Air source heat pump

Abstract

The utility model provides an air source heat pump. The air source heat pump comprises a machine shell which is provided with an air outlet and an air inlet and comprises a bottom plate; the middle partition plate is arranged in the machine shell so as to divide the machine shell into a fan chamber and a machine chamber; the heat exchanger is at least partially arranged in the fan chamber; the fan is arranged in the fan chamber, and the fan rotates to drive air to flow in from the air inlet, flow through the heat exchanger and then be blown out from the air outlet; the compressor is arranged at the bottom of the machine chamber; the first tank body is connected with the middle partition plate; the threaded connection hole is formed in the middle partition plate; the first tank body is provided with at least one extension mounting plate, and threaded connection holes are formed in the extension mounting plates; the threaded connecting piece is arranged in the threaded connecting hole of the middle partition plate and the threaded connecting hole of the extending mounting plate in a penetrating mode at the same time. The bottom of the first tank body does not make contact with the bottom plate, and the first tank body and the middle partition plate are connected through the threaded connecting piece so that the first tank body can be hung on the middle partition plate, installation is convenient, and the space utilization rate is high.

Description

Technical Field

[0001] The utility model relates to the technical field of electrical appliances, in particular to an air source heat pump. Background Art

[0002] With the rapid development of air source heat pumps, people have put forward requirements for more stable tank installation in air source heat pumps.

[0003] Air source heat pumps are available in split and integrated types. Split air source heat pumps are similar to air source heat pumps and also include indoor and outdoor units. Integrated air source heat pumps are installed outdoors, which can save indoor space.

[0004] The integrated air source heat pump includes a middle partition, which divides the entire shell to form a fan room and equipment. When the equipment is installed, a water system is set in the mechanical room. The water system mainly includes a shell and tube heat exchanger, a water pump, and a water pipe connected between the shell and tube heat exchanger and the water pump. A fan is arranged in the fan room, and an air outlet is arranged on the shell of the air source heat pump. The fan is arranged directly opposite the air outlet. The fan rotates to make the air flow flow from the air outlet into the shell, thereby exchanging heat with the heat exchanger in the fan room.

[0005] The shell and tube heat exchanger is heavy. The high-efficiency tank is a type of shell and tube heat exchanger. When installing it, a larger installation space and a higher-strength support structure are required.

[0006] In the prior art, the shell and tube heat exchanger is arranged in the machine room, and the shell and tube heat exchanger is usually fixedly connected to the bottom plate of the air source heat pump, or fixed to the support base on the bottom plate. These two installation methods easily increase the size of the air source heat pump, and part of the space in the shell is occupied by the support base, resulting in waste of space and increase in the cost of the whole machine. Utility Model Content

[0007] The utility model solves one of the technical problems in the related art at least to a certain extent.

[0008] To this end, the present application aims to provide an air source heat pump.

[0009] The air source heat pump according to the present application comprises:

[0010] A housing having an air outlet and an air inlet, and including a bottom plate;

[0011] A middle partition plate is arranged in the casing to divide the casing into a fan room and a machine room;

[0012] a heat exchanger, at least partially disposed within the fan chamber;

[0013] A fan is arranged in the fan chamber, and the fan rotates to drive air to flow from the air inlet and pass through the heat exchanger, and then blow out from the air outlet;

[0014] A compressor, which is arranged at the bottom of the machine room;

[0015] A first tank body connected to the middle partition;

[0016] A threaded connection hole, which is provided on the middle partition plate;

[0017] An extended mounting plate, wherein the first tank body has at least one extended mounting plate, and a threaded connection hole is provided on the extended mounting plate;

[0018] A threaded connection piece, which is inserted into the threaded connection hole of the middle partition plate and the threaded connection hole of the extension mounting plate at the same time;

[0019] The bottom of the first tank body is not in contact with the bottom plate, and the first tank body and the middle partition plate are connected via the threaded connector.

