Air conditioning system vibration reduction unit and air conditioning system

Abstract

The present application relates to a kind of air conditioning system damping unit and air conditioning system, including compressor component and intermediate support assembly, the intermediate support assembly is supported below the compressor component.The compressor component and the intermediate support assembly are rigid member, the rigidity mass ratio M0 of the compressor component is not equal to the rigidity mass ratio M1 of the intermediate support assembly.Based on the rigidity mass ratio M0 of the compressor component is not equal to the rigidity mass ratio M1 of the intermediate support assembly, so there will be energy loss in the process of vibration transmission between the compressor component and the intermediate support assembly, reach the effect of damping.And based on the compressor component and the intermediate support assembly are rigid member, so the deformation of the compressor component and the intermediate support assembly is smaller in the environment such as handling and shipborne, so the stability of compressor body is higher.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of vibration reduction, in particular to an air conditioning system vibration reduction unit and an air conditioning system. BACKGROUND

[0002] The compressor is an important component in the air conditioning system. With the development of technology, the energy efficiency of the compressor has been optimized to a high level, and people pay more and more attention to the size of the compressor vibration noise. Generally, the method for reducing the vibration noise of the compressor is to provide an elastic support member, such as a rubber pad, at the bottom of the compressor. Although this vibration reduction method can have a certain damping effect, it has the problem of low stability in transportation and ship loading environments. SUMMARY

[0003] In order to solve the problem of low stability caused by achieving a certain damping effect, the present application provides an air conditioning system vibration reduction unit and an air conditioning system. The stiffness to mass ratio M0 of the compressor component and the stiffness to mass ratio M1 of the intermediate support assembly are designed to be different, thereby achieving the effect of reducing vibration. Moreover, since the compressor component and the intermediate support assembly are both rigid body components, the stability is high in transportation and ship loading environments.

[0004] An air conditioning system vibration reduction unit comprises:

[0005] A compressor component, the compressor component comprising a compressor body and a compressor support foot for supporting below the compressor body, the stiffness to mass ratio M0 of the compressor component being k0 / m0, wherein k0 represents the stiffness of the compressor component and has a unit of N·m-1, and m0 represents the mass of the compressor component and has a unit of kg;

[0006] An intermediate support assembly, the intermediate support assembly being supported below the compressor component, the stiffness to mass ratio M1 of the intermediate support assembly being k1 / m1, wherein k1 represents the stiffness of the intermediate support assembly and has a unit of N·m-1, and m1 represents the mass of the intermediate support assembly and has a unit of kg;

[0007] The compressor component and the intermediate support assembly are both rigid body components, and the stiffness to mass ratio M0 of the compressor component is different from the stiffness to mass ratio M1 of the intermediate support assembly.

[0008] In one of the embodiments, the air conditioning system vibration reduction unit further comprises a shell-and-tube heat exchanger, the shell-and-tube heat exchanger being located below the intermediate support assembly, a transition support assembly being provided between the shell-and-tube heat exchanger and the intermediate support assembly, the stiffness to mass ratio M2 of the transition support assembly being k2 / m2, wherein k2 represents the stiffness of the transition support assembly and has a unit of N·m-1, and m2 represents the mass of the transition support assembly and has a unit of kg.

[0009] The transition support assembly is a rigid member, and a rigidity-mass ratio M1 of the intermediate support assembly is not equal to a rigidity-mass ratio M2 of the transition support assembly.

[0010] In one of the embodiments, the transition support assembly comprises a first horizontal plate, two first vertical plates, two second vertical plates, and two first arc-shaped plates, the first horizontal plate is connected with the intermediate support assembly, the two first vertical plates and the two second vertical plates are located on a side of the first horizontal plate away from the intermediate support assembly, and the two first vertical plates and the two second vertical plates are connected with the first horizontal plate, the two first vertical plates are arranged in a first direction, the two second vertical plates are arranged in a second direction, the first direction intersects the second direction, the two first arc-shaped plates are supported above a shell of the shell-and-tube heat exchanger, the second vertical plate is connected with the first arc-shaped plate, and the first arc-shaped plate corresponds to the second vertical plate in one-to-one manner.

[0011] In one of the embodiments, the first arc-shaped plate is welded with the shell of the shell-and-tube heat exchanger;

[0012] and / or, the second vertical plate is welded with the first arc-shaped plate;

[0013] and / or, the two first vertical plates and the two second vertical plates are welded with the first horizontal plate;

[0014] and / or, a first connecting member is arranged between the first horizontal plate and the intermediate support assembly.

[0015] In one of the embodiments, a thickness of the first horizontal plate is not less than 20 mm;

[0016] and / or, a thickness of each of the first vertical plates is not less than 12 mm;

[0017] and / or, a thickness of each of the second vertical plates is not less than 12 mm.

[0018] In one of the embodiments, a rigidity-mass ratio M3 of the shell-and-tube heat exchanger is M3=k3 / m3, where k3 represents a rigidity of the shell-and-tube heat exchanger and has a unit of N·m-1, and m3 represents a mass of the shell-and-tube heat exchanger and has a unit of kg, and the rigidity-mass ratio M2 of the transition support assembly is not equal to the rigidity-mass ratio M3 of the shell-and-tube heat exchanger.

[0019] In one of the embodiments, a shell-and-tube support assembly is arranged below the shell-and-tube heat exchanger, a rigidity-mass ratio M4 of the shell-and-tube support assembly is M4=k4 / m4, where k4 represents a rigidity of the shell-and-tube support assembly and has a unit of N·m-1, and m4 represents a mass of the shell-and-tube support assembly and has a unit of kg.

