Compressor damping end cover and compressor comprising same

Abstract

The damping end cover comprises a cover body, the cover body comprises an air cavity and an adjusting cavity communicated with the air cavity, the air cavity is located at the end, close to a scroll plate assembly, of the cover body, the adjusting cavity comprises a first channel and a second channel, and the first channel and the second channel are distributed in the radial direction of the cover body. One end of the first channel communicates with the air cavity, the other end of the first channel communicates with the second channel, the end, away from the first channel, of the second channel penetrates through the cover body in the radial direction of the cover body and is used for being connected with an air conditioner pipeline, and the radial size of the first channel is smaller than that of the second channel; the compressor comprises the damping end cover, a good damping effect can be achieved, resonance in a passenger compartment is weakened, and the vehicle using experience is improved.

Description

Technical Field

[0001] The utility model relates to the technical field of compressors, in particular to a compressor shock-absorbing end cover and a compressor containing the same. Background Art

[0002] An electric scroll compressor refers to a device that achieves gas compression through the relative rotation of a scroll moving plate and a scroll stationary plate. The compressor plays an important role in the automobile's air-conditioning system. In the air-conditioning system, the compressor can compress the low-temperature and low-pressure gaseous refrigerant from the evaporator outlet into a high-temperature and high-pressure gaseous refrigerant, and discharge it to the condenser for heat exchange to meet the vehicle's cooling and heating needs.

[0003] When the compressor compresses the gas, it will continuously exhaust air, and pulsation will be generated in the exhaust process. Exhaust pulsation, as a kind of energy wave, can be transmitted to the passenger compartment through the air-conditioning pipe with the refrigerant as the transmission medium. It is specifically manifested as the roar and micro-vibration of the air-conditioning main unit. As the speed of the compressor increases, the roar becomes louder, which can easily affect the NVH performance of the car and the riding experience of the people in the car, and there will be numbness in the steering wheel and pedals at the driver's seat, affecting the driver's driving experience. Utility Model Content

[0004] In view of this, the purpose of the utility model is to provide a compressor shock-absorbing end cover and a compressor containing the same, which can reduce vibration from the compressor, reduce the resonance of the passenger compartment and the air-conditioning duct, help reduce the roar of the compressor when it is working, and help improve the performance of the vehicle.

[0005] The utility model provides a shock-absorbing end cover of a compressor, comprising a cover body, wherein the cover body comprises an air cavity and an adjusting cavity connected to the air cavity, wherein the air cavity is located at one end of the cover body close to a scroll assembly, wherein the adjusting cavity comprises a first channel and a second channel distributed radially along the cover body, wherein one end of the first channel is connected to the air cavity, and the other end is connected to the second channel, and an end of the second channel away from the first channel penetrates the cover body radially along the cover body for connecting an air-conditioning duct, and the radial dimension of the first channel is smaller than the radial dimension of the second channel.

[0006] In one embodiment, a radial dimension of the air conditioning duct is smaller than a radial dimension of the second channel and larger than a radial dimension of the first channel.

[0007] In one embodiment, the first channel, the second channel and the air conditioning duct are coaxially arranged.

[0008] In one embodiment, the first channel and the second channel are eccentrically arranged, and the second channel and the air conditioning duct are coaxially arranged or eccentrically arranged.

[0009] In one embodiment, when the second channel is eccentrically arranged with respect to the air conditioning duct, the first channel is coaxially arranged with respect to the air conditioning duct.

[0010] In one embodiment, the scroll assembly includes a moving disk and a stationary disk, the stationary disk includes an exhaust hole, and a radial dimension of the first channel is the same as a radial dimension of the exhaust hole.

[0011] In one embodiment, the ratio of the radial dimension of the first channel to the radial dimension of the second channel is 1:3.

[0012] In one embodiment, an axial length of the first channel is the same as an axial length of the second channel.

[0013] In one embodiment, the air cavity includes a first cavity and a second cavity, a partition wall is provided between the first cavity and the second cavity, the first cavity is located in the middle position of the cover body, the second cavity surrounds the outer periphery of the first cavity and is connected to the first channel, and the depth of the first cavity along the axial direction of the cover body is smaller than the axial depth of the second cavity.

