CN210921673U - Heat exchanger and water chilling unit - Google Patents
Heat exchanger and water chilling unit Download PDFInfo
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- CN210921673U CN210921673U CN201922028917.3U CN201922028917U CN210921673U CN 210921673 U CN210921673 U CN 210921673U CN 201922028917 U CN201922028917 U CN 201922028917U CN 210921673 U CN210921673 U CN 210921673U
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Abstract
The utility model relates to an air conditioner refrigeration technology field discloses a heat exchanger and cooling water set, and the heat exchanger includes: a housing; the liquid inlet pipe is arranged at the bottom of the shell; the air outlet pipe is arranged at the upper part of the shell; a plurality of heat exchange tubes arranged in parallel in the housing; the tube plate is arranged at the end part of the shell in a mode of being perpendicular to the heat exchange tubes, the end part of each heat exchange tube is inserted into the tube plate, the shell internally comprises a first heat exchange tube area and a second heat exchange tube area, and the pressure loss of a refrigerant flow path of the second heat exchange tube area is smaller than that of the refrigerant flow path of the first heat exchange tube area. The utility model discloses a heat exchanger is through changing the arrangement structure of the inside heat exchange tube evenly distributed of casing, and it is regional with the second heat exchange tube in that the casing is inside to through heat exchange tube arrangement structure's difference, make two regional refrigerant flow path loss of heat exchange tube pressure different, can guarantee when abundant heat transfer, compromise not excessively greatly increase refrigerant pressure loss and lead to the system negative pressure to reduce.
Description
Technical Field
The utility model relates to an air conditioner refrigeration technology field, in particular to heat exchanger and cooling water set.
Background
In the flooded evaporator in the prior art, the heat exchange tubes are completely immersed by the refrigerant, the refrigerant transfers heat on the surfaces of the heat exchange tubes to generate boiling bubbles, the bubbles are gathered at the two to three layers of heat exchange tubes at the top, and the bubbles continue to absorb heat to form superheated gas, and then the superheated gas enters the compressor.
In the heat exchanger in the prior art, a tube distribution mode as shown in fig. 2 is generally adopted, and turbulent flow is formed on the surface of a heat exchange tube in the rising process of a refrigerant, so that the effect of enhancing heat exchange is achieved. In order to improve the evaporation temperature and ensure the suction superheat degree of the refrigerant before entering the compressor, the number of heat exchange tubes in the flow direction of the refrigerant is increased or other measures for increasing the heat exchange area are needed, but the increase of the heat exchange tubes can lead to the increase of the pressure loss of the refrigerant, the low pressure of the system is too low, and the increase of the heat exchange area inevitably brings the cost. Ensuring sufficient heat exchange and maintaining low pressure of the system are difficult to be considered.
SUMMERY OF THE UTILITY MODEL
The utility model discloses a solve above-mentioned technical problem and propose, aim at provides a heat exchanger. The utility model discloses a heat exchanger is through changing the inside heat exchange tube evenly distributed's of casing arrangement structure, and it is regional with the second heat exchange tube in that the casing is inside to through heat exchange tube arrangement structure's difference, make one of them for example the regional refrigerant flow path loss of second heat exchange tube, be less than another the regional refrigerant flow path loss of first heat exchange tube promptly. Through setting up two refrigerant flow path pressure loss different heat exchange tube regions, can guarantee when abundant heat transfer, compromise not excessively greatly to increase refrigerant pressure loss and lead to the system negative pressure to reduce.
Particularly, the utility model provides a heat exchanger, include:
a housing;
the liquid inlet pipe is used for the inflow of refrigerant and is arranged at the bottom of the shell;
the gas outlet pipe is communicated with the liquid inlet pipe and is arranged at the upper part of the shell;
a plurality of heat exchange tubes arranged in parallel in the housing;
and the tube plate is arranged at the end part of the shell in a mode of being vertical to the heat exchange tube, and the end part of the heat exchange tube is inserted through the tube plate.
