Air conditioner

Abstract

The invention provides an air conditioner. The air conditioner comprises a double-rotor compressor which is provided with two rotors and is provided with an air suction port and an air exhaust port; one end of the first heat exchanger is connected with the air suction port; one end of the second heat exchanger is connected with the exhaust port; the two ends of the throttling device are connected between the first heat exchanger and the second heat exchanger; the air supply pipeline is connected between the double-rotor compressor and the first heat exchanger; the method comprises the following steps: before preparing an air supply pipeline, establishing a compressor-air supply pipeline finite element model, and performing modal simulation on the air supply pipeline to obtain inherent frequencies f1, f2, f3... fn; if the inherent frequencies f1, f2 and f3 all belong to an interval [f < initial >, 2f < pressure >], and at least one of f1, f2 and f3 is not less than f < pressure >; if yes, harmonic response analysis based on a modal superposition method is carried out, and the maximum displacement values and occurrence positions corresponding to the inherent frequencies f1, f2 and f3 of the air supply pipeline when the frequency of the double-rotor compressor is within the frequency doubling range [f initial, 2f pressure] are obtained; obtaining the maximum vibration displacement wmax and the vibration frequency fwmax, and judging whether the maximum displacement meets the displacement test reference or not; and if not, adding a damping hammer at the maximum vibration displacement, and carrying out harmonic response analysis based on the modal superposition method again.

Description

Technical Field

[0001] The present invention relates to the technical field of household appliances, and in particular to an air conditioner. Background Art

[0002] As people have higher and higher requirements for the stability of air-conditioning operation, twin-rotor compressors are increasingly widely used in air-conditioning.

[0003] It should be noted that air source heat pump is also a type of air conditioner.

[0004] The air conditioner includes a twin-rotor compressor.

[0005] The twin-rotor compressor has two rotors at an angle of 180 degrees. When the twin-rotor compressor is running, the centrifugal forces generated by the eccentricity of the two rotors can offset each other, so the twin-rotor compressor has higher operating stability.

[0006] When the rotors rotate one full revolution, the cylinders compress the refrigerant twice. Therefore, the vibration frequency of a twin-rotor compressor is roughly twice the compressor's operating frequency, known as double-frequency vibration. Double-frequency vibration noise is low-frequency, travels a long distance, and dissipates little energy during transmission, making it highly penetrating. This noise can easily cause nuisance to people during air conditioning operation.

[0007] The double-frequency noise of the twin-rotor compressor is mainly concentrated in the low-frequency range of 100Hz-200Hz. The current pipeline design often shows the problem of double-frequency vibration noise in the noise test of the air conditioner as a whole, and then the pipeline is rectified, and it is rarely possible to prevent it in advance.

[0008] For the double frequency noise of the twin-rotor compressor, the main correction method is to add counterweights such as shock-absorbing hammers to the pipes connected to the compressor to reduce the noise of the air conditioner.

[0009] Since the diameter of the air supply pipe is relatively thin, if a shock-absorbing hammer is blindly added to the air supply pipe, although the vibration noise problem is temporarily solved, due to the addition of counterweight, the pipe may break at weak positions such as the pipe welding points or bends during subsequent vibration tests on the platform, and repeated vibration tests are required. Summary of the Invention

[0010] The present invention solves one of the technical problems in the related art at least to a certain extent.

[0011] To this end, the present application aims to provide an air conditioner.

[0012] The air conditioner according to the present application includes: a twin-rotor compressor having two rotors and having an air intake port and an air discharge port;

[0013] a first heat exchanger, one end of which is connected to the air intake;

[0014] a second heat exchanger, one end of which is connected to the exhaust port;

[0015] a throttling device, both ends of which are connected between the first heat exchanger and the second heat exchanger;

[0016] an air supply pipeline connected between the twin-rotor compressor and the first heat exchanger;

[0017] Before preparing the air supply pipeline, a compressor-air supply pipeline finite element model is established, and a modal simulation is performed on the air 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 [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than fpressure;

[0019] A harmonic response analysis based on the modal superposition method is performed to obtain the maximum displacement value and occurrence position corresponding to the natural frequencies f1, f2, and f3 of the air supply pipeline when the frequency of the dual-rotor compressor is within the double frequency 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;

[0020] If not, add a shock-absorbing hammer at the maximum vibration displacement and perform harmonic response analysis based on the modal superposition method again.

[0021] The air conditioner according to the present application includes: a twin-rotor compressor having two rotors and having an air intake port and an air discharge port;

[0022] a first heat exchanger, one end of which is connected to the air intake;

[0023] a second heat exchanger, one end of which is connected to the exhaust port;

[0024] a throttling device, both ends of which are connected between the first heat exchanger and the second heat exchanger;

[0025] an air supply pipeline connected between the twin-rotor compressor and the first heat exchanger;

[0026] Before preparing the air supply pipeline, a compressor-air supply pipeline finite element model is established, and a modal simulation is performed on the air 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 [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than fpressure;

[0028] A harmonic response analysis based on the modal superposition method is performed to obtain the maximum displacement value and occurrence position corresponding to the natural frequencies f1, f2, and f3 of the air supply pipeline when the frequency of the dual-rotor compressor is within the double frequency 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;

[0029] When the maximum displacement meets the displacement test benchmark, a random vibration simulation is performed on the air supply pipeline with the added shock-absorbing hammer;

[0030] If the maximum stress value is less than the stress test benchmark, prepare the air supply pipeline for testing.

[0031] In some embodiments of the present application, if the first-order natural frequency, the second-order natural frequency and the third-order natural frequency are not greater than the maximum frequency fpressure of the compressor, the diameter of the air supply pipeline is changed and / or the length of the air supply pipeline is changed until the natural frequencies f1, f2 and f3 meet the first fixed frequency condition.

