CN217303667U - Double-pipe heat exchanger and bidirectional countercurrent system - Google Patents
Double-pipe heat exchanger and bidirectional countercurrent system Download PDFInfo
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- CN217303667U CN217303667U CN202123254503.6U CN202123254503U CN217303667U CN 217303667 U CN217303667 U CN 217303667U CN 202123254503 U CN202123254503 U CN 202123254503U CN 217303667 U CN217303667 U CN 217303667U
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Abstract
The utility model belongs to the technical field of air conditioner heat transfer system, a double-pipe heat exchanger and two-way adverse current system is disclosed, which comprises a compressor, valving, air side heat exchanger and a plurality of communicating pipe, valving includes and connects in the compressor through communicating pipe, double-pipe heat exchanger's first valving and connect in air side heat exchanger, first valving, double-pipe heat exchanger's second valving, when using in air conditioning system, accessible system design, through changing heat transfer medium, the flow direction of refrigerant, make the evaporation side, no matter refrigeration or heating of condensation side heat exchanger, the refrigerant flow direction all with by heat transfer medium, as air, the flow opposite direction of water, promote air conditioning system efficiency, promote the heat transfer effect, improve unit performance.
Description
Technical Field
The utility model belongs to the technical field of the air conditioner heat transfer system, concretely relates to double-pipe heat exchanger and two-way countercurrent system.
Background
In a heat exchange system of an air conditioner, it is known from a heat transfer formula Q ═ KA (Δ Tm) that the heat exchange amount Q is larger as the heat exchange temperature difference Δ Tm is larger. The magnitude of the heat exchange temperature difference is related to the relative flow direction of the cold fluid and the hot fluid. The parallel cocurrent flow of the two heat exchange fluids is called as cocurrent flow; parallel countercurrent flow is referred to as "countercurrent flow". Under the condition that the properties, flow, inlet and outlet temperatures and heat exchange areas of the cold fluid and the hot fluid are the same, when the cold fluid and the hot fluid are arranged in a counter-flow mode, the cold fluid and the hot fluid have larger heat exchange temperature difference and smaller downstream flow. Therefore, when other conditions are the same, the larger the heat exchange temperature difference is, the larger the heat transfer quantity is, and the heat exchange effect is good. The required heat transfer area can be reduced for transferring as much heat. It can be understood that, during reverse heat exchange, under the condition that the time and the area of the mutual contact of the two media are relatively concurrent, the contact area is larger, the contact time (if the flow rates of the two media are different) is longer, and the heat exchange can be fully carried out.
In addition, the temperature of the hot fluid at the same section position in the heat exchanger is higher than that of the cold fluid, and if the concurrent arrangement is adopted, the final temperature of the hot fluid outlet is still higher than that of the cold fluid outlet; with a counter-flow arrangement, the outlet temperature of the hot fluid can be much lower than the outlet temperature of the cold fluid. This is the case with the main heat exchanger. Therefore, when the heat exchanger is designed, the flow directions of the cold fluid and the hot fluid are mostly in a counter-flow arrangement.
In a traditional heat exchange scheme, the flowing direction of a refrigerant is just opposite during refrigeration and heating, so that the flowing direction of the refrigerant in a certain mode in refrigeration or heating is always opposite to the wind direction during heating and heating of a traditional fin heat exchanger, and the heat exchange effect of the fin heat exchanger is influenced.
Disclosure of Invention
In order to overcome the above-mentioned shortcoming of prior art, the utility model aims to provide a double-pipe heat exchanger aims at solving the problem that the heat transfer effect that prior art exists is low.
The utility model discloses a reach its purpose, the technical scheme who adopts as follows:
a double-tube heat exchanger comprising:
a heat exchanger housing;
the fluorine side outlet, the fluorine side inlet, the water side outlet and the water side inlet are arranged on the heat exchanger shell, the liquid separation plate and a plurality of inner cylinders are arranged in the heat exchanger shell, and a plurality of heat exchange tubes are arranged in the inner cylinders;
and an outlet pipeline is arranged at the outlet of the fluorine side, and one end of the outlet pipeline is positioned in the heat exchanger shell and between the adjacent inner cylinders.