The shell interior includes a first heat exchange tube region and a second heat exchange tube region,
the pressure loss of the refrigerant flow path in the second heat exchange tube area is less than that of the refrigerant flow path in the first heat exchange tube area.
Compared with the prior art, the utility model provides a heat exchanger through the arrangement that changes the inside heat exchange tube evenly distributed of casing, and it is regional with the second heat exchange tube in the inside first heat exchange tube of formation of casing to through heat exchange tube arrangement's difference, make one of them for example the regional refrigerant flow path pressure loss of second heat exchange tube, be less than another the regional refrigerant flow path pressure loss of first heat exchange tube promptly. Through setting up two refrigerant flow path pressure loss different heat exchange tube regions, can guarantee when abundant heat transfer, compromise not excessively greatly to increase refrigerant pressure loss and lead to the system negative pressure to reduce.
As the utility model discloses a preferred technical scheme, regional at first heat exchange tube, the heat exchange tube is arranged to the form that constitutes first equilateral triangle with the cross section of arbitrary adjacent three heat exchange tube, and regional at the second heat exchange tube, then arranges the heat exchange tube with the form that the cross section of arbitrary adjacent three heat exchange tube constitutes second equilateral triangle, wherein, first equilateral triangle is different with second equilateral triangle's inclination.
According to the preferred technical scheme, heat exchange tubes with the same tube diameter can be used, no special structure or part is needed, and the pressure loss of the refrigerant flow paths in the first heat exchange tube area and the second heat exchange tube area can be adjusted only by adjusting the arrangement mode of the adjacent heat exchange tubes, namely adjusting the different inclination angles formed by the equilateral triangles formed by the three adjacent heat exchange tubes on the tube plate plane, so that the pressure loss of the refrigerant flow paths in the second heat exchange tube area is realized and is smaller than that of the refrigerant flow paths in the first heat exchange tube area.
As another preferred technical scheme of the utility model, the regional first equilateral triangle of first heat exchange tube has with the casing in refrigerant shell side flow direction vertically an limit, the regional second equilateral triangle of second heat exchange tube has with the casing in refrigerant shell side flow direction parallel an limit.
According to the preferable technical scheme, the first equilateral triangle in the first heat exchange tube region is provided with one side perpendicular to the flowing direction of the shell pass of the refrigerant in the shell through the arrangement relation of the adjacent three heat exchange tubes, so that one heat exchange tube in the three heat exchange tubes forming the first equilateral triangle can be opposite to the flowing direction of the shell pass of the refrigerant, the refrigerant flows in through a passage between the other two heat exchange tubes, and heat exchange and absorption are carried out on the surfaces of the three heat exchange tubes and media in the heat exchange tubes, so that sufficient heat exchange is realized. And through the mutual position arrangement relationship of the adjacent three heat exchange tubes, the second equilateral triangle in the second heat exchange tube region is provided with a side parallel to the flowing direction of the shell of the refrigerant, so that a passage between two heat exchange tubes in the three heat exchange tubes forming the second equilateral triangle is opposite to the flowing direction of the shell of the refrigerant, and the refrigerant can smoothly flow through the heat exchange tube region by utilizing the characteristic of low pressure loss of the passage between the two heat exchange tubes while exchanging heat between the refrigerant and each heat exchange tube, so that the pressure loss of the refrigerant is increased without low, and the low pressure of the system is ensured.
As another preferred technical scheme of the utility model, refrigerant shell side flow direction in the casing, the regional low reaches that are located the second heat exchange tube region of first heat exchange tube.
In the whole heat exchange tube area in the shell, as the refrigerant flows into the shell from the liquid inlet tube in a low-temperature and low-pressure liquid form, and after heat exchange with the heat exchange tube, part of the refrigerant absorbs heat and evaporates to form a gas medium refrigerant, and the gas medium refrigerant carries fine liquid refrigerant to continuously flow towards the gas outlet tube and continuously absorb heat until the refrigerant is overheated, as the low-temperature and low-pressure refrigerant is continuously evaporated and expanded, the pressure loss of the flow path is increasingly required to be reduced on the downstream side of the refrigerant flow path.