[0020] The shell-and-tube support assembly is a rigid member, and a stiffness-to-mass ratio M4 of the shell-and-tube support assembly is different from a stiffness-to-mass ratio M3 of the shell-and-tube heat exchanger.

[0021] In one of the embodiments, the shell-and-tube support assembly comprises a second arc-shaped plate, two third vertical plates, two vibration-isolating masses and a second horizontal plate, the second arc-shaped plate is supported below the shell of the shell-and-tube heat exchanger, the second horizontal plate is arranged below the second arc-shaped plate at intervals, the two third vertical plates are supported between the second arc-shaped plate and the second horizontal plate, and the two third vertical plates are arranged at intervals in a third direction, each vibration-isolating mass is connected to the two third vertical plates, and the two vibration-isolating masses are arranged at intervals in a fourth direction, the third direction intersects the fourth direction.

[0022] In one of the embodiments, the second arc-shaped plate is welded to the shell of the shell-and-tube heat exchanger.

[0023] And / or, each third vertical plate is welded to the second arc-shaped plate and to the second horizontal plate.

[0024] And / or, the vibration-isolating mass is welded to the third vertical plate.

[0025] And / or, the second horizontal plate has a thickness of no less than 20 mm.

[0026] And / or, the vibration-isolating mass has a thickness of no less than 60 mm.

[0027] In one of the embodiments, M0 / M1 is greater than 3, M1 / M2 is less than 0.75, M2 / M3 is greater than 10, and M3 / M4 is less than 0.1.

[0028] In one of the embodiments, a bottom base is further arranged below the shell-and-tube support assembly, and a stiffness-to-mass ratio M5 of the bottom base is k5 / m5, where k5 represents the stiffness of the bottom base and has a unit of N·m-1, and m5 represents the mass of the bottom base and has a unit of kg.

[0029] The stiffness-to-mass ratio M4 of the shell-and-tube support assembly is different from a stiffness-to-mass ratio M5 of the bottom base.

[0030] In one of the embodiments, a second connecting member is arranged between the shell-and-tube support assembly and the bottom base.

[0031] In one of the embodiments, the shell of the shell-and-tube heat exchanger has a thickness of 7 mm to 9 mm.

[0032] In one of the embodiments, the intermediate support assembly comprises a C-shaped steel and a support panel, the C-shaped steel and the support panel are connected to form a hollow structure, a surface of the C-shaped steel away from the support panel is connected with the compressor component, or a surface of the support panel away from the C-shaped steel is connected with the compressor component.

[0033] In one of the embodiments, the C-shaped steel and the support panel are welded.

[0034] And / or, the C-shaped steel is a steel plate with a thickness of no more than 6mm.

[0035] And / or, the thickness of the support panel is no less than 20mm.

[0036] In one of the embodiments, the shell of the compressor body and the compressor support foot are integrally casted.

[0037] In one of the embodiments, a plurality of first reinforcing rib plates are arranged between the compressor support foot and the shell of the compressor body, and the thickness of each of the first reinforcing rib plates is no less than 6mm.

[0038] And / or, a plurality of second reinforcing rib plates are arranged on the side of the compressor support foot away from the shell of the compressor body, and the thickness of the second reinforcing rib plates is no less than 6mm.

[0039] An air conditioning system comprising the above air conditioning system vibration reduction unit.

[0040] The above scheme provides an air conditioning system vibration reduction unit and an air conditioning system, when the compressor component vibrates, the vibration is sequentially transmitted downward through the intermediate support assembly. Based on the fact that the stiffness-mass ratio M0 of the compressor component and the stiffness-mass ratio M1 of the intermediate support assembly are not equal, energy loss will occur in the process of vibration transmission between the compressor component and the intermediate support assembly, achieving the effect of vibration reduction. Moreover, based on the fact that the compressor component and the intermediate support assembly are both rigid members, the deformation of the compressor component and the intermediate support assembly is small in the environment of transportation and ship loading, so the stability of the compressor body is high. BRIEF DESCRIPTION OF DRAWINGS

[0041] The accompanying drawings, which form a part of this application, are included to provide a further understanding of the application, and are incorporated in and constitute a part of this application. The embodiments of the application illustrated in the drawings, and their description, are presented to explain the present application and not to limit or define the present application.

[0042] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings needed in the embodiments description will be briefly introduced as follows. Obviously, the drawings in the following description only some embodiments of the present application, and for those skilled in the art, other drawings can be obtained without creative labor on the basis of these drawings.

[0043] Figure 1 The structural schematic diagram of the compressor device in the embodiment is shown in the figure.

[0044] Figure 2 The structural schematic diagram of the compressor component in the embodiment is shown in the figure.

[0045] Figure 3 The structural schematic diagram of the intermediate support assembly in the embodiment is shown in the figure.

[0046] Figure 4 The structural schematic diagram of the transition support assembly in the embodiment is shown in the figure.

[0047] Figure 5 The structural schematic diagram of the shell-and-tube support assembly in the embodiment is shown in the figure.

[0048] Figure 6 The impedance diagram corresponding to the vibration reduction unit of the air conditioning system in the embodiment is shown in the figure.

