Water chilling unit

Abstract

The utility model relates to a water chilling unit which comprises a compressor and an evaporator, the evaporator comprises a shell and a heat exchange pipe set, a liquid inlet pipe is arranged at the bottom of the shell, and an air suction pipe is arranged at the top of the shell; the heat exchange tube set comprises a plurality of heat exchange tubes, the heat exchange tubes extend in the length direction of the shell and are arranged in parallel, the heat exchange tube set is provided with a plurality of heat exchange areas from bottom to top in the height direction of the shell, and the diameters of the heat exchange tubes in the adjacent heat exchange areas are different and / or the arrangement densities of the heat exchange tubes in the adjacent heat exchange areas are different. The heat exchange tubes with different tube diameter specifications are used, and different arrangement distances, arrangement densities and arrangement forms are adopted in different heat exchange areas to adapt to the escape flowing speed of a refrigerant working medium at the position, so that the flowing resistance of the refrigerant is reduced, the refrigerant liquid is uniformly distributed, and the liquid carrying phenomenon at an air suction port of an evaporator can be reduced.

Description

Technical Field

[0001] The utility model belongs to the technical field of refrigeration equipment, and in particular relates to a water chiller. Background Art

[0002] During the operation of the chiller, the refrigerant undergoes an evaporation phase change between the heat exchange tubes in the evaporator. Since each heat exchange tube element in the flooded evaporator is immersed in the refrigerant, the heat flux density in the entire heat exchanger space and the intensity of the refrigerant evaporation phase change are not the same, resulting in different velocities of the refrigerant gaseous medium escaping from the heat exchange tubes after the phase change.

[0003] In conventional flooded evaporators, the heat exchange tube elements have the same structural form, arrangement spacing, and arrangement density at all positions, without corresponding layered and differentiated arrangement design. Such an arrangement cannot well match the refrigerant working medium escape flow velocity at different positions, and easily causes problems such as large refrigerant flow resistance at local positions and uneven refrigerant liquid distribution.

[0004] The above information disclosed in the background technology is only used to increase the understanding of the background technology of the present application, and therefore, it may include information that does not constitute the prior art known to ordinary technicians in the field. Summary of the invention

[0005] The utility model aims to provide a chiller to solve the problems existing in the prior art that the arrangement of heat exchange tubes in the evaporator of the existing chiller cannot match the refrigerant flow state at the corresponding position, resulting in large refrigerant flow resistance at local positions and uneven refrigerant liquid distribution.

[0006] In order to achieve the above-mentioned utility model purpose, the utility model adopts the following technical solutions:

[0007] The utility model proposes a chiller, which comprises:

[0008] compressor;

[0009] an evaporator connected to the compressor, the evaporator comprising a shell and a heat exchange tube group arranged in the shell, a heat exchange inner cavity is formed in the shell, a liquid inlet pipe is arranged at the bottom of the shell, and an air intake pipe is arranged at the top of the shell, and the liquid inlet pipe and the air intake pipe are both in communication with the heat exchange inner cavity;

[0010] Wherein, the heat exchange tube group includes a plurality of heat exchange tubes, each of which extends along the length direction of the shell and is arranged parallel to each other. The heat exchange tube group is arranged into a plurality of heat exchange zones from top to bottom along the height direction of the shell, and the diameters of the heat exchange tubes in adjacent heat exchange zones are different and / or the arrangement densities of the heat exchange tubes in adjacent heat exchange zones are different.

[0011] In some embodiments of the present application, the shell includes a first heat exchange zone, a second heat exchange zone, a third heat exchange zone and a fourth heat exchange zone from bottom to top along the height direction of the shell.

[0012] In some embodiments of the present application, the diameter of the heat exchange tube in the first heat exchange zone is smaller than the diameter of the heat exchange tube in the second heat exchange zone, and the arrangement density of the heat exchange tube in the first heat exchange zone is greater than the arrangement density of the heat exchange tube in the second heat exchange zone.

[0013] In some embodiments of the present application, the diameter of the heat exchange tube in the fourth heat exchange zone is smaller than the diameter of the heat exchange tube in the third heat exchange zone, and the arrangement density of the heat exchange tube in the fourth heat exchange zone is greater than the arrangement density of the heat exchange tube in the third heat exchange zone.

[0014] In some embodiments of the present application, a water inlet pipe section and a water outlet pipe section are provided at the end of the shell, the water inlet pipe section is located below the water outlet pipe section, and both ends of each heat exchange tube are respectively connected to the water inlet pipe section and the water outlet pipe section.

[0015] In some embodiments of the present application, a plurality of support members are arranged at intervals in the heat exchange inner cavity, a support hole is formed on each of the support members, and the heat exchange tube passes through the corresponding support hole.

[0016] In some embodiments of the present application, an air intake baffle is provided on the top of the heat exchange inner cavity, and the air intake baffle is located directly below the air intake pipe to prevent liquid refrigerant from being output from the air intake pipe along with the gaseous refrigerant.

