Air conditioner
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- QINGDAO HISENSE HITACHI AIR CONDITIONING SYST
- Filing Date
- 2024-03-07
- Publication Date
- 2026-07-21
Smart Images
Figure CN120609143B_ABST
Abstract
Description
Technical Field
[0001] This invention relates to the field of household appliance technology, and more particularly to an air conditioner. Background Technology
[0002] As people demand higher and higher stability in the operation of air conditioners, twin-rotor compressors are being used more and more widely in air conditioners.
[0003] It should be noted that air source heat pumps are also a type of air conditioner.
[0004] Air conditioners include twin-rotor compressors.
[0005] A twin-rotor compressor has two rotors at a 180° angle. When the twin-rotor compressor is running, the centrifugal forces generated by the eccentricity of the two rotors can cancel each other out, thus making the twin-rotor compressor more stable in operation.
[0006] When the rotor rotates once, the cylinder compresses the refrigerant twice. Therefore, the vibration frequency of a twin-rotor compressor is approximately twice the compressor's operating frequency, i.e., double-frequency vibration. Double-frequency vibration noise is low-frequency noise, with a long propagation distance, low dissipation during propagation, and strong penetrating power. This makes the noise from air conditioner operation prone to disturbing residents.
[0007] The double-frequency noise of a twin-rotor compressor is mainly concentrated in the low-frequency range of 100Hz-200Hz. Current pipeline designs often only address the double-frequency vibration noise problem when it is discovered during the noise test of the entire air conditioner, and then make pipeline modifications. It is rare to be able to prevent it in advance.
[0008] To address the double-frequency noise of a twin-rotor compressor, the main rectification method is to add counterweights such as vibration dampers to the pipeline connected to the compressor in order to reduce the noise of the air conditioner.
[0009] Because the diameter of the air supply pipe is relatively small, blindly adding a vibration damper to the air supply pipe may temporarily solve the vibration and noise problem, but due to the added weight, the pipe may break at weak points such as welds or bends during subsequent vibration tests on the test bench, requiring repeated vibration tests. Summary of the Invention
[0010] This invention at least partially solves one of the technical problems in the related art.
[0011] Therefore, this application aims to provide an air conditioner.
[0012] The air conditioner according to this application includes: a dual-rotor compressor having two rotors and an intake port and an exhaust port;
[0013] The first heat exchanger has one end connected to the air intake port;
[0014] The second heat exchanger has one end connected to the exhaust port;
[0015] A throttling device, the two ends of which are connected between the first heat exchanger and the second heat exchanger;
[0016] A gas supply line is connected between the twin-rotor compressor and the first heat exchanger;
[0017] Before fabricating the gas supply pipeline, a finite element model of the compressor-gas supply pipeline is established, and modal simulation is performed on the gas supply pipeline to obtain the natural frequencies f1, f2, f3...fn;
[0018] If the natural frequencies f1, f2, and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2, and f3 is not less than f_pressure;
[0019] Then, a harmonic response analysis based on the modal superposition method is performed to obtain the maximum displacement value and the location of occurrence of the natural frequencies f1, f2 and f3 of the gas supply pipeline when the frequency of the dual rotor compressor is within the second harmonic range [f_initial, 2f_pressure]. The maximum vibration displacement wmax and vibration frequency fwmax are obtained, and it is determined whether the maximum displacement meets the displacement test benchmark.
[0020] If not, add a damping hammer at the maximum vibration displacement and perform harmonic response analysis based on modal superposition method again.
[0021] The air conditioner according to this application includes: a dual-rotor compressor having two rotors and an intake port and an exhaust port;
[0022] The first heat exchanger has one end connected to the air intake port;
[0023] The second heat exchanger has one end connected to the exhaust port;
[0024] A throttling device, the two ends of which are connected between the first heat exchanger and the second heat exchanger;
[0025] A gas supply line is connected between the twin-rotor compressor and the first heat exchanger;
[0026] Before fabricating the gas supply pipeline, a finite element model of the compressor-gas supply pipeline is established, and modal simulation is performed on the gas supply pipeline to obtain the natural frequencies f1, f2, f3...fn;
[0027] If the natural frequencies f1, f2, and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2, and f3 is not less than f_pressure;
[0028] Then, a harmonic response analysis based on the modal superposition method is performed to obtain the maximum displacement value and the location of occurrence of the natural frequencies f1, f2 and f3 of the gas supply pipeline when the frequency of the dual rotor compressor is within the second harmonic range [f_initial, 2f_pressure]. The maximum vibration displacement wmax and vibration frequency fwmax are obtained, and it is determined whether the maximum displacement meets the displacement test benchmark.
[0029] When the maximum displacement meets the displacement test benchmark, random vibration simulation is performed on the air supply pipeline with added shock absorber.
[0030] If the maximum stress value is less than the stress test benchmark, then prepare the gas supply pipeline for testing.
[0031] In some embodiments of this application, if the first-order natural frequency, the second-order natural frequency, and the third-order natural frequency are all not greater than the compressor's maximum frequency f_pressure, then the diameter of the air supply line is changed and / or the length of the air supply line is changed until the natural frequencies f1, f2, and f3 satisfy the first fixed-frequency condition.
[0032] In some embodiments of this application, the first fixed-frequency condition is that the natural frequencies f1, f2 and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2 and f3 is not less than the compressor's maximum operating range f_pressure.
[0033] In some embodiments of this application, finitial is the initial operating frequency of the compressor, and 2fpressure is twice the maximum operating frequency fpressure of the compressor.
[0034] In some embodiments of this application, random vibration simulation is enhanced by applying a PSD power spectral density, with data taken from relevant data on vertical random vibration of highway transportation, and the test time is calculated based on a transportation distance of 3000km according to the calculation formula provided by the national standard.
[0035] In some embodiments of this application, if at least one of the inherent frequencies f1, f2 and f3 does not belong to the interval [f_initial, 2f_pressure], the pipeline is redesigned and the pipe type and / or wall thickness of the air supply pipeline is changed so that the inherent frequencies f1, f2 and f3 satisfy the first fixed frequency condition.