In the preferred embodiment, a first heat exchange tube region is disposed on the upstream side of the refrigerant flow path, which is a heat exchange tube region adjacent to the liquid inlet tube, and a second heat exchange tube region is disposed on the downstream side of the refrigerant flow path, which is a heat exchange tube region adjacent to the gas outlet tube. Therefore, the heat exchange tube area with smaller pressure loss is arranged at the downstream side of the refrigerant flow path, so that the heat exchange can be fully carried out at the downstream side to prepare the superheated refrigerant steam, and simultaneously, the requirement of the downstream side flow path on pressure loss reduction is met, and the superheated refrigerant steam pressure near the air outlet pipe is ensured to meet the requirement of a compressor.
Further, as a preferred aspect, the preferred technical solution of the present invention may be that the side length of the first equilateral triangle and/or the second equilateral triangle is 22.5-23.8 mm.
According to the preferred scheme, the distance between the adjacent heat exchange tubes is small and proper, the heat exchange area in the unit area of the tube plate can be ensured, and the pressure loss of the channels of the first heat exchange tube region and the second heat exchange tube region can be properly controlled.
In addition, the distance between the heat exchange tubes in the first heat exchange tube region, the distance between the heat exchange tubes in the second heat exchange tube region and the respective tube diameters can be set to be the same parameter, so that the process and management of tube plate hole opening are reduced.
In addition, as preferred, the utility model discloses a preferred technical scheme can be, the external diameter of heat exchange tube is less than 0.433 times of second equilateral triangle's length of side.
According to the numerical relationship between the outer diameter of the heat exchange tube and the equilateral triangle, only when the outer diameter of the heat exchange tube is more than 0.433 times smaller than the side length of the equilateral triangle, in other words, the outer diameter of the heat exchange tube is less than 43.3% of the side length of the equilateral triangle formed by the heat exchange tube, a channel which is not influenced by other heat exchange tubes and is opposite to a refrigerant flow path can be ensured to be formed between two adjacent heat exchange tubes, so that the pressure loss is reduced.
In addition, as preferred, the technical scheme of the utility model, can also be including setting up refrigerant distributor between second heat exchange tube region and feed liquor pipe and setting up the fender liquid board between outlet duct and first heat exchange tube region.
According to the preferred technical scheme, the refrigerant distributor is arranged, so that the refrigerant flowing into the liquid inlet pipe can be uniformly distributed to each heat exchange pipe section part of the second heat exchange pipe area, and the uniformity of heat exchange is ensured.
The liquid baffle can prevent refrigerant steam carrying fine liquid drops from directly entering the inlet of the compressor, and liquid impact on the compressor caused by the liquid drops is avoided.
Further, preferably, the heat exchanger is an evaporator. More preferably a flooded evaporator.
The flooded evaporator mainly exchanges heat between liquid refrigerant and chilled water in the heat exchange process, gaseous refrigerant generated by heat absorption and boiling is separated out from the liquid refrigerant, and further absorbs heat to form superheated refrigerant gas, and then the superheated refrigerant gas is sucked from the compressor and enters the compressor. Therefore, the heat exchange area of the heat exchange tube can be effectively utilized, the heat exchange efficiency of the heat exchanger is high, and the heat exchange efficiency and the refrigerating capacity of the unit are correspondingly improved.
In addition, the number of heat exchange tubes in the first heat exchange tube region is preferably smaller than the number of heat exchange tubes in the second heat exchange tube region.
In a flooded evaporator, the gaseous refrigerant, which has been absorbed and evaporated and rises in the second heat exchange tube region, collects in the first heat exchange tube region, e.g., the uppermost 2-3 layers of heat exchange tubes, and continues to absorb heat to form superheated gas, which is then fed to the compressor. Therefore, the number of layers of the heat exchange tubes in the second heat exchange tube area is less than that of the heat exchange tubes in the first heat exchange tube area, so that the characteristic of a flooded evaporator can be properly matched, and the characteristics of ensuring heat exchange in the second heat exchange tube area and ensuring pressure loss controllability in the first heat exchange tube area are fully realized.