[0020] The air source heat pump according to the present application comprises:

[0021] A housing having an air outlet and an air inlet, and including a bottom plate;

[0022] A middle partition plate is arranged in the casing to divide the casing into a fan room and a machine room;

[0023] a heat exchanger, at least partially disposed within the fan chamber;

[0024] A fan is arranged in the fan chamber, and the fan rotates to drive air to flow from the air inlet and pass through the heat exchanger, and then blow out from the air outlet;

[0025] A compressor, which is arranged at the bottom of the machine room;

[0026] A first tank body connected to the middle partition;

[0027] a water inlet pipe connected to the first tank;

[0028] a water outlet pipe connected to the first tank;

[0029] A support plate, which is fixedly connected to the bottom plate and extends in the up-down direction;

[0030] A top connecting plate, the top of the support plate is connected to the top connecting plate, the top connecting plate extends along the width direction or the length direction of the casing, and at least one water pipe connecting hole is provided on the top connecting plate, and the water inlet pipe and / or the water outlet pipe is connected to the top support plate.

[0031] In some embodiments of the present application, the extended mounting plate is a bent plate, including a longitudinal plate and a transverse plate, the longitudinal plate is provided with bolt holes, the longitudinal plate is connected to the middle partition plate 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 first tank body.

[0032] In some embodiments of the present application, the threaded connection member is a bolt and / or a screw, and the threaded connection hole is a bolt hole and / or a screw hole.

[0033] In some embodiments of the present application, a connecting plate is further provided at the bolt hole of the middle partition, and the connecting plate and the middle partition are fixed by fixing parts. The connecting plate is provided with bolt holes, and the bolt holes on the connecting plate and the bolt holes on the middle partition are arranged relative to each other, so that the same bolt can be simultaneously passed through the bolt holes on the connecting plate and the bolt holes on the middle partition.

[0034] In some embodiments of the present application, the middle portion of the connecting plate protrudes in a direction away from the middle partition plate to form a protruding surface, and a bolt hole is provided on the protruding surface.

[0035] In some embodiments of the present application, there is a gap between the protruding surface and the middle partition.

[0036] In some embodiments of the present application, the middle partition is a bent plate, having a first partition extending along the width direction of the casing and a second partition extending along the length direction of the casing, and the second partition is connected to the rear end of the first partition.

[0037] In some embodiments of the present application, the middle partition has at least one bolt hole, the extended mounting plate is provided with at least one bolt hole, and at least one bolt is simultaneously passed through the bolt hole on the middle partition and the bolt hole on the extended mounting plate, so that the first tank body and the middle partition are connected by the bolt.

[0038] In some embodiments of the present application, the rotation axis of the first tank body is defined as a first axis, and a central angle formed by the centers of the two bolt holes is 90°.

[0039] This application has at least the following positive effects:

[0040] The utility model proposes an air source heat pump. The air source heat pump includes a casing, which is provided with an air outlet and an air inlet, including a bottom plate; a middle partition plate, which is arranged in the casing to divide the casing into a fan room and a machine room; a heat exchanger, which is at least partially arranged in the fan room; a fan, which is arranged in the fan room, and the fan rotates to drive air to flow into the air inlet and flow through the heat exchanger, and then blow out from the air outlet; a compressor, which is arranged at the bottom of the machine room; a first tank body, which is connected to the middle partition plate; a threaded connection hole, which is arranged on the middle partition plate; an extended mounting plate, the first tank body has at least one extended mounting plate, and the extended mounting plate is provided with a threaded connection hole; a threaded connector, which is simultaneously penetrated in the threaded connection hole of the middle partition plate and the threaded connection hole of the extended mounting plate; the bottom of the first tank body does not contact the bottom plate, and the first tank body and the middle partition plate are connected by a threaded connector, so that the first tank body can be suspended on the middle partition plate, which is convenient for installation and has high space utilization. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] In order to more clearly illustrate the embodiments of the utility model or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the utility model. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0042] Figure 1 is a view of a partially removed housing of an air source heat pump according to an embodiment of the present application;

[0043] Figure 2 is a view of a partially removed housing of an air source heat pump according to an embodiment of the present application;

[0044] Figure 3 is a view of a partially removed housing of an air source heat pump according to an embodiment of the present application;

[0045] Figure 4 is a view of a partially removed housing and a partially removed fan of an air source heat pump according to an embodiment of the present application;