[0032] In some embodiments of the present application, the first fixed frequency condition is that the natural frequencies f1, f2 and f3 all belong to the interval [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than the maximum operating range of the compressor fpressure.

[0033] In some embodiments of the present 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 the present application, the random vibration simulation increases the application of PSD power spectral density, the data is taken from the vertical random vibration related data of highway transportation, and the test time is calculated according to the calculation formula provided by the national standard based on a transportation distance of 3000 km.

[0035] In some embodiments of the present application, if at least one of the values ​​of the natural frequencies f1, f2, and f3 does not fall within the interval [finitial, 2fpressure], the pipeline is redesigned by changing the pipe type and / or wall thickness of the gas supply pipeline so that the natural frequencies f1, f2, and f3 meet 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 [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than the maximum operating range of the compressor fpressure.

[0037] In some embodiments of the present application, if at least one of the values ​​of the natural frequencies f1, f2, and f3 does not fall within the interval [finitial, 2fpressure], the pipeline is redesigned by changing the pipe type and / or wall thickness of the gas supply pipeline so that the natural frequencies f1, f2, and f3 meet 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 [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than the maximum operating range of the compressor fpressure.

[0039] In some embodiments of the present application, the displacement test benchmark is that when the compressor operating frequency is below 50 Hz, the vibration displacement peak does not exceed 800 μm.

[0040] In some embodiments of the present 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 air supply tank, the Z-axis is along the axis of the compressor, and the Y-axis is perpendicular to the XZ-axis plane; a load is applied to the compressor along the set coordinate axis, and the load is mainly gas torque and unbalanced centrifugal force.

[0041] This application has at least the following positive effects:

[0042] The present invention proposes an air conditioner. The air conditioner includes a twin-rotor compressor having two rotors and an air intake and an air exhaust port; a first heat exchanger, one end of which is connected to the air intake port; a second heat exchanger, one end of which is connected to the air exhaust port; a throttling device, both ends of which are connected between the first heat exchanger and the second heat exchanger; and an air supply pipeline connected between the twin-rotor compressor and the first heat exchanger. Before preparing the air supply pipeline, a compressor-air supply pipeline finite element model is established, and a modal simulation is performed on the air supply pipeline to obtain 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 a modal superposition-based simulation is performed. The additive harmonic response analysis obtains the maximum displacement value and occurrence position corresponding to the natural frequencies f1, f2 and f3 of the air supply pipeline when the frequency of the dual-rotor compressor is within the double frequency range [finitial, 2fpressure]; obtains the maximum vibration displacement wmax and the vibration frequency fwmax, and determines whether the maximum displacement meets the displacement test benchmark; if not, adds a shock-absorbing hammer at the maximum vibration displacement, and performs the harmonic response analysis based on the modal superposition method again, so that the air supply pipeline can take the vibration noise problem into consideration at the beginning of the design, and the noise problem can be avoided before preparation, which effectively saves time and production costs, and can play an effective role in reducing the noise of the air supply pipeline. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0044] Figure 1 is a view of a partially removed housing of an air source heat pump according to an embodiment of the present application;

[0045] Figure 2 is a view of a partially removed housing of an air source heat pump according to an embodiment of the present application;

[0046] Figure 3 is a view of a partially removed housing of an air source heat pump according to an embodiment of the present application;

[0047] Figure 4 This is a view of an air source heat pump according to an embodiment of the present application with part of the housing and part of the fan removed;

[0048] Figure 5 yes Figure 4 A magnified image in Figure A;

[0049] Figure 6 is a schematic diagram of an XY axis established by harmonic response analysis of an air conditioner based on a modal superposition method according to an embodiment of the present application;

[0050] Figure 7 is a schematic diagram of the connection between the compressor and the air supply pipeline of the air conditioner according to an embodiment of the present application;

[0051] Figure 8 Schematic diagram of the connection between the compressor, air supply pipeline and weight-reducing hammer of the air conditioner according to the embodiment of the present application;

[0052] Figure 9 The power spectrum density curve of the random vibration simulation of the air conditioner according to the embodiment of the present application is

[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 embodiment of the present application meets the requirements;

[0054] Figure 11 This is a process for designing an air supply line for an air conditioner according to an embodiment of the present application;

[0055] Figure 12 This is a process for designing an air supply line for an air conditioner according to an embodiment of the present application;

[0056] Figure 13 Schematic diagram of the load of the air supply pipeline of the air conditioner according to the embodiment of the present application;

[0057] In the above figures: 100, air source heat pump; 1, casing; 11, air inlet; 12, air outlet; 13, bottom plate; 2, middle partition; 21, threaded connection hole; 22, connecting plate; 221, protruding surface; 3, heat exchanger; 4, fan; 51, compressor; 52, air supply pipeline; 53, weight-reducing hammer; 6, first tank body; 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 DESCRIPTION

[0058] The present invention is described in detail below by way of exemplary embodiments, but it should be understood that elements, structures, and features of one embodiment may be beneficially combined in other embodiments without further description.

[0059] In the description of the present invention, it should be understood that the terms "center", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention.

[0060] The terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features.

[0061] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted," "connected," and "connected" should be understood broadly. For example, they may refer to fixed connections, detachable connections, or integral connections; they may refer to direct connections, indirect connections via an intermediate medium, or internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on the specific circumstances.

[0062] In the following, reference will be made to the Figure 1-5 The embodiments of the present application are described in detail.

[0063] The present application provides an air source heat pump with a hanging high-efficiency tank installation structure.

[0064] The air source heat pump of the present application includes a casing 1, which constitutes the overall appearance of the air source heat pump. The casing 1 is located at the outermost side of the air source heat pump unit.