The utility model also provides a water chilling unit, including compressor, condenser, choke valve and evaporimeter, the evaporimeter adopts among the aforementioned arbitrary technical scheme the heat exchanger.
Drawings
Fig. 1 is a schematic cross-sectional structure diagram of a heat exchanger according to a first embodiment of the present invention;
fig. 2 is a schematic view of heat exchange tubes arranged according to a first pattern in a first embodiment of the present invention;
fig. 3 is a schematic view of heat exchange tubes arranged according to a second pattern in a first embodiment of the present invention;
fig. 4 is a schematic view of the internal structure of a heat exchanger according to a first embodiment of the present invention (only one heat exchange tube is shown in the figure, and the others are omitted);
fig. 5 is a schematic cross-sectional structure diagram of a heat exchanger according to a second embodiment of the present invention;
fig. 6 is a schematic structural diagram of a water chiller according to a third embodiment of the present invention.
Description of reference numerals:
1. the heat exchange tube comprises a heat exchange tube body, a shell body, a tube plate, a liquid inlet tube, a gas outlet tube, a refrigerant distributing plate, a refrigerant distributing hole, a refrigerant distributing plate, a refrigerant distributing hole, a refrigerant baffle plate, a refrigerant compressor, a refrigerant condenser, an expansion valve, an evaporator, a refrigerant shell pass, a refrigerant A, a refrigerant B, chilled water, a refrigerant shell pass flowing direction, a refrigerant D, a first equilateral triangle, a refrigerant E, a second equilateral triangle, a heat exchange tube area P, a heat exchange tube area H, a heat exchange tube area α.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings. The structures of the heat exchanger, the water chilling unit and the like are schematically and simply shown in the attached drawings.
In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention.
Implementation mode one
The utility model discloses an embodiment one provides a heat exchanger, and it is shown with reference to fig. 1, including many heat exchange tubes 1, many heat exchange tubes 1 set up in a casing 2 mutually parallel, are provided with tube sheet 3 respectively at the both ends of casing 2, and the both ends of many heat exchange tubes 1 all extend with the planar direction of the board of perpendicular to tube sheet 3 and insert and lead to tube sheet 3. The bottom of the shell 2 is provided with a liquid inlet pipe 4 which is communicated with the inside of the shell 2 and is used for liquid refrigerant A to flow in. An air outlet pipe 5 is arranged at the upper part of the shell 2, is communicated with the inside of the shell 2 and is used for the gaseous refrigerant A to flow out. The interior of the shell 2 is divided into a first heat exchange tube region P and a second heat exchange tube region H, and the first heat exchange tube region P and the second heat exchange tube region H are independently arranged. The pressure loss of the refrigerant flow path of the heat exchange tube positioned in the first heat exchange tube region P is different from that of the heat exchange tube 1 positioned in the second heat exchange tube region H, and the pressure loss of the refrigerant flow path of the second heat exchange tube region H is smaller than that of the refrigerant flow path of the first heat exchange tube region P.
The heat exchanger is a flooded evaporator which has the characteristics of high heat transfer coefficient and small heat transfer temperature difference.
Compared with the prior art, in the heat exchanger provided by the embodiment, the arrangement structure of the heat exchange tubes 1 in the shell 2 is changed to form the first heat exchange tube region P and the second heat exchange tube region H in the shell 2, and the pressure loss of the refrigerant flow path of one of the heat exchange tubes, for example, the second heat exchange tube region H, is smaller than the pressure loss of the refrigerant flow path of the other heat exchange tube region, that is, the first heat exchange tube region P, due to the difference of the arrangement structures of the heat exchange tubes 1. By arranging the two heat exchange pipe regions P, H with different refrigerant flow path pressure losses, the system negative pressure can be reduced without excessively increasing the pressure loss of the refrigerant A while ensuring sufficient heat exchange.
