Heat exchanger and air conditioning unit

Abstract

The application provides a heat exchanger and an air conditioning unit. The heat exchanger comprises a shell, a superheating zone, a condensing zone and a subcooling zone are sequentially formed inside the shell; and a heat pipe is arranged in the shell, and a first end of the heat pipe is located in the superheating zone and a second end of the heat pipe is located in the subcooling zone. The heat exchanger and the air conditioning unit provided by the application can directly transfer the heat of the refrigerant (the refrigerant flowing into the superheating zone) entering the shell to the subcooling zone by the heat transfer property of the heat pipe, the heat transfer efficiency of the heat pipe is higher than that of the heat exchange pipe in the prior art, the heat transfer efficiency of the heat exchanger can be effectively improved, the heat pipe can also guide the airflow entering the shell, the fluid flow field in the heat exchanger can be effectively improved, the flow dead zone can be reduced, and the heat transfer efficiency of the heat exchanger is further increased.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of air treatment equipment, in particular to a heat exchanger and air conditioning unit. BACKGROUND

[0002] The heat exchanger is an important component of the water chiller. The high-temperature and high-pressure refrigerant gas discharged by the compressor enters the horizontal shell-and-tube condenser. The cooling water in the heat exchange tube absorbs the heat of the refrigerant to increase the temperature. The gas-phase refrigerant releases heat and condenses into liquid. The liquid refrigerant becomes low-temperature and low-pressure refrigerant after passing through the throttling component of the water chiller and enters the evaporator. The horizontal shell-and-tube condenser is an essential component of the water chiller. The commonly used condenser has two-phase and single-phase heat exchange in the heat exchange area. The cooling heat exchange of the superheated gas accounts for about 4-8% of the total heat exchange. However, due to single-phase heat exchange, the actual proportion of the heat exchange area of this part is as high as 25-40%, which leads to unreasonable structure design of the existing superheated zone and low heat exchange efficiency of the condenser. SUMMARY

[0003] In order to solve the technical problem of low heat exchange efficiency of the heat exchanger in the prior art, a heat exchanger with heat pipes to improve heat exchange efficiency and an air conditioning unit are provided.

[0004] A heat exchanger comprises:

[0005] A shell, wherein the inside of the shell is sequentially formed with a superheated zone, a condensing zone and a subcooled zone;

[0006] A heat pipe, wherein the heat pipe is arranged in the shell, and a first end of the heat pipe is located in the superheated zone and a second end of the heat pipe is located in the subcooled zone.

[0007] The heat exchanger further comprises a first baffle, wherein the first baffle is arranged in the shell and the first baffle is sleeved on the heat pipe.

[0008] The heat exchanger further comprises an air inlet pipe, wherein the air inlet pipe is arranged on the shell, the air inlet pipe is in communication with the superheated zone, and the air outlet direction of the air inlet pipe is towards the first baffle.

[0009] The heat exchanger further comprises a liquid distribution structure, wherein the liquid distribution structure is arranged on the first baffle, and the tip of the liquid distribution structure is towards the air inlet pipe.

[0010] The maximum height h1 of the liquid distribution structure ranges from 30mm to 200mm.

[0011] The first baffle has a first side surface towards the air inlet pipe, the first side surface is provided with a flow guide groove, and the fluid flowing through the flow guide groove flows away from the condensing zone.

[0012] The cross section of the flow guide groove is V-shaped, the top angle β of the V-shaped is in the range of 45°≤β≤160°; and / or, the maximum depth h3 of the flow guide groove is in the range of 5mm≤h3≤40mm.

[0013] The distance K1 between the first end of the heat pipe and the first baffle is in the range of 20mm≤K1≤100mm; and / or, the heat exchange pipe is arranged in the overheating area, and the minimum distance K2 between the first baffle and the heat exchange pipe in the overheating area is in the range of 50mm≤K2≤200mm.