[0065] The housing 1 includes a front panel, on which an air inlet 11 is provided. The location of the front panel of the housing 1 is defined as the front side of the air source heat pump.

[0066] The casing 1 further includes a back panel, which is arranged opposite to the front panel. The position of the back panel of the casing 1 is defined as the rear side of the air source heat pump.

[0067] At least one air outlet 12 is provided on the front panel of the housing 1 so that the air flow in the housing 1 can be blown out to the outdoor space through the air outlet 12 .

[0068] The housing 1 further includes side panels connected between the front panel and the back 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 have the same shape and size.

[0070] A bottom plate 13 is provided at the bottom of the housing 1 , and the bottom plate 13 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 arranged on the back panel and / or the side panel so that air flows into the interior of the housing 1 through the air inlet 11 .

[0072] The air source heat pump further includes a fan 4 , which is disposed inside the casing 1 and correspondingly disposed at the air outlet 12 .

[0073] A heat exchange air duct communicating with the air outlet 12 and the air inlet 11 is provided in the casing 1 , and the fan 4 is arranged in the heat exchange air duct.

[0074] A heat exchanger 3 is provided in the casing 1, and the refrigerant flows from the inside of the heat exchanger 3. The fan 4 rotates to form a low-pressure area in the casing 1, so that the air flow enters the casing 1 from the air inlet 11, flows through the heat exchange duct, and is blown out from the air outlet 12 after heat exchange with the heat exchanger 3.

[0075] The side panel located at the top of the housing 1 is defined as a top side panel, and the top side panel is located on the top of the front panel and the back panel.

[0076] The front panel includes a front plate.

[0077] The front panel also includes a front side maintenance panel. The front panel and the front side maintenance panel can be installed or removed separately.

[0078] The side panel located on the right side of the casing 1 is defined as the right side panel. The right side panel is a bent panel and is not only provided on the right side of the casing 1 but also on the rear side of the casing 1 .

[0079] In some embodiments of the present application, an air inlet 11 is provided at the bottom end of the right side panel, and the air inlet 11 is connected to the heat exchange air duct in the casing 1, and the air flows from the air inlet 11 into the heat exchange air duct.

[0080] A middle partition 2 is provided inside the casing 1, and the middle partition 2 extends along the height direction of the casing 1. The bottom of the middle partition 2 is connected to the bottom plate 13 of the casing 1 so that the middle partition 2 is fixed on the bottom plate 13, and the top of the middle partition 2 is connected to the top side plate of the casing 1 so that the top and bottom of the middle partition 2 are respectively connected to the casing 1.

[0081] The middle partition 2 divides the space in the casing 1 into a fan 4 room and a machine room, and the fan 4 is provided in the fan 4 room.

[0082] In some embodiments of the present application, there are two fans 4 arranged at an upper and lower interval, and a first air outlet 12 and a second air outlet 12 are provided on the front panel of the casing 1. When the fan 4 rotates, the air flows into the fan 4 room from the air inlet 11 on the right 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 in the casing 1.

[0083] In some other embodiments of the present application, there is one fan 4 , and one fan 4 is correspondingly arranged at the air outlet 12 on the front panel, so that the wind blown by the fan 4 can be blown out directly from the air outlet 12 on the front panel.

[0084] In some embodiments, the heat exchanger 3 is an evaporator, which is close to the inner wall of the casing 1. The main body of the evaporator is located in the fan 4 room. The air flow drives the heat on the evaporator under the drive of the fan 4. The end of the evaporator extends to the mechanical room and is connected to the components in the mechanical room.

[0085] In some embodiments, the evaporator is a curved plate heat exchanger 3 having a refrigerant tube and fins. The refrigerant tube is passed through the fins. Refrigerant flows in the refrigerant tube. The high-temperature and high-pressure refrigerant condenses in the condenser and releases heat to the air flow passing through the evaporator. The heated air flow is blown out by the fan 4.

[0086] The air source heat pump includes a compressor 51 for providing flow power for the refrigerant.

[0087] The air source heat pump includes a condenser, in which the refrigerant undergoes a condensation process.

[0088] The air source heat pump includes a throttling device, and the refrigerant is throttled when flowing through the throttling device.

[0089] An air-source heat pump includes an evaporator, where the refrigerant evaporates. This process, which is followed by a compressor 51, a condenser, a throttling device, and the evaporator, creates a cooling or heating cycle. These cycles involve compression, condensation, expansion, and evaporation. The refrigerant absorbs and releases heat, providing cooling or heating to the indoor space, thereby regulating the indoor temperature.

[0090] The 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 liquid refrigerant, releasing heat to the surrounding environment through the condensation process.

[0091] The liquid refrigerant flowing out of the condenser enters the throttling device, which expands the high-temperature, high-pressure liquid refrigerant condensed in the condenser into low-pressure liquid refrigerant. The low-pressure liquid refrigerant flowing out of the throttling device enters the evaporator. As it passes through the evaporator, it absorbs heat and evaporates into low-temperature, low-pressure refrigerant gas. The low-temperature, low-pressure refrigerant gas returns to the compressor 51. The evaporator can achieve a cooling effect by utilizing the latent heat of evaporation of the refrigerant to exchange heat with the material to be cooled. Throughout the entire cycle, the air source heat pump can regulate the temperature of the indoor space.

[0092] The air source heat pump also includes an electrical box, which is located in the machine room and is connected to a power source.

[0093] The air source heat pump also includes a water supply component, which is arranged in the machine room.

[0094] The air source heat pump also includes a compressor 51, which is arranged in the mechanical room. The compressor 51, the condenser, the evaporator and the throttling device together constitute a refrigeration system, and the refrigerant flows between the compressor 51, the condenser, the evaporator and the throttling device.

[0095] The electrical box is set at the highest point in the mechanical room to prevent water from the water supply assembly from dripping onto the electrical box.