In the first heat exchange tube region P, the heat exchange tubes 1 are arranged in a manner that the cross sections of any adjacent three heat exchange tubes 1 form a first equilateral triangle D, and in the second heat exchange tube region H, the heat exchange tubes 1 are arranged in a manner that the cross sections of any adjacent three heat exchange tubes 1 form a second equilateral triangle E, wherein the inclination angles α of the first equilateral triangle D and the second equilateral triangle E are different, in the present embodiment, the inclination angle α refers to the included angle between the first equilateral triangle D and the second equilateral triangle E and the horizontal plane, no special structure or component is needed, the heat exchange tubes 1 with the same tube diameter can be used, and the refrigerant flow path pressure loss in the second heat exchange tube region H can be adjusted only by adjusting the arrangement mode of the adjacent heat exchange tubes 1, namely adjusting the inclination angle α formed by the equilateral triangle formed by the three adjacent heat exchange tubes 1 on the plane of the tube plate 3, so that the refrigerant flow path pressure loss in the first heat exchange tube region P and the second heat exchange tube region H is smaller than the flow path pressure loss of the first.
Specifically, referring to fig. 2 and 3, a first equilateral triangle D having an inclination angle α of 0 °, a first equilateral triangle D of a first heat exchange tube region P having a side perpendicular to a shell-side flow direction C of a refrigerant in a casing 2, a second equilateral triangle E having an inclination angle α of 30 °, a second equilateral triangle E of a second heat exchange tube region H having a side parallel to the shell-side flow direction C of the refrigerant in the casing 2, through the positional relationship of adjacent three heat exchange tubes 1 with each other, the first equilateral triangle D of the first heat exchange tube region P having a side perpendicular to the shell-side flow direction C of the refrigerant in the casing 2, it is possible to allow one heat exchange tube 1 of the three heat exchange tubes 1 constituting the first equilateral triangle D to face the shell-side flow direction C of the refrigerant, the refrigerant a to flow through a passage between the other two heat exchange tubes 1, and to absorb heat exchange heat from a medium inside the three heat exchange tubes 1 on the surface of the heat exchange tube 1 with a medium inside the heat exchange tubes 1, to achieve sufficient heat exchange, through the positional relationship of the adjacent three heat exchange tubes 1 with each other heat exchange tubes, the second equilateral triangle E, the heat exchange tubes E and the heat exchange tubes 1 to allow the refrigerant to flow through the heat exchange system with a low pressure loss of the heat exchange tubes a refrigerant flowing through the heat exchange tubes 1, and the heat exchange system, and the heat exchange tubes a low pressure loss of the heat exchange tubes C, and the heat exchange tubes 1.
The refrigerant A passes through the shell pass, and the chilled water B (see figure 4) passes through the tube pass. In the working process of the heat exchanger, the refrigerant A completely immerses the heat exchange tubes 1, the liquid refrigerant A exchanges heat on the surfaces of the heat exchange tubes 1, absorbs heat and evaporates to form a gaseous refrigerant A, and then the gaseous refrigerant A is discharged out of the heat exchanger. The liquid refrigerant A flows among the plurality of heat exchange tubes 1 in the second heat exchange tube region H and exchanges heat to form a gaseous refrigerant A. Due to the pipe distribution mode of the second equilateral triangle E, a channel which is consistent with the flow direction of the shell side is formed between every two rows of heat exchange pipes 1, the pressure of the liquid refrigerant A flowing in the channel is small, the speed is high, the pressure loss is small, and therefore the pressure loss at the second heat exchange pipe area H is reduced, and the low pressure of the system is guaranteed.
Subsequently, the liquid refrigerant a flows between the plurality of heat exchange tubes 1 in the first heat exchange tube region P and exchanges heat continuously on the surfaces of the heat exchange tubes 1. Due to the pipe distribution mode of the first equilateral triangle D, a channel which faces to the next row of heat exchange pipes 1 vertically is formed between every two rows of heat exchange pipes 1, and the refrigerant A can form turbulent flow on the surface of the heat exchange pipes 1 in the flowing process, so that the heat exchange effect can be enhanced.