[0017] In some embodiments of the present application, a liquid inlet barrier is also provided at the bottom of the heat exchange inner cavity, and the liquid inlet barrier is arranged along the length direction of the heat exchange inner cavity. A liquid inlet cavity is formed between the liquid inlet barrier and the shell, and a plurality of liquid inlet holes are dispersedly formed on the liquid inlet barrier for uniformly transporting the liquid refrigerant into the heat exchange inner cavity.

[0018] In some embodiments of the present application, a liquid balancing plate is provided on the side wall of the heat exchange inner cavity, and the liquid balancing plate is symmetrically arranged above the second heat exchange zone to prevent the liquid refrigerant from being transported upward along with the gaseous refrigerant.

[0019] On the other hand, the present application also proposes a chiller, which comprises:

[0020] compressor;

[0021] an evaporator connected to the compressor, the evaporator comprising a shell and a heat exchange tube group arranged in the shell, a heat exchange inner cavity is formed in the shell, a liquid inlet pipe is arranged at the bottom of the shell, and an air intake pipe is arranged at the top of the shell, and the liquid inlet pipe and the air intake pipe are both in communication with the heat exchange inner cavity;

[0022] Wherein, the heat exchange tube group includes a plurality of heat exchange tubes, and the heat exchange tube group is arranged into a plurality of heat exchange zones from top to bottom along the height direction of the shell, and the heat exchange zones at least include a bottom heat exchange zone located at the bottom of the heat exchange inner cavity and a top heat exchange zone located at the top of the heat exchange inner cavity, and the bottom heat exchange zone and the top heat exchange zone are configured so that when the refrigerant flows through the bottom heat exchange zone and the top heat exchange zone, the flow rate of the refrigerant is reduced to improve the stability of the refrigerant flow.

[0023] Compared with the prior art, the advantages and positive effects of the utility model are:

[0024] The chiller involved in the present application is provided with a plurality of heat exchange zones, and the diameters of the heat exchange tubes in adjacent heat exchange zones are different and / or the arrangement densities of the heat exchange tubes in adjacent heat exchange zones are different. By using heat exchange tubes with different tube diameters, different arrangement spacings, arrangement densities and arrangement forms are adopted in different heat exchange zones to adapt to the escape flow speed of the refrigerant working medium at the position, thereby achieving the reduction of the refrigerant flow resistance and the uniform distribution of the refrigerant liquid, and can reduce the liquid carryover phenomenon at the suction port of the evaporator.

[0025] After reading the specific embodiments of the present invention in conjunction with the accompanying drawings, other features and advantages of the present invention will become more clear. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] 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 some embodiments of the utility model. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0027] Figure 1 is one of the schematic diagrams of the evaporator structure according to the embodiment;

[0028] Figure 2 This is a second schematic diagram of the structure of an evaporator according to an embodiment;

[0029] Figure 3 is a schematic diagram of installing a support member in a heat exchange inner cavity according to an embodiment;

[0030] Figure 4 is a schematic diagram of the disassembly of the support member and the evaporator according to an embodiment;

[0031] Figure 5 is a schematic diagram of a supporting member structure according to an embodiment;

[0032] Figure 6 is a schematic diagram of a cross-section of an evaporator according to an embodiment;

[0033] Figure 7 is a schematic diagram of a housing structure according to an embodiment;

[0034] Figure 8 is a schematic structural diagram of a first support base according to an embodiment;

[0035] Fig. 9 is a schematic diagram of the structure of the second support base;

[0036] Fig.10 is a schematic diagram of the connection between the first support seat and the water inlet pipe section and the water outlet pipe section;

[0037] Reference numerals:

[0038] 100, shell; 101, first heat exchange zone; 102, second heat exchange zone; 103, third heat exchange zone; 104, fourth heat exchange zone;

[0039] 110, liquid inlet pipe; 120, air intake pipe; 130, liquid inlet baffle; 140, air intake baffle; 150, liquid equalizing plate; 160, liquid baffle plate;

[0040] 200, first support seat; 210, first support leg; 220, first fixing hole; 230, first water hole;

[0041] 300, second support base; 310, second support leg; 320, second fixing hole; 330, second water hole; 340, second connecting shell;

[0042] 400, circulating water group; 410, first connecting shell; 411, horizontal baffle; 420, water outlet pipe section; 430, water inlet pipe section;

[0043] 500, heat exchange tube;

[0044] 600, support member; 610, first support area; 620, second support area; 630, third support area; 640, fourth support area. DETAILED DESCRIPTION

[0045] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0046] In the description of the present application, 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 application and simplifying the description, and do not indicate or imply that the device or element referred to 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 application.

[0047] The terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of this application, unless otherwise specified, "plurality" means two or more.

[0048] In the description of this application, 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 mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected 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 this application can be understood according to specific circumstances.