[0096] The water supply assembly includes a water pump, which provides the power for water flow and is connected to the water supply assembly.

[0097] The water supply component also includes a water pipeline connected to the water pump, and the water pump and the water supply component are connected through the water pipeline.

[0098] To reduce the size of an air-source heat pump, a shell-and-tube heat exchanger 3 is typically used as the outdoor heat exchanger. This canister-shaped shell-and-tube heat exchanger 3 features high heat exchange efficiency and a compact size. It is widely used in water-based heat pumps, industrial chillers, and heat pump water heaters. High-efficiency canister heat exchangers are a type of shell-and-tube heat exchanger.

[0099] Compared with the plate heat exchanger 3, the high-efficiency tank has 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 relatively wide, which can facilitate the cleaning of scale in the flow path, so that the flow of refrigerant or water is smoother.

[0100] The high-efficiency tank is large in size and heavy in weight, so a relatively large installation space needs to be reserved in the housing 1, and a supporting structure with strong supporting capacity is provided to support the high-efficiency tank.

[0101] In the existing technology, the high-efficiency tank is mostly fixed directly on the bottom plate 13 of the casing 1, or fixed on the support base of the bottom plate 13 of the casing 1. These two installation methods require a certain amount of installation space to be reserved on the bottom plate 13 of the casing 1, which easily causes the casing 1 of the air source heat pump to be larger. At the same time, most of the space in the casing 1 is occupied by the support base or the high-efficiency tank, resulting in a waste of space in the casing 1. If other components are to be arranged in the casing 1, the size of the casing 1 can only be further increased, resulting in an increase in the cost of the entire machine.

[0102] The present application provides an air source heat pump with a hanging high-efficiency tank installation structure.

[0103] The compressor 51 is mounted on the bottom plate 13 , the high-efficiency tank is mounted above the compressor 51 , and the high-efficiency tank and the middle partition plate 2 are connected by bolts and nuts.

[0104] The front end of the middle partition plate 2 is connected to the front panel, and the rear end of the middle partition plate 2 is connected to the heat exchanger 3 .

[0105] In some embodiments, the middle partition 2 is a bent plate having a first partition extending in the front-to-back direction and a second partition extending in the left-to-right direction, wherein the second partition is 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 middle partition plate 2 and the extended mounting plate 61 are connected via a threaded connector 7 , and the bolt is a type of the threaded connector 7 .

[0108] There is at least one bolt hole on the middle partition 2, and the first tank body has at least one extended mounting plate 61. The extended mounting plate 61 is provided with at least one bolt hole. At least one bolt is simultaneously passed through the bolt hole on the middle partition 2 and the bolt hole on the extended mounting plate 61, so that the first tank body and the middle partition 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 body onto the middle partition 2, it is necessary to first align the bolt holes of the extended mounting plate 61 on the first tank body with the bolt holes on the middle partition 2, then insert the bolts into the bolt holes, and then rotate the nut and make the nut and the bolt fit together to connect the extended mounting plate 61 of the first tank body and the middle partition 2, so that the first tank body is fixed on the middle partition 2.

[0111] Compared with the prior art, the lower portion of the first tank body 6 of the present application has an installation space that can be used to install other components, saving installation space within the casing 1, reducing the volume of the casing 1, and thus reducing the cost of the casing 1.

[0112] In some embodiments, four bolt holes are provided on the middle partition 2, two of which are located on the first partition, and the other two bolt holes are provided 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 body is defined as the first axis, and the central angle formed by the centers of the two bolt holes is 90°, so that the force on the first tank body is 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 the longitudinal plate is connected to the middle partition plate 2 by bolts. The transverse plate is connected to one end of the longitudinal plate close to the first tank body, and the transverse plate is connected to the tank body.

[0115] When the longitudinal plate and the middle partition 2 are fixedly connected by bolts and nuts, since the transverse plate and the longitudinal plate are connected, the longitudinal plate is fixed to fix the transverse plate and the middle partition 2, and the transverse plate is fixed to fix the tank body of the first tank body and the middle partition 2.

[0116] In some embodiments, the longitudinal plate and the transverse plate are integrally formed, and there is no need to assemble the transverse plate and the longitudinal plate, thereby reducing the number of production steps.

[0117] In some embodiments, a connecting plate 22 is further provided at the bolt hole of the middle partition 2. The connecting plate 22 and the middle partition 2 are fixed by fixing parts. Bolt holes are provided on the connecting plate 22. The bolt holes on the connecting plate 22 and the bolt holes on the middle partition 2 are arranged relative to each other so that the same bolt can be passed through the bolt holes on the connecting plate 22 and the bolt holes on the middle partition 2 at the same time.

[0118] When the bolts are simultaneously passed through the middle partition 2, the connecting plate 22 and the extended mounting plate 61, in order to fix the three, the nut is connected to the side of the connecting plate 22 away from the middle partition 2, and the nut is rotated to tighten the nut and the bolt. The nut applies force to the connecting plate 22 toward the middle partition 2, and the middle partition 2 is subjected to the pressure given by the connecting plate 22 toward the extended mounting plate 61.

[0119] In some embodiments, the middle portion of the connecting plate 22 protrudes away from the middle diaphragm 2 to form a protruding surface 221, and a bolt hole is provided in the protruding surface 221. When a bolt is inserted into the bolt hole, the protruding surface 221 of the connecting plate 22 does not completely contact the middle diaphragm 2. A certain distance exists between the protruding surface 221 and the middle diaphragm 2, thereby creating a certain deformation gap between the protruding surface 221 and the middle diaphragm 2. When the protruding surface 221 undergoes a small deformation, the protruding surface 221 cannot directly press against the middle diaphragm 2, thereby reducing the probability of deformation of the middle diaphragm 2.