[0046] Figure 5 yes Figure 4 A in the enlarged view;

[0047] Figure 6 is a schematic diagram of an XY axis established by harmonic response analysis based on a modal superposition method of an air conditioner according to an embodiment of the present application;

[0048] Figure 7 is a schematic diagram of the connection between the compressor and the air supply pipeline of the air conditioner according to the embodiment of the present application;

[0049] Figure 8is a schematic diagram of the connection between the compressor, the air supply pipeline and the weight-reducing hammer of the air conditioner according to the embodiment of the present application;

[0050] Fig. 9 is a power spectral density curve of random vibration simulation of the air conditioner according to the embodiment of the present application

[0051] Fig.10 It is a process for determining whether the diameter or length of the air supply pipeline of the air conditioner according to the implementation mode of the present application meets the requirements;

[0052] Fig.11 It is a process of designing an air supply pipeline of an air conditioner according to an embodiment of the present application;

[0053] Fig.12 It is a process of designing an air supply pipeline of an air conditioner according to an embodiment of the present application;

[0054] Fig.13 is a load diagram of an air supply pipeline of an air conditioner according to an embodiment of the present application;

[0055] 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 reduction 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 connecting hole. DETAILED DESCRIPTION

[0056] The present invention is described in detail below by way of exemplary embodiments. However, it should be understood that, without further description, elements, structures and features in one embodiment may also be beneficially combined in other embodiments.

[0057] 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 orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0058] The terms "first", "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 indicated technical features. Thus, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features.

[0059] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0060] In the following, reference will be made to the Figure 1-5 The embodiments of the present application are described in detail.

[0061] The present application provides an air source heat pump with a hanging high-efficiency tank installation structure.

[0062] The air source heat pump of the present application comprises a casing 1, which constitutes the overall appearance of the air source heat pump, and the casing 1 is located at the outermost side of the air source heat pump unit.

[0063] The casing 1 includes a front panel, on which an air inlet 11 is arranged, and the position of the front panel of the casing 1 is defined as the front side of the air source heat pump.

[0064] The casing 1 also includes a back plate, which is arranged opposite to the front plate, and the position of the back plate of the casing 1 is defined as the rear side of the air source heat pump.

[0065] At least one air outlet 12 is disposed on the front panel of the housing 1 so that the airflow in the housing 1 can be blown out to the outdoor space through the air outlet 12 .

[0066] The housing 1 further comprises 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 respectively located at the left and right sides of the front panel.

[0067] 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.

[0068] A bottom plate 13 is disposed 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 .

[0069] 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 a back panel and / or a side panel so that air flows into the housing 1 from the air inlet 11 .

[0070] 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 .

[0071] 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.

[0072] 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 air duct, and is blown out from the air outlet 12 after heat exchange with the heat exchanger 3.

[0073] 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.

[0074] The front panel includes a front plate.

[0075] The front panel also includes a front side maintenance panel. The front panel and the front side maintenance panel are installed or removed separately.

[0076] The side panel located on the right side of the casing 1 is defined as a right side panel. The right side panel is a bent panel and is not only arranged on the right side of the casing 1 but also on the rear side of the casing 1 .

[0077] In some embodiments of the present application, an air inlet 11 is provided at the bottom end of the right side plate, the air inlet 11 is connected to the heat exchange air duct in the housing 1, and the air flows from the air inlet 11 into the heat exchange air duct.

[0078] 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.

[0079] The middle partition 2 divides the space in the casing 1 into a fan room and a machine room, and the fan 4 is arranged in the fan room.

[0080] In some embodiments of the present application, there are two fans 4 arranged at an interval up and down, 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.

[0081] 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 directly blown out from the air outlet 12 on the front panel.

[0082] 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 airflow 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.

[0083] 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.

[0084] The air source heat pump includes a compressor 51 for providing flow power for the refrigerant.

[0085] The air source heat pump includes a condenser, in which the refrigerant undergoes a condensation process.

[0086] The air source heat pump includes a throttling device, and the refrigerant is throttled when flowing through the throttling device.