[0036] The first fixed-frequency condition is that the natural frequencies f1, f2 and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2 and f3 is not less than the compressor's maximum operating range f_pressure.
[0037] In some embodiments of this application, if at least one of the inherent frequencies f1, f2 and f3 does not belong to the interval [f_initial, 2f_pressure], the pipeline is redesigned and the pipe type and / or wall thickness of the air supply pipeline is changed so that the inherent frequencies f1, f2 and f3 satisfy the first fixed frequency condition.
[0038] The first fixed-frequency condition is that the natural frequencies f1, f2 and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2 and f3 is not less than the compressor's maximum operating range f_pressure.
[0039] In some embodiments of this application, the displacement test benchmark is that when the compressor operating frequency is below 50Hz, the peak vibration displacement does not exceed 800µm.
[0040] In some embodiments of this application, the harmonic response analysis based on the modal superposition method is as follows: an X-axis is established connecting the axis of the dual-rotor compressor and the axis of the gas supply tank, the Z-axis is along the direction of the compressor axis, and the Y-axis is perpendicular to the XZ-axis plane; a load is applied to the compressor along the established coordinate axis, and the load is mainly gas torque and unbalanced centrifugal force.
[0041] This application has at least the following positive effects:
[0042] This invention proposes an air conditioner. The air conditioner includes a dual-rotor compressor with two rotors and an intake port and an exhaust port; a first heat exchanger connected at one end to the intake port; a second heat exchanger connected at one end to the exhaust port; a throttling device connected at both ends between the first and second heat exchangers; and a gas supply pipeline connected between the dual-rotor compressor and the first heat exchanger. Before fabricating the gas supply pipeline, a finite element model of the compressor-gas supply pipeline is established, and modal simulation is performed on the gas supply pipeline to obtain the natural frequencies f1, f2, f3...fn. If the natural frequencies f1, f2, and f3 all belong to the interval [finitial, 2fpressure], and at least one of f1, f2, and f3 is not less than fpressure, then modal superposition is performed. Additive harmonic response analysis is used to obtain the maximum displacement values and locations corresponding to the natural frequencies f1, f2, and f3 of the air supply pipeline within the second harmonic range [finitial, 2fpressure]. The maximum vibration displacement wmax and vibration frequency fwmax are obtained to determine whether the maximum displacement meets the displacement test benchmark. If not, a vibration damping hammer is added at the maximum vibration displacement, and harmonic response analysis based on modal superposition is performed again. This ensures that vibration and noise issues are considered from the beginning of the design of the air supply pipeline, and noise problems are avoided in the design before manufacturing. This effectively saves time and production costs and can effectively reduce the noise of the air supply pipeline. Attached Figure Description
[0043] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.
[0044] Figure 1 This is a view of the removed portion of the housing of an air source heat pump according to an embodiment of this application;
[0045] Figure 2 This is a view of the removed portion of the housing of an air source heat pump according to an embodiment of this application;
[0046] Figure 3 This is a view of the removed portion of the housing of an air source heat pump according to an embodiment of this application;
[0047] Figure 4 This is a view of a partially disassembled housing and part of a fan of an air source heat pump according to an embodiment of this application;
[0048] Figure 5 yes Figure 4 Enlarged image A in the image;
[0049] Figure 6 This is a schematic diagram of the XY axes established by the harmonic response analysis of an air conditioner based on the modal superposition method according to an embodiment of this application;
[0050] Figure 7 This is a schematic diagram showing the connection between the compressor and the gas supply line of an air conditioner according to an embodiment of this application;
[0051] Figure 8 This is a schematic diagram showing the connection of the compressor, air supply line, and weight reduction hammer of an air conditioner according to an embodiment of this application;
[0052] Figure 9 The power spectral density curve of the air conditioner under random vibration simulation according to the embodiments of this application is shown.
[0053] Figure 10 This is a process for determining whether the diameter or length of the air supply pipeline of the air conditioner according to the embodiments of this application meets the requirements;
[0054] Figure 11 This is the flow chart of the air supply pipeline design for an air conditioner according to the embodiments of this application;
[0055] Figure 12 This is the flow chart of the air supply pipeline design for an air conditioner according to the embodiments of this application;
[0056] Figure 13 This is a load diagram of the air supply pipeline of an air conditioner according to an embodiment of this application;
[0057] In the above figures: 100, Air source heat pump; 1, Housing; 11, Air inlet; 12, Air outlet; 13, Base plate; 2, Middle partition plate; 21, Threaded connection hole; 22, Connecting plate; 221, Protruding surface; 3, Heat exchanger; 4, Fan; 51, Compressor; 52, Air supply line; 53, Weight reduction hammer; 6, First tank; 61, Extension mounting plate; 62, Water inlet pipe; 63, Water outlet pipe; 7, Threaded connector; 8, Support plate; 9, Top connecting plate; 91, Water pipe connection hole. Detailed Implementation
[0058] The present invention will now be described in detail through exemplary embodiments. However, it should be understood that, without further description, elements, structures, and features in one embodiment may be advantageously incorporated into other embodiments.
[0059] In the description of this invention, it should be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this 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. Therefore, they should not be construed as limiting this invention.
[0060] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature.
[0061] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.
[0062] In the following text, reference will be made to the appendix. Figure 1-5 The implementation methods of this application are described in detail.
[0063] This application provides an air source heat pump with a hanging, high-efficiency tank mounting structure.
[0064] The air source heat pump of this application includes a housing 1, which constitutes the overall appearance of the air source heat pump and is located on the outermost side of the air source heat pump unit.
[0065] The housing 1 includes a front panel with an air inlet 11. The location of the front panel of the housing 1 is defined as the front side of the air source heat pump.
[0066] The housing 1 also includes a rear panel, which is positioned opposite to the front panel. The location of the rear panel of the housing 1 is defined as the rear side of the air source heat pump.
[0067] The front panel of the housing 1 is provided with at least one air outlet 12 so that the airflow inside the housing 1 can be blown out to the outdoor space through the air outlet 12.
[0068] The housing 1 also includes side panels that connect the front panel and the rear panel. There are at least three side panels, one of which is located at the top of the front panel, and the other two are located on the left and right sides of the front panel, respectively.