[0014] The heat pipe comprises a vertical section and an inclined section, the inclined section is connected to the vertical section, and the included angle θ between the inclined section and the vertical section is in the range of 95°≤θ≤180°.

[0015] The heat exchanger further comprises a second baffle, the second baffle is sleeved on the heat pipe, and the second baffle is located in the condensation area.

[0016] The minimum distance K3 between the second baffle and the lowest point of the shell is in the range of 50mm≤K3≤400mm.

[0017] The number of the heat pipes is multiple, and all the heat pipes are distributed in the shell in a ring shape with the axis of the air inlet pipe as the axis.

[0018] The first end of the heat pipe is located in the air inlet pipe.

[0019] An air conditioning unit comprising the heat exchanger.

[0020] The heat exchanger and the air conditioning unit provided by the application utilize the heat transfer property of the heat pipe to directly transfer the heat of the refrigerant just entering the shell (the refrigerant flowing into the overheating area) to the supercooling area, and the heat transfer efficiency of the heat pipe is higher than that of the heat exchange pipe in the prior art, so that the heat transfer efficiency of the heat exchanger can be effectively improved, and the heat pipe can also guide the airflow entering the shell, so that the flow field in the heat exchanger can be effectively improved, the flow dead zone is reduced, and the heat transfer efficiency of the heat exchanger is further increased. BRIEF DESCRIPTION OF DRAWINGS

[0021] Figure 1 A cross-sectional view of the heat exchanger provided by the embodiment of the application;

[0022] Figure 2 A cross-sectional view of the first baffle provided by the embodiment of the application;

[0023] Figure 3 A top view of the first baffle provided by the embodiment of the application;

[0024] Figure 4A structure diagram of a second baffle provided for an embodiment of the present application is shown in the figure.

[0025] Figure 5 A structure diagram of a heat pipe provided for an embodiment of the present application is shown in the figure.

[0026] In the figure:

[0027] 1, shell; 11, superheating zone; 12, condensing zone; 13, subcooling zone; 2, heat pipe; 3, first baffle; 4, air inlet pipe; 5, liquid separation structure; 31, flow guide groove; 6, heat exchange pipe; 21, vertical section; 22, inclined section; 7, second baffle. DETAILED DESCRIPTION

[0028] In order to make the purpose, technical solutions and advantages of the present application more clear, the present application is further described in detail below in combination with the figures and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and do not limit the present application.

[0029] As shown in the figure, a heat exchanger comprises a shell 1, a heat pipe 2 and a first baffle 3. Figures 1 to 5 The shell 1 is internally formed with a superheating zone 11, a condensing zone 12 and a subcooling zone 13 in sequence; the heat pipe 2 is arranged in the shell 1, and a first end of the heat pipe 2 is located in the superheating zone 11 and a second end of the heat pipe 2 is located in the subcooling zone 13. The heat pipe 2 is used to directly transfer the heat of the refrigerant just entering the shell 1 (the refrigerant flowing into the superheating zone 11) to the subcooling zone 13, and the heat exchange efficiency of the heat pipe 2 is higher than that of the heat exchange pipe 6 in the prior art, which can effectively improve the heat exchange efficiency of the heat exchanger, and the heat pipe 2 can also guide the airflow entering the shell 1, which can effectively improve the fluid flow field in the heat exchanger, reduce the flow dead zone and further increase the heat exchange efficiency of the heat exchanger.

[0030] The superheating zone 11, the condensing zone 12 and the subcooling zone 13 are arranged along the height direction of the shell 1.

[0031] In the prior art, the refrigerant entering the shell 1 can only diffuse around the center of the diameter of the air inlet, which causes the flow rate of the refrigerant in the middle region of the shell 1 to be large, and the flow rate of the refrigerant near the side wall of the shell 1 to be small, which causes the flow field in the shell 1 to be unevenly distributed and the flow dead zone to exist, and causes the heat exchange efficiency of the heat exchanger to decrease.

