves on processing costs.

[0159] Example 3

[0160] In this embodiment, the basic structure of the vehicle horizontal rotary compressor 100 is the same as that in Embodiment 1, the difference being that, referring to... Figure 5 The first cylinder channel 3311 is open on the side facing the main bearing 31. The main bearing 31 is provided with a bearing channel 311, and the bearing channel 311 is open in the direction facing the first cylinder 331. The bearing channel 311 cooperates with the first cylinder channel 3311 and extends in the same direction. In this way, the bearing channel 311 and the first cylinder channel 3311 are combined into a channel.

[0161] The second cylinder passage 3321 is open on the side facing the partition plate 36.

[0162] The automotive horizontal rotary compressor 100 in this embodiment 3 optimizes the intake effect to a certain extent while reducing processing costs.

[0163] Example 4

[0164] In this embodiment, the basic structure of the vehicle horizontal rotary compressor 100 is the same as that in Embodiment 1, the difference being that, referring to... Figure 6 The first cylinder passage 3311 is open on the side facing the main bearing 31.

[0165] The second cylinder passage 3321 is open on the side facing the middle partition 36. The middle partition 36 is provided with a partition passage 361, which is open in the direction facing the auxiliary bearing 32. The partition passage 361 cooperates with the second cylinder passage 3321 and extends in the same direction, so that the partition passage 361 and the second cylinder passage 3321 form a single passage.

[0166] The automotive horizontal rotary compressor 100 in this embodiment 4 optimizes the intake effect to a certain extent while reducing processing costs.

[0167] Example 5

[0168] In this embodiment, the basic structure of the vehicle horizontal rotary compressor 100 is the same as that in Embodiment 1, the difference being that, referring to... Figure 7 The first cylinder passage 3311 is open on the side facing the main bearing 31. The main bearing 31 is provided with a bearing passage 311, which is open in the direction facing the first cylinder 331. The bearing passage 311 and the first cylinder passage 3311 cooperate and extend in the same direction, so that the bearing passage 311 and the first cylinder passage 3311 form a single channel.

[0169] The extension direction of the first cylinder passage 3311 has an angle α1 with the extension direction of the main passage 35, satisfying 30°≤α1≤60°.

[0170] The second cylinder 332 is connected to the side of the partition plate 36 facing the auxiliary bearing 32. The second cylinder passage 3321 is open on the side facing the partition plate 36. The partition plate 36 is provided with a partition channel 361, which is open in the direction facing the auxiliary bearing 32. The partition channel 361 cooperates with the second cylinder passage 3321 and extends in the same direction, so that the partition channel 361 and the second cylinder passage 3321 form a single channel.

[0171] The extension direction of the second cylinder passage 3321 has an angle α2 with the extension direction of the main passage 35, satisfying 30°≤α2≤60°.

[0172] However, the values ​​of α1 and α2 are not equal.

[0173] Other components of the vehicle-mounted horizontal rotary compressor according to embodiments of the present invention, such as vehicles and their operation, are known to those skilled in the art and will not be described in detail here.

[0174] In the description of this specification, references to terms such as "embodiment," "example," 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.

[0175] Although embodiments of the invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and variations 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 comprising: The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor.

2. The in-line rotary compressor of claim 1, wherein, The application relates to a vehicle horizontal rotary compressor.

3. The in-line rotary compressor of claim 1, wherein, The application relates to a vehicle horizontal rotary compressor.

4. The in-line rotary compressor of claim 1, wherein, The application relates to a vehicle horizontal rotary compressor.

5. The in-line rotary compressor of claim 4, wherein, The application relates to a vehicle horizontal rotary compressor.

6. The in-line rotary compressor of any one of claims 1-5, wherein, The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor.

7. The in-line rotary compressor of claim 6, wherein The application relates to a vehicle horizontal rotary compressor.

8. The in-line rotary compressor of claim 7, wherein, The application relates to a vehicle horizontal rotary compressor.

9. The in-line rotary compressor of any one of claims 1-5, wherein, The application relates to a vehicle horizontal rotary compressor.

10. The in-line rotary compressor of any one of claims 1-5, wherein, The application relates to a vehicle horizontal rotary compressor.

11. An air conditioning system, characterised in that, The application relates to a vehicle horizontal rotary compressor.

12. A vehicle characterized by comprising: The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary compressor. The application relates to a vehicle horizontal rotary

Images