[0069] It should be noted that the two side panels located on the left and right sides of the front panel are identical in shape and size.
[0070] The bottom of the housing 1 is provided with a base plate 13, which is opposite to the side plate located at the top of the housing 1.
[0071] The housing 1 is provided with an air inlet 11, and there is at least one air inlet 11. The air inlet 11 is located on the rear panel and / or side panel so that airflow enters the interior of the housing 1 from the air inlet 11.
[0072] The air source heat pump also includes a fan 4, which is located inside the casing 1 and is correspondingly located at the air outlet 12.
[0073] The casing 1 is provided with a heat exchange duct that communicates with the air outlet 12 and the air inlet 11, and the fan 4 is installed in the heat exchange duct.
[0074] A heat exchanger 3 is installed inside the casing 1. The refrigerant flows from the inside of the heat exchanger 3. The fan 4 rotates to form a low-pressure area inside the casing 1 so that the airflow enters the casing 1 from the air inlet 11, flows through the heat exchange air duct, exchanges heat with the heat exchanger 3, and is blown out from the air outlet 12.
[0075] The side panel located at the top of the housing 1 is defined as the top side panel, which is located on top of the front panel and the rear panel.
[0076] The front panel includes the front plate.
[0077] The front panel also includes a front access panel. The front panel and the front access panel can be installed or removed separately.
[0078] The side panel located on the right side of the housing 1 is defined as the right side panel. The right side panel is a bent panel, which is not only set on the right side of the housing 1, but also on the rear side of the housing 1.
[0079] In some embodiments of this application, an air inlet 11 is provided at the bottom of the right side plate. The air inlet 11 is connected to the heat exchange duct inside the casing 1, and the airflow flows into the heat exchange duct from the air inlet 11.
[0080] The interior of the housing 1 is provided with a partition 2, which extends along the height direction of the housing 1. The bottom of the partition 2 is connected to the bottom plate 13 of the housing 1 so that the partition 2 is fixed on the bottom plate 13. The top of the partition 2 is connected to the top side plate of the housing 1 so that the top and bottom of the partition 2 are connected to the housing 1 respectively.
[0081] The partition 2 divides the space inside the casing 1 into a fan 4 chamber and a mechanical chamber, with a fan 4 installed in the fan 4 chamber.
[0082] In some embodiments of this application, there are two fans 4 arranged vertically and vertically. The front panel of the housing 1 is provided with a first air outlet 12 and a second air outlet 12. When the fan 4 rotates, the airflow flows into the fan 4 chamber from the air inlet 11 on the right side panel. Driven by the fan 4, the air then flows out from the first air outlet 12 and the second air outlet 12, taking away the heat inside the housing 1.
[0083] In some other embodiments of this application, there is one fan 4, and one fan 4 is correspondingly disposed at the air outlet 12 on the front panel so that the air blown by the fan 4 can be directly blown out from the air outlet 12 on the front panel.
[0084] In some embodiments, the heat exchanger 3 is an evaporator, which is closely attached to the inner wall of the casing 1. The main body of the evaporator is located in the fan 4 chamber. The airflow carries the heat on the evaporator under the drive of the fan 4. The end of the evaporator extends to the mechanical chamber and is connected to the components inside the mechanical chamber.
[0085] In some embodiments, the evaporator is a curved plate heat exchanger 3 with refrigerant pipes and fins. The refrigerant pipes pass through the fins, and refrigerant flows inside the refrigerant pipes. The high-temperature and high-pressure refrigerant condenses in the condenser and releases heat to the airflow flowing through the evaporator. The heated airflow is blown out by the fan 4.
[0086] The air source heat pump includes a compressor 51 for providing the flow power of the refrigerant.
[0087] An air source heat pump includes a condenser, in which the refrigerant undergoes a condensation process.
[0088] Air source heat pumps include a throttling device that restricts the flow of refrigerant.
[0089] An air source heat pump includes an evaporator where the refrigerant undergoes an evaporation process. The compressor 51, condenser, throttling device, and evaporator together execute a refrigeration or heating cycle. The refrigeration and heating cycles include compression, condensation, expansion, and evaporation processes. By utilizing the refrigerant's heat absorption and release processes, cooling or heating is provided to the indoor space, thus regulating the indoor temperature.
[0090] Compressor 51 compresses the refrigerant gas into a high-temperature, high-pressure state and discharges the compressed refrigerant gas, which flows into the condenser. The condenser condenses the compressed, high-temperature, high-pressure gaseous refrigerant into a liquid refrigerant, and the heat is released to the surrounding environment through the condensation process.
[0091] The liquid refrigerant flowing from the condenser enters the throttling device, which causes the high-temperature, high-pressure liquid refrigerant condensed in the condenser to expand into a low-pressure liquid refrigerant. The low-pressure liquid refrigerant flowing from the throttling device enters the evaporator, where it absorbs heat and evaporates into a low-temperature, low-pressure refrigerant gas. This low-temperature, low-pressure refrigerant gas returns to the compressor 51. The evaporator achieves a cooling effect by utilizing the latent heat of refrigerant evaporation to exchange heat with the material being cooled. Throughout the cycle, the air-source heat pump regulates the temperature of the indoor space.
[0092] Air source heat pumps also include an electrical box, which is located in the machine room and connected to a power source.
[0093] Air source heat pumps also include a water supply component, which is located in the machine room.
[0094] The air source heat pump also includes a compressor 51, which is located in the machine room. The compressor 51, together with the condenser, evaporator and throttling device, forms a refrigeration system. The refrigerant flows between the compressor 51, the condenser, the evaporator and the throttling device.
[0095] The electrical box is located at the highest point in the machine room to prevent water droplets from the water supply components from falling onto it.
[0096] The water supply system includes a water pump that provides the power for water flow and is connected to the water supply system.
[0097] The water supply assembly also includes water pipes connected to the water pump, and the water pump and the water supply assembly are connected by water pipes.