[0049] In the present utility model, unless otherwise clearly specified and limited, a first feature being "above" or "below" a second feature may include that the first and second features are in direct contact, or may include that the first and second features are not in direct contact but are in contact through another feature between them. Moreover, a first feature being "above", "above" and "above" a second feature includes that the first feature is directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature. A first feature being "below", "below" and "below" a second feature includes that the first feature is directly below and obliquely below the second feature, or simply indicates that the first feature is lower in level than the second feature.

[0050] The disclosure below provides many different embodiments or examples for realizing different structures of the utility model. In order to simplify the disclosure of the utility model, the components and settings of specific examples are described below. Of course, they are merely examples, and the purpose is not to limit the utility model. In addition, the utility model may repeat reference numbers and / or reference letters in different examples, and such repetition is for the purpose of simplification and clarity, and does not itself indicate the relationship between the various embodiments and / or settings discussed. In addition, the utility model provides various specific examples of processes and materials, but those of ordinary skill in the art may be aware of the application of other processes and / or the use of other materials.

[0051] The present application proposes a water chiller, which includes a compressor, a condenser, a throttle valve and an evaporator connected through pipelines.

[0052] The evaporator is specifically connected to the output end of the compressor, refer to Figure 1-Figure 3 The evaporator includes a shell 100 and a heat exchange tube group arranged in the shell 100. A heat exchange inner cavity is formed in the shell 100. The heat exchange tube group includes a plurality of heat exchange tubes 500.

[0053] A liquid inlet pipe 110 is disposed at the bottom of the shell 100 . Specifically, the shell 100 is a horizontally placed cylindrical shape, and the liquid inlet pipe 110 is plugged into the bottom of the shell 100 .

[0054] An air intake pipe 120 is disposed on the top of the housing 100 . Specifically, the air intake pipe 120 is plugged into the top of the housing 100 , and the connection position between the air intake pipe and the housing 100 is sealed.

[0055] The liquid inlet pipe 110 and the air intake pipe 120 are both connected to the heat exchange inner cavity. The liquid inlet pipe 110 transports the refrigerant to the bottom of the heat exchange inner cavity. The heat exchange tube 500 is filled with high-temperature liquid. After the heat exchange tube 500 exchanges heat with the refrigerant, the refrigerant changes from liquid to gas and is finally output from the air intake pipe 120.

[0056] The heat exchange tube group is arranged from top to bottom along the height direction of the shell 100 to form a plurality of heat exchange zones, and each heat exchange zone includes at least one layer of heat exchange tubes 500 .

[0057] That is, along the height direction of the heat exchange inner cavity, each heat exchange zone includes at least one layer of heat exchange tubes 500 , or, along the height direction of the heat exchange inner cavity, the heat exchange zone includes multiple layers of heat exchange tubes 500 .

[0058] The number of heat exchange tubes 500 in each layer is determined according to the diameter of the heat exchange tubes 500 , the width of the heat exchange inner cavity at the corresponding position, and the spacing between adjacent heat exchange tubes 500 .

[0059] In order to achieve the purpose of better liquid equalization and liquid blocking for the refrigerant in response to the flow state of different refrigerants and to make the liquid flow state more stable, the present application designs the heat exchange tubes 500 in adjacent heat exchange zones to have different diameters and / or different arrangement densities of the heat exchange tubes 500 in adjacent heat exchange zones.

[0060] Combination Figure 8 , Fig. 9 , both ends of the shell 100 are blocked by the first support base 200 and the second support base 300.

[0061] In addition to blocking both ends of the housing 100 , the first support base 200 and the second support base 300 also support the housing 100 .

[0062] Combination Fig.10 The first support base 200 is externally connected to a circulating water group 400 , and the circulating water group 400 includes a first connecting shell 410 detachably connected to the outside of the first support base 200 and a water outlet pipe section 420 and a water inlet pipe section 430 connected to the first connecting shell 410 .

[0063] The first support base 200 and the second support base 300 are specifically vertically arranged plate-shaped structures.

[0064] A first connecting inner cavity extending in a direction away from the first supporting seat 200 is formed on the first connecting shell 410 .

[0065] A second connection shell 340 is further connected to the outside of the second support base 300 , and a second communicating inner cavity is formed between the second connection shell 340 and the second support base 300 .

[0066] A first support leg 210 is disposed at the bottom of the first support base 200 , and a second support leg 310 is disposed at the bottom of the second support base 300 for supporting and fixing.

[0067] The first support base 200 is formed with first fixing holes 220 distributed in an annular manner, and the second support base 300 is formed with second fixing holes 320 distributed in an annular manner, which are used for detachable connection with two ends of the housing 100 .

[0068] The water inlet pipe section 430 and the water outlet pipe section 420 are arranged up and down on the first connecting shell 410 , and the water inlet pipe section 430 is located below the water outlet pipe section 420 .

[0069] A transverse partition 411 is provided in the first communicating inner cavity, and the transverse partition 411 divides the first communicating inner cavity into a water inlet cavity and a water outlet cavity.

[0070] The water inlet pipe section 430 is communicated with the water inlet cavity, and the water outlet pipe section 420 is communicated with the water outlet cavity.