[0014] The utility model also proposes a compressor, including the above-mentioned compressor shock-absorbing end cover, and includes a vortex plate assembly, the vortex plate assembly includes a moving plate and a stationary plate, the moving plate can rotate axially relative to the stationary plate, and the stationary plate is provided with an exhaust hole, and the exhaust hole is connected to the air cavity.

[0015] The beneficial effects of the compressor shock-absorbing end cover of the utility model are:

[0016] By dividing the regulating chamber into a first channel and a second channel that are connected, and by setting the radial size of the first channel, the first channel can weaken the intensity of the energy wave in the refrigerant. By setting the radial size of the second channel to be larger than that of the first channel, the second channel can further weaken the intensity of the energy wave, so that the energy wave carried by the refrigerant discharged from the second channel to the air-conditioning duct is weakened, thereby weakening the vibration of the air-conditioning duct and the air-conditioning main unit brought by the refrigerant, reducing the roar in the passenger compartment, making the vehicle have good NVH performance, and being able to prevent the resonance in the passenger compartment from causing vibration of the steering wheel and pedals, avoiding the problem of numbness of the driver's hands and feet, and improving the driving experience of the driver and the riding experience of the people in the car.

[0017] The compressor of the utility model has the beneficial effect that, by adopting the shock-absorbing end cover, the intensity of the energy wave discharged from the compressor as the refrigerant is discharged can be weakened, the resonance probability in the passenger compartment is reduced, and the utility model has good practicality. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the technical solutions of the embodiments of the utility model, the drawings required for use in the embodiments will be briefly introduced below. It should be understood that the following drawings only show certain embodiments of the utility model and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other relevant drawings can be obtained based on these drawings without paying creative work.

[0019] Figure 1 This is a schematic diagram of the overall structure of a cover body according to an embodiment of the utility model;

[0020] Figure 2 A cross-sectional view of a cover body at the adjustment cavity of an embodiment of the utility model;

[0021] Figure 3 Another structural schematic diagram of a cover body according to an embodiment of the utility model;

[0022] Figure 4 A schematic diagram of pulsation analysis of a regulating chamber and an air conditioning duct according to an embodiment of the utility model;

[0023] Figure 5 A schematic diagram of pulsation analysis of a regulating chamber and an air conditioning duct according to another embodiment of the utility model;

[0024] Figure 6 This is a data table showing the relationship between the radial dimension and axial dimension of the regulating cavity and the pulsation of an embodiment of the utility model;

[0025] Figure 7 This is a data table showing the relationship between the radial size of the regulating cavity and the compressor efficiency according to an embodiment of the present utility model.

[0026] In the figure:

[0027] 10-cover body; 11-air cavity; 111-first cavity; 112-second cavity; 113-partition wall; 114-first connecting rib; 115-second connecting rib;

[0028] 12-adjusting chamber; 121-first channel; 122-second channel; 123-air conditioning duct. DETAILED DESCRIPTION

[0029] The following will describe in detail a specific embodiment of the utility model in conjunction with the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the utility model, not all of the embodiments. Based on the description of the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0030] Unless otherwise clearly specified and limited, the terms "disposed", "installed", "connected" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to specific circumstances.

[0031] The directions or positional relationships indicated by terms such as "upper", "lower", "left", "right", "front", "back", "top", "bottom", "inside" and "outside" are based on the directions or positional relationships shown in the accompanying drawings, or are the directions or positional relationships in which the utility model product is usually placed when in use. They are only for the convenience of description and simplified description, and do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction, and therefore should not be understood as a limitation on the utility model.

[0032] The terms "first", "second", "third" and the like are merely used to distinguish elements of similar nature, and do not indicate or imply relative importance or a particular order.

[0033] The terms "comprises," "comprising," or any other variations thereof, are intended to cover a non-exclusive inclusion of the elements listed and may also include additional elements not expressly listed.

[0034] As attached Figure 1 As shown, the compressor shock absorbing end cover proposed by the utility model includes a cover body 10, the cover body 10 includes an air cavity 11 and an adjusting cavity 12, the adjusting cavity 12 is connected with the air cavity 11, the air cavity 11 is located at one end of the cover body 10 close to the scroll assembly, and the air cavity 11 is recessed along the axial direction of the cover body 10 to the side away from the scroll assembly, the adjusting cavity 12 runs through one side of the cover body 10 along the radial direction, one end of the adjusting cavity 12 is connected with the air cavity 11, and the air cavity 11 is located at one end of the cover body 10 close to the scroll assembly, and the air cavity 11 is recessed along the axial direction of the cover body 10 to the side away from the scroll assembly, and the adjusting cavity 12 runs through one side of the cover body 10 along the radial direction, and one end of the adjusting cavity 12 is connected with the air cavity 11. Figure 4 and attached Figure 5 The other end of the regulating cavity 12 penetrates the cover body 10 along the radial direction of the cover body 10 and is connected to the air conditioning duct 123 .