[0087] The air source heat pump includes an evaporator, in which the refrigerant undergoes an evaporation process, and performs a refrigeration cycle or a heating cycle through a compressor 51, a condenser, a throttling device, and an evaporator. The refrigeration cycle and the heating cycle include a compression process, a condensation process, an expansion process, and an evaporation process, and provide cooling or heat to the indoor space through the heat absorption and heat release process of the refrigerant to achieve temperature regulation of the indoor space.

[0088] The compressor 51 compresses the refrigerant gas into a high-temperature and high-pressure state and discharges the compressed refrigerant gas, which flows into the condenser. The condenser condenses the compressed high-temperature and high-pressure gaseous refrigerant into liquid refrigerant, and heat is released to the surrounding environment through the condensation process.

[0089] The liquid refrigerant flowing out of the condenser enters the throttling device, which expands the high-temperature and high-pressure liquid refrigerant condensed in the condenser into a low-pressure liquid refrigerant. The low-pressure liquid refrigerant flowing out of the throttling device enters the evaporator. When the liquid refrigerant flows through the evaporator, it absorbs heat and evaporates into a low-temperature and low-pressure refrigerant gas. The refrigerant gas in a low-temperature and low-pressure state 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. In the entire cycle, the air source heat pump can adjust the temperature of the indoor space.

[0090] The air source heat pump also includes an electrical box, which is located in the mechanical room and is connected to a power source.

[0091] The air source heat pump also includes a water supply component, which is arranged in the mechanical room.

[0092] The air source heat pump also includes a compressor 51, which is arranged in a mechanical room. The compressor 51, the condenser, the evaporator and the throttling device together constitute a refrigeration system, and the refrigerant flows among the compressor 51, the condenser, the evaporator and the throttling device.

[0093] The electrical box is set at the highest point in the mechanical room to prevent water from the water supply components from dripping onto the electrical box.

[0094] The water supply assembly includes a water pump, which provides the power for water flow and is connected to the water supply assembly.

[0095] 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.

[0096] In order to reduce the size of the air source heat pump, a shell and tube heat exchanger 3 is usually set as the outdoor heat exchanger 3, and the shell and tube heat exchanger 3 has the shape of a tank. The shell and tube heat exchanger 3 has the characteristics of 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 and other units using water as the heat exchange medium. The high-efficiency tank heat exchanger 3 is a type of shell and tube heat exchanger 3.

[0097] 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 to make the flow of refrigerant or water smoother.

[0098] The high-efficiency tank is relatively 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.

[0099] In the prior art, 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 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 in size. 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.

[0100] The present application provides an air source heat pump with a hanging high-efficiency tank installation structure.

[0101] The compressor 51 is installed on the bottom plate 13, and the high-efficiency tank is installed above the compressor 51. The high-efficiency tank and the middle partition plate 2 are connected by bolts and nuts.

[0102] 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 .

[0103] 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, and the second partition is connected to the rear end of the first partition.

[0104] 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.

[0105] 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 .

[0106] The middle partition 2 has at least one bolt hole, 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, and 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.

[0107] In some embodiments, the first tank is a high efficiency tank.

[0108] 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 to make the nut and the bolt fit together, so that the extended mounting plate 61 of the first tank body is connected to the middle partition 2, thereby fixing the first tank body on the middle partition 2.

[0109] 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, thereby saving installation space in the casing 1, reducing the volume of the casing 1, and thus reducing the cost of the casing 1.

[0110] 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.

[0111] It should be noted that the rotation axis of the first tank body is defined as the first axis, and the center angle formed by the centers of the two bolt holes is 90°, so that the force on the first tank body is more uniform.

[0112] 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. 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.

[0113] 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.

[0114] 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.

[0115] 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 inserted into the bolt holes on the connecting plate 22 and the bolt holes on the middle partition 2 at the same time.

[0116] When the bolts penetrate the middle partition 2, the connecting plate 22 and the extended 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 middle partition 2, and the nut is rotated to tighten the nut and the bolt. The nut applies a 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.