[0071] In order to achieve communication between the heat exchange tube 500 and the water inlet chamber and the water outlet chamber, a first water through hole 230 is formed on the first support seat 200 , and a second water through hole 330 is formed on the second support seat 300 .

[0072] In some embodiments of the present application, each heat exchange tube 500 in the heat exchange tube group is linear, and both ends of each heat exchange tube 500 are connected to the first connecting inner cavity and the second connecting inner cavity through the first water hole 230 and the second water hole 330 respectively.

[0073] Both ends of the part of the heat exchange tubes 500 located at the lower side are respectively connected to the second communicating inner cavity and the water inlet cavity, and both ends of the part of the heat exchange tubes 500 located at the upper side are respectively connected to the second communicating inner cavity and the water outlet cavity.

[0074] The water inlet pipe section 430 is connected to the pump body. Driven by the pump body, the fluid is transported to the second connecting inner cavity through the water inlet cavity and the lower heat exchange tube 500. Under the continuous action of the fluid pressure, the fluid in the second connecting inner cavity is transported back to the water outlet cavity through the upper heat exchange tube 500 and finally output from the water outlet pipe section 420.

[0075] refer to Figure 6 Specifically, in some embodiments of the present application, the shell 100 includes a first heat exchange zone 101, a second heat exchange zone 102, a third heat exchange zone 103 and a fourth heat exchange zone 104 from top to bottom along the height direction of the shell 100.

[0076] A gap is formed between the highest position of the heat exchange zone and the top of the heat exchange inner cavity, and the gaseous refrigerant after the heat exchange is completed passes upward through the gap and is output from the suction pipe 120.

[0077] The first heat exchange zone 101 , the second heat exchange zone 102 , the third heat exchange zone 103 and the fourth heat exchange zone 104 each include at least one layer of heat exchange tubes 500 .

[0078] For example but not limited to, the first heat exchange zone 101 at the bottom layer includes a layer of heat exchange tubes 500, the diameter of the heat exchange tubes 500 is d1, and the gap between adjacent heat exchange tubes 500 is L1, that is, the minimum gap between two adjacent heat exchange tubes 500 in the first heat exchange zone 101 is L1.

[0079] Of course, the first heat exchange zone 101 may also include at least two layers of heat exchange tubes 500 arranged along the height direction of the heat exchange inner cavity, and the gaps between the heat exchange tubes 500 of the same layer or between adjacent layers of heat exchange tubes 500 in the first heat exchange zone 101 are both L1.

[0080] The second heat exchange zone 102 located above the first heat exchange zone 101 includes at least one layer of heat exchange tubes 500. The diameter of the heat exchange tubes 500 is d2, and the gap between adjacent heat exchange tubes 500 is L2, that is, the minimum gap between two adjacent heat exchange tubes 500 in the second heat exchange zone 102 is L2.

[0081] In some embodiments of the present application, the second heat exchange zone 102 includes a plurality of heat exchange tubes 500 arranged along the height direction of the heat exchange inner cavity, and the gaps between the heat exchange tubes 500 of the same layer or between adjacent layers in the second heat exchange zone 102 are both L2.

[0082] Among them, the diameter d1 of the heat exchange tube 500 in the first heat exchange zone 101 is smaller than the diameter d2 of the heat exchange tube 500 in the second heat exchange zone 102, and the minimum gap L1 between two adjacent heat exchange tubes 500 in the first heat exchange zone 101 is smaller than the minimum gap L2 between two adjacent heat exchange tubes 500 in the second heat exchange zone 102.

[0083] That is, compared with the second heat exchange zone 102 , the heat exchange tubes 500 in the first heat exchange zone 101 have smaller diameters and are densely arranged.

[0084] When the refrigerant flows through the first heat exchange zone 101, due to the small spacing between the heat exchange tubes 500 and the heat exchange tubes 500, the liquid refrigerant will be evenly divided into multiple parts and flow through this part of the area; in addition, since the diameter of the heat exchange tubes 500 in the first heat exchange zone 101 is small, when the liquid inside the heat exchange tubes 500 flows along the tubes, its flow resistance is relatively large, and the flow rate of the liquid is slower than the flow rate inside the heat exchange tubes 500 in the second heat exchange zone 102, so that the evaporation phase change rate of the refrigerant outside the heat exchange tubes 500 in the first heat exchange zone 101 is slower, and thus the flow state of the liquid refrigerant is relatively stable.

[0085] The third heat exchange zone 103 located above the second heat exchange zone 102 includes at least one layer of heat exchange tubes 500 . The diameter of the heat exchange tubes 500 is d3, and the gap between adjacent heat exchange tubes 500 is L3. That is, the minimum gap between two adjacent heat exchange tubes 500 in the third heat exchange zone 103 is L3.

[0086] In some embodiments of the present application, the third heat exchange zone 103 includes multiple layers of heat exchange tubes 500 arranged along the height direction of the heat exchange inner cavity, and the gaps between the heat exchange tubes 500 of the same layer or between adjacent layers of heat exchange tubes 500 in the third heat exchange zone 103 are both L3.