[0032] To this end, the heat exchanger further comprises a first baffle 3, which is arranged in the shell 1 and sleeved on the heat pipe 2. The first baffle 3 limits the inflow of the gaseous refrigerant in the superheating zone 11 into the subcooling zone 13 at a faster speed, that is, reduces the flow rate of the refrigerant in the middle region of the shell 1, thereby uniformizing the internal flow field of the shell 1 and improving the heat exchange efficiency of the heat exchanger.

[0033] Specifically, the heat exchanger further comprises an air inlet pipe 4, which is arranged on the shell 1 and communicates with the superheating zone 11, and the air outlet direction of the air inlet pipe 4 is towards the first baffle 3. That is, the first baffle 3 can block the gaseous refrigerant discharged from the air inlet pipe 4, forcing the gaseous refrigerant to flow towards the side wall of the shell 1, thereby effectively improving the internal flow field of the shell 1 and improving the heat exchange efficiency of the heat exchanger.

[0034] Preferably, the thickness h2 of the first baffle 3 ranges from 10 mm to 50 mm, preferably 12 mm.

[0035] The heat exchanger further comprises a liquid distribution structure 5, which is arranged on the first baffle 3 and the tip of which is towards the air inlet pipe 4. The liquid distribution structure 5 can distribute the gaseous refrigerant discharged from the air inlet pipe 4, thereby increasing the flow guiding effect of the first baffle 3 on the gaseous refrigerant.

[0036] Preferably, the liquid distribution structure 5 is conical, which can distribute the gaseous refrigerant by the tip of the cone and guide the gaseous refrigerant by the inclined surface of the cone, thereby gradually increasing the speed component of the gaseous refrigerant flowing towards the side wall of the shell 1, increasing the amount of gaseous refrigerant flowing to the side wall of the shell 1, effectively optimizing the flow field in the shell 1 and improving the heat exchange efficiency of the heat exchanger.

[0037] Preferably, the maximum height h1 of the liquid distribution structure 5 ranges from 30 mm to 200 mm. Avoiding the liquid distribution structure 5 being too high to affect the height dimension of the heat exchanger, and avoiding the liquid distribution structure 5 being too low to achieve the liquid distribution effect.

[0038] The first baffle 3 has a first side surface towards the air inlet pipe 4, and a flow guiding groove 31 is arranged on the first side surface, and the fluid flowing through the flow guiding groove 31 flows away from the condensation zone 12. The flow guiding groove 31 guides the gaseous refrigerant flowing through the first baffle 3, thereby further improving the blocking effect of the first baffle 3 on the gaseous refrigerant.

[0039] The cross section of the flow guide groove 31 is V-shaped, and the top angle β of the V-shaped angle ranges from 45° to 160°. The gas flow can flow into the V-shaped side close to the distribution structure 5, and flow out from the other side of the V-shaped, so as to change the flow direction of the gaseous refrigerant, optimize the flow field in the shell 1, and improve the heat exchange efficiency of the heat exchanger.

[0040] The maximum depth h3 of the flow guide groove 31 ranges from 5mm to 40mm. The depth of the flow guide groove 31 is avoided to be too large to form a dead zone at the bottom of the flow guide groove 31, and the depth of the flow guide groove 31 is also avoided to be too small to produce a reliable flow guide effect on the gaseous refrigerant.

[0041] Preferably, the first baffle 3 is a circular truncated cone structure, and the diameter d4 of the first baffle 3 ranges from 100mm to 500mm, preferably 120mm.

[0042] The bottom surface of the distribution structure 5 is also circular, and the diameter d2 of the bottom surface of the distribution structure 5 ranges from 30mm to 200mm, preferably 40mm.

[0043] The shape of the flow guide groove 31 is annular, and the annular axis of the flow guide groove 31 is collinear with the central axis of the first baffle 3. The outer diameter d3 of the annular flow guide groove 31 ranges from 80mm to 450mm, preferably 100mm, and the inner diameter d5 of the annular flow guide groove 31 ranges from 70mm to 350mm, preferably 90mm.