[0117] In some embodiments, the middle portion of the connecting plate 22 protrudes in a direction away from the middle partition plate 2 to form a protruding surface 221, and a bolt hole is provided on the protruding surface 221. When the bolt is inserted into the bolt hole, since the protruding surface 221 of the connecting plate 22 does not completely contact the middle partition plate 2, there is a certain distance between the protruding surface 221 and the middle partition plate 2, so that there is a certain deformation gap between the protruding surface 221 and the middle partition plate 2. When the protruding surface 221 is slightly deformed, the protruding surface 221 cannot directly squeeze the middle partition plate 2, which can reduce the probability of deformation of the middle partition plate 2.

[0118] In some embodiments, the connecting plate 22 and the middle partition plate 2 are connected by welding, which is easy to operate.

[0119] In some embodiments, a support plate 8 is disposed 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.

[0120] 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.

[0121] In some embodiments, two water pipe connection holes 91 are provided on the top connection plate 9, one of which is connected to the water inlet pipe 62 of the first tank body, and the other is connected to the water outlet pipe 63 of the first tank body. The water inlet pipe 62 of the first tank body and the water outlet pipe 63 of the first tank body have a certain weight. The top connection plate 9 is supported by the support plate 8 and supports the water pipes passing through the top connection plate 9.

[0122] In other embodiments, the top connecting plate 9 extends along the left-right direction.

[0123] The following describes in detail the steps for installing the first tank:

[0124] 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.

[0125] 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 .

[0126] It should be noted that a hoisting 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 hoists the first tank body and the middle partition 2, and the installer hoists the first tank body and the middle partition 2 and installs them on the bottom plate 13.

[0127] 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.

[0128] 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.

[0129] Finally, the buckle of the top connecting plate 9 and the slot of the supporting plate 8 are matched and connected, and fixed by screws, which is convenient for installation and reduces the number of installation steps.

[0130] In the following, reference will be made to the Figure 6-13 The embodiments of the present application are described in detail.

[0131] As people have higher and higher requirements for the stability of air-conditioning operation, the twin-rotor compressor 51 is more and more widely used in air-conditioning.

[0132] It should be noted that air source heat pump is also a type of air conditioner.

[0133] The air conditioner includes a twin-rotor compressor 51 .

[0134] 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.

[0135] When the rotor rotates one circle, the cylinder compresses the refrigerant twice, so the vibration frequency of the twin-rotor compressor 51 is approximately twice the operating frequency of the compressor 51, that is, the twin-rotor compressor 51 vibrates at a double frequency. The double frequency vibration noise is low-frequency noise, has a long propagation distance, low dissipation in the propagation process, and strong penetration, which makes the noise easily disturbing to people during the operation of the air conditioner.

[0136] The double frequency noise of the twin-rotor compressor 51 is mainly concentrated in the low frequency range of 100Hz-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.

[0137] 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.

[0138] 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 pipe welding points or bends in the subsequent vibration test on the platform, and the vibration test needs to be repeated.

[0139] The present application provides an air conditioner having an air supply pipeline 52 with a good vibration reduction effect.

[0140] The air supply pipeline 52 of the air conditioner of the present application is first calculated and then prepared according to the calculated size.

[0141] 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.

[0142] According to design experience, the air supply pipeline 52 of the twin-rotor compressor 51 often vibrates at a double frequency.

[0143] If the natural frequencies f1, f2, f3, ..., fp are not greater than the maximum operating frequency f of the compressor 51, the probability of pipeline resonance occurring when the compressor 51 operates normally is high.

[0144] Among them, p≥3.

[0145] 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 being 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 relatively high.

[0146] If f1 in the natural frequency is not less than 2f, the vibration energy of the compressor 51 will be transmitted to the components connected to it through the pipeline, and the air supply pipeline 52 will be too rigid, and the double-frequency sound will be amplified.

[0147] Among them, 2f pressure is the double frequency of the maximum operating frequency f pressure of the compressor 51, and the air supply pipeline 52 of the dual-rotor compressor 51 often vibrates at the double frequency.

[0148] 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 double frequency 2f of the maximum operating range of the compressor 51, the vibration energy of the compressor 51 will be transmitted to the components connected to it through the pipeline, and then transmitted to the bottom plate 13 and the surrounding sheet metal, causing the harmonic sound to be amplified.