[0087] The fourth heat exchange zone 104 at the top layer also includes at least one layer of heat exchange tubes 500 . The diameter of the heat exchange tubes 500 is d4 , and the gap between adjacent heat exchange tubes 500 is L4 , that is, the minimum gap between two adjacent heat exchange tubes 500 in the fourth heat exchange zone 104 is L4 .

[0088] Of course, the fourth heat exchange zone 104 may also include at least two layers of heat exchange tubes 500 arranged along the height direction of the heat exchange inner cavity, and the gaps between the heat exchange tubes 500 of the same layer or between adjacent layers of heat exchange tubes 500 in the fourth heat exchange zone 104 are both L4.

[0089] Among them, the diameter d4 of the heat exchange tube 500 in the fourth heat exchange zone 104 is smaller than the diameter d3 of the heat exchange tube 500 in the third heat exchange zone 103, and the minimum gap L4 between two adjacent heat exchange tubes 500 in the fourth heat exchange zone 104 is smaller than the minimum gap L3 between two adjacent heat exchange tubes 500 in the third heat exchange zone 103.

[0090] That is, compared with the third heat exchange zone 103, the heat exchange tubes 500 in the fourth heat exchange zone 104 located on the top layer have smaller diameters and are densely arranged.

[0091] When the refrigerant flows through the fourth heat exchange zone 104, due to the small spacing between the heat exchange tubes 500 and the heat exchange tubes 500, the liquid refrigerant will be evenly divided into multiple parts and flow through this part of the area; in addition, since the diameter of the heat exchange tubes 500 in the fourth heat exchange zone 104 is small, when the liquid inside the heat exchange tubes 500 flows along the tubes, its flow resistance is relatively large, and the flow rate of the liquid is slower than the flow rate inside the heat exchange tubes 500 in the third heat exchange zone 103, so that the evaporation phase change rate of the refrigerant outside the heat exchange tubes 500 in the fourth heat exchange zone 104 is slower, and thus the flow state of the liquid refrigerant is relatively stable.

[0092] The first heat exchange zone 101 at the bottom and the fourth heat exchange zone 104 at the top of the heat exchange tubes 500 can achieve better liquid distribution and liquid blocking, and the flow state of the liquid refrigerant is more stable.

[0093] The diameter and arrangement density of the heat exchange tubes 500 in the second heat exchange zone 102 may be the same or different.

[0094] In contrast, the heat exchange tubes 500 in the second heat exchange zone 102 and the third heat exchange zone 103 arranged in the heat exchange inner cavity have large diameters and are sparsely arranged. The heat exchange tubes 500 selected in this area have large diameters, and when the water inside the heat exchange tubes 500 flows along the tubes, the flow resistance is small. Therefore, the water flow rate and water flow rate of the heat exchange tubes 500 in the second heat exchange zone 102 and the third heat exchange zone 103 are high, and the liquid refrigerant outside the heat exchange tubes 500 evaporates at a faster phase change rate, which is the main area of ​​boiling evaporation heat exchange and can achieve most of the heat exchange.

[0095] refer to Figure 4 , Figure 5 In some embodiments of the present application, since the heat exchange tube 500 is relatively long, in order to prevent the heat exchange tube 500 from deforming, the present application arranges a plurality of support members 600 in the heat exchange inner cavity at intervals along the length direction of the heat exchange inner cavity.

[0096] Each support member 600 is a support plate structure fixed on the side wall of the heat exchange inner cavity. A support hole is formed on each support member 600. The specific arrangement of the support holes is adapted to the specific arrangement of the heat exchange tubes 500 in different heat exchange zones.

[0097] In the installed state, the heat exchange tube 500 passes through the corresponding support hole, and the heat exchange tube 500 is supported by the support member 600 .

[0098] Corresponding to the first heat exchange zone 101, the second heat exchange zone 102, the third heat exchange zone 103 and the fourth heat exchange zone 104, the support holes on the support member 600 are also divided into a first support zone 610, a second support zone 620, a third support zone 630 and a fourth support zone 640, and the size of the support holes in each support zone is adapted to the size of the heat exchange tube 500 in the corresponding heat exchange zone.

[0099] The number of support members 600 and the interval between adjacent support members 600 are determined according to actual needs.

[0100] refer to Figure 7 In some embodiments of the present application, a liquid inlet barrier 130 is also provided at the bottom of the heat exchange cavity.

[0101] A liquid inlet cavity is formed between the liquid inlet baffle 130 and the shell 100, and the liquid inlet cavity is connected to the liquid inlet pipe 110. The refrigerant is transported from the liquid inlet pipe 110 to the liquid inlet cavity. Through the action of the liquid inlet baffle 130, the refrigerant is evenly transported along the length direction of the heat exchange inner cavity to the first heat exchange zone 101.