[0098] To reduce the size of air source heat pumps, a shell-and-tube heat exchanger 3 is typically used as the outdoor heat exchanger 3. The shell-and-tube heat exchanger 3 has a tank-like shape. It features high heat exchange efficiency and small size, and is widely used in heat pump air source heat pump industrial chillers and heat pump water heaters that use water as the heat exchange medium. The high-efficiency tank heat exchanger 3 is a type of shell-and-tube heat exchanger 3.
[0099] Compared to plate heat exchangers 3, high-efficiency tanks have a simpler internal structure, simpler manufacturing steps, and lower manufacturing costs. In addition, the flow area between different flow paths inside the high-efficiency tank is wider, which makes it easier to clean the scale in the flow path and make the flow of refrigerant or water smoother.
[0100] The high-efficiency tank is large in volume and heavy in weight, so a large installation space needs to be reserved inside the housing 1, and a support structure with strong support capacity needs to be set up to support the high-efficiency tank.
[0101] In the existing technology, most high-efficiency tanks are directly fixed to the base plate 13 of the housing 1, or fixed to the support base of the base plate 13 of the housing 1. These two installation methods require a certain amount of installation space on the base plate 13 of the housing 1, which easily results in a large size of the housing 1 of the air source heat pump. At the same time, most of the space inside the housing 1 is occupied by the support base or the high-efficiency tank, resulting in a waste of space inside the housing 1. If other components are to be installed inside the housing 1, the size of the housing 1 can only be further increased, resulting in an increase in the overall cost of the machine.
[0102] This application provides an air source heat pump with a hanging, high-efficiency tank mounting structure.
[0103] The compressor 51 is mounted on the base plate 13, and the high-efficiency tank is mounted above the compressor 51. The high-efficiency tank and the middle partition plate 2 are connected by bolts and nuts.
[0104] The front end of the partition 2 is connected to the front panel, and the rear end of the partition 2 is connected to the heat exchanger 3.
[0105] In some embodiments, the partition 2 is a bent plate having a first partition extending in a front-rear direction and a second partition extending in a left-right direction, the second partition being connected to the rear end of the first partition.
[0106] It should be noted that the front end of the first partition is connected to the front panel, and the rear end of the second partition is connected to the evaporator.
[0107] The partition plate 2 and the extension mounting plate 61 are connected by a threaded connector 7, and the bolt is one type of threaded connector 7.
[0108] The partition plate 2 has at least one bolt hole, and the first tank has at least one extension mounting plate 61. The extension mounting plate 61 has at least one bolt hole, and at least one bolt passes through both the bolt hole on the partition plate 2 and the bolt hole on the extension mounting plate 61, so that the first tank and the partition plate 2 are connected by bolts.
[0109] In some embodiments, the first tank is a high-efficiency tank.
[0110] It should be noted that when installing the first tank onto the partition plate 2, the bolt holes of the extension mounting plate 61 on the first tank should be aligned with the bolt holes on the partition plate 2 first, then the bolts should be inserted into the bolt holes, and then the nuts should be rotated to make the nuts and bolts fit together, thereby connecting the extension mounting plate 61 of the first tank and the partition plate 2, thus fixing the first tank onto the partition plate 2.
[0111] Compared with the prior art, the lower part of the first tank 6 of this application has an installation space, which can be used to install other components, saving the installation space inside the housing 1, reducing the volume of the housing 1, and thus reducing the cost of the housing 1.
[0112] In some embodiments, the partition 2 is provided with four bolt holes, two of which are located on the first partition and the other two are located on the second partition. The two bolt holes on the first partition are on the same straight line perpendicular to the bottom plate 13, and the two bolt holes on the second partition are on the same straight line perpendicular to the bottom plate 13.
[0113] It should be noted that the rotation axis of the first tank is defined as the first axis, and the central angle formed by the centers of the two bolt holes is 90°, so as to make the force on the first tank more uniform.
[0114] In some embodiments, the extended mounting plate 61 is a bent plate, including a longitudinal plate and a transverse plate. The longitudinal plate is provided with bolt holes and is connected to the middle partition plate 2 by bolts. The transverse plate is connected to the end of the longitudinal plate near the first tank body and is connected to the tank body.
[0115] When the longitudinal plate and the middle partition plate 2 are fixedly connected by bolts and nuts, the longitudinal plate is fixed to fix the transverse plate and the middle partition plate 2, and the transverse plate is fixed to fix the tank body and the middle partition plate 2 of the first tank body.
[0116] In some embodiments, the longitudinal and transverse plates are integrally formed, eliminating the need to assemble the transverse and longitudinal plates separately, thus reducing production steps.
[0117] In some embodiments, a connecting plate 22 is also provided at the bolt hole of the partition plate 2. The connecting plate 22 and the partition plate 2 are fixed by fasteners. The connecting plate 22 is provided with bolt holes. The bolt holes on the connecting plate 22 and the bolt holes on the partition plate 2 are arranged opposite to each other so that the same bolt can be inserted into the bolt holes on the connecting plate 22 and the partition plate 2 at the same time.
[0118] When the bolt passes through the partition plate 2, the connecting plate 22 and the extension mounting plate 61 at the same time, in order to fix the three, the nut is connected to the side of the connecting plate 22 away from the partition plate 2. The nut is rotated to tighten the nut and the bolt. The nut gives the connecting plate 22 a force toward the partition plate 2, and the partition plate 2 is subjected to the pressure given by the connecting plate 22 toward the extension mounting plate 61.
[0119] In some embodiments, the middle portion of the connecting plate 22 protrudes in a direction away from the partition plate 2 to form a protruding surface 221, and bolt holes are provided on the protruding surface 221. When a bolt is inserted into the bolt hole, since the protruding surface 221 of the connecting plate 22 does not completely contact the partition plate 2, there is a certain distance between the protruding surface 221 and the partition plate 2, thereby creating a certain deformation gap between the protruding surface 221 and the partition plate 2. When the protruding surface 221 undergoes a small deformation, the protruding surface 221 cannot directly compress the partition plate 2, which can reduce the probability of the partition plate 2 deforming.
[0120] In some embodiments, the connecting plate 22 and the partition plate 2 are connected by welding, which is simple to operate.
[0121] In some embodiments, a support plate 8 is provided on the base plate 13, the bottom of the support plate 8 is fixed on the base plate 13, and the support plate 8 extends in the vertical direction.