[0120] In some embodiments, the connecting plate 22 and the middle partition plate 2 are connected by welding, which is easy to operate.

[0121] In some embodiments, a support plate 8 is provided on the bottom plate 13 , the bottom of the support plate 8 is fixed on the bottom plate 13 , and the support plate 8 extends in the up-down direction.

[0122] In some embodiments, the top of the support plate 8 is connected to the top connecting plate 9, and the top connecting plate 9 extends along the front-to-back direction. At least one water pipe connecting hole 91 is provided on the top support plate 8, 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 first tank's water inlet pipe 62, and the other to the first tank's water outlet pipe 63. The first tank's water inlet pipe 62 and the first tank's water outlet pipe 63 have a certain weight. The top connecting plate 9 is supported by the support plate 8 and supports the water pipes passing through it.

[0124] In other embodiments, the top connecting plate 9 extends along the left-right direction.

[0125] The following describes in detail the steps for installing the first tank:

[0126] First, the first tank body and the middle partition plate 2 are installed, and the extended mounting plate 61 on the first tank body and the middle partition plate 2 are connected and fixed by bolts and nuts.

[0127] Next, the first tank body and the middle partition plate 2 are fixedly hoisted as a whole, and then the first tank body and the middle partition plate 2 are installed on the bottom plate 13 .

[0128] It should be noted that a lifting hole is provided on the first tank body. In some embodiments, the weight of the first tank body is 15 kg, and the total weight of the first tank body and the middle partition 2 is 20 kg. The cantilever lifts the first tank body and the middle partition 2, and the installer lifts the first tank body and the middle partition 2 and installs them on the base plate 13.

[0129] Afterwards, the support plate 8 and the bottom plate 13 are connected, and then the top connecting plate 9 and the water inlet pipe 62 and the water outlet pipe 63 are connected.

[0130] In some embodiments, the support plate 8 and the bottom plate 13 are connected by screws, the water inlet pipe 62 and the water outlet pipe 63 are provided with brass parts, and the top connecting plate 9 is connected to the water inlet pipe 62 and the water outlet pipe 63.

[0131] Finally, the buckles of the top connecting plate 9 and the slots of the support plate 8 are matched and connected, and fixed with screws, which facilitates installation and reduces installation steps.

[0132] In the following, reference will be made to the Figure 6-13 The embodiments of the present application are described in detail.

[0133] As people have higher and higher requirements for the stability of air-conditioning operation, the twin-rotor compressor 51 is increasingly widely used in air-conditioning.

[0134] It should be noted that air source heat pump is 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 an angle of 180°. When the twin-rotor compressor 51 is running, the centrifugal forces generated by the eccentricity of the two rotors can offset each other, so the operation stability of the twin-rotor compressor 51 is higher.

[0137] When the rotors rotate one full revolution, the cylinders compress the refrigerant twice. Therefore, the vibration frequency of the twin-rotor compressor 51 is approximately twice the operating frequency of the compressor 51, i.e., the twin-rotor compressor 51 vibrates at a double frequency. Double frequency vibration noise is low-frequency, has a long propagation distance, and exhibits low dissipation during propagation, resulting in strong penetration. This noise can easily disturb people during air conditioning operation.

[0138] The double frequency noise of the twin-rotor compressor 51 is mainly concentrated in the low frequency range of 100Hz to 200Hz. In the current pipeline design, the problem of double frequency vibration noise often occurs in the noise test of the air conditioner as a whole, and the pipeline is then rectified, but it is rarely possible to prevent it in advance.

[0139] As for the double frequency noise of the twin-rotor compressor 51, the main rectification method is to add a counterweight such as a shock-absorbing hammer to the pipeline connected to the compressor 51 to reduce the noise of the air conditioner.

[0140] Since the diameter of the air supply pipe is relatively thin, if a shock-absorbing hammer is blindly added to the air supply pipe 52, although the vibration noise problem is temporarily solved, due to the addition of counterweight, the pipe may break at weak positions such as the pipe welding points or bends during the subsequent vibration test on the platform, and the vibration test needs to be repeated.

[0141] The present application provides an air conditioner having an air supply pipeline 52 with a good vibration reduction effect.

[0142] The air supply pipeline 52 of the air conditioner of the present application is first calculated and then prepared according to the calculated size.

[0143] Before preparing the air supply pipeline 52 , a finite element model of the compressor 51 - air supply pipeline 52 is established, and a modal simulation is performed on the air supply pipeline 52 to obtain the natural frequencies f1, f2, f3 . . . fn.

[0144] According to design experience, the air supply pipeline 52 of the twin-rotor compressor 51 often vibrates at a double frequency.

[0145] If the natural frequencies f1, f2, f3, ..., fp are not greater than the maximum operating frequency fp of the compressor 51, the probability of pipeline resonance occurring when the compressor 51 operates normally is high.

[0146] Among them, p≥3.

[0147] Specifically, when the air supply pipeline 52 is designed to be too flexible, the fixed frequency is shown as exceeding the third-order fixed frequency and is located within the maximum operating range f pressure of the compressor 51 , and the probability of pipeline resonance occurring within the operating range of the compressor 51 is high.

[0148] If f1 in the natural frequency is not less than 2f pressure, the vibration energy of the compressor 51 will be transmitted to the components connected to it through the pipeline, the air supply pipeline 52 is too rigid, and the double-frequency sound is amplified.

[0149] 2fpressure is the double frequency of the maximum operating frequency fpressure of the compressor 51, and the air supply pipeline 52 of the dual-rotor compressor 51 often vibrates at the double frequency.