Preferably, the fluorine side outlet and the fluorine side inlet are located at the top of the heat exchanger shell, the water side outlet and the water side inlet are located on the side surface of the heat exchanger shell, and the water side outlet is oppositely arranged at the upper end of the water side inlet.
Preferably, the liquid separation plate is positioned at the upper end of the inner cylinder body, through holes for the outlet pipelines to pass through are formed in the liquid separation plate, and a plurality of liquid separation holes are uniformly formed in the periphery of the through holes.
Preferably, the heat exchange tubes are arranged in the inner cylinder in a regular triangle and are arranged along the axial direction of the inner cylinder.
Preferably, the outlet pipeline is provided with a pressure equalizing hole.
The utility model also discloses a two-way adverse current system, including foretell double-pipe heat exchanger, still include compressor, valving, air side heat exchanger and a plurality of communicating pipe, valving includes through communicating pipe connect in compressor, double-pipe heat exchanger's first valving and connect in air side heat exchanger, first valving, double-pipe heat exchanger's second valving.
Preferably, the first valve device is a four-way valve, four valve ports of the first valve device are respectively connected with the exhaust port and the suction port of the compressor through the communicating pipe, the fluorine side outlet and the fluorine side inlet of the double-pipe heat exchanger are connected with the second valve device, the communicating pipe between the first valve device and the double-pipe heat exchanger is provided with a stop valve, and the fluorine side outlet and the fluorine side inlet of the double-pipe heat exchanger are connected with the second valve device.
Preferably, the second valve device comprises two stop valve sets, wherein one stop valve set is connected with an outlet of the air side heat exchanger, and the other stop valve set is connected with an inlet of the air side heat exchanger.
Preferably, the second valve device is a four-way valve.
Preferably, a communication pipe between the second valve device and the air-side heat exchanger is provided with a throttling part and a third valve device, and the communication pipe between the second valve device and the double-pipe heat exchanger is provided with a throttling part.
Compared with the prior art, the beneficial effects of the utility model are that:
the utility model provides a two-way system against current when applying in air conditioning system, accessible system design is through the flow direction who changes heat transfer medium (refrigerant) for no matter evaporation side, condensation side heat exchanger refrigerate or heat, the refrigerant flow direction all with by the flow opposite direction of heat transfer medium (like air, water), promote air conditioning system efficiency, promote heat transfer effect, improve the unit performance.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without any creative effort.
Fig. 1 is a schematic view of a heating flow according to a first embodiment of the present invention;
fig. 2 is a schematic diagram of the refrigeration flow according to the first embodiment of the present invention;
fig. 3 is a schematic view of a heating flow according to a second embodiment of the present invention;
fig. 4 is a schematic view of a heating flow according to a second embodiment of the present invention;
fig. 5 is a structural diagram of the double pipe heat exchanger of the present invention;
fig. 6 is a structural sectional view of the double-pipe heat exchanger of the present invention;
FIG. 7 is a structural view of the liquid separating plate of the present invention;
FIG. 8 is a graph of the flow effect of a conventional linear arrangement;
FIG. 9 is a schematic flow diagram of the interior of a conventional heat exchanger;
fig. 10 is a schematic structural view of an outlet pipeline of the present invention;
fig. 11 is a flow effect diagram of the heat exchange tube arrangement of the present invention;
fig. 12 is a schematic flow diagram of the inside of the double pipe heat exchanger of the present invention;
description of reference numerals:
1-double pipe heat exchanger, 2-compressor, 3-air side heat exchanger, 4-communicating pipe, 5-first valve device, 6-second valve device, 601-first stop valve, 602-second stop valve, 603-third stop valve, 604-fourth stop valve, 7-fluorine side outlet, 8-fluorine side inlet, 9-fifth stop valve, 10-sixth stop valve, 11-first throttling component, 12-second throttling component, 13-third valve device, 14-fourth valve device, 15-fifth valve device, 16-sixth valve device, 17-heat exchanger shell, 18-water side outlet, 19-water side inlet, 20-liquid separating plate, 21-inner cylinder, 22-heat exchanging pipe, 23-outlet pipeline, 24-pressure equalizing holes, 25-through holes and 26-liquid separating holes.