[0149] Determine the relationship between the natural frequencies f1, f2 and f3 and the interval [finitial, 2fpressure].

[0150] Wherein, finitial is the initial operating frequency of the compressor 51 , and 2fpressure is the double frequency of the maximum operating frequency of the compressor 51 .

[0151] 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 the maximum operating range fpressure of the compressor 51, it is determined 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.

[0152] 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.

[0153] If at least one of the natural frequencies f1, f2 and f3 does not belong to 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.

[0154] 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 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 meet the first fixed frequency condition.

[0155] The following describes the specific embodiments:

[0156] In some embodiments, the air supply pipeline 52 is connected between the dual-rotor compressor 51 and the plate heat exchanger 3 , and the designed diameter of the air supply pipeline 52 is D1 , and the pipeline length is L1 .

[0157] In some embodiments, D1 = 9.53 mm. The operating frequency of the compressor 51 is 20-110 Hz, and L1 is 870 mm.

[0158] The models of the dual-rotor compressor 51 and the air supply pipeline 52 are imported into the finite element analysis software ANSYS workbench, a compressor 51-air supply pipeline 52 finite element model is established, and a modal simulation is performed on the air supply pipeline 52 to obtain the first-order, second-order, third-order and fourth-order natural frequencies.

[0159] As shown in Table 1 below:

[0160] First level Second order Third level Fourth level 57.8HZ 68.5HZ 101.5HZ 160.7HZ

[0161] Table 1

[0162] Obtain the natural frequency range of the first three orders;

[0163] 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 air supply pipeline 52 is designed to be too flexible and cannot meet the fixed frequency design requirements. There is a high probability that resonance will occur within the double frequency operation range of the compressor 51. Therefore, the strength of the air supply pipeline 52 needs to be increased: the diameter of the air supply pipeline 52 is increased to D2, D2≥D1, or the length of the air supply pipeline 52 is reduced to L2, L2≤L1, so as to reduce the air supply pipeline 52 from being too flexible 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.

[0164] 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.

[0165] 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 imported into the finite element analysis software ANSYS workbench again, a finite element model of the compressor 51-air supply pipeline 52 is established, a 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.

[0166] As shown in Table 2 below:

[0167] First level Second order Third level Fourth level 85.2HZ 157.6HZ 205.7HZ 406.4HZ

[0168] Table 2

[0169] 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 requirements are met.

[0170] In some embodiments, the double frequency range of the compressor 51 is (20HZ, 220HZ).

[0171] 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, then 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.

[0172] In order to determine whether the weight of the weight-reducing hammer 53 is sufficient, the frequency of the compressor 51 is obtained in the double frequency range [finitial, 2fpressure], and the maximum displacement value and occurrence position corresponding to the natural frequencies f1, f2 and f3 of the air supply pipeline 52 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.

[0173] 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 um.

[0174] If yes, prepare the line for testing.

[0175] If not, add a shock-absorbing hammer at the maximum vibration displacement and re-perform the harmonic response analysis.

[0176] In some embodiments, the initial weight of the shock absorbing hammer is 9.53 dia.-180g, 12.7 dia.-240g.

[0177] Determine whether the displacement at the same maximum vibration position after adding a shock-absorbing hammer to the pipeline meets the displacement test benchmark.

[0178] If the displacement meets the displacement test benchmark, it meets the design and random vibration simulation is performed.

[0179] If the displacement does not meet the displacement test standard, the mass of the shock absorbing hammer is continuously increased by 50 g each time until the displacement test standard is met, thereby reducing the peak value of the maximum vibration displacement to reduce the vibration of the air supply pipeline 52 and thus reduce the noise.

[0180] The following describes the specific embodiments:

[0181] refer to Figure 6In 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 to 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.

[0182] A load is applied to the compressor 51 along the set coordinate axis, and the load is mainly gas torque and unbalanced centrifugal force.

[0183] 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.

[0184] In some embodiments, the unbalanced centrifugal force refers to the centrifugal force of the upper balancing block, the lower balancing block, and the eccentric portion 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.