[0049] Explanation of reference signs:

[0050] 20, vibration reduction unit of air conditioning system; 21, compressor component; 211, compressor body; 212, compressor support foot; 2121, support bottom plate; 2122, support side plate; 213, first reinforcing rib plate; 214, second reinforcing rib plate; 22, intermediate support assembly; 221, C-shaped steel; 222, support panel; 23, transition support assembly; 231, first horizontal plate; 232, first vertical plate; 233, second vertical plate; 234, first arc-shaped plate; 24, shell-and-tube heat exchanger; 25, shell-and-tube support assembly; 251, second arc-shaped plate; 252, third vertical plate; 253, vibration damping mass; 254, second horizontal plate; 26, base. DETAILED DESCRIPTION

[0051] In order to make the above-mentioned objects, features and advantages of the present application more apparent and comprehensible, the specific embodiments of the present application will be described in detail below with reference to the drawings. In the following description, a lot of specific details are set forth in order to fully understand the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without departing from the spirit of the present application, so the present application is not limited to the specific embodiments disclosed below.

[0052] As Figure 1As shown, in one embodiment, an air conditioning system damping unit 20 is provided, comprising a compressor component 21 and an intermediate support assembly 22.

[0053] The compressor component 21 comprises a compressor body 211 and a compressor support foot 212 for supporting below the compressor body 211. The stiffness to mass ratio M0=k0 / m0 of the compressor component 21, wherein k0 represents the stiffness of the compressor component 21 and has a unit of N·m-1, and m0 represents the mass of the compressor component 21 and has a unit of kg;

[0054] The intermediate support assembly 22 is supported below the compressor component 21. The stiffness to mass ratio M1=k1 / m1 of the intermediate support assembly 22, wherein k1 represents the stiffness of the intermediate support assembly 22 and has a unit of N·m-1, and m1 represents the mass of the intermediate support assembly 22 and has a unit of kg;

[0055] The stiffness to mass ratio M0 of the compressor component 21 is not equal to the stiffness to mass ratio M1 of the intermediate support assembly 22.

[0056] When the compressor body 211 arranged on the compressor support foot 212 vibrates, the vibration of the compressor body 211 is sequentially transmitted downward through the compressor support foot 212 and the intermediate support assembly 22. Based on the stiffness to mass ratio M0 of the compressor component 21 being not equal to the stiffness to mass ratio M1 of the intermediate support assembly 22, there is energy loss in the process of vibration transmission between the compressor component 21 and the intermediate support assembly 22, thereby achieving the effect of vibration damping.

[0057] Further, the compressor component 21 and the intermediate support assembly 22 are both rigid body members. In the present application, the rigid body member refers to an object whose deformation after being stressed is extremely small relative to the geometric size of the object itself, and this deformation can be ignored when studying the motion of the object. For example, a steel member.

[0058] Based on the fact that the deformation of the rigid body member after being stressed is extremely small and can be ignored, the deformation of the compressor component 21 and the intermediate support assembly 22 is small in the environment of transportation and ship loading, thereby making the stability of the compressor body 211 higher.

[0059] In the present application, the use of rigid damping not only achieves the purpose of damping, but also makes the stability of the compressor body 211 higher in the environment of obvious shaking such as transportation and ship loading. Moreover, the material properties of the general rigid body member are relatively stable, and its decay speed or aging speed is slow over time, so it can maintain good damping performance for a long time, and the maintenance investment is small in the later period.

[0060] Specifically, as shown in Figure 2 the housing of the compressor body 211 is integrally cast connected with the compressor support foot 212.

[0061] The vibration generated by the movement of each device in the compressor body 211 will be transmitted to the compressor support foot 212 through the housing of the compressor body 211.

[0062] As shown in Figure 2 the compressor support foot 212 comprises a support bottom plate 2121 and a support side plate 2122, the support bottom plate 2121 is arranged transversely below the housing of the compressor body 211, and the support bottom plate 2121 is connected with the housing of the compressor body 211 through the support side plate 2122.

[0063] The support bottom plate 2121, the support side plate 2122 and the housing of the compressor body 211 are integrally cast together.

[0064] Further, the thickness of the support bottom plate 2121 is not less than 16 mm. The thickness of the support side plate 2122 is not less than 16 mm. So that the compressor support foot 212 has sufficient rigidity to support the compressor body 211.

[0065] For example, in an embodiment, the thickness of the support bottom plate 2121 is 16 mm, 18 mm, 20 mm, 22 mm, 24 mm, 26 mm or 28 mm. The thickness of the support side plate 2122 is 16 mm, 18 mm, 20 mm, 22 mm, 24 mm, 26 mm or 28 mm.

[0066] Further, as shown in Figure 2 the compressor support foot 212 and the housing of the compressor body 211 are provided with a plurality of first reinforcing rib plates 213, and the thickness of each first reinforcing rib plate 213 is not less than 6 mm. The first reinforcing rib plates 213 further improve the support stability of the compressor support foot 212, and the rigidity of the first reinforcing rib plates 213 with a thickness of not less than 6 mm can also meet the support requirements. Moreover, the arrangement of a plurality of first reinforcing rib plates 213 also enables the vibration of each part of the compressor body 211 to be transmitted to the compressor support foot 212 in a relatively balanced manner.

[0067] Specifically, in an embodiment, the thickness of the first reinforcing rib plate 213 is 6 mm, 7 mm, 8 mm or 9 mm.

[0068] Further, in order to improve the rigidity of the compressor component 21 itself, as shown in Figure 2As shown, a plurality of second reinforcing ribs 214 are arranged on the side of the compressor support foot 212 away from the shell of the compressor body 211, and the thickness of the second reinforcing ribs 214 is not less than 6 mm.