[0150] Specifically, when the air supply pipeline 52 is designed to be too rigid, that is, the first-order natural frequency f1 of the air supply pipeline 52 is higher than the second harmonic frequency 2f outside the maximum operating range of the compressor 51, the vibration energy of the compressor 51 will be transmitted through the pipeline to the components connected to it, and then transmitted to the bottom 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 [finitial, 2fpressure].

[0152] Wherein, finitial is the initial operating frequency of the compressor 51. 2fpressure is the double frequency of the maximum operating frequency of the compressor 51.

[0153] 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 the maximum operating range fpressure of the compressor 51, it is determined that the air supply pipeline 52 is neither too flexible nor 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 the natural frequencies f1, f2 and f3 all belonging to the interval [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than the maximum operating range fpressure of the compressor 51.

[0155] If at least one of the natural frequencies f1, f2 and f3 does not fall within the interval [finitial, 2fpressure], the pipeline is redesigned by changing 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 fixed frequency condition.

[0156] If the natural frequencies f1, f2, and f3 are all less than the maximum operating range fpressure of the compressor 51, the pipeline is redesigned by changing 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 fixed frequency condition.

[0157] The following describes the specific embodiments:

[0158] In some embodiments, the air supply pipeline 52 is connected between the dual-rotor compressor 51 and the plate heat exchanger 3 . The designed diameter of the air supply pipeline 52 is D1 , and the length of the pipeline is L1 .

[0159] In some embodiments, D1 = 9.53 mm. The operating frequency of the compressor 51 is 20-110 Hz, and L1 = 870 mm.

[0160] The models of the dual-rotor compressor 51 and the air supply pipeline 52 were imported into the finite element analysis software ANSYS workbench to establish a finite element model of the compressor 51-air supply pipeline 52. Modal simulation was performed on the air supply pipeline 52 to obtain the first-order, second-order, third-order and fourth-order natural frequencies.

[0161] As shown in Table 1 below:

[0162] First level Second order Third level Fourth level 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-order natural frequency, the second-order natural frequency and the third-order natural frequency are all not greater than the maximum frequency fpressure of the compressor 51, it is judged that the design of the air supply pipeline 52 is too soft and cannot meet the fixed frequency design requirements. There is a high probability that resonance will occur within the double frequency operating range of the compressor 51. Therefore, it is necessary to increase the strength of the air supply pipeline 52: increase the diameter of the air supply pipeline 52 to D2, D2≥D1, or reduce the length of the air supply pipeline 52 to L2, L2≤L1, so as to reduce the air supply pipeline 52 from being too soft or too rigid. Only when the air supply pipeline 52 is in a relatively normal range, the noise generated by the vibration of the air supply pipeline 52 will be reduced.

[0166] In some embodiments, f pressure is 110HZ. If the first-order natural frequency, the second-order natural frequency and the third-order natural frequency tested in this embodiment are not greater than the maximum frequency f pressure of the compressor 51, it is judged that the air supply pipeline 52 is designed to be too flexible. After adjustment, the first-order natural frequency, the second-order natural frequency, the third-order natural frequency and the fourth-order natural frequency are tested again.

[0167] The models of the dual-rotor compressor 51 and the air supply pipeline 52 with the length or diameter of the air supply pipeline 52 changed are again imported into the finite element analysis software ANSYS wOrkbench, and a finite element model of the compressor 51-air supply pipeline 52 is established. Modal simulation is performed on the air supply pipeline 52, and the first-order, second-order, third-order and fourth-order natural frequencies are obtained again.

[0168] As shown in Table 2 below:

[0169] First level Second order Third level Fourth level 85.2HZ 157.6HZ 205.7HZ 406.4HZ

[0170] Table 2

[0171] If the first-order natural frequency, the second-order natural frequency, and the third-order natural frequency are all within the double frequency range of the compressor 51, the fixed frequency design requirement is met.

[0172] In some embodiments, the double frequency range of the compressor 51 is (20HZ, 220HZ).

[0173] At this time, the natural frequencies f1, f2 and f3 all belong to the interval [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than the maximum operating range fpressure of the compressor 51. It is judged that the air supply pipeline 52 is not too soft or too rigid, and then a harmonic response analysis based on the modal superposition method is performed.

[0174] In order to determine whether the weight of the weight-reducing hammer 53 is sufficient, the maximum displacement value and occurrence position corresponding to the natural frequencies f1, f2 and f3 of the air supply pipeline 52 when the frequency of the compressor 51 is within the double frequency range [finitial, 2fpressure] are obtained through harmonic response analysis based on the modal superposition method; 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 standard is that when the operating frequency of the compressor 51 is below 50 Hz, the vibration displacement peak value does not exceed 800 μm.

[0176] If yes, prepare the line for testing.

[0177] If not, add a shock absorber at the maximum vibration displacement and repeat the harmonic response analysis.

[0178] In some embodiments, the initial weight of the shock absorbing hammer is 9.53 mm diameter = 180 g, and 12.7 mm diameter = 240 g.

[0179] Determine whether the displacement at the same maximum vibration position after adding a shock-absorbing hammer to the pipeline meets the displacement test benchmark.

[0180] If the displacement meets the displacement test benchmark, it meets the design and random vibration simulation is performed.

[0181] If the displacement does not meet the displacement test standard, continue to increase the mass of the shock absorbing hammer by 50g each time until the displacement test standard is met, so as to reduce the peak value of the maximum vibration displacement to reduce the vibration of the air supply pipeline 52 and thus reduce the noise.

[0182] The following describes the specific embodiments:

[0183] refer to Figure 6 In order to perform harmonic response analysis based on the modal superposition method and obtain the maximum response of the structure under each modal vibration mode, an X-axis connected by the axis of the compressor 51 and the axis of the air supply tank is established, the Z-axis is along the axis of the compressor 51, and the Y-axis is perpendicular to the XZ-axis plane.