[0185] The load data is obtained by experiment. Some load data are shown in the figure.

[0186] The load is solved and calculated 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.

[0187] 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.

[0188] The calculated maximum vibration displacement occurs at the first-order fixed frequency K1. According to the double-frequency 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 bending position of the air supply pipeline 52, and the maximum vibration displacement is 1064um.

[0189] According to the displacement judgment standard, when the operating frequency of the compressor 51 is below 50H1, the vibration displacement peak value does not exceed 800um. Therefore, it is judged that the displacement standard requirement is not met, and it is necessary to add a shock-absorbing hammer to reduce the value of the displacement peak value, thereby weakening the vibration of the air supply pipeline 52 and reducing noise, and then re-performing the harmonic response analysis.

[0190] 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.

[0191] The load data is obtained by the same test as the above steps. The maximum vibration displacement of point A is reduced to 170um, and the resonance frequency point is transferred to 42HZ. The corresponding operating frequency of 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 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.

[0192] After the air supply pipeline 52 is equipped with a weight-reducing hammer 53, the pipeline is prone to breakage at weak locations such as welding points or bends of the pipeline due to the increase in the weight of the air supply pipeline 52. Therefore, it is necessary to determine the influence of the random vibration of the air supply pipeline 52 on the pipeline strength.

[0193] As shown in Table 3 below:

[0194] First level Second order Third level Fourth level 42.2HZ 88.7HZ 165.3HZ 301.2HZ

[0195] Table 3

[0196] 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.

[0197] A random vibration simulation is performed on the air supply pipeline 52 with the damping hammer added.

[0198] It should be noted that the random vibration simulation was performed using the software ANSYS workbench.

[0199] 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.

[0200] If yes, prepare the air supply line 52 for testing.

[0201] 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.

[0202] In some embodiments of the present application, random vibration simulation is performed in ANSYS workbench.

[0203] refer to Fig. 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, and the test time is calculated according to the calculation formula provided by the national standard based on a transportation distance of 3000 km.

[0204] As shown in Table 4 below:

[0205]

[0206] Table 4

[0207] According to the random vibration judgment standard, the maximum Mises equivalent stress value of the pipeline under the 3σ confidence interval is less than the judgment standard 150Mpa, so the random vibration test requirements are met, and 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 under the 3σ confidence interval of 75Mpa, the random vibration experiment requirements are met.

[0208] According to 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.

[0209] The design process of the air supply pipeline 52 of the air conditioner of the present application is as follows:

[0210] 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;

[0211] 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;

[0212] S12: Determine whether f1 in the natural frequency is less than 2f; if so, S13;

[0213] S13: changing the diameter of the air supply pipeline 52 or changing the length of the air supply pipeline 52;

[0214] 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;

[0215] S22: judging that at least one of the natural frequencies f1, f2 and f3 does not belong to the interval [finitial, 2fpressure], then S24;

[0216] S23: If it is determined that the natural frequencies f1, f2, and f3 are all less than the maximum operating range f pressure of the compressor 51, then S24;

[0217] 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;

[0218] 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];

[0219] 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;

[0220] S33: preparing the gas supply pipeline 52;

[0221] S34: Add a shock-absorbing hammer at the maximum vibration displacement;

[0222] S41: Determine whether the displacement at the same maximum vibration position after adding a shock-absorbing hammer to the pipeline meets the displacement test standard, if so, proceed to S42, if not, proceed to S43;

[0223] S42: The weight of the weight-reducing hammer 53 is no longer increased;

[0224] S43: Continue to increase the mass of the shock absorbing hammer and return to S41;

[0225] S51: Perform random vibration simulation on the air supply pipeline 52 with the damping hammer added to determine whether the maximum stress value is less than the stress test benchmark; if so, proceed to S52; if not, proceed to S53;

[0226] S52: preparing the air supply pipeline 52 for testing;

[0227] S53: redesigning the air supply pipeline 52.

[0228] 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 and noise at the beginning of the design, and then be prepared after the noise problem is designed around, 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 perfectly designed, generates less noise, and has better safety performance.