[0069] In some embodiments, the thickness of the second reinforcing ribs 214 is 6 mm, 7 mm, 8 mm or 9 mm.

[0070] The intermediate support assembly 22 and the compressor component 21 can be connected by a connecting member such as a bolt, or the intermediate support assembly 22 and the compressor component 21 can be welded.

[0071] Further, in some embodiments, as shown, Figure 3 As shown, the intermediate support assembly 22 comprises a C-shaped steel 221 and a support panel 222, and the C-shaped steel 221 and the support panel 222 are connected to form a hollow structure.

[0072] The surface of the C-shaped steel 221 away from the support panel 222 is connected to the compressor component 21, or the surface of the support panel 222 away from the C-shaped steel 221 is connected to the compressor component 21.

[0073] The vibration transmitted by the compressor component 21 is first received by one of the C-shaped steel 221 and the support panel 222, and then transmitted to the other. The hollow structure makes the vibration reduction effect of the intermediate support assembly 22 better.

[0074] Specifically, the C-shaped steel 221 is formed by bending a steel plate, and the thickness of the steel plate is less than the thickness of the support panel 222, so that the stiffness of the two is different, there is a stiffness mutation, so that the mechanical impedance is higher, thereby improving the vibration reduction effect.

[0075] In some embodiments, the thickness of the steel plate used to form the C-shaped steel 221 is not greater than 6 mm. For example, the thickness of the steel plate of the C-shaped steel 221 is 4 mm, 5 mm or 6 mm.

[0076] The thickness of the support panel 222 is not less than 20 mm. For example, the thickness of the support panel 222 is 20 mm, 21 mm or 22 mm.

[0077] In one embodiment, the C-shaped steel 221 and the support panel 222 are welded. Alternatively, other connection methods can also be used between the C-shaped steel 221 and the support panel 222, which are not limited here.

[0078] The C-shaped steel 221 is connected with the compressor component 21 by bolts. In a specific embodiment, the C-shaped steel 221 is connected with the support bottom plate 2121 by the bolts.

[0079] Further, in some embodiments, as Figure 1 As shown, the air conditioning system damping unit 20 further comprises a shell-and-tube heat exchanger 24, which is located below the intermediate support assembly 22. A transition support assembly 23 is arranged between the shell-and-tube heat exchanger 24 and the intermediate support assembly 22, and the stiffness-to-mass ratio M2=k2 / m2 of the transition support assembly 23, where k2 represents the stiffness of the transition support assembly 23 and has a unit of N·m-1, and m2 represents the mass of the transition support assembly 23 and has a unit of kg.

[0080] The transition support assembly 23 is a rigid member, and the stiffness-to-mass ratio M1 of the intermediate support assembly 22 is different from the stiffness-to-mass ratio M2 of the transition support assembly 23.

[0081] The vibration generated by the compressor component 21 is transmitted to the transition support assembly 23 through the intermediate support assembly 22, and based on the fact that the stiffness-to-mass ratio M2 of the transition support assembly 23 is different from the stiffness-to-mass ratio M1 of the intermediate support assembly 22, the energy is again attenuated in the process of transmitting the vibration from the intermediate support assembly 22 to the transition support assembly 23, and the vibration is further reduced.

[0082] When the vibration is transmitted from the compressor component 21 to the intermediate support assembly 22, a part of the energy is lost due to the difference in the stiffness-to-mass ratio between the two; when the vibration is transmitted from the intermediate support assembly 22 to the transition support assembly 23, a part of the energy is again lost due to the difference in the stiffness-to-mass ratio between the two. Finally, the vibration transmitted to the shell-and-tube heat exchanger 24 is relatively reduced.

[0083] Further, the transition support assembly 23 is also a rigid member, and the deformation amount during transportation or shipping is small and can be ignored, so that the stability of the compressor body 211 is high.

[0084] Specifically, the shell-and-tube heat exchanger 24 and the compressor body 211 belong to the same air conditioning system. The shell-and-tube heat exchanger 24 serves as an intermediate link for damping the vibration of the compressor component 21, and at the same time makes the overall structure of the air conditioning system as compact as possible.

[0085] Specifically, in some embodiments, as Figure 4As shown, the transition support assembly 23 comprises a first horizontal plate 231, two first vertical plates 232, two second vertical plates 233 and two first arc-shaped plates 234. The first horizontal plate 231 is connected with the intermediate support assembly 22. The two first vertical plates 232 and the two second vertical plates 233 are located on the side of the first horizontal plate 231 away from the intermediate support assembly 22, and the two first vertical plates 232 and the two second vertical plates 233 are connected with the first horizontal plate 231. The two first vertical plates 232 are arranged in a first direction, the two second vertical plates 233 are arranged in a second direction, and the first direction intersects the second direction. The two first arc-shaped plates 234 are supported above the shell of the shell-and-tube heat exchanger 24, the second vertical plates 233 are connected with the first arc-shaped plates 234, and the first arc-shaped plates 234 correspond to the second vertical plates 233 one by one.

[0086] As shown in Figure 1 , the shell of the shell-and-tube heat exchanger 24 is generally in a cylindrical structure, so the transition support assembly 23 comprises two first arc-shaped plates 234, which are used to cooperate with the shell of the shell-and-tube heat exchanger 24 to achieve higher stability. Specifically, the two first arc-shaped plates 234 can be attached to the shell of the shell-and-tube heat exchanger 24. The two first vertical plates 232 and the two second vertical plates 233 are arranged in a cross shape, forming a " " type structure as shown in Figure 4 , so that the transition support assembly 23 has higher rigidity. Specifically, in an embodiment, the first direction is perpendicular to the second direction. The first arc-shaped plates 234 are used to connect with the intermediate support assembly 22.