[0184] A load is applied to the compressor 51 along the set coordinate axis, and the load is mainly gas torque and unbalanced centrifugal force.

[0185] In some embodiments, the gas torque is applied to the surface of the diaphragm 2 in the cylinder of the compressor 51 in an upward direction along the Z axis.

[0186] In some embodiments, the unbalanced centrifugal force refers to the centrifugal force of the upper balancing weight, the lower balancing weight, and the eccentric part of the crankshaft of the rotor. These unbalanced centrifugal forces are in the same plane and are directed along the X-axis of the compressor 51.

[0187] The load data is obtained from experiments. Some of the load data is shown in the figure.

[0188] The load is calculated and solved to obtain the maximum displacement value and occurrence position corresponding to the first-order, second-order and third-order fixed frequencies of the air supply pipeline 52 within the double frequency range of the compressor 51.

[0189] The position where the maximum vibration of the air supply pipeline 52 occurs is located at point A, and the maximum vibration displacement wmax and vibration frequency fwmax of point A are obtained.

[0190] The calculated maximum vibration displacement occurs at the first-order fixed frequency K1. According to the double-harmonic vibration characteristics of the dual-rotor compressor 51, the frequency of the compressor 51 corresponding to K1 is at (1 / 2K1±2)HZ. The occurrence position is located at the second bend position of the air supply pipeline 52, and the maximum vibration displacement is 1064um.

[0191] According to the displacement judgment standard, when the operating frequency of compressor 51 is below 50H1, the vibration displacement peak does not exceed 800μm. Therefore, it is judged that the displacement standard requirement is not met. It is necessary to add a shock-absorbing hammer to reduce the value of the displacement peak, thereby weakening the vibration of the air supply pipeline 52 and reducing noise. Then, the harmonic response analysis can be re-performed.

[0192] refer to Figure 8 A weight-reducing hammer 53 is added at position B where the vibration of the air supply pipeline 52 is the largest. The weight of the weight-reducing hammer 53 is S1. After adding the weight-reducing hammer 53, the harmonic response analysis is continued.

[0193] The load data is obtained by the same test as the above steps. Calculation is performed based on the load data. The maximum vibration displacement of point A is reduced to 170um, the resonance frequency point is transferred to 42HZ, the corresponding operating frequency of the compressor 51 is 21HZ, and the maximum vibration displacement is reduced to 586mm, which meets the displacement judgment standard. The displacement test standard is that when the operating frequency of the compressor 51 is below 50HZ, the vibration displacement peak does not exceed 800um, and it is judged that the weight of the weight-reducing hammer 53 is sufficient.

[0194] After the air supply pipeline 52 is equipped with a weight-reducing hammer 53, the pipeline 52 is prone to breakage at weak locations such as welds or bends due to the added weight. Therefore, it is necessary to determine the impact of random vibration of the air supply pipeline 52 on the pipeline strength.

[0195] As shown in Table 3 below:

[0196] First level Second order Third level Fourth level 42.2HZ 88.7HZ 165.3HZ 301.2HZ

[0197] Table 3

[0198] The fixed frequency is recalculated. When the fixed frequency meets the first fixed frequency condition, the air supply pipeline 52 is in a state of being neither too flexible nor too rigid.

[0199] A random vibration simulation is performed on the air supply pipeline 52 with the added shock-absorbing hammer.

[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 the shock-absorbing hammer, and whether the maximum stress value is less than the stress test benchmark.

[0202] If so, prepare the air supply line 52 for testing.

[0203] If not, the air supply pipeline 52 is redesigned and the process is repeated to finally complete the air supply pipeline 52 that meets the stress test benchmark requirements.

[0204] In some embodiments of the present application, random vibration simulation is performed in ANSYS workbench.

[0205] refer to Figure 9 In some embodiments, random vibration simulation requires the addition of applied PSD power spectrum density. The data is taken from the vertical random vibration related data of highway transportation. The test time is calculated according to the calculation formula provided by the national standard based on a transportation distance of 3000 km.

[0206] As shown in Table 4 below:

[0207]

[0208]

[0209] Table 4

[0210] According to the random vibration judgment standard, the maximum Mises equivalent stress value of the pipeline within the 3σ confidence interval must be less than the judgment standard of 150 MPa. Therefore, the random vibration test requirements are met. The counterweight of the air supply pipeline 52 does not need to be changed again, nor does the length or diameter of the air supply pipeline 52 need to be changed again. For example, when the simulation obtains the maximum Mises equivalent stress value of the pipeline within the 3σ confidence interval of 75 MPa, the random vibration test requirements are met.

[0211] Based on the length and diameter of the air supply pipeline 52 and the position of the counterweight obtained from the above calculation and simulation analysis, the air supply pipeline 52 can be prepared and then tested.

[0212] The design process of the air supply pipeline 52 of the air conditioner of this application is as follows:

[0213] S10: Establishing a finite element model of the compressor 51 and the air supply pipeline 52, performing modal simulation on the air supply pipeline 52, and obtaining natural frequencies f1, f2, f3, ..., fn;

[0214] S11: Determine whether the natural frequencies f1, f2, f3, ..., fp are not greater than the maximum operating frequency f pressure of the compressor 51. If so, proceed to S13;

[0215] S12: Determine whether f1 in the natural frequency is less than 2f pressure; if so, proceed to S13;

[0216] S13: changing the diameter of the air supply pipeline 52 or changing the length of the air supply pipeline 52;

[0217] S21: If it is determined that 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 the maximum operating range fpressure of the compressor 51, a harmonic response analysis based on the modal superposition method is performed, and the process proceeds to S31;

[0218] S22: Determine that at least one of the natural frequencies f1, f2, and f3 does not belong to the interval [finitial, 2fpressure], then S24;

[0219] S23: Determine that the natural frequencies f1, f2, and f3 are all less than the maximum operating range fpressure of the compressor 51, then S24;