The pipe arrangement mode cooperation of first equilateral triangle D and second equilateral triangle E when guaranteeing evaporation heat exchange efficiency, can also reduce loss of pressure, guarantees the system low pressure, improves refrigerant A's the superheat degree of breathing in simultaneously, and the compressor of follow-up connection is breathed in and is difficult for receiving the liquid and hits, protection compressor. The pipe arrangement mode of the first equilateral triangle D and the second equilateral triangle E are matched, the flowing type and the flowing direction of the refrigerant A on the shell side are changed, heat exchange can be enhanced, and the heat exchange coefficient is improved.
In the operating condition of the heat exchanger, the first heat exchange tube region P is located in the upper half part inside the shell 2 and is arranged closer to the gas outlet tube 5, and the second heat exchange tube region H is located in the lower half part inside the shell 2 and is arranged closer to the liquid inlet tube 4. In the whole area of the heat exchange tube 1 inside the shell 2, as the refrigerant a flows into the shell 2 from the liquid inlet tube 4 in the form of low-temperature low-pressure liquid, and after heat exchange with the heat exchange tube 1, part of the refrigerant a absorbs heat and evaporates to form a gas medium refrigerant a, and carries a fine liquid refrigerant a to continue flowing towards the air outlet tube 5 and continuously absorb heat until overheating, as the low-temperature low-pressure refrigerant a is continuously evaporated and expanded, the pressure loss of the flow path is increasingly required to be reduced on the downstream side of the flow path of the refrigerant a.
In the refrigerant shell side flow direction C in the shell 2, the first heat exchange tube region P is located downstream of the second heat exchange tube region H. A first heat exchange tube region P is provided in a heat exchange tube region adjacent to the liquid inlet tube 4, i.e., an upstream side of the flow path of the refrigerant a, and a second heat exchange tube region H is provided in a heat exchange tube region adjacent to the gas outlet tube 5, i.e., a downstream side of the flow path of the refrigerant a. Therefore, the first heat exchange tube region P with smaller pressure loss is arranged at the downstream side of the refrigerant a flow path, so that the downstream side can also exchange heat sufficiently to prepare superheated refrigerant a steam, and simultaneously, the requirement of the downstream side flow path on reducing pressure loss is met, and the pressure of the superheated refrigerant a steam near the outlet pipe 5 is ensured to meet the requirement of the compressor. The liquid refrigerant A is reduced or avoided being sent into the compressor, and the risk of liquid impact of the compressor is reduced.
The heat exchange tubes 1 are all of circular tube structures with equal tube diameters, the side length of the first equilateral triangle D and/or the second equilateral triangle E is 22.5-23.8mm, namely the axial distance (hereinafter referred to as tube center distance) between the adjacent heat exchange tubes 1 in the first heat exchange tube region P is 22.5-23.8mm, and the tube center distance between the adjacent heat exchange tubes 1 in the second heat exchange tube region H is 22.5-23.8mm and 38.7-41.0 mm. The tube center distances between adjacent heat exchange tubes 1 are all equal, but in some embodiments, may be different. The heat exchange tubes 1 are parallel and have the same pipe diameter, the pipe center distances between the adjacent heat exchange tubes 1 are also equal, the heat exchange area of each heat exchange tube 1 is equal to that of the refrigerant A, the heat exchange area and the heat exchange speed of each position of each heat exchange tube 1 are equal, the fluctuation caused by uneven heat exchange is reduced, and the heat exchange efficiency is improved. The smaller and proper distance between the adjacent heat exchange tubes 1 can ensure the heat exchange area in the unit area of the tube plate 3, and meanwhile, the pressure loss of the channels of the first heat exchange tube region P and the second heat exchange tube region H can be properly controlled.
The outer diameter of the heat exchange tube 1 is less than 0.433 times of the side length of the second equilateral triangle E, and preferably 8-10 mm. According to the numerical relationship between the outer diameter of the heat exchange tube 1 and the equilateral triangle, only when the outer diameter of the heat exchange tube 1 is smaller than more than 0.433 times of the side length of the equilateral triangle, in other words, the outer diameter of the heat exchange tube 1 is less than 43.3% of the side length of the equilateral triangle formed by the heat exchange tube 1, the channel which is not influenced by other heat exchange tubes 1 and is opposite to the refrigerant A flow path can be ensured to be formed between the two adjacent heat exchange tubes 1, so that the pressure loss is reduced.