[0122] In some embodiments, the top of the support plate 8 is connected to the top connecting plate 9, the top connecting plate 9 extends in the front-back direction, and the top support plate 8 is provided with at least one water pipe connection hole 91, and the water pipe is connected to the top support plate 8.
[0123] In some embodiments, the top connecting plate 9 is provided with two water pipe connection holes 91, one of which is connected to the water inlet pipe 62 of the first tank and the other is connected to the water outlet pipe 63 of the first tank. The water inlet pipe 62 and the water outlet pipe 63 of the first tank have a certain weight. The top connecting plate 9 is supported by the support plate 8 and supports the water pipes passing through the top connecting plate 9.
[0124] In other embodiments, the top connecting plate 9 extends in the left-right direction.
[0125] The steps for installing the first tank are described in detail below:
[0126] First, the first tank body and the middle partition 2 are installed, and the extension mounting plate 61 on the first tank body and the middle partition 2 are connected and fixed by bolts and nuts.
[0127] Next, the first tank and the middle partition 2 are hoisted together and then installed onto the base plate 13.
[0128] It should be noted that a lifting hole is provided on the first tank. In some embodiments, the weight of the first tank is 15kg, and the total weight of the first tank and the middle partition 2 is 20kg. The cantilever lifts the first tank and the middle partition 2, and the installer lifts the first tank and the middle partition 2 and installs them onto the base plate 13.
[0129] Next, connect the support plate 8 and the base plate 13, and then connect the top connecting plate 9 to the water inlet pipe 62 and the water outlet pipe 63.
[0130] In some embodiments, the support plate 8 and the base plate 13 are connected by screws, the inlet pipe 62 and the outlet pipe 63 are provided with brass parts, and the top connecting plate 9 is connected to the inlet pipe 62 and the outlet pipe 63.
[0131] Finally, the buckles of the top connecting plate 9 and the slots of the support plate 8 are connected and fixed with screws, which makes installation convenient and reduces installation steps.
[0132] In the following text, reference will be made to the appendix. Figure 6-13 The implementation methods of this application are described in detail.
[0133] As people demand higher and higher stability in the operation of air conditioners, the 51 twin-rotor compressor is being used more and more widely in air conditioners.
[0134] It should be noted that air source heat pumps are also a type of air conditioner.
[0135] The air conditioner includes a twin-rotor compressor 51.
[0136] The twin-rotor compressor 51 has two rotors at a 180° angle. When the twin-rotor compressor 51 is running, the centrifugal forces generated by the eccentricity of the two rotors can cancel each other out, thus making the twin-rotor compressor 51 more stable in operation.
[0137] When the rotor rotates once, the cylinder compresses the refrigerant twice. Therefore, the vibration frequency of the dual-rotor compressor 51 is approximately twice the operating frequency of the compressor 51, i.e., the dual-rotor compressor 51 vibrates at twice the frequency. This twice-frequency vibration noise is low-frequency noise, with a long propagation distance, low dissipation during propagation, and strong penetrating power. This makes the noise from the air conditioner easily disturb residents during operation.
[0138] The double-frequency noise of the dual-rotor compressor 51 is mainly concentrated in the low frequency range of 100Hz-200Hz. Current pipeline designs often only address the double-frequency vibration noise problem when it is discovered during the noise test of the whole air conditioner, and then make pipeline modifications. It is rare to be able to prevent it in advance.
[0139] To address the double-frequency noise of the twin-rotor compressor 51, the main rectification method is to add counterweights such as vibration dampers to the pipeline connected to the compressor 51 to reduce the noise of the air conditioner.
[0140] Because the diameter of the air supply pipe is relatively small, blindly adding a vibration damper to the air supply pipe 52 may temporarily solve the vibration and noise problem, but due to the added weight, the pipe may break at weak points such as welds or bends during subsequent vibration tests on the platform, requiring repeated vibration tests.
[0141] This application provides an air conditioning system with a gas supply pipe 52 that has a good vibration reduction effect.
[0142] The air supply pipe 52 of the air conditioner in this application is first calculated, and then manufactured according to the calculated dimensions.
[0143] Before fabricating the gas supply line 52, a finite element model of the compressor 51-gas supply line 52 is established, and modal simulation of the gas supply line 52 is performed to obtain the natural frequencies f1, f2, f3...fn.
[0144] Based on design experience, the air supply line 52 of the twin-rotor compressor 51 often vibrates at the second harmonic frequency.
[0145] If the natural frequencies f1, f2, f3...fp are not greater than the maximum operating frequency fpressure of compressor 51, then the probability of pipeline resonance occurring during normal operation of compressor 51 is relatively high.
[0146] Where p≥3.
[0147] Specifically, when the gas supply line 52 is designed to be too flexible, its fixed frequency will exceed the third order within the maximum operating range f pressure of the compressor 51, and the probability of pipeline resonance within the operating range of the compressor 51 will be relatively high.
[0148] If f1 in the natural frequency is not less than 2f, the energy of the compressor 51 vibration will be transmitted to the connected components through the pipeline, the air supply pipeline 52 is too rigid, and the double frequency sound is amplified.
[0149] Among them, 2f pressure is twice the maximum operating frequency f pressure of compressor 51, and the gas supply line 52 of the dual rotor compressor 51 usually vibrates at the second frequency.
[0150] Specifically, when the air supply line 52 is designed to be too rigid, that is, when the first natural frequency f1 of the air supply line 52 is higher than the second harmonic 2f of the maximum operating range of the compressor 51, the energy of the compressor 51 vibration will be transmitted through the line to the components connected to it, and then to the base plate 13 and the surrounding sheet metal, causing the harmonic sound to be amplified.
[0151] Determine the relationship between the natural frequencies f1, f2, and f3 and the interval [f_initial, 2f_pressure].
[0152] Where finitial is the initial operating frequency of compressor 51. 2fpressure is twice the maximum operating frequency of compressor 51.
[0153] If the natural frequencies f1, f2, and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2, and f3 is not less than the maximum operating range f_pressure of compressor 51, then it is determined that the gas supply line 52 is not too flexible or too rigid, and then a harmonic response analysis based on the modal superposition method is performed.