[0102] Specifically, in some embodiments of the present application, the cross-sectional shape of the liquid inlet barrier 130 tapers along the flow direction of the liquid, that is, a folded angle is formed at the top of the liquid inlet barrier 130 to reduce obstruction to the water flow.

[0103] The liquid inlet baffle 130 is arranged along the length direction of the heat exchange inner cavity, and a plurality of liquid inlet holes are dispersedly formed on the liquid inlet baffle 130. After the refrigerant is transported from the liquid inlet pipe 110 to the liquid inlet cavity, it is evenly transported to the heat exchange inner cavity through the liquid inlet holes.

[0104] At the liquid inlet pipe 110, the liquid refrigerant flow is the largest and the flow velocity is the highest. The liquid inlet baffle 130 provided here can achieve a better liquid blocking effect and prevent a large amount of liquid from being washed through the heat exchange tube 500 in a short time and having no time for heat exchange.

[0105] The liquid refrigerant forms a gaseous refrigerant after exchanging heat with the high-temperature fluid in the heat exchange tube 500 in the heat exchange inner cavity, and flows toward the intake pipe 120 through the upper part of the shell 100. In this process, in order to prevent the liquid refrigerant from being carried to the intake pipe 120 by the gaseous refrigerant and causing the evaporator to inhale liquid, an intake barrier 140 is provided on the top of the heat exchange inner cavity.

[0106] In some other embodiments of the present application, the suction baffle 140 is located directly below the suction pipe 120 to prevent the liquid refrigerant from being output from the suction pipe 120 along with the gaseous refrigerant.

[0107] Specifically, both ends of the air intake baffle are open, and an air intake cavity is formed between the air intake baffle 140 and the top of the heat exchange cavity. The gaseous refrigerant formed after heat exchange in the heat exchange area enters the air intake cavity from both ends of the air intake baffle 140 and is finally output from the air intake pipe 120.

[0108] In addition, a liquid baffle 160 is provided above the fourth heat exchange zone 104. After the liquid refrigerant exchanges heat with the water flowing in the heat exchange tube 500 in the heat exchange inner cavity, it flows through the intake pipe 120. The setting of the liquid baffle 160 and the intake baffle 140 can effectively reduce the liquid refrigerant carried upward due to the flow of the refrigerant gas, thereby reducing the phenomenon of liquid in the intake air.

[0109] In some other embodiments of the present application, a liquid equalizing plate 150 is provided on the side wall of the heat exchange inner cavity to prevent the liquid refrigerant from being transported upward along with the gaseous refrigerant.

[0110] The liquid balancing plate 150 is located above the second heat exchange zone 102 . The liquid balancing plate 150 is symmetrically arranged on both sides of the inner wall of the shell 100 and horizontally extends a certain length into the heat exchange inner cavity.

[0111] The water flow rate in the heat exchange tube 500 of the second heat exchange zone 102 is relatively high, and the boiling and evaporation heat exchange here is relatively intense. Arranging a liquid equalizing plate 150 above this area can prevent the liquid refrigerant from being excessively and too quickly washed through the heat exchange tube 500 due to intense boiling and evaporation, without enough time for heat exchange.

[0112] The provision of the liquid balancing plate 150 and the air suction baffle 140 can make the refrigerant more evenly distributed in the flooded evaporator.

[0113] After the refrigerant enters the flooded evaporator from the liquid inlet pipe 110, it passes through the following areas in sequence:

[0114] The low-temperature and low-pressure refrigerant gas-liquid mixture enters the heat exchange cavity from the liquid inlet pipe 110 at the bottom of the shell 100 through the liquid inlet baffle 130.

[0115] The liquid inlet baffle 130 has multiple liquid inlet holes dispersedly opened along the length direction of the heat exchange cavity. The liquid refrigerant enters the area where the heat exchange tube 500 is arranged through the liquid inlet holes, which ensures that the liquid refrigerant can enter the heat exchange cavity evenly along the length direction.

[0116] The first heat exchange zone 101 located at the bottom of the heat exchange cavity is arranged with one or several rows of dense heat exchange tubes 500. When the refrigerant just enters the heat exchange cavity, the heat exchange is not complete. At this time, the refrigerant is mainly liquid with a low dryness. The refrigerant with a low dryness will evaporate evenly along the width direction of the heat exchange cavity. The gas-liquid mixture after the evaporation phase change will then enter the second heat exchange zone 102.

[0117] When the refrigerant flows through the second heat exchange zone 102 and the third heat exchange zone 103, as the evaporation phase change process gradually proceeds, the heat exchange gradually accumulates, the gas content in the refrigerant gradually increases, the refrigerant dryness increases, and the specific volume increases. The heat exchange tubes 500 in these two areas are sparsely arranged, so that the flow resistance of the refrigerant between the heat exchange tubes 500 is small and the flow is smoother.

[0118] In order to prevent the liquid refrigerant from rising along the cylinder wall under the effect of being carried by the refrigerant gas during the flow process, liquid equalizing plates 150 are symmetrically arranged on the side walls of the heat exchange cavity above the second heat exchange area 102 to reduce the liquid refrigerant climbing up along the cylinder wall.