[0044] The distance K1 between the first end of the heat pipe 2 and the first baffle 3 ranges from 20mm to 100mm. The contact area of the heat pipe 2 and the gaseous refrigerant is avoided to be affected by the shielding of the first baffle 3, so as to ensure the heat exchange efficiency of the heat pipe 2.

[0045] The heat exchange pipe 6 is arranged in the superheating zone 11, and the minimum distance K2 between the first baffle 3 and the heat exchange pipe 6 in the superheating zone 11 ranges from 50mm to 200mm. The shielding of the first baffle 3 is avoided to cause the decrease of the gaseous refrigerant flowing to the heat exchange pipe 6 in the superheating zone 11, so as to ensure the heat exchange efficiency of the heat pipe 2.

[0046] The heat pipe 2 includes a vertical section 21 and an inclined section 22, the inclined section 22 is connected to the vertical section 21, and the included angle θ between the inclined section 22 and the vertical section 21 ranges from 95° to 180°. By arranging the inclined section 22, the capillary force inside the heat pipe 2 can be increased, and the effect of gravity on the working fluid in the pipe can be reduced, thereby improving the overall heat exchange efficiency of the heat pipe 2. Preferably, the included angle θ is 120°.

[0047] Preferably, the length h5 of the vertical section 21 ranges from 250 mm to 700 mm, preferably 280 mm. The length h6 of the inclined section 22 ranges from 100 mm to 400 mm, preferably 120 mm.

[0048] The heat exchanger further comprises a second baffle plate 7, which is sleeved on the heat pipe 2 and located in the condensation zone 12. The second baffle plate 7 supports the structure of the heat pipe 2. It ensures that the second end of the heat pipe 2 does not move relative to the shell 1, and ensures the reliability of the structure of the heat pipe 2.

[0049] The minimum distance K3 from the second baffle plate 7 to the lowest point of the shell 1 ranges from 50 mm to 400 mm. This avoids the second baffle plate 7 affecting the arrangement of the heat exchange pipes 6 in the supercooling zone 13 and the heat exchange pipes 6 in the condensation zone 12.

[0050] The shell 1 is also provided with a liquid outlet pipe, and K3 can also be expressed as the distance from the second baffle plate 7 to the connection between the liquid outlet pipe and the shell 1.

[0051] The thickness h4 of the second baffle plate 7 ranges from 8 mm to 20 mm, and the preferred value is 10 mm. This ensures the structural strength of the second baffle plate 7.

[0052] Preferably, the distance K1 from the first end of the heat pipe 2 to the first baffle plate 3, the minimum distance K2 from the first baffle plate 3 to the heat exchange pipe 6 in the superheating zone 11, and the minimum distance K3 from the second baffle plate 7 to the lowest point of the shell 1 increase in turn.

[0053] Preferably, the heat pipe 2 is divided into an evaporation section, an adiabatic section, and a condensation section along the height direction of the shell. The first baffle plate 3 is located at the connection between the evaporation section and the adiabatic section, and the second baffle plate 7 is located at the connection between the adiabatic section and the condensation section.

[0054] As an embodiment, the number of heat pipes 2 is multiple, and all the heat pipes 2 are distributed in the shell 1 in a ring shape around the axis of the air inlet pipe 4. This further improves the heat exchange efficiency of the heat exchanger.

[0055] The number of rings formed by the heat pipes 2 is at least 1, and preferably ranges from 1 to 4.

[0056] The inclined section 22 of each heat pipe 2 faces the outside of the ring.

[0057] The first baffle plate 3 and the second baffle plate 7 are both provided with mounting holes for the heat pipe 2 to pass through.

[0058] Preferably, the mounting holes are annularly distributed. The diameter d1 of the mounting holes ranges from 5mm to 20mm, preferably 8mm. The heat pipe can have a groove type, a wire mesh type, a sintered core, a parallel wire core, etc., preferably a parallel wire core; the working fluid can be methanol, acetone, ammonia, R11, R22, etc., preferably R22; the pipe diameter d6 of the heat pipe ranges from 5mm to 20mm, preferably 8mm.