[0229] The above is only a specific implementation of the utility model, but the protection scope of the utility model is not limited thereto. Any technician familiar with the technical field can easily think of changes or substitutions within the technical scope disclosed by the utility model, which should be included in the protection scope of the utility model. Therefore, the protection scope of the utility model should be based on the protection scope of the claims.

Claims

1. An air source heat pump, characterized in that: include: A housing having an air outlet and an air inlet, and including a bottom plate; A middle partition plate is arranged in the casing to divide the casing into a fan room and a machine room; a heat exchanger, at least partially disposed within the fan chamber; A fan is arranged in the fan chamber, and the fan rotates to drive air to flow from the air inlet and pass through the heat exchanger, and then blow out from the air outlet; A compressor, which is arranged at the bottom of the machine room; A first tank body connected to the middle partition; A threaded connection hole, which is provided on the middle partition plate; An extended mounting plate, wherein the first tank body has at least one extended mounting plate, and a threaded connection hole is provided on the extended mounting plate; A threaded connection piece, which is inserted into the threaded connection hole of the middle partition plate and the threaded connection hole of the extension mounting plate at the same time; The bottom of the first tank body is not in contact with the bottom plate, and the first tank body and the middle partition plate are connected via the threaded connector.

2. An air source heat pump, characterized in that: include: A housing having an air outlet and an air inlet, and including a bottom plate; A middle partition plate is arranged in the casing to divide the casing into a fan room and a machine room; a heat exchanger, at least partially disposed within the fan chamber; A fan is arranged in the fan chamber, and the fan rotates to drive air to flow from the air inlet and pass through the heat exchanger, and then blow out from the air outlet; A compressor, which is arranged at the bottom of the machine room; A first tank body connected to the middle partition; a water inlet pipe connected to the first tank; a water outlet pipe connected to the first tank; A support plate, which is fixedly connected to the bottom plate and extends in the up-down direction; A top connecting plate, the top of the support plate is connected to the top connecting plate, the top connecting plate extends along the width direction or the length direction of the casing, and at least one water pipe connecting hole is provided on the top connecting plate, and the water inlet pipe and / or the water outlet pipe is connected to the top support plate.

3. The air source heat pump according to claim 1 or 2, characterized in that: The extended mounting plate is a bent plate, including a longitudinal plate and a transverse plate. The longitudinal plate is provided with bolt holes. The longitudinal plate is connected to the middle partition plate by bolts. The transverse plate is connected to one end of the longitudinal plate close to the first tank body. The transverse plate is connected to the first tank body.

4. The air source heat pump according to claim 1 or 2, characterized in that: The threaded connection piece is a bolt and / or a screw, and the threaded connection hole is a bolt hole and / or a screw hole.

5. The air source heat pump according to claim 4, characterized in that: A connecting plate is also provided at the bolt hole of the middle partition, and the connecting plate and the middle partition are fixed by fixing parts. The connecting plate is provided with bolt holes, and the bolt holes on the connecting plate and the bolt holes on the middle partition are arranged relatively to each other, so that the same bolt can be simultaneously passed through the bolt holes on the connecting plate and the bolt holes on the middle partition.

6. The air source heat pump according to claim 5, characterized in that: The middle portion of the connecting plate protrudes in a direction away from the middle partition plate to form a protruding surface, and a bolt hole is arranged on the protruding surface.

7. The air source heat pump according to claim 6, characterized in that: A gap is provided between the protruding surface and the middle partition plate.

8. The air source heat pump according to claim 1 or 2, characterized in that: The middle partition is a bent plate, comprising a first partition extending in the width direction of the casing and a second partition extending in the length direction of the casing, wherein the second partition is connected to the rear end of the first partition.

9. The air source heat pump according to claim 1 or 2, characterized in that: The middle partition is provided with at least one bolt hole, the extended mounting plate is provided with at least one bolt hole, and at least one bolt is simultaneously passed through the bolt hole on the middle partition and the bolt hole on the extended mounting plate, so that the first tank body and the middle partition are connected by the bolt.

10. The air source heat pump according to claim 4, characterized in that: The rotation axis of the first tank body is defined as a first axis, and the center angle formed by the centers of the two bolt holes is 90°.

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