Detailed Description
In order to make the technical problem solved by the present invention, the technical solutions adopted by the present invention and the technical effects achieved by the present invention clearer, the embodiments of the present invention are described in further detail below, and it is obvious that the described embodiments are only some embodiments of the present invention, but not all embodiments. Based on the embodiments in the present invention, all other embodiments obtained by those skilled in the art without creative efforts belong to the protection scope of the present invention.
In the present disclosure, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may comprise direct contact between the first and second features, or may comprise contact between the first and second features not directly. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
The utility model discloses a two-way adverse current system has two embodiments, and is specific as follows:
the first embodiment is as follows:
referring to fig. 1, the heat exchanger comprises a double-pipe heat exchanger 1, a compressor 2, a valve device, an air-side heat exchanger 3 and a plurality of communicating pipes 4, wherein the valve device comprises a first valve device 5 connected to the compressor 2 and the double-pipe heat exchanger 1 through the communicating pipes 4 and a second valve device 6 connected to the air-side heat exchanger 3, the first valve device 5 and the double-pipe heat exchanger 1, wherein the first valve device 5 is a four-way valve, and the second valve device 6 comprises two stop valve groups;
as for the connection structure of the first valve device 5, specifically, the four valve ports of the first valve device 5 are respectively the valve port D, the valve port S, the valve port C, and the valve port E, which are connected to the exhaust port and the suction port of the compressor 2, the fluorine-side outlet 7 and the fluorine-side inlet 8 of the double pipe heat exchanger 1, and the second valve device 6 through the communication pipe 4;
as for the connection structure of the second valve device 6, specifically, the first group of stop valve sets includes a first stop valve 601 and a second stop valve 602, and the second group of stop valve sets includes a third stop valve 603 and a fourth stop valve 604, wherein the first group of stop valve sets is connected to the outlet of the air-side heat exchanger 3, the second group of stop valve sets is connected to the inlet of the air-side heat exchanger 3, the first stop valve 601 and the fourth stop valve 604 are connected to the first valve device 5, and the second stop valve 602 and the third stop valve 603 are respectively connected to the fluorine-side inlet 8 and the fluorine-side outlet 7 of the double pipe heat exchanger 1;
a fifth stop valve 9 and a sixth stop valve 10 are respectively arranged at the position of a communicating pipe 4 between the first valve device 5 and the double-pipe heat exchanger 1, a first throttling part 11 is arranged at the position of the communicating pipe 4 between the third stop valve 603 and the double-pipe heat exchanger 1, and a second throttling part 12 and a third valve device 13 are arranged at the position of the communicating pipe 4 between the first group of stop valve blocks and the outlet of the air-side heat exchanger 3;
the working principle is as follows:
referring to fig. 1, during heating, high-temperature and high-pressure refrigerant gas discharged from a compressor 2 enters a double pipe heat exchanger 1 from a fluorine-side inlet 8 of the double pipe heat exchanger 1 through a valve port D, a valve port C and a sixth cutoff valve 10 of a first valve device 5, is condensed into medium-temperature and medium-pressure refrigerant liquid, enters an air-side heat exchanger 3 under the action of a second valve device 6 after being throttled by a first throttling component 11, is evaporated, and then flows out of the air-side heat exchanger 3, at which time the second throttling component 12 is completely closed, the third valve device 13 is opened, refrigerant returns to a valve port E of the first valve device 5 under the action of the third valve device 13 and the second valve device 6, and refrigerant returns to an air suction port of the compressor 2 through the first valve device 5 according to a communication structure of the valve port E and the valve port S of the four-way valve device 5. In the process, the flowing direction of the refrigerant in the air side heat exchanger 3 and the casing heat exchanger 1 is always opposite to the flowing direction of the heat-exchanged medium (air and water), so that countercurrent heat exchange is formed, and the heat exchange effect is improved.