[0059] The axis of the annular ring is collinear with the axis of the gas inlet pipe 4.

[0060] The first end of the heat pipe 2 is located in the gas inlet pipe 4.

[0061] The second end of the heat pipe 2 is located at the lowermost heat exchange pipe 6 in the condensing zone 12, thereby maximizing the heat exchange efficiency between the heat pipe 2 and the liquid refrigerant.

[0062] An air conditioning unit comprising the heat exchanger described above.

[0063] The above embodiments only express several embodiments of the present application, and the description is more specific and detailed, but it cannot be understood as a limitation on the scope of the patent of the present application. It should be noted that for ordinary skilled in the art, without departing from the concept of the present application, several modifications and improvements can be made, which are all within the scope 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 heat exchanger, characterized by: The heat exchanger comprises: a shell (1), inside which a superheating zone (11), a condensing zone (12) and a supercooling zone (13) are sequentially formed; a heat pipe (2) arranged in the shell (1), a first end of the heat pipe (2) being located in the superheating zone (11) and a second end of the heat pipe (2) being located in the supercooling zone (13).

2. The heat exchanger of claim 1, wherein: The heat exchanger further comprises a first baffle (3) arranged in the shell (1), the first baffle (3) being sleeved on the heat pipe (2).

3. The heat exchanger of claim 2, wherein: The heat exchanger further comprises an air inlet pipe (4) arranged on the shell (1), the air inlet pipe (4) being in communication with the superheating zone (11), and an air outlet direction of the air inlet pipe (4) being towards the first baffle (3).

4. The heat exchanger of claim 3, wherein: The heat exchanger further comprises a liquid distribution structure (5) arranged on the first baffle (3), and a tip of the liquid distribution structure (5) being towards the air inlet pipe (4).

5. The heat exchanger of claim 4, wherein: A maximum height h1 of the liquid distribution structure (5) ranges from 30 mm to 200 mm.

6. The heat exchanger of claim 3, wherein: The first baffle (3) has a first side surface towards the air inlet pipe (4), a flow guide groove (31) is arranged on the first side surface, and fluid flowing through the flow guide groove (31) flows away from the condensing zone (12).

7. The heat exchanger of claim 6, wherein: A cross section of the flow guide groove (31) is V-shaped, an included angle β of the V-shaped range is from 45° to 160°, and / or a maximum depth h3 of the flow guide groove (31) ranges from 5 mm to 40 mm.

8. The heat exchanger of claim 2, wherein: A spacing K1 between the first end of the heat pipe (2) and the first baffle (3) ranges from 20 mm to 100 mm, and / or a minimum distance K2 between the first baffle (3) and a heat exchange pipe (6) in the superheating zone (11) ranges from 50 mm to 200 mm.

9. The heat exchanger of claim 1, wherein: The heat pipe (2) comprises a vertical section (21) and an inclined section (22), the inclined section (22) is connected to the vertical section (21), and an included angle θ between the inclined section (22) and the vertical section (21) ranges from 95° to 180°.

10. The heat exchanger of claim 9, wherein: The heat exchanger further comprises a second baffle (7) sleeved on the heat pipe (2), and the second baffle (7) is located in the condensing zone (12).

11. The heat exchanger of claim 10, wherein: A minimum spacing K3 between the second baffle (7) and a lowest point of the shell (1) ranges from 50 mm to 400 mm.

12. The heat exchanger of claim 3, wherein: The heat pipe (2) is in a plurality, and all the heat pipes (2) are distributed in the shell (1) in a ring shape with an axis of the air inlet pipe (4) as an axis.

13. The heat exchanger of claim 3, wherein: The first end of the heat pipe (2) is located in the air inlet pipe (4).

14. An air conditioning unit characterized by: The heat exchanger comprises any one of claims 1 to 13.

Images