[0119] When the refrigerant passes through the fourth heat exchange zone 104 where the heat exchange tubes 500 are small in diameter and densely arranged, the liquid refrigerant in the refrigerant further evaporates. At this time, the liquid refrigerant splashed due to the boiling and evaporation phase change will be intercepted by the densely arranged heat exchange tubes 500 and will not easily pass through the heat exchange tube 500 area. However, the refrigerant gas can pass through the heat exchange tube 500 area and continue to rise and leave.

[0120] In order to prevent the liquid refrigerant from rising along the cylinder wall under the effect of being carried by the refrigerant gas during the flow process, a liquid baffle 160 is arranged on the cylinder wall. The splashing liquid refrigerant will be blocked by the liquid baffle 160, reducing the liquid refrigerant climbing up along the cylinder wall. The liquid refrigerant can leave the evaporator only after further evaporation and becoming gas.

[0121] The chiller involved in the present application has an evaporator that is a fully liquid evaporator. The heat exchange tubes 500 in the evaporator are arranged in two dense and sparse zones according to the states of the refrigerant at different positions in the heat exchanger, thereby achieving the good effects of reducing the refrigerant flow resistance, uniformly distributing the liquid refrigerant, and having no liquid at the evaporator outlet.

[0122] The present application also proposes a chiller, which includes a compressor, a condenser, a throttle valve and an evaporator connected through a heat exchange pipe 500.

[0123] The evaporator is connected to the compressor, and includes a shell 100 and a heat exchange tube group arranged in the shell 100. A heat exchange inner cavity is formed in the shell 100. A liquid inlet pipe 110 is arranged at the bottom of the shell 100, and an air intake pipe 120 is arranged at the top of the shell 100. Both the liquid inlet pipe 110 and the air intake pipe 120 are connected to the heat exchange inner cavity.

[0124] Among them, the heat exchange tube group includes a plurality of heat exchange tubes 500, and the heat exchange tube group is arranged from top to bottom into a plurality of heat exchange zones along the height direction of the shell 100. The heat exchange zones include at least a bottom heat exchange zone located at the bottom of the heat exchange inner cavity and a top heat exchange zone located at the top of the heat exchange inner cavity. The bottom heat exchange zone and the top heat exchange zone are configured so that when the refrigerant flows through the bottom heat exchange zone and the top heat exchange zone, the flow rate of the refrigerant is reduced to improve the stability of the refrigerant flow.

[0125] The specific settings of the bottom heat exchange area and the top heat exchange area can be achieved in the following three ways:

[0126] Method 1:

[0127] A bottom heat exchange zone, a middle heat exchange zone and a top heat exchange zone are arranged in sequence from bottom to top along the height direction of the heat exchange inner cavity. The diameter of the heat exchange tubes 500 in the bottom heat exchange zone and the top heat exchange zone is smaller than the diameter of the heat exchange tubes 500 in the middle heat exchange zone, and the arrangement density of the heat exchange tubes 500 in the bottom heat exchange zone and the top heat exchange zone is greater than the density of the heat exchange tubes 500 in the middle heat exchange zone.

[0128] Method 2:

[0129] In some embodiments of the present application, a liquid inlet baffle 130 is further provided at the bottom of the heat exchange inner cavity, and the liquid inlet baffle 130 is located between the bottom heat exchange area and the liquid inlet pipe 110 .

[0130] That is, a liquid inlet cavity is formed between the liquid inlet baffle 130 and the shell 100, and the liquid inlet cavity is connected to the liquid inlet pipe 110. The refrigerant is transported from the liquid inlet pipe 110 to the liquid inlet cavity, and through the action of the liquid inlet baffle 130, the refrigerant is evenly transported along the length direction of the heat exchange inner cavity to the first heat exchange zone 101.

[0131] The liquid inlet baffle 130 is arranged along the length direction of the heat exchange inner cavity, and a plurality of liquid inlet holes are dispersedly formed on the liquid inlet baffle 130. After the refrigerant is transported from the liquid inlet pipe 110 to the liquid inlet cavity, it is evenly transported to the heat exchange inner cavity through the liquid inlet holes.

[0132] At the liquid inlet pipe 110, the liquid refrigerant flow is the largest and the flow velocity is the highest. The liquid inlet baffle 130 provided here can achieve a better liquid blocking effect and prevent a large amount of liquid from being washed through the heat exchange tube 500 in a short time and having no time for heat exchange.

[0133] Method 3:

[0134] In order to prevent the liquid refrigerant from being carried by the gaseous refrigerant to the suction pipe 120 and causing the evaporator suction to carry liquid, a suction baffle 140 is provided on the top of the heat exchange inner cavity.

[0135] In some other embodiments of the present application, the suction baffle 140 is located directly below the suction pipe 120 to prevent the liquid refrigerant from being output from the suction pipe 120 along with the gaseous refrigerant.