A refrigerant distributing plate 7 is further arranged inside the shell 2, and the refrigerant distributing plate 7 is arranged between the second heat exchange tube region H and the liquid inlet tube 4. The refrigerant distributing plate 7 is provided with a plurality of refrigerant distributing holes 8, and the liquid refrigerant A introduced from the liquid inlet pipe 4 can be uniformly distributed to the pipe section parts of the heat exchange pipes 1 in the second heat exchange pipe area H under the action of the refrigerant distributing plate 7, so that the heat exchange is ensured to be uniform.
An air baffle plate 9 is further arranged inside the shell 2, and the air baffle plate 9 is arranged between the first heat exchange pipe region P and the air outlet pipe 5. The length direction of the air baffle plate 9 is consistent with the axial direction of the shell 2, and the plate plane of the air baffle plate 9 is horizontally arranged. By utilizing the air baffle plate 9, the vapor of the refrigerant A carrying fine liquid drops can be prevented from directly entering the inlet of the compressor, and the liquid impact of the liquid drops on the compressor is avoided.
The heat exchanger is an evaporator, more preferably a flooded evaporator. The flooded evaporator mainly exchanges heat between a liquid refrigerant A and chilled water B in the heat exchange process, a gaseous refrigerant A generated by heat absorption and boiling is separated out from the liquid refrigerant A, and further absorbs heat to form superheated refrigerant A gas, and then the gas is sucked from the compressor and enters the compressor. Therefore, the heat exchange area of the heat exchange tube 1 can be effectively utilized, the heat exchange efficiency of the heat exchanger is high, and the heat exchange efficiency and the refrigerating capacity of the unit are correspondingly improved.
The number of layers of the heat exchange tubes 1 located in the first heat exchange tube region P is greater than that of the heat exchange tubes 1 located in the second heat exchange tube region H. In the flooded evaporator, the gaseous refrigerant evaporated and rising after being absorbed in the second heat exchange tube region H is collected at the first heat exchange tube region P, for example, the uppermost 2-3 layers of heat exchange tubes 1, and continues to absorb heat to form superheated gas, thereby entering the compressor. Therefore, the number of layers of the heat exchange tubes 1 in the second heat exchange tube region H is greater than that of the heat exchange tubes 1 in the first heat exchange tube region P, so that the characteristic of a flooded evaporator can be properly matched, and the characteristics of ensuring heat exchange of the second heat exchange tube region H and ensuring controllable pressure loss of the first heat exchange tube region P are fully realized.
Second embodiment
The utility model discloses a second embodiment provides a heat exchanger, and the second embodiment is right
Further modifications of the first embodiment, which are not specifically described, include reference numerals and text descriptions, which are the same as those of the first embodiment, and are not repeated herein.
The main improvement of the second embodiment over the first embodiment is that in the second embodiment of the present invention, as seen in fig. 5, the inclination angle α of the second equilateral triangle E of the second heat exchange tube region H is 15 °, in other embodiments, the inclination angles α of the first equilateral triangle D and the second equilateral triangle E are both adjustable between 0 ° and 60 °, and the pressure loss of the first heat exchange tube region P and the second heat exchange tube region H can be made different by adjusting the inclination angles α of the first equilateral triangle D and the second equilateral triangle E to be different.
Third embodiment
The utility model discloses a third embodiment provides a water chilling unit, heat exchanger in the first embodiment, the part that does not do the special explanation includes reference numeral and word description, all is the same with first embodiment, no longer gives unnecessary details here.
In a third embodiment of the present invention, as seen in fig. 6, the chiller includes a compressor 11, a condenser 12, an expansion valve 13, and an evaporator, which are connected in this order and form a circulation circuit, and the evaporator is the heat exchanger 14 in the first embodiment. The refrigerant a circulates and flows through the compressor 11, the condenser 12, the expansion valve 13, and the heat exchanger 14 in this order, and the chilled water B flows through the heat exchanger 14 and exchanges heat with the refrigerant a in the heat exchanger 14.