[0087] Further specifically, a first connecting member is arranged between the first horizontal plate 231 and the intermediate support assembly 22. The first connecting member can be a bolt or a screw, etc.

[0088] As shown in Figure 1 , Figure 3 , and Figure 4 , the first horizontal plate 231 is connected with the support panel 222 through the first connecting member.

[0089] In an embodiment, the first arc-shaped plates 234 are welded with the shell of the shell-and-tube heat exchanger 24. Alternatively, the first arc-shaped plates 234 can also be connected with the shell of the shell-and-tube heat exchanger 24 in other ways, such as bonding, etc.

[0090] Similarly, the second vertical plates 233 are welded with the first arc-shaped plates 234. Alternatively, the second vertical plates 233 can also be connected with the first arc-shaped plates 234 in other ways, which are not limited here.

[0091] Both the first vertical plates 232 and the second vertical plates 233 are welded with the first horizontal plate 231. The first vertical plates 232 and / or the second vertical plates 233 can also be connected with the first horizontal plate 231 by other means.

[0092] As shown in FIG. 2, the first vertical plates 232 and the second vertical plates 233 are arranged along the longitudinal direction of the transition support assembly 23. Figure 4 As shown in FIG. 2, the longitudinal plane of the second vertical plates 233 intersects the corresponding first arc-shaped plates 234, and the positions where the first vertical plates 232 intersect the second vertical plates 233 are all above the corresponding first arc-shaped plates 234, so that the load received by the first horizontal plate 231 can be reliably transmitted to the first arc-shaped plates 234.

[0093] As shown in FIG. 2, the second vertical plates 233 are arranged along the longitudinal direction, and the axis of the first arc-shaped plates 234 is perpendicular to the longitudinal plane of the second vertical plates 233. Figure 1

[0094] In some embodiments, the thickness of the first horizontal plate 231 is not less than 20 mm; for example, the thickness of the first horizontal plate 231 is 20 mm, 21 mm, or 22 mm.

[0095] The thickness of each first vertical plate 232 is not less than 12 mm; for example, the thickness of the first vertical plate 232 is 12 mm, 13 mm, or 14 mm.

[0096] The thickness of each second vertical plate 233 is not less than 12 mm; for example, the thickness of the second vertical plate 233 is 12 mm, 13 mm, or 14 mm.

[0097] The thickness of each first arc-shaped plate 234 is not less than 12 mm; for example, the thickness of the first arc-shaped plate 234 is 12 mm, 13 mm, or 14 mm.

[0098] Further, in one embodiment, the stiffness-to-mass ratio M3 of the shell-and-tube heat exchanger 24, where k3 represents the stiffness of the shell-and-tube heat exchanger 24 and has the unit of N·m-1, and m3 represents the mass of the shell-and-tube heat exchanger 24 and has the unit of kg, is not equal to the stiffness-to-mass ratio M2 of the transition support assembly 23.

[0099] In other words, when the vibration is transmitted from the transition support assembly 23 to the shell-and-tube heat exchanger 24, the energy is attenuated due to the difference in the stiffness-to-mass ratio.

[0100] As shown in FIG. 2, the first vertical plates 232 and the second vertical plates 233 are arranged along the longitudinal direction of the transition support assembly 23. Figure 1 ​As shown, a shell-and-tube support assembly 25 is provided below the shell-and-tube heat exchanger 24. The stiffness-to-mass ratio of the shell-and-tube support assembly 25 is M4=k4 / m4, where k4 represents the stiffness of the shell-and-tube support assembly 25 in N·m-1 and m4 represents the mass of the shell-and-tube support assembly 25 in kg.

[0101] The shell-and-tube support assembly 25 is a rigid component, and the stiffness-to-mass ratio M3 of the shell-and-tube heat exchanger 24 is not equal to the stiffness-to-mass ratio M4 of the shell-and-tube support assembly 25.

[0102] Vibration is transmitted from the compressor component 21 to the shell and tube support assembly 25. Due to the unequal stiffness-to-mass ratios between adjacent components, specifically M0 and M1, M1 and M2, M2 and M3, and M3 and M4, the vibration energy undergoes at least four attenuations.

[0103] Similarly, since the shell of the shell-and-tube heat exchanger 24 is a cylindrical structure, in some embodiments, such as Figure 5 As shown, the shell-and-tube support assembly 25 includes a second arc-shaped plate 251, two third vertical plates 252, two vibration-damping mass blocks 253, and a second horizontal plate 254. The second arc-shaped plate 251 is supported below the shell of the shell-and-tube heat exchanger 24. The second horizontal plate 254 is spaced below the second arc-shaped plate 251. The two third vertical plates 252 are both supported between the second arc-shaped plate 251 and the second horizontal plate 254, and the two third vertical plates 252 are spaced apart in a third direction. Each vibration-damping mass block 253 is connected to two third vertical plates 252, and the two vibration-damping mass blocks 253 are spaced apart in a fourth direction, which intersects with the fourth direction.

[0104] The vibrations received by the shell-and-tube heat exchanger 24 are transmitted to the second arc-shaped plate 251. The vibration-damping mass block 253 can achieve a mass-damping effect.