Referring to fig. 2, during cooling, high-temperature and high-pressure refrigerant gas discharged from the compressor 2 is discharged from the discharge port thereof through the valve ports D and E of the first valve device 5, enters the air-side heat exchanger 3 under the action of the second valve device 6, is condensed, and then flows out of the air-side heat exchanger 3, at which time the second throttling part 12 is opened, the third valve device 13 is closed, refrigerant enters the double pipe heat exchanger 1 through the fluorine-side inlet 8 of the double pipe heat exchanger 1 under the action of the second valve device 6, is evaporated, and then flows out of the fluorine-side outlet 7, returns to the valve port C of the first valve device 5 through the fifth cutoff valve 9, and, according to the communication structure of the valve port C and the valve port S of the four-way valve device 5, the refrigerant returns to the suction port of the compressor 2 through the first valve device 5. In the process, the flowing direction of the refrigerant in the air side heat exchanger 3 and the sleeve heat exchanger 1 is always opposite to the flowing direction of the heat-exchanged medium (air and water), so that countercurrent heat exchange is formed, and the heat exchange effect is improved.
Example two:
referring to fig. 3, the heat exchanger includes a double-pipe heat exchanger 1, a compressor 2, a valve device, an air-side heat exchanger 3, and a plurality of communicating pipes 4, wherein the valve device includes a first valve device 5 connected to the compressor 2 and the double-pipe heat exchanger 1 through the communicating pipes 4, and a second valve device 6 connected to the air-side heat exchanger 3, the first valve device 5, and the double-pipe heat exchanger 1, and the first valve device 5 and the second valve device 6 are four-way valves;
as for the connection structure of the first valve device 5, specifically, the four valve ports of the first valve device 5 are respectively a valve port D, a valve port S, a valve port C, and a valve port E, which are connected to the exhaust port and the suction port of the compressor 2 through the communicating pipe 4, and the fluorine-side outlet 7 and the fluorine-side inlet 8 of the double-pipe heat exchanger 1 are connected to the second valve device 6;
as for the connection structure of the second valve device 6, specifically, the four valve ports of the second valve device 6 are respectively connected with the inlet and the outlet of the air-side heat exchanger 3, the fluorine-side outlet 7 and the fluorine-side inlet 8 of the first valve device 5 and the double-pipe heat exchanger 1 through the communicating pipe 4;
a fifth stop valve 9 and a sixth stop valve 10 are respectively arranged at the position of a communicating pipe 4 between the first valve device 5 and the double-pipe heat exchanger 1, a first throttling part 11 and a fourth valve device 14 are arranged at the position of the communicating pipe 4 between the second valve device 6 and the double-pipe heat exchanger 1, and a second throttling part 12 and a third valve device 13 are arranged at the position of the communicating pipe 4 between the second valve device 6 and the outlet of the air-side heat exchanger 3;
the working principle is as follows:
referring to fig. 3, during heating, the valve port D and the valve port C of the first valve device 5 are communicated with each other, the valve port S and the valve port E are communicated with each other, the valve port S and the valve port C are communicated with each other, high-temperature and high-pressure refrigerant gas discharged from the compressor 2 is discharged from the exhaust port thereof, enters the double pipe heat exchanger 1 from the fluorine-side inlet 8 of the double pipe heat exchanger 1 through the valve port D, the valve port C and the sixth stop valve 10 of the first valve device 5, is condensed into medium-temperature and medium-pressure refrigerant liquid, enters the air-side heat exchanger 3 through the valve port D and the valve port E of the second valve device 6 after being throttled by the first throttle device 11, is evaporated, and then flows out of the air-side heat exchanger 3, at this time, the second throttle device 12 is completely closed, the third valve device 13 is opened, and the refrigerant returns to the valve port E of the first valve device 5 through the third valve device 13 and the second valve device 6, and according to the communication structure of the valve port E and the valve port S of the four-way valve, the first valve device 5 is used for returning the refrigerant to the suction port of the compressor 2 through the first valve device 5. In the process, the flowing direction of the refrigerant in the air side heat exchanger 3 and the casing heat exchanger 1 is always opposite to the flowing direction of the heat-exchanged medium (air and water), so that countercurrent heat exchange is formed, and the heat exchange effect is improved.