[0035] The scroll assembly includes a moving disk and a stationary disk. An exhaust hole is provided on the stationary disk, which can be connected to the air cavity 11. The moving disk and the stationary disk can cooperate to form a compression cavity. When the compressor is working, the moving disk rotates axially relative to the stationary disk and compresses the refrigerant gas. The temperature and pressure of the refrigerant gradually increase during the rotation of the moving disk until the refrigerant flows to the exhaust hole of the stationary disk. The refrigerant enters the air cavity 11 from the exhaust hole and is discharged to the air-conditioning duct 123 through the regulating cavity 12.

[0036] When one exhaust is completed, an exhaust pressure pulsation will be generated, and the pressure pulsation is at a peak state. The pulsation enters the air-conditioning duct 123 from the compressor as the refrigerant is discharged, and is transmitted to the air-conditioning main unit and the passenger compartment through the air-conditioning duct 123, causing resonance inside the passenger compartment and vibration of the air-conditioning main unit, and a roaring sound will be generated.

[0037] As attached Figure 2 As shown, the regulating chamber 12 includes a first channel 121 and a second channel 122 distributed radially along the cover body 10 and connected. One end of the first channel 121 is connected to the air cavity 11, and the other end is connected to the second channel 122. The end of the second channel 122 away from the first channel 121 passes through the cover body 10 in the radial direction of the cover body 10 and is used to communicate with the outside. When the compressor is applied to an air conditioning system, combined with the attached Figure 4 and attached Figure 5 The second channel 122 is connected to the air conditioning pipe 123 , wherein the radial dimension of the first channel 121 along its own radial direction is smaller than the radial dimension of the second channel 122 .

[0038] The setting of the first channel 121 can suppress the pulsation amplitude of the compressor and consume the pulsation energy on the compressor as much as possible. When the refrigerant gas in the air cavity 11 enters the first channel 121, the fluid resistance of the refrigerant increases and the pulsation carried by the refrigerant is weakened. The setting of the second channel 122 can slow down the release rate of the pulsation energy, thereby reducing the pulsation energy carried by the refrigerant discharged into the air-conditioning duct 123, weakening the vibration transmitted from the compressor to the air-conditioning duct 123, and reducing the roar caused by the vibration.

[0039] During the operation of the compressor, the refrigerant will carry the refrigerant oil out of the compressor, resulting in a reduction in the refrigerant oil in the compressor. Since the radial dimension of the first channel 121 is smaller than the radial dimension of the second channel 122, the first channel 121 increases the flow resistance of the refrigerant. When passing through the second channel 122, the flow speed of the refrigerant slows down due to the increase in the radial dimension, and the amount of refrigerant oil it carries is reduced, thereby ensuring the normal lubrication of the compressor and the quality of heat exchange.

[0040] In one embodiment of the present invention, as shown in the attached Figure 3As shown, the air cavity 11 includes a first cavity 111 and a second cavity 112. The first cavity 111 is located in the middle of the cover body 10, and the second cavity 112 is surrounded by the outer periphery of the first cavity 111, and the second cavity 112 is communicated with the first channel 121. A partition wall 113 is provided between the first cavity 111 and the second cavity 112. The depth dimension of the partition wall 113 along the axial direction of the cover body 10 is smaller than the axial thickness dimension of the cover body 10, so that the depth of the first cavity 111 along the axial direction of the cover body 10 is smaller than the axial depth of the second cavity 112. The first cavity 111 is used to communicate with the exhaust hole of the stator disk. The refrigerant from the exhaust hole will preferentially enter the first cavity 111, and then enter the second cavity 112 through the first cavity 111, and finally be discharged from the first channel 121 and the second channel 122. The first cavity 111 and the second cavity 112 cooperate to curb the pulsation of the refrigerant, to a certain extent weaken the vibration caused by the pulsation, and to reduce the noise caused by the vibration.