[0105] Furthermore, to improve the vibration damping effect, the thickness of the vibration damping mass block 253 can be designed to be no less than 60mm. For example, the thickness of the vibration damping mass block 253 can be 60mm, 65mm, 70mm, 75mm, or 80mm.

[0106] like Figure 5 As shown, the thickness of the vibration damping mass block 253 refers to the thickness value of the vibration damping mass block 253 in the spacing direction between the second arc-shaped plate 251 and the second horizontal plate 254.

[0107] The thickness of the third vertical plate 252 is 13mm, 14mm or 15mm;

[0108] The thickness of the second horizontal plate 254 is not less than 20 mm. For example, the thickness of the second horizontal plate 254 is 20 mm, 21 mm, 22 mm or 23 mm.

[0109] The vibration resistance mass 253 is welded with the third vertical plate 252. Alternatively, other connection methods can also be used between the vibration resistance mass 253 and the third vertical plate 252.

[0110] The second arc-shaped plate 251 is welded with the shell of the shell-and-tube heat exchanger 24. Other connection methods can also be used between the second arc-shaped plate 251 and the shell of the shell-and-tube heat exchanger 24.

[0111] In some embodiments, the second arc-shaped plate 251 is attached to the shell of the shell-and-tube heat exchanger 24.

[0112] In one embodiment, each third vertical plate 252 is welded with the second arc-shaped plate 251, and each third vertical plate 252 is welded with the second horizontal plate 254. The welding between the components of the shell-and-tube support assembly 25 makes the rigidity of the transition support assembly 23 larger.

[0113] Further, as Figure 1 shown in some embodiments, a base 26 is further provided below the shell-and-tube support assembly 25. The rigidity-to-mass ratio M5=k5 / m5 of the base 26, where k5 represents the rigidity of the base 26 and has the unit of N·m-1, and m5 represents the mass of the base 26 and has the unit of kg.

[0114] The rigidity-to-mass ratio M4 of the shell-and-tube support assembly 25 is not equal to the rigidity-to-mass ratio M5 of the base 26.

[0115] The vibration generated by the compressor 11 is transmitted to the base 26 through the compressor component 21, the intermediate support assembly 22, the transition support assembly 23, the shell of the shell-and-tube heat exchanger 24 and the shell-and-tube support assembly 25 in sequence, and finally transmitted out by the base 26. In this process, the rigidity-to-mass ratio of each adjacent component is not equal, so the vibration energy is attenuated multiple times.

[0116] Suppose the attenuation of vibration in the transmission process is analyzed by using the electromechanical analogy method, as Figure 6 shown in the corresponding impedance diagram. According to the impedance diagram, the impedance is as follows:

[0117]

[0118] wherein, is the rigidity impedance, is the mass impedance, R i (i=2, 3, 4, 5) isFigure 6 The overall impedance corresponding to each position.

[0119] According to the impedance relationship, the ratio of the displacement of the terminal response point x5 to the displacement of the excitation point x1, x5 / x1, satisfies the following formula:

[0120]

[0121] The ratio x5 / x1 reflects the displacement transmission coefficient of the vibration in this process, and represents the vibration damping characteristics of the air conditioning system damping unit 20.

[0122] It is assumed that the stiffness-to-mass ratio of each component in the air conditioning system damping unit 20 is as shown in Table 1 below.

[0123] Table 1 Stiffness-to-mass ratio of each component in the air conditioning system damping unit

[0124] Number Component Mass / kg stiffness (N-m -1 )]]> stiffness / mass (N-m / kg -1 · kg -1 )]]> 1 Compressor component 314 8.71 x 10 9 ]] 3.72 x 10 7 ]] 2 Intermediate support assembly 11 1.16 x 10 8 ]]> 1.05 x 10 7 ]] 3 Transition support assembly 65 9.66 x 10 8 ]] 1.49 x 10 7 ]] 4 Shell and tube heat exchanger 82.3 6.58 x 10 7 ]]> 7.99 x 10 5 ]] 5 Shell and tube support assembly 68.5 7.08 x 10 8 ]] 1.03 x 10 7 ]]>

[0125] According to the data in the table 1 and the formula satisfied by the above ratio x5 / x1, the displacement vibration transmission coefficient of the compressor component 21 under different excitation frequencies can be obtained, as shown in Table 2 below:

[0126] Table 2 Transmission coefficient of the compressor component under different excitation frequencies

[0127] Excitation frequency 1 times meshing frequency 2 times meshing frequency 3 times meshing frequency 4 times meshing frequency Transmission coefficient 0.10 0.33 0.46 0.044

[0128] Therefore, by using the above air conditioning system damping unit 20, the displacement transmission coefficient of the compressor component 21 after passing through the air conditioning system damping unit 20 is less than 1 when the compressor component 21 operates at the main excitation frequency, which achieves good damping effect. Especially in the case of high excitation frequency, the damping effect of the air conditioning system damping unit 20 is better.

[0129] It should be noted that M0 is not equal to M1, which includes M0 greater than M1, and also includes M0 less than M1. Similarly, M1 is not equal to M2, which includes M1 greater than M2, and also includes M1 less than M2. M2 is not equal to M3, which includes M2 greater than M3, and also includes M2 less than M3. M3 is not equal to M4, which includes M3 greater than M4, and also includes M3 less than M4. M4 is not equal to M5, which includes M4 greater than M5, and also includes M4 less than M5. As long as the stiffness-to-mass ratio between adjacent components is not equal, there will be energy loss when the vibration is transmitted between them.