[0136] Specifically, both ends of the air intake baffle are open, and an air intake cavity is formed between the air intake baffle 140 and the top of the heat exchange cavity. The gaseous refrigerant formed after heat exchange in the heat exchange area enters the air intake cavity from both ends of the air intake baffle 140 and is finally output from the air intake pipe 120.

[0137] The above three methods can be a combination of method 1 and method 2, or a combination of method 1 and method 3, or a combination of method 1, method 2 and method 3.

[0138] In the description of the above embodiments, specific features, structures, materials or characteristics may be combined in a suitable manner in any one or more embodiments or examples.

[0139] The above is only a specific implementation of the utility model, but the protection scope of the utility model is not limited to this. Any changes or substitutions that can be easily thought of by technicians familiar with the technical field within the technical scope disclosed by the utility model 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. A chiller, characterized in that: include: compressor; an evaporator connected to the compressor, the evaporator comprising a shell and a heat exchange tube group arranged in the shell, a heat exchange inner cavity is formed in the shell, a liquid inlet pipe is arranged at the bottom of the shell, and an air intake pipe is arranged at the top of the shell, and the liquid inlet pipe and the air intake pipe are both in communication with the heat exchange inner cavity; Wherein, the heat exchange tube group includes a plurality of heat exchange tubes, each of which extends along the length direction of the shell and is arranged parallel to each other. The heat exchange tube group is arranged into a plurality of heat exchange zones from top to bottom along the height direction of the shell, and the diameters of the heat exchange tubes in adjacent heat exchange zones are different and / or the arrangement densities of the heat exchange tubes in adjacent heat exchange zones are different.

2. The chiller according to claim 1, characterized in that: The shell includes a first heat exchange zone, a second heat exchange zone, a third heat exchange zone and a fourth heat exchange zone from bottom to top along the height direction of the shell.

3. The chiller according to claim 2, characterized in that: The diameter of the heat exchange tube in the first heat exchange zone is smaller than the diameter of the heat exchange tube in the second heat exchange zone, and the arrangement density of the heat exchange tube in the first heat exchange zone is greater than the arrangement density of the heat exchange tube in the second heat exchange zone.

4. The chiller according to claim 2, characterized in that: The diameter of the heat exchange tube in the fourth heat exchange zone is smaller than the diameter of the heat exchange tube in the third heat exchange zone, and the arrangement density of the heat exchange tube in the fourth heat exchange zone is greater than the arrangement density of the heat exchange tube in the third heat exchange zone.

5. The chiller according to claim 1, characterized in that: An inlet pipe section and an outlet pipe section are provided at the end of the shell, the inlet pipe section is located below the outlet pipe section, and both ends of each heat exchange tube are connected to the inlet pipe section and the outlet pipe section respectively.

6. The water chiller according to claim 1, characterized in that: A plurality of support members are arranged at intervals in the heat exchange inner cavity, and a support hole is formed on each of the support members, and the heat exchange tube passes through the corresponding support hole.

7. The water chiller according to claim 1, characterized in that: An air suction baffle is provided on the top of the heat exchange inner cavity. The air suction baffle is located directly below the air suction pipe and is used to prevent liquid refrigerant from being output from the air suction pipe along with the gaseous refrigerant.

8. The chiller according to claim 1, characterized in that: A liquid inlet baffle is also provided at the bottom of the heat exchange inner cavity. The liquid inlet baffle is arranged along the length direction of the heat exchange inner cavity. A liquid inlet cavity is formed between the liquid inlet baffle and the shell. A plurality of liquid inlet holes are dispersedly formed on the liquid inlet baffle for uniformly transporting the liquid refrigerant into the heat exchange inner cavity.

9. The water chiller according to claim 2, characterized in that: A liquid balancing plate is disposed on the side wall of the heat exchange inner cavity, and the liquid balancing plate is symmetrically disposed above the second heat exchange zone to prevent the liquid refrigerant from being transported upward along with the gaseous refrigerant.

10. A chiller, characterized in that: include: compressor; an evaporator connected to the compressor, the evaporator comprising a shell and a heat exchange tube group arranged in the shell, a heat exchange inner cavity is formed in the shell, a liquid inlet pipe is arranged at the bottom of the shell, and an air intake pipe is arranged at the top of the shell, and the liquid inlet pipe and the air intake pipe are both in communication with the heat exchange inner cavity; Wherein, the heat exchange tube group includes a plurality of heat exchange tubes, and the heat exchange tube group is arranged into a plurality of heat exchange zones from top to bottom along the height direction of the shell, and the heat exchange zones at least include a bottom heat exchange zone located at the bottom of the heat exchange inner cavity and a top heat exchange zone located at the top of the heat exchange inner cavity, and the bottom heat exchange zone and the top heat exchange zone are configured so that when the refrigerant flows through the bottom heat exchange zone and the top heat exchange zone, the flow rate of the refrigerant is reduced to improve the stability of the refrigerant flow.

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