[0041] In one example, as shown in the attached Figure 3 As shown, at least one first connecting rib 114 is protrudingly provided on the cavity wall of the first cavity 111, and one end of the first connecting rib 114 is connected to the partition wall 113. By setting the first connecting rib 114, the structural strength and stability of the first cavity 111 can be increased, and the strength of the partition wall 113 can be improved. When the refrigerant carrying pulsating energy waves is discharged into the first cavity 111, the first connecting rib 114 can play a role in weakening the energy waves to a certain extent, so as to weaken the pulsating energy waves carried by the refrigerant discharged into the air-conditioning duct 123, thereby weakening the vibration transmitted from the compressor to the air-conditioning duct 123.

[0042] Optionally, the first connecting rib 114 extends radially along the cover body 10, with one end of the first connecting rib 114 located in the middle of the cover body 10 and the other end extending to connect with the partition wall 113. The first connecting rib 114 can guide the refrigerant in the first cavity 111 to the second cavity 112, thereby changing the flow direction of the refrigerant to weaken the pulsating energy wave carried in the refrigerant.

[0043] Optional, as attached Figure 3 As shown, when the number of the first connecting ribs 114 is set to two or more, the first connecting ribs 114 are distributed in the first cavity 111 in a ring array.

[0044] Optionally, the first connecting rib 114 is integrally formed with the first cavity 111 and the partition wall 113 .

[0045] In one example, as shown in the attached Figure 3As shown, a second connecting rib 115 is protruding on the cavity wall of the second cavity 112, and the axial height of the second connecting rib 115 along the cover body 10 is smaller than the axial height of the partition wall 113, so that the refrigerant can flow in the second cavity 112 and be discharged through the regulating cavity 12. The second connecting rib 115 can slow down the flow rate of the refrigerant, thereby playing a role in curbing pulsation.

[0046] One end of the second connecting rib 115 is connected to the partition wall 113, and the other end is connected to the side of the second cavity 112 away from the partition wall 113. The second connecting rib 115 can increase the stability of the partition wall 113, and can cooperate with the first connecting rib 114 to improve the strength of the partition wall 113. The second connecting rib 115 can buffer the refrigerant airflow, so that the refrigerant has a certain energy loss during the flow process, so as to further reduce the exhaust pulsation, which is beneficial to improving the working performance of the compressor and has a good vibration reduction effect.

[0047] Optionally, the second connecting rib 115 extends along the radial direction of the cover body 10 .

[0048] Optionally, the second connecting rib 115 and the first connecting rib 114 are arranged to have the same diameter.

[0049] Optionally, when the number of the second connecting ribs 115 is set to two or more, the second connecting ribs 115 are distributed in the second cavity 112 in a ring array, and the first channel 121 is disposed between two adjacent second connecting ribs 115 .

[0050] Optionally, the second connecting rib 115 is integrally formed with the second cavity 112 and the partition wall 113 .

[0051] Embodiment 1

[0052] Attached Figure 4 It is a curve diagram of the amplitude and frequency changes of the pulsating energy wave in the regulating chamber 12 and the air-conditioning duct 123, wherein L1 is the change curve of the pulsating energy wave.

[0053] As attached Figure 4 As shown, the first channel 121 and the second channel 122 are eccentrically arranged, that is, the central axes of the first channel 121 and the second channel 122 are not located on the same straight line, the first channel 121, the second channel 122 and the air-conditioning duct 123 are connected, the radial dimension of the first channel 121 is smaller than the radial dimension of the second channel 122, and the radial dimension of the air-conditioning duct 123 is smaller than the radial dimension of the second channel 122.

[0054] Referring to curve L1, when the pulsating energy wave is discharged from the air cavity 11 to the first channel 121 along with the refrigerant, its amplitude is suppressed by the first channel 121, the amplitude is reduced, but its frequency is still relatively large; when the pulsating energy wave is discharged from the first channel 121 to the second channel 122 along with the flow of the refrigerant, the flow rate of the refrigerant slows down, the amplitude of the pulsating energy wave increases relative to the amplitude in the first channel 121, but the frequency is reduced relative to the frequency in the first channel 121; when the energy wave is discharged from the second channel 122 to the air-conditioning duct 123 along with the refrigerant, it is suppressed by the air-conditioning duct 123, the amplitude is reduced, and the frequency is similar to that in the second channel 122.