It will be appreciated by those of ordinary skill in the art that in the embodiments described above, numerous technical details are set forth in order to provide a better understanding of the present application. However, the technical solutions claimed in the claims of the present application can be basically implemented without these technical details and various changes and modifications based on the above-described embodiments. Accordingly, in actual practice, various changes in form and detail may be made to the above-described embodiments without departing from the spirit and scope of the invention.
Claims (10)
1. A heat exchanger, comprising:
a housing;
the liquid inlet pipe is used for the inflow of refrigerant and is arranged at the bottom of the shell;
the gas outlet pipe is communicated with the liquid inlet pipe and is arranged at the upper part of the shell;
a plurality of heat exchange tubes arranged in parallel with each other in the housing;
a tube plate disposed at an end of the case in a manner perpendicular to the heat exchange tube, the end of the heat exchange tube being inserted through the tube plate,
it is characterized in that the preparation method is characterized in that,
the shell interior includes a first heat exchange tube region and a second heat exchange tube region,
and the pressure loss of the refrigerant flow path in the second heat exchange tube region is less than that of the refrigerant flow path in the first heat exchange tube region.
2. The heat exchanger of claim 1,
in the first heat exchange tube area, the heat exchange tubes are arranged in a mode that the cross sections of any adjacent three heat exchange tubes form a first equilateral triangle;
in the second heat exchange tube region, the heat exchange tubes are arranged in a manner that the cross sections of any adjacent three heat exchange tubes form a second equilateral triangle,
wherein the first equilateral triangle and the second equilateral triangle have different inclination angles.
3. The heat exchanger of claim 2,
the first equilateral triangle is provided with a side which is vertical to the flowing direction of the shell pass of the refrigerant in the shell;
the second equilateral triangle is provided with a side parallel to the flowing direction of the shell side of the refrigerant in the shell.
4. The heat exchanger of claim 1, wherein the first heat exchange tube region is downstream of the second heat exchange tube region in a refrigerant shell-side flow direction within the shell.
5. A heat exchanger according to claim 2 or 3, wherein the first equilateral triangle and/or the second equilateral triangle have a side length of 22.5-23.8 mm.
6. The heat exchanger of claim 5, wherein the heat exchange tube has an outer diameter less than 0.433 times the side length of the second equilateral triangle.
7. The heat exchanger of any one of claims 1 to 4, further comprising:
the refrigerant distributor is arranged between the liquid inlet pipe and the heat exchange pipe;
and the liquid baffle is arranged between the air outlet pipe and the heat exchange pipe.
8. The heat exchanger of claim 7, wherein the heat exchanger is a flooded heat exchanger.
9. The heat exchanger of claim 8, wherein the number of layers of the heat exchange tubes in the first heat exchange tube region is less than the number of layers of the heat exchange tubes in the second heat exchange tube region.
10. A water chilling unit comprising a compressor, a condenser, a throttle valve and an evaporator, wherein the evaporator employs a heat exchanger according to any one of claims 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922028917.3U CN210921673U (en) | 2019-11-21 | 2019-11-21 | Heat exchanger and water chilling unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922028917.3U CN210921673U (en) | 2019-11-21 | 2019-11-21 | Heat exchanger and water chilling unit |
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| CN210921673U true CN210921673U (en) | 2020-07-03 |
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| CN201922028917.3U Active CN210921673U (en) | 2019-11-21 | 2019-11-21 | Heat exchanger and water chilling unit |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113654276A (en) * | 2021-07-30 | 2021-11-16 | 青岛海尔空调电子有限公司 | Design method of flooded evaporator, flooded evaporator and refrigeration system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113654276A (en) * | 2021-07-30 | 2021-11-16 | 青岛海尔空调电子有限公司 | Design method of flooded evaporator, flooded evaporator and refrigeration system |
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