[0130] In a specific embodiment, considering that the compressor component 21 has large mass and stiffness, M0 / M1 is limited to be greater than 3, and M1 / M2 is limited to be less than 0.75.

[0131] The shell of the shell-and-tube heat exchanger 24 is in a cylindrical structure, and the rigidity of the shell-and-tube heat exchanger 24 can be designed to be smaller, so the ratio M2 / M3 of the rigidity mass ratio M2 of the transition support assembly 23 to the rigidity mass ratio M3 of the shell-and-tube heat exchanger 24 is greater than 10.

[0132] Similarly, the ratio M3 / M4 of the rigidity mass ratio M3 of the shell-and-tube heat exchanger 24 to the rigidity mass ratio M4 of the shell-and-tube support assembly 25 is less than 0.1.

[0133] Further, in some embodiments, a second connecting member is arranged between the shell-and-tube support assembly 25 and the base 26. The second connecting member can be a bolt or a screw, etc.

[0134] Specifically as shown in Figure 1 The second transverse plate 254 is connected to the base 26 through the second connecting member.

[0135] The thickness of the shell of the shell-and-tube heat exchanger 24 is 7mm-9mm. Specifically, in some embodiments, the thickness of the shell of the shell-and-tube heat exchanger 24 is 7mm, 8mm or 9mm.

[0136] Further, in yet some embodiments, an air conditioning system is provided, which comprises the above-mentioned air conditioning system vibration reduction unit 20.

[0137] The compressor component 21 in the air conditioning system is supported by the intermediate support assembly 22, and the vibration reduction effect is obvious, and the air conditioning system will not shake obviously during transportation, and the stability is high. In particular, when the air conditioning system is applied to a ship or the like where shaking is obvious, the advantage of stability is more obvious.

[0138] In the description of the present application, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and therefore cannot be understood as indicating or implying that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application.

[0139] In addition, the terms "first", "second", etc. are used herein only to describe different instances, and are not used to denote or imply relative importance or a number of indications of the technical features indicated. Thus, the technical features defined with "first", "second", etc. can explicitly or implicitly include at least one of the technical features. In the description of the present application, the meaning of "a plurality of" is at least two, such as two, three, etc., unless otherwise explicitly specified and limited.

[0140] In the present application, unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connecting", "fixing" and the like should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or it can be integrated; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the internal communication of two elements or the interaction relationship between two elements, unless otherwise explicitly limited. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0141] In the present application, unless otherwise explicitly specified and limited, the first feature is "on" or "under" the second feature, which can be direct contact between the first and second features, or indirect contact between the first and second features through an intermediate medium. Moreover, the first feature "above", "above" and "above" the second feature can be directly above or obliquely above the first feature, or only indicate that the horizontal height of the first feature is higher than that of the second feature. The first feature "below", "below" and "below" the second feature can be directly below or obliquely below the first feature, or only indicate that the horizontal height of the first feature is less than that of the second feature.

[0142] It should be noted that when an element is referred to as "fixed to" or "disposed on" another element, it can be directly on the other element or there can be a middle element. When an element is referred to as "connected to" another element, it can be directly connected to the other element or there can be a middle element. The terms "vertical", "horizontal", "up", "down", "left", "right" and similar expressions used herein are for illustrative purposes only and are not the only implementation.

[0143] The technical features of the above-described embodiments can be combined in any manner. In order to make the description concise, all possible combinations of the technical features in the above-described embodiments are not described, but as long as the combination of the technical features does not exist, it should be considered as the scope of the present application.

[0144] The above embodiments only express several implementation manners of the present application, and the description is more specific and detailed, but it should not be understood as a limitation on the scope of the patent. It should be noted that for ordinary skilled persons in the art, without departing from the concept of the present application, several modifications and improvements can be made, which are within the scope of protection of the present application. Therefore, the protection scope of the patent of the present application should be subject to the appended claims.

Claims

1. A vibration damping unit for an air conditioning system, characterized in that, Compressor component, the compressor component includes compressor body and compressor support foot for supporting below the compressor body, the stiffness mass ratio M0=k0 / m0 of the compressor component, wherein k0 represents the stiffness of the compressor component and the unit is N·m-1, m0 represents the mass of the compressor component and the unit is kg; Intermediate support assembly, the intermediate support assembly is supported below the compressor component, the stiffness mass ratio M1=k1 / m1 of the intermediate support assembly, wherein k1 represents the stiffness of the intermediate support assembly and the unit is N·m-1, m1 represents the mass of the intermediate support assembly and the unit is kg; The compressor component and the intermediate support assembly are both rigid members, the stiffness mass ratio M0 of the compressor component is not equal to the stiffness mass ratio M1 of the intermediate support assembly; The intermediate support assembly includes C-shaped steel and support panel, the C-shaped steel is connected with the support panel to form a hollow structure, the surface of the C-shaped steel away from the support panel is connected with the compressor component, or the surface of the support panel away from the C-shaped steel is connected with the compressor component; The C-shaped steel is formed by bending steel plate, and the thickness of the C-shaped steel is less than the thickness of the support panel; The shell of the compressor body is integrally cast connected with the compressor support foot; A plurality of first reinforcing rib plates are arranged between the compressor support foot and the shell of the compressor body, and the thickness of each first reinforcing rib plate is not less than 6 mm; And / or, a plurality of second reinforcing rib plates are arranged on the side of the compressor support foot away from the shell of the compressor body, and the thickness of the second reinforcing rib plate is not less than 6 mm. The vibration reduction unit of the air conditioning system further includes a shell-and-tube heat exchanger located below the intermediate support assembly, a transition support assembly is arranged between the shell-and-tube heat exchanger and the intermediate support assembly, the stiffness mass ratio M2=k2 / m2 of the transition support assembly, wherein k2 represents the stiffness of the transition support assembly and the unit is N·m-1, m2 represents the mass of the transition support assembly and the unit is kg; 2. The air conditioning system damping unit of claim 1, wherein The transition support assembly is a rigid member, and the stiffness mass ratio M1 of the intermediate support assembly is not equal to the stiffness mass ratio M2 of the transition support assembly. The transition support assembly includes a first horizontal plate, two first vertical plates, two second vertical plates and two first arc-shaped plates, the first horizontal plate is connected with the intermediate support assembly, the two first vertical plates and the two second vertical plates are located on the side of the first horizontal plate away from the intermediate support assembly, and the two first vertical plates and the two second vertical plates are connected with the first horizontal plate, the two first vertical plates are arranged in a first direction, the two second vertical plates are arranged in a second direction, the first direction intersects the second direction, and the two first arc-shaped plates are supported above the shell of the shell-and-tube heat exchanger, the second vertical plate is connected with the first arc-shaped plate, and the first arc-shaped plate corresponds to the second vertical plate one by one.