[0154] The first fixed-frequency condition is defined as follows: the natural frequencies f1, f2 and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2 and f3 is not less than the maximum operating range f_pressure of the compressor 51.
[0155] If at least one of the natural frequencies f1, f2, and f3 does not belong to the interval [f_initial, 2f_pressure], the pipeline is redesigned, and the pipe type and / or wall thickness of the air supply pipeline 52 are changed so that the natural frequencies f1, f2, and f3 satisfy the first fixed frequency condition.
[0156] If the natural frequencies f1, f2, and f3 are all less than the maximum operating range f pressure of the compressor 51, the pipeline will be redesigned, and the pipe type and / or wall thickness of the gas supply pipeline 52 will be changed so that the natural frequencies f1, f2, and f3 meet the first fixed frequency condition.
[0157] The following describes the specific implementation examples:
[0158] In some embodiments, the gas supply line 52 is connected between the twin-rotor compressor 51 and the plate heat exchanger 3. The gas supply line 52 is designed with a diameter of D1 and a length of L1.
[0159] In some embodiments, D1 = 9.53 mm. The compressor 51 operates at a frequency of 20-110 Hz, and L1 = 870 mm.
[0160] The models of the twin-rotor compressor 51 and the air supply line 52 were imported into the finite element analysis software ANSYS Workbench to establish a finite element model of compressor 51 and air supply line 52. Modal simulation was performed on the air supply line 52 to obtain the first, second, third and fourth natural frequencies.
[0161] As shown in Table 1 below:
[0162] 57.8HZ 68.5HZ 101.5HZ 160.7HZ
[0163] Table 1
[0164] Obtain the natural frequency range of the first three orders;
[0165] If the first, second, and third natural frequencies are all not greater than the maximum frequency f of the compressor 51, it is determined that the design of the air supply line 52 is too flexible and cannot meet the requirements of the natural frequency design. It is likely to resonate within the second harmonic operating range of the compressor 51. Therefore, it is necessary to increase the strength of the air supply line 52: increase the diameter of the air supply line 52 to D2, D2≥D1, or reduce the length of the air supply line 52 to L2, L2≤L1, so that the air supply line 52 is neither too flexible nor too rigid. Only when the air supply line 52 is within a relatively normal range will the noise generated by the vibration of the air supply line 52 be reduced.
[0166] In some embodiments, f pressure is 110 Hz. If the first-order natural frequency, second-order natural frequency and third-order natural frequency tested in this embodiment are not greater than the maximum frequency f pressure of the compressor 51, it is determined that the air supply line 52 is designed to be too flexible. After adjustment, the first-order natural frequency, second-order natural frequency, third-order natural frequency and fourth-order natural frequency are tested again.
[0167] The model of the dual-rotor compressor 51 and the air supply line 52 with the length or diameter of the air supply line 52 changed is imported into the finite element analysis software ANSYS wOrkbench to establish a finite element model of compressor 51 and air supply line 52. Modal simulation is performed on the air supply line 52 to obtain the first, second, third and fourth natural frequencies again.
[0168] As shown in Table 2 below:
[0169] 85.2HZ 157.6HZ 205.7HZ 406.4HZ
[0170] Table 2
[0171] If the first, second, and third natural frequencies are all within the second harmonic range of the compressor 51, then the solid-frequency design requirements are met.
[0172] In some embodiments, the compressor 51 has a frequency range of (20 Hz, 220 Hz).
[0173] At this time, the natural frequencies f1, f2 and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2 and f3 is not less than the maximum operating range f_pressure of compressor 51. Therefore, it is determined that the gas supply line 52 is not too flexible or too rigid. Then, harmonic response analysis based on modal superposition method is performed.
[0174] To determine whether the weight of the weight-reducing hammer 53 is sufficient, the maximum displacement value and the location of occurrence of the natural frequencies f1, f2 and f3 of the air supply pipeline 52 are obtained by harmonic response analysis based on the modal superposition method when the frequency of the compressor 51 is within the second harmonic range [f_initial, 2f_pressure]. The maximum vibration displacement wmax and vibration frequency fwmax are obtained to determine whether the maximum displacement meets the displacement test benchmark.
[0175] It should be noted that the displacement test benchmark is that when the compressor 51 operates at a frequency below 50Hz, the peak vibration displacement does not exceed 800µm.
[0176] If so, prepare the piping and test it.
[0177] If not, add a damping hammer at the maximum vibration displacement and re-perform the harmonic response analysis.
[0178] In some embodiments, the initial weight of the shock absorber is 180g for a pipe diameter of 9.53 mm and 240g for a pipe diameter of 12.7 mm.
[0179] Determine whether the displacement at the location of maximum vibration after adding a vibration damper to the pipeline meets the displacement test benchmark.
[0180] If the displacement meets the displacement test benchmark, it conforms to the design, and random vibration simulation is performed.
[0181] If the displacement does not meet the displacement test benchmark, the mass of the damping hammer will be increased by 50g each time until the displacement test benchmark is met. This will reduce the peak value of the displacement with the maximum vibration, thereby reducing the vibration of the air supply line 52 and thus reducing noise.
[0182] The following describes the specific implementation examples:
[0183] refer to Figure 6 In order to obtain the maximum response of the structure under each mode shape based on the modal superposition method for harmonic response analysis, an X-axis is established with the compressor 51 axis and the air tank axis connected, the Z-axis is along the compressor 51 axis, and the Y-axis is perpendicular to the XZ-axis plane.
[0184] Loads are applied to compressor 51 along the established coordinate axes. The loads are mainly gas torque and unbalanced centrifugal force.
[0185] In some embodiments, a gas torque is applied to the surface of the partition 2 in the cylinder of compressor 51, in the direction of upward along the Z-axis.
[0186] In some embodiments, unbalanced centrifugal force refers to the centrifugal force of the upper balance block, lower balance block, and crankshaft eccentricity of the rotor. These unbalanced centrifugal forces are in the same plane and their direction is set along the compressor 51X axis.
[0187] The load data were obtained experimentally. Some load data are shown in the figure.