[0220] S24: redesigning the pipeline, changing 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 fixed frequency condition;

[0221] S31: Obtaining the maximum displacement value and occurrence position corresponding to the natural frequencies f1, f2, and f3 of the air supply pipeline 52 when the frequency of the compressor 51 is within the double frequency range [finitial, 2fpressure];

[0222] S32: Obtain the maximum vibration displacement wmax and the vibration frequency fwmax, and determine whether the maximum displacement meets the displacement test standard; if so, proceed to S33; if not, proceed to S34;

[0223] S33: preparing the gas supply pipeline 52;

[0224] S34: Add a shock-absorbing hammer at the maximum vibration displacement;

[0225] S41: Determine whether the displacement at the same maximum vibration position after adding the shock-absorbing hammer to the pipeline meets the displacement test standard. If so, proceed to S42; if not, proceed to S43;

[0226] S42: The weight of the weight-reducing hammer 53 is no longer increased;

[0227] S43: Continue to increase the mass of the shock-absorbing hammer and return to S41;

[0228] S51: Perform random vibration simulation on the air supply pipeline 52 with the added shock-absorbing hammer to determine whether the maximum stress value is less than the stress test benchmark; if so, proceed to S52; if not, proceed to S53;

[0229] S52: Prepare the air supply pipeline 52 for testing;

[0230] S53: Redesign the air supply pipeline 52.

[0231] Compared with the prior art, the air supply pipeline 52 of the present application is designed first and then produced after the design conditions are met, so that the air supply pipeline 52 can take into account the problem of vibration noise at the beginning of the design, and the noise problem is designed to be avoided before preparation, which effectively saves time and production costs, and can play an effective role in reducing the noise of the air supply pipeline 52. In the prior art, the role of the air supply pipeline 52 is not considered during production, and only weight-added parts can be added during use, and the design is not perfect. The air supply pipeline 52 of the air conditioner of the present application is more perfect in 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 modifications or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in the present invention should be included in the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be based on the scope of protection of the claims.

Claims

1. An air conditioner, characterized in that: include: A twin-rotor compressor having two rotors and having an air intake port and an air discharge port; a first heat exchanger, one end of which is connected to the air intake; a second heat exchanger, one end of which is connected to the exhaust port; a throttling device, both ends of which are connected between the first heat exchanger and the second heat exchanger; an air supply pipeline connected between the twin-rotor compressor and the first heat exchanger; Before preparing the air supply pipeline, a compressor-air supply pipeline finite element model is established, and a modal simulation is performed on the air 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, f3 is not less than fpressure; A harmonic response analysis based on the modal superposition method is performed to obtain the maximum displacement value and occurrence position corresponding to the natural frequencies f1, f2, and f3 of the air supply pipeline when the frequency of the dual-rotor compressor is within the double frequency 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, add a shock-absorbing hammer at the maximum vibration displacement and perform harmonic response analysis based on the modal superposition method again.

2. An air conditioner, characterized in that: include: A twin-rotor compressor having two rotors and having an air intake port and an air discharge port; a first heat exchanger, one end of which is connected to the air intake; a second heat exchanger, one end of which is connected to the exhaust port; a throttling device, both ends of which are connected between the first heat exchanger and the second heat exchanger; an air supply pipeline connected between the twin-rotor compressor and the first heat exchanger; Before preparing the air supply pipeline, a compressor-air supply pipeline finite element model is established, and a modal simulation is performed on the air 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, f3 is not less than fpressure; A harmonic response analysis based on the modal superposition method is performed to obtain the maximum displacement value and occurrence position corresponding to the natural frequencies f1, f2, and f3 of the air supply pipeline when the frequency of the dual-rotor compressor is within the double frequency 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; When the maximum displacement meets the displacement test benchmark, a random vibration simulation is performed on the air supply pipeline with the added shock-absorbing hammer; If the maximum stress value is less than the stress test benchmark, prepare the air supply pipeline 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 not greater than the maximum frequency fpressure of the compressor, the diameter of the air supply pipeline is changed and / or the length of the air supply pipeline is changed until the natural frequencies f1, f2 and f3 meet the first fixed 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 [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than the maximum operating range of the compressor fpressure.

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 the double frequency of the maximum operating frequency of the compressor, fpressure.

6. The air conditioner according to claim 1 or 2, characterized in that: The random vibration simulation increases the applied PSD power spectrum density. The data is taken from the relevant data of vertical random vibration of highway transportation. The test time is calculated according to the calculation formula provided by the national standard based on a transportation distance of 3000km.

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 fall within the interval [finitial, 2fpressure], the pipeline is redesigned by changing the pipe type and / or wall thickness of the air supply pipeline so that the natural frequencies f1, f2, and f3 meet the first fixed frequency condition; The first fixed frequency condition is that the natural frequencies f1, f2 and f3 all belong to the interval [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than the maximum operating range of the compressor fpressure.

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 fall within the interval [finitial, 2fpressure], the pipeline is redesigned by changing the pipe type and / or wall thickness of the air supply pipeline so that the natural frequencies f1, f2, and f3 meet the first fixed frequency condition; The first fixed frequency condition is that the natural frequencies f1, f2 and f3 all belong to the interval [finitial, 2fpressure], and at least one of f1, f2, f3 is not less than the maximum operating range of the compressor fpressure.

9. The air conditioner according to claim 1 or 2, characterized in that: The displacement test standard is that when the compressor operating frequency is below 50Hz, the vibration displacement peak 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 air supply tank, the Z-axis is along the axis of the compressor, and the Y-axis is perpendicular to the XZ-axis plane; a load is applied to the compressor along the set coordinate axis, and the load is mainly gas torque and unbalanced centrifugal force.

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