[0055] In one example, the air conditioning duct 123 is eccentrically connected to the second channel 122 . Optionally, the air conditioning duct 123 is coaxially arranged with the first channel 121 .

[0056] In one example, the air conditioning duct 123 is coaxially connected to the second channel 122 , that is, the central axis of the air conditioning duct 123 and the central axis of the second channel 122 are located on the same straight line.

[0057] In one example, the radial dimension of the air conditioning duct 123 is greater than the radial dimension of the first channel 121 .

[0058] In one example, the axial lengths of the first channel 121 and the second channel 122 are the same. Optionally, the axial length of the first channel 121 is determined by the displacement and rated compression ratio of the compressor, and those skilled in the art can select a suitable axial length according to actual application scenarios and requirements.

[0059] In one example, both the first channel 121 and the second channel 122 are cylindrical channels.

[0060] By setting the first channel 121 and the second channel 122 with different diameters and being eccentric, the amplitude and frequency of the pulsation in the refrigerant can be weakened, so that when the refrigerant in the compressor is discharged into the air-conditioning duct 123, the pulsation is weakened, and the pulsation energy wave is weakened at the source of the compressor, thereby weakening the vibration transmitted to the air-conditioning duct 123 and the passenger compartment through the refrigerant, avoiding causing a loud roar, improving the NVH performance of the vehicle, and reducing numbness.

[0061] Embodiment 2

[0062] Attached Figure 5 It is a curve diagram of the amplitude and frequency changes of the pulsating energy wave in the regulating chamber 12 and the air-conditioning duct 123, wherein L2 is the change curve of the pulsating energy wave.

[0063] As attached Figure 5As shown, the first channel 121 and the second channel 122 are coaxially arranged, and the second channel 122 and the air-conditioning duct 123 are coaxially arranged, that is, the central axes of the first channel 121, the second channel 122 and the air-conditioning duct 123 are located on the same straight line, the first channel 121, the second channel 122 and the air-conditioning duct 123 are connected, and the radial dimension of the first channel 121 is smaller than the radial dimension of the second channel 122.

[0064] In one example, the radial dimension of the air conditioning duct 123 is smaller than the radial dimension of the second channel 122 , and the radial dimension of the air conditioning duct 123 is larger than the radial dimension of the first channel 121 .

[0065] Referring to curve L2, when the pulsating energy wave is discharged from the air cavity 11 to the first channel 121 along with the refrigerant, its amplitude is suppressed by the first channel 121, and the amplitude is reduced, but its frequency is still relatively large. When the pulsating energy wave is discharged from the first channel 121 to the second channel 122 along with the refrigerant, its amplitude increases relative to the amplitude in the first channel 121, but the frequency is significantly reduced relative to the frequency in the first channel 121. When the energy wave is discharged from the second channel 122 to the air-conditioning duct 123 along with the refrigerant, the amplitude is reduced, and the frequency is similar to that in the second channel 122.

[0066] In one example, the axial lengths of the first channel 121 and the second channel 122 are the same. Optionally, the axial length of the first channel 121 is determined by the displacement and rated compression ratio of the compressor, and those skilled in the art can select a suitable axial length according to actual application scenarios and requirements.

[0067] See attached Figure 6 , attached Figure 6 This is a data table of the radial dimension setting and axial dimension setting (characteristics) of the first channel 121 and the second channel 122, the rotation speed (rpm) of the compressor, and the exhaust pulsation (pulsation), wherein "two holes concentric" in the characteristic part indicates that the first channel 121 and the second channel 122 are coaxially arranged, and "two holes non-concentric" indicates that the first channel 121 and the second channel 122 are eccentrically arranged. The first data in the characteristic part indicates the radial dimension and axial length of the first channel 121, such as "φ6×20" indicates that the radial dimension of the first channel 121 is 6 mm, and the axial length is 20 mm. The second data indicates the radial dimension and axial length of the second channel 122, such as "φ18×20" indicates that the radial dimension of the second channel 122 is 18 mm, and the axial length is 20 mm.

[0068] Based on the attached Figure 6It can be concluded from the table data that when the first channel 121 and the second channel 122 are coaxially arranged, and the radial dimension of the first channel 121 is set to 5 mm, and the radial dimension of the second channel 122 is set to 18 mm, the pulsation value is the smallest, and the pulsation weakening effect is best.