[0188] The maximum displacement values and their locations corresponding to the first, second, and third order fixed frequencies of the gas supply pipeline 52 are obtained by solving the calculation based on the load within the second harmonic range of compressor 51 operation.
[0189] Locate point A at the location where the maximum vibration of the air supply pipeline 52 occurs, and obtain the maximum vibration displacement wmax and vibration frequency fwmax at point A.
[0190] The calculated maximum vibration displacement occurs at the first-order solid frequency K1. According to the second harmonic vibration characteristics of the dual-rotor compressor 51, the compressor 51 frequency corresponding to K1 is at (1 / 2K1±2)HZ, and the location of the occurrence is at the second bend of the gas supply line 52, with a maximum vibration displacement of 1064um.
[0191] According to the displacement judgment criteria, when the compressor 51 operates at a frequency below 50H1, the peak vibration displacement does not exceed 800um. Therefore, it is determined that the displacement criterion requirement is not met, and a damping hammer needs to be added to reduce the value of the peak displacement, thereby weakening the vibration of the air supply line 52 and reducing noise. Then, the harmonic response analysis is performed again.
[0192] refer to Figure 8 A weight-reducing hammer 53 with a weight of S1 is added at position B where the vibration of the air supply line 52 is the greatest. After adding the weight-reducing hammer 53, the harmonic response analysis is continued.
[0193] Based on the load data obtained from the same test as above, calculations were performed based on the load data. The maximum vibration displacement at point A was reduced to 170 μm, the resonance frequency shifted to 42 Hz, the corresponding operating frequency of compressor 51 was 21 Hz, and the maximum vibration displacement was reduced to 586 mm, which met the displacement judgment criteria. The displacement test criteria is that when the operating frequency of compressor 51 is below 50 Hz, the peak vibration displacement does not exceed 800 μm, thus determining that the weight of the weight reduction hammer 53 is sufficient.
[0194] After adding the counterweight 53 to the gas supply line 52, the increased weight makes the line more prone to breakage at weak points such as welds or bends. Therefore, it is necessary to determine the impact of random vibration on the strength of the gas supply line 52.
[0195] As shown in Table 3 below:
[0196] 42.2HZ 88.7HZ 165.3HZ 301.2HZ
[0197] Table 3
[0198] Recalculate the fixed frequency. When the fixed frequency meets the first fixed frequency condition, the air supply line 52 is in a state that is neither too flexible nor too rigid.
[0199] Random vibration simulation was performed on the air supply line 52 with added shock absorber.
[0200] It should be noted that the random vibration simulation was performed using the software ANSYS Workbench.
[0201] After random vibration simulation, determine the stress performance during random vibration after adding a damping hammer, and whether the maximum stress value is less than the stress test benchmark.
[0202] If so, prepare the gas supply line 52 for testing.
[0203] If not, the gas supply line 52 is redesigned, and this process is repeated until a gas supply line 52 that meets the stress test benchmark requirements is finally completed.
[0204] In some embodiments of this application, random vibration simulation is performed in ANSYS Workbench.
[0205] refer to Figure 9 In some embodiments, random vibration simulation requires the application of PSD power spectral density, with data taken from relevant data on vertical random vibration of highway transportation, and the test time calculated according to the calculation formula provided by the national standard based on a transportation distance of 3000km.
[0206] As shown in Table 4 below:
[0207]
[0208]
[0209] Table 4
[0210] According to the random vibration judgment criteria, the maximum Mises equivalent stress value of the pipeline under the 3σ confidence interval should be less than the judgment criterion of 150 MPa. Therefore, it meets the requirements of random vibration test. The counterweight of the air supply pipeline 52 does not need to be changed again, nor does it need to be changed again in length or diameter. For example, when the simulation shows that the maximum Mises equivalent stress value of the pipeline under the 3σ confidence interval is 75 MPa, it meets the requirements of random vibration test.
[0211] Based on the length and diameter of the air supply pipe 52 obtained from the above calculations and simulation analysis, as well as the position of the counterweight, the air supply pipe 52 can be fabricated and then tested.
[0212] The design process of the air supply pipeline 52 for the air conditioner in this application is as follows:
[0213] S10: Establish a finite element model of compressor 51 and air supply pipeline 52, perform modal simulation on air supply pipeline 52, and obtain the natural frequencies f1, f2, f3...fn;
[0214] S11: Determine whether the inherent frequencies f1, f2, f3...fp are not greater than the maximum operating frequency fpressure of compressor 51. If so, proceed to S13.
[0215] S12: Determine if f1 in the natural frequency is not less than 2f voltage; if so, then S13;
[0216] S13: Change the diameter of the air supply line 52 or change the length of the air supply line 52.
[0217] S21: If the natural frequencies f1, f2 and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2 and f3 is not less than the maximum operating range f_pressure of compressor 51, then perform harmonic response analysis based on modal superposition method and proceed to S31;
[0218] S22: Determine that at least one of the natural frequencies f1, f2, and f3 does not belong to the interval [f_initial, 2f_pressure], then S24;
[0219] S23: If the natural frequencies f1, f2, and f3 are all less than the maximum operating range fpressure of compressor 51, then S24;
[0220] S24: Redesign the pipeline, change the pipe type and / or wall thickness of the air supply pipeline 52, so that the natural frequencies f1, f2 and f3 meet the first natural frequency condition;
[0221] S31: Obtain the maximum displacement value and location of the natural frequencies f1, f2 and f3 of the gas supply line 52 when the frequency of the compressor 51 is within the second harmonic range [f_initial, 2f_pressure].
[0222] S32: Obtain the maximum vibration displacement wmax and vibration frequency fwmax, and determine whether the maximum displacement meets the displacement test benchmark; if yes, proceed to S33; otherwise, proceed to S34.
[0223] S33: Prepare the gas supply pipeline 52;
[0224] S34: Add a damping hammer at the point of maximum vibration displacement;
[0225] S41: Determine whether the displacement at the location of maximum vibration after adding a damping hammer to the pipeline meets the displacement test benchmark. If yes, proceed to S42; otherwise, proceed to S43.