3. The air conditioning system vibration reduction unit of claim 2, wherein The first arc-shaped plate is welded with the shell of the shell-and-tube heat exchanger.

4. The air conditioning system damping unit of claim 3, wherein ​ And / or, the second vertical plate is welded with the first arc-shaped plate; And / or, the two first vertical plates and the two second vertical plates are welded with the first horizontal plate; And / or, a first connecting piece is arranged between the first horizontal plate and the intermediate support assembly.

5. The air conditioning system vibration reduction unit of claim 3, wherein The thickness of the first horizontal plate is not less than 20mm; And / or, the thickness of each first vertical plate is not less than 12mm; And / or, the thickness of each second vertical plate is not less than 12mm.

6. The air conditioning system vibration reduction unit of claim 2, wherein The stiffness mass ratio M3=k3 / m3 of the shell-and-tube heat exchanger, wherein k3 represents the stiffness of the shell-and-tube heat exchanger and the unit is N·m-1, and m3 represents the mass of the shell-and-tube heat exchanger and the unit is kg; the stiffness mass ratio M2 of the transition support assembly is not equal to the stiffness mass ratio M3 of the shell-and-tube heat exchanger.

7. The air conditioning system vibration reduction unit of claim 6, wherein A shell-and-tube support assembly is arranged below the shell-and-tube heat exchanger, the stiffness mass ratio M4=k4 / m4 of the shell-and-tube support assembly, wherein k4 represents the stiffness of the shell-and-tube support assembly and the unit is N·m-1, and m4 represents the mass of the shell-and-tube support assembly and the unit is kg; The stiffness mass ratio M3 of the shell-and-tube heat exchanger is not equal to the stiffness mass ratio M4 of the shell-and-tube support assembly.

8. The air conditioning system vibration reduction unit of claim 7, wherein, The shell-and-tube support assembly comprises a second arc-shaped plate, two third vertical plates, two vibration-blocking mass blocks and a second horizontal plate, the second arc-shaped plate is supported below the shell of the shell-and-tube heat exchanger, the second horizontal plate is arranged below the second arc-shaped plate in a spaced manner, the two third vertical plates are supported between the second arc-shaped plate and the second horizontal plate, and the two third vertical plates are arranged in a spaced manner in a third direction, each vibration-blocking mass block is connected with the two third vertical plates, the two vibration-blocking mass blocks are arranged in a spaced manner in a fourth direction, and the third direction intersects with the fourth direction.

9. The air conditioning system vibration reduction unit of claim 8, wherein, The second arc-shaped plate is welded with the shell of the shell-and-tube heat exchanger; And / or, each third vertical plate is welded with the second arc-shaped plate and the second horizontal plate; And / or, the vibration-blocking mass block is welded with the third vertical plate; And / or, the thickness of the second horizontal plate is not less than 20mm; And / or, the thickness of the vibration-blocking mass block is not less than 60mm.

10. The air conditioning system vibration reduction unit of claim 7, wherein M0 / M1 is greater than 3, M1 / M2 is less than 0.75, M2 / M3 is greater than 10, and M3 / M4 is less than 0.

1.

11. The air conditioning system vibration reduction unit of claim 7, wherein A base is further arranged below the shell-and-tube support assembly, the stiffness mass ratio M5=k5 / m5 of the base, wherein k5 represents the stiffness of the base and the unit is N·m-1, and m5 represents the mass of the base and the unit is kg; The stiffness mass ratio M4 of the shell-and-tube support assembly is not equal to the stiffness mass ratio M5 of the base.

12. The air conditioning system vibration reduction unit of claim 11, wherein, A second connecting piece is arranged between the shell-and-tube support assembly and the base.

13. The air conditioning system vibration reduction unit of claim 6, wherein, The thickness of the shell of the shell-and-tube heat exchanger is 7mm-9mm.

14. The air conditioning system vibration reduction unit of claim 1, wherein, The C-shaped steel is welded with the support panel; And / or, the C-shaped steel is a steel plate with a thickness not greater than 6mm which is bent to form; And / or, the thickness of the support panel is not less than 20mm.

15. An air conditioning system, characterised in that, The air conditioning system vibration reduction unit comprises the air conditioning system vibration reduction unit according to any one of claims 1 to 14.

Images