Referring to fig. 4, during cooling, the high-temperature and high-pressure refrigerant gas discharged from the compressor 2 is discharged from the exhaust port thereof, passes through the valve ports D and E of the first valve device 5, enters the air-side heat exchanger 3 through the valve ports C and D of the second valve device 6, is condensed, and then flows out of the air-side heat exchanger 3, at which time the second throttling element 12 is opened, the third valve device 13 is closed, the refrigerant enters the double-pipe heat exchanger 1 through the second throttling element 12, the valve port S of the second valve device 6, and the valve port E from the fluorine-side inlet 8 of the double-pipe heat exchanger 1, is evaporated, flows out of the fluorine-side outlet 7, returns to the valve port C of the first valve device 5 through the fifth cut-off valve 9, and returns to the suction port of the compressor 2 through the first valve device 5 according to the communication structure of the valve ports C and S of the four-way valve device 5. In the process, the flowing direction of the refrigerant in the air side heat exchanger 3 and the casing heat exchanger 1 is always opposite to the flowing direction of the heat-exchanged medium (air and water), so that countercurrent heat exchange is formed, and the heat exchange effect is improved.
By adopting the two-way counter-flow system of the two schemes, when the refrigerating/heating double-counter-flow heat exchanger is applied to the air conditioning system, the flow direction of the heat exchange medium (refrigerant) is changed, so that the flow direction of the refrigerant is opposite to the flow direction of the heat exchange medium (such as air and water) to be heat-exchanged no matter the heat exchangers at the evaporation side and the condensation side are refrigerated or heated, the efficiency of the air conditioning system is improved, and the performance of the unit is improved
Through the setting of check valve, cross valve in the system, change the refrigerant flow direction for under the refrigeration or the heating state, air side heat exchanger 3, double-pipe heat exchanger 1 are opposite with the flow direction of the heat transfer medium (like air, water) all the time, thereby promote heat transfer effect.
The heating and the refrigerating are respectively controlled by different throttling components through the adjustment of the positions and the number of the throttling components, and the refrigerant quantity requirements of the system under different working conditions are met more accurately.
For further optimization of the two solutions, the third valve device 13 and the fourth valve device 14 may be solenoid valves, manual shut-off valves, or other valves capable of performing on-off function.
Further, the communication pipe 4 at the outlet of the air-side heat exchanger 3 is provided with a fifth valve device 15 and a sixth valve device 16, which may be solenoid valves, manual shutoff valves, or other valves capable of performing on-off functions. When the difference between the diameters and lengths of the capillary tubes on the fifth valve device 15 side and the sixth valve device 16 side is large, the resistance of the capillary tubes on the sixth valve device 16 side is large, and the sixth valve device 16 may not be configured.
In a further improvement, the first throttling component 11 and the second throttling component 12 may be any component having a throttling function, such as an electronic expansion valve, a thermostatic expansion valve, a capillary tube, and the like, and because the demand of the system for the refrigerant is inconsistent (larger during refrigeration) during refrigeration and heating, the first throttling component 11 and the second throttling component 12 select appropriate throttling components according to the demand of the refrigerant during heating/refrigeration respectively.
Further improvement, other components such as a filter, a gas-liquid separator, a liquid storage tank and the like can be added in the system according to actual requirements.
With respect to the structure of the double pipe heat exchanger 1 in the above-described bidirectional counterflow system, in particular, with reference to fig. 5 and 6, it comprises a heat exchanger housing 17; the fluorine side outlet 7, the fluorine side inlet 8, the water side outlet 18 and the water side inlet 19 are arranged on the heat exchanger shell 17, a liquid separation plate 20 and a plurality of inner cylinders 21 are arranged in the heat exchanger shell 17, and a plurality of heat exchange tubes 22 are arranged in the inner cylinders 21; an outlet pipeline 23 is arranged at the fluorine side outlet 7, and one end of the outlet pipeline 23 is positioned in the heat exchanger shell 17 and between the adjacent inner cylinders 21. The fluorine side outlet 7 and the fluorine side inlet 8 are positioned at the top of the heat exchanger shell 17, the water side outlet 18 and the water side inlet 19 are positioned at the side part of the heat exchanger shell 17, and the water side outlet 18 is oppositely arranged at the upper end of the water side inlet 19.
During refrigeration/heating, refrigerant enters the double-pipe heat exchanger 1 from the fluorine side inlet 8, flows through the heat exchange pipe 22 from top to bottom, flows out from the fluorine side outlet 7, and water enters the double-pipe heat exchanger 1 from the water side outlet 18, flows from bottom to top and keeps countercurrent heat exchange with the refrigerant all the time.