[0226] S42: No further increase in the weight of the weight-reducing hammer 53;
[0227] S43: Continue to increase the mass of the shock absorber hammer, then return to S41;
[0228] S51: Perform random vibration simulation on the air supply line 52 with added shock absorber, and determine whether the maximum stress value is less than the stress test benchmark; if yes, then S52; if no, then S53.
[0229] S52: Prepare the gas supply line 52 and test it;
[0230] S53: Then the air supply pipeline 52 needs to be redesigned.
[0231] Compared to existing technologies, the air supply pipe 52 in this application is designed first and then manufactured only after the design conditions are met. This allows the air supply pipe 52 to take vibration and noise issues into account from the initial design stage, effectively saving time and production costs. It also effectively reduces the noise of the air supply pipe 52. In contrast, existing technologies do not consider the role of the air supply pipe 52 during production and can only add weight-bearing components during use, resulting in an imperfect design. The air supply pipe 52 of the air conditioner in this application has a more complete design, generates less noise, and has better safety performance.
[0232] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.
Claims
1. An air conditioner, characterized in that, include: A twin-rotor compressor has two rotors and an intake port and an exhaust port; The first heat exchanger has one end connected to the air intake port; The second heat exchanger has one end connected to the exhaust port; A throttling device, the two ends of which are connected between the first heat exchanger and the second heat exchanger; A gas supply line is connected between the twin-rotor compressor and the first heat exchanger; Before fabricating the gas supply pipeline, a finite element model of the compressor-gas supply pipeline is established, and modal simulation is performed on the gas supply pipeline to obtain the natural frequencies f1, f2, f3...fn; If the natural frequencies f1, f2, and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2, and f3 is not less than f_pressure; Then, a harmonic response analysis based on the modal superposition method is performed to obtain the maximum displacement value and the location of occurrence of the natural frequencies f1, f2 and f3 of the gas supply pipeline when the frequency of the dual rotor compressor is within the second harmonic range [f_initial, 2f_pressure]. The maximum vibration displacement wmax and vibration frequency fwmax are obtained, and it is determined whether the maximum displacement meets the displacement test benchmark. If not, add a damping hammer at the maximum vibration displacement and perform harmonic response analysis based on modal superposition method again.
2. An air conditioner, characterized in that, include: A twin-rotor compressor has two rotors and an intake port and an exhaust port; The first heat exchanger has one end connected to the air intake port; The second heat exchanger has one end connected to the exhaust port; A throttling device, the two ends of which are connected between the first heat exchanger and the second heat exchanger; A gas supply line is connected between the twin-rotor compressor and the first heat exchanger; Before fabricating the gas supply pipeline, a finite element model of the compressor-gas supply pipeline is established, and modal simulation is performed on the gas supply pipeline to obtain the natural frequencies f1, f2, f3...fn; If the natural frequencies f1, f2, and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2, and f3 is not less than f_pressure; Then, a harmonic response analysis based on the modal superposition method is performed to obtain the maximum displacement value and the location of occurrence of the natural frequencies f1, f2 and f3 of the gas supply pipeline when the frequency of the dual rotor compressor is within the second harmonic range [f_initial, 2f_pressure]. The maximum vibration displacement wmax and vibration frequency fwmax are obtained, and it is determined whether the maximum displacement meets the displacement test benchmark. When the maximum displacement meets the displacement test benchmark, random vibration simulation is performed on the air supply pipeline with added shock absorber. If the maximum stress value is less than the stress test benchmark, then a gas supply line is prepared for testing.
3. The air conditioner according to claim 1 or 2, characterized in that, If the first-order natural frequency, the second-order natural frequency, and the third-order natural frequency are all not greater than the compressor's maximum frequency f_pressure, then the diameter of the air supply line and / or the length of the air supply line are changed until the natural frequencies f1, f2, and f3 satisfy the first natural frequency condition.
4. The air conditioner according to claim 3, characterized in that, The first fixed-frequency condition is that the natural frequencies f1, f2 and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2 and f3 is not less than the compressor's maximum operating range f_pressure.
5. The air conditioner according to claim 1 or 2, characterized in that, finitial is the initial operating frequency of the compressor, and 2fpressure is twice the maximum operating frequency fpressure of the compressor.
6. The air conditioner according to claim 1 or 2, characterized in that, The random vibration simulation was enhanced by applying a PSD power spectral density. The data was taken from relevant data on vertical random vibration of highway transportation. The test time was calculated based on a transportation distance of 3000km according to the calculation formula provided by the national standard.
7. The air conditioner according to claim 1 or 2, characterized in that, If at least one of the natural frequencies f1, f2, and f3 does not belong to the interval [f_initial, 2f_pressure], the pipeline shall be redesigned and the pipe type and / or wall thickness of the air supply pipeline shall be changed so that the natural frequencies f1, f2, and f3 satisfy the first natural frequency condition. The first fixed-frequency condition is that the natural frequencies f1, f2 and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2 and f3 is not less than the compressor's maximum operating range f_pressure.
8. The air conditioner according to claim 1 or 2, characterized in that, If at least one of the natural frequencies f1, f2, and f3 does not belong to the interval [f_initial, 2f_pressure], the pipeline shall be redesigned and the pipe type and / or wall thickness of the air supply pipeline shall be changed so that the natural frequencies f1, f2, and f3 satisfy the first natural frequency condition. The first fixed-frequency condition is that the natural frequencies f1, f2 and f3 all belong to the interval [f_initial, 2f_pressure], and at least one of f1, f2 and f3 is not less than the compressor's maximum operating range f_pressure.
9. The air conditioner according to claim 1 or 2, characterized in that, The displacement test benchmark is that when the compressor operating frequency is below 50Hz, the peak vibration displacement does not exceed 800um.
10. The air conditioner according to claim 1 or 2, characterized in that, The harmonic response analysis based on the modal superposition method is as follows: an X-axis is established connecting the axis of the dual-rotor compressor and the axis of the gas supply tank, the Z-axis is along the direction of the compressor axis, and the Y-axis is perpendicular to the XZ-axis plane; loads are applied to the compressor along the established coordinate axes, and the loads are mainly gas torque and unbalanced centrifugal force.