[0069] When the axial lengths of the first channel 121 and the second channel 122 are different, the pulsation value is larger. When the axial lengths of the first channel 121 and the second channel 122 are both 20 mm, the pulsation is best weakened.

[0070] Therefore, in a preferred example of the present invention, the radial dimension of the first channel 121 is set to 5 mm, the radial dimension of the second channel 122 is set to 18 mm, and the axial lengths of the first channel 121 and the second channel 122 are both 20 mm.

[0071] See attached Figure 7 , attached Figure 7 The table shows the radial and axial dimensions of the first channel 121 and the second channel 122, the speed of the compressor (rpm), and the efficiency COP (coefficient of performance, energy conversion efficiency ratio). Figure 6 They are basically the same and will not be elaborated here.

[0072] Among them, efficiency COP is one of the important parameters for evaluating the working performance of the compressor. The larger the value of efficiency COP, the higher the efficiency of the compressor and the better the performance.

[0073] Based on the attached Figure 7 , combined with the first and sixth rows of data, when the radial dimensions of the first channel 121 and the second channel 122 remain unchanged, and the axial dimension parameters remain unchanged, when the first channel 121 and the second channel 122 are coaxially arranged, the efficiency COP value is larger, and the working performance of the compressor is better. Figure 6 , setting the first channel 121 and the second channel 122 to be coaxial can enable the compressor to have smaller exhaust pulsation and better working performance.

[0074] Combined with the data from the first to third rows, when the first channel 121 and the second channel 122 are coaxially arranged and have the same axial length, when the compressor is in a low speed state, the radial dimension of the first channel 121 is set to 6 mm, the radial dimension of the second channel 122 is set to 18 mm, and the radial dimension of the first channel 121 is set to 7 mm, the radial dimension of the second channel 122 is set to 18 mm, the efficiency COP value is larger, and the working performance of the compressor is better. Since the moving disk of the compressor completes an exhaust and intake process every time it rotates relative to the static disk, the pulsation will be more obvious in the low speed state. As the speed increases, the pulsation will gradually stabilize. Combined with the attached Figure 6 In the pulsation values ​​of the first and second rows, when the radial dimension of the first channel 121 is set to 6 mm and the radial dimension of the second channel 122 is set to 18 mm, the compressor can have a smaller pulsation value at a low speed and a higher efficiency COP.

[0075] Combining the data of the first, fourth and fifth rows, when the radial dimension of the first channel 121 is 6 mm, the radial dimension of the second channel 122 is 18 mm, and the first channel 121 and the second channel 122 are coaxially arranged, when the axial lengths of the first channel 121 and the second channel 122 are different, the efficiency COP value is slightly greater than the efficiency COP value when the axial lengths are the same, but the combined effect of the attached Figure 6 In the pulsation values ​​of the first, fourth and fifth rows, when the axial lengths of the first channel 121 and the second channel 122 are both 20 mm, the pulsation values ​​are relatively small. At the same time, the efficiency COP value can be better, which has a better effect on weakening the pulsation.

[0076] Therefore, combined with the Figure 6 and attached Figure 7 In a preferred example of the present invention, the first channel 121 and the second channel 122 are coaxially arranged, the radial dimension of the first channel 121 is set to 6 mm, the radial dimension of the second channel 122 is set to 18 mm, and the axial lengths of the first channel 121 and the second channel 122 are both 20 mm, which can reduce the exhaust pulsation of the compressor at low speed and have better working performance.

[0077] In a preferred example of the present invention, the ratio of the radial dimension of the first channel 121 to the radial dimension of the second channel 122 is 1:3.

[0078] In a preferred example of the present invention, the axial lengths of the first channel 121 and the second channel 122 are equal.

[0079] Based on the above-mentioned compressor shock-absorbing end cover, the utility model also proposes a compressor, including the above-mentioned cover body 10, and a vortex plate assembly matched with the cover body 10, the vortex plate assembly includes a coaxially arranged movable plate and a stationary plate, the movable plate can rotate axially relative to the stationary plate to form a compression space for compressing refrigerant between the movable plate and the stationary plate, and an exhaust hole is opened on the stationary plate, the exhaust hole is connected to the compression space and connected to the air cavity 11.