Specifically, referring to fig. 7, the liquid separation plate 20 is located at the upper end of the inner cylinder 21, a through hole 25 through which the outlet pipeline 23 passes is formed in the liquid separation plate 20, and a plurality of liquid separation holes 26 are uniformly formed around the through hole 25.
During heating, a high-temperature and high-pressure refrigerant enters the double-pipe heat exchanger 1 from the fluorine side inlet 8, and the liquid separation plate 20 has two functions, namely, a buffering function is realized, so that high-pressure refrigerant gas is prevented from directly impacting the heat exchange pipe 22; secondly, the refrigerant gas is distributed more evenly. The throttled gas-liquid mixed refrigerant can uniformly enter the area of the heat exchange tube 22 after being distributed by the liquid separating plate 20 during refrigeration, and simultaneously, under the action of gravity and vacuum, the gas-liquid mixture of the refrigerant can be sprayed on the surface of the heat exchange tube 22 during refrigeration, so that the refrigerant forms a uniform film shape on the surface of the heat exchange tube 22 and flows from top to bottom, and the heat exchange effect is enhanced.
Specifically, the heat exchange tubes 22 are arranged in the inner cylinder 21 in a regular triangle and are arranged along the axial direction thereof. Compared with the traditional linear arrangement, the flow effect is shown in fig. 8 and 11, in the traditional linear arrangement, a certain gap is formed between every two rows of heat exchange tubes 22, when the refrigerant flows, most of the refrigerant flows out from the gap of the heat exchange tubes 22, the contact area between the refrigerant and the heat exchange tubes 22 is reduced, and the heat exchange effect is greatly attenuated; the heat exchange tubes 22 are arranged in a regular triangle, gaps do not exist among the heat exchange tubes 22, meanwhile, the disturbance of the refrigerant on the surfaces of the heat exchange tubes 22 is enhanced, and the contact area between the refrigerant and the heat exchange tubes 22 is increased, so that the heat exchange performance is improved.
Specifically, the fluorine side and the outlet are both arranged at the axis position of the heat exchanger shell 17, compared with the traditional heat exchanger outlet on the side surface of the shell, the flow schematic diagram of the heat exchanger refers to fig. 9 and 12, when the traditional double-pipe heat exchanger is used as an evaporator, the fluorine side outlet 7 is arranged on the side surface of the shell, at the moment, due to the air extraction function of the compressor 2, the vacuum degree of the position close to the fluorine side outlet 7 is higher, the refrigerant liquid level inside the heat exchanger is inclined, refrigerant flowing dead corners are generated on the heat exchange pipe 22 right opposite to the fluorine side outlet 7, the refrigerant liquid level height is not enough, the heat exchange is not uniform, and the heat exchange effect is influenced. The fluorine side inlet and the fluorine side outlet are both arranged at the axis position of the heat exchanger shell 17, so that the liquid level of the refrigerant in the heat exchanger shell 17 is close to the level, the flowing dead angle of the refrigerant is eliminated, and the heat exchange effect is enhanced.
Specifically, the outlet pipeline 23 is provided with a pressure equalizing hole 24, as shown in fig. 10, during the refrigeration or defrosting process, the fluorine side outlet 7 of the double-pipe heat exchanger 1 is directly connected with the return air port of the compressor 2, and when the compressor 2 is stopped, refrigerant liquid may enter the compressor 2, which causes the compressor 2 to start with liquid when the compressor 2 is started next time, and damages the compressor 2. The pressure equalizing hole 24 is provided to quickly equalize the pressure between the inside of the heat exchanger and the suction port of the compressor 2 when the compressor 2 is stopped, thereby preventing refrigerant liquid from entering the compressor 2.
In the description herein, it is to be understood that the terms "upper," "lower," "left," "right," and the like are used merely for convenience in description and simplicity in operation, and do not indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting. Furthermore, the terms "first" and "second" are used merely for descriptive purposes and are not intended to have any special meaning.
In the description herein, references to "an embodiment," "an example" or the like are intended to mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example.
Furthermore, it should be understood that although the present description refers to embodiments, not every embodiment may contain only a single embodiment, and such description is for clarity only, and those skilled in the art should integrate the description, and the embodiments may be appropriately combined to form other embodiments as will be appreciated by those skilled in the art.
The technical principle of the present invention has been described above with reference to specific embodiments. The description is made for the purpose of illustrating the principles of the invention and is not to be construed in any way as limiting the scope of the invention. Based on the explanations herein, those skilled in the art will be able to conceive of other embodiments of the present invention without any inventive effort, which would fall within the scope of the present invention.
Claims (10)
1. A double-tube heat exchanger, comprising:
a heat exchanger housing;
the fluorine side outlet, the fluorine side inlet, the water side outlet and the water side inlet are arranged on the heat exchanger shell, the liquid separation plate and a plurality of inner cylinders are arranged in the heat exchanger shell, and a plurality of heat exchange tubes are arranged in the inner cylinders;
and an outlet pipeline is arranged at the outlet of the fluorine side, and one end of the outlet pipeline is positioned in the heat exchanger shell and between the adjacent inner cylinders.
2. The double-tube heat exchanger of claim 1, wherein the fluorine-side outlet and the fluorine-side inlet are located at a top portion of the heat exchanger shell, the water-side outlet and the water-side inlet are located at side portions of the heat exchanger shell, and the water-side outlet is oppositely disposed at an upper end of the water-side inlet.
3. The double-pipe heat exchanger according to claim 1, wherein the liquid separation plate is located at the upper end of the inner cylinder, a through hole for the outlet pipeline to pass through is formed in the liquid separation plate, and a plurality of liquid separation holes are uniformly formed around the through hole.
4. The double-pipe heat exchanger according to claim 1, wherein the heat exchange pipes are arranged in a regular triangle in the inner cylinder and are arranged in an axial direction thereof.
5. The double pipe heat exchanger according to claim 1, wherein the outlet line is provided with a pressure equalizing hole.
6. A bi-directional counterflow system comprising the double-pipe heat exchanger of any of claims 1-5, further comprising a compressor, a valve arrangement, an air-side heat exchanger, and a plurality of communication pipes, the valve arrangement comprising a first valve arrangement connected to the compressor, the double-pipe heat exchanger through the communication pipes, and a second valve arrangement connected to the air-side heat exchanger, the first valve arrangement, the double-pipe heat exchanger.
7. The system according to claim 6, wherein the first valve device is a four-way valve, four ports of the first valve device are connected to the exhaust port and the suction port of the compressor, the fluorine-side outlet and the fluorine-side inlet of the double-pipe heat exchanger, and the second valve device through the communication pipe, the communication pipe between the first valve device and the double-pipe heat exchanger is provided with a stop valve, and the fluorine-side outlet and the fluorine-side inlet of the double-pipe heat exchanger are connected to the second valve device.
8. A bi-directional reversing flow system according to claim 7 wherein said second valve means comprises two shut-off valve blocks, one of said shut-off valve blocks being connected to the outlet of said air side heat exchanger and the other of said shut-off valve blocks being connected to the inlet of said air side heat exchanger.
9. A bi-directional reversing flow system according to claim 7, wherein the second valve means is a four-way valve.
10. A bi-directional counterflow system as in any of claims 8-9, wherein the communication tube between the second valve arrangement and the air-side heat exchanger is provided with a throttle member, a third valve arrangement, and the communication tube between the second valve arrangement and the double-tube heat exchanger is provided with a throttle member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202123254503.6U CN217303667U (en) | 2021-12-21 | 2021-12-21 | Double-pipe heat exchanger and bidirectional countercurrent system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202123254503.6U CN217303667U (en) | 2021-12-21 | 2021-12-21 | Double-pipe heat exchanger and bidirectional countercurrent system |
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| Publication Number | Publication Date |
|---|---|
| CN217303667U true CN217303667U (en) | 2022-08-26 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202123254503.6U Active CN217303667U (en) | 2021-12-21 | 2021-12-21 | Double-pipe heat exchanger and bidirectional countercurrent system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN217303667U (en) |
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2021
- 2021-12-21 CN CN202123254503.6U patent/CN217303667U/en active Active
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