[0080] In one example, a silencer bag is provided on the air-conditioning duct 123, and the silencer bag cooperates with the compressor of the present invention to improve the shock absorption effect, thereby improving the comfort of the entire vehicle.

[0081] By adopting the compressor shock-absorbing end cover of the utility model, the regulating chamber 12 is divided into a first channel 121 and a second channel 122 which are connected. By setting the radial dimension of the first channel 121, the first channel 121 can weaken the intensity of the energy wave in the refrigerant. By setting the radial dimension of the second channel 122 larger than that of the first channel 121, the second channel 122 can further weaken the intensity of the energy wave, so that the energy wave carried in the refrigerant discharged from the second channel 122 to the air-conditioning duct 123 is weakened, thereby weakening the vibration brought to the air-conditioning duct 123 and the air-conditioning main unit by the refrigerant, reducing the roar in the passenger compartment, making the vehicle have good NVH performance, and preventing the resonance in the passenger compartment from causing vibration of the steering wheel and pedals, avoiding the problem of numb hands and feet of the driver, and improving the driving experience of the driver and the riding experience of the passengers in the vehicle.

[0082] The compressor of the utility model can reduce the intensity of the energy wave discharged from the compressor as the refrigerant is discharged, thereby reducing the resonance probability in the passenger compartment and having good practicality.

[0083] The above is only a specific implementation of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily thought of by any technician familiar with the technical field within the technical scope disclosed in the present invention should be included in the protection scope of the present invention.

Claims

1. A shock-absorbing end cover for a compressor, characterized in that: The invention comprises a cover body (10), wherein the cover body (10) comprises an air cavity (11) and an adjusting cavity (12) connected to the air cavity (11); the air cavity (11) is located at one end of the cover body (10) close to a scroll assembly; the adjusting cavity (12) comprises a first channel (121) and a second channel (122) distributed radially along the cover body (10); one end of the first channel (121) is connected to the air cavity (11), and the other end is connected to the second channel (122); one end of the second channel (122) away from the first channel (121) passes through the cover body (10) in the radial direction of the cover body (10) and is used for connecting an air conditioning duct (123); the radial dimension of the first channel (121) is smaller than the radial dimension of the second channel (122).

2. The compressor shock absorbing end cover according to claim 1, characterized in that: The radial dimension of the air conditioning duct (123) is smaller than the radial dimension of the second channel (122), and larger than the radial dimension of the first channel (121).

3. The compressor shock absorbing end cover according to claim 1, characterized in that: The first channel (121), the second channel (122) and the air conditioning duct (123) are coaxially arranged.

4. The compressor shock absorbing end cover according to claim 1, characterized in that: The first channel (121) and the second channel (122) are eccentrically arranged, and the second channel (122) and the air conditioning pipe (123) are coaxially arranged or eccentrically arranged.

5. The compressor damping end cover according to claim 4, characterized in that: When the second channel (122) and the air conditioning duct (123) are eccentrically arranged, the first channel (121) and the air conditioning duct (123) are coaxially arranged.

6. The compressor damping end cover according to claim 3 or 4, characterized in that: The scroll assembly comprises a moving disk and a stationary disk, the stationary disk comprises an exhaust hole, and the radial dimension of the first channel (121) is the same as the radial dimension of the exhaust hole.

7. The compressor damping end cover according to claim 1, characterized in that: The ratio of the radial dimension of the first channel (121) to the radial dimension of the second channel (122) is 1:

3.

8. The compressor damping end cover according to claim 1, characterized in that: The axial length of the first channel (121) is the same as the axial length of the second channel (122).

9. The compressor damping end cover according to claim 1, characterized in that: The air cavity (11) comprises a first cavity (111) and a second cavity (112); a partition wall (113) is provided between the first cavity (111) and the second cavity (112); the first cavity (111) is located in the middle of the cover body (10); the second cavity (112) surrounds the outer periphery of the first cavity (111) and is connected to the first channel (121); the depth of the first cavity (111) along the axial direction of the cover body (10) is less than the axial depth of the second cavity (112).

10. A compressor, characterized in that: It comprises the compressor damping end cover as described in any one of claims 1 to 9, and comprises a scroll assembly, the scroll assembly comprises a moving disk and a stationary disk, the moving disk can rotate axially relative to the stationary disk, the stationary disk is provided with an exhaust hole, and the exhaust hole is connected to the air cavity (11).

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