CN112629077B - Heat exchanger and air conditioning system - Google Patents
Heat exchanger and air conditioning system Download PDFInfo
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- CN112629077B CN112629077B CN202011552414.7A CN202011552414A CN112629077B CN 112629077 B CN112629077 B CN 112629077B CN 202011552414 A CN202011552414 A CN 202011552414A CN 112629077 B CN112629077 B CN 112629077B
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- heat exchange
- refrigerant
- pipe
- heat
- heat exchanger
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00321—Heat exchangers for air-conditioning devices
- B60H1/00328—Heat exchangers for air-conditioning devices of the liquid-air type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/02—Tubular elements of cross-section which is non-circular
- F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
- F28F9/0214—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions
- F28F9/0217—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only longitudinal partitions the partitions being separate elements attached to header boxes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/09—Improving heat transfers
Abstract
The invention discloses a heat exchanger and an air conditioning system, and relates to the technical field of heat exchange. The heat exchanger comprises a first heat exchange assembly, a second heat exchange assembly and a heat exchange assembly, wherein the first heat exchange assembly is provided with a refrigerant inlet and comprises a plurality of rows of first heat exchange tubes arranged in rows; the second heat exchange assembly is provided with a refrigerant outlet, is fixed with and communicated with the first heat exchange assembly and comprises a plurality of rows of second heat exchange tubes arranged in rows, and the hydraulic diameter of each second heat exchange tube is smaller than that of each first heat exchange tube. Compared with the prior art, the hydraulic diameter of the second heat exchange tube is smaller than that of the first heat exchange tube, so that the phase change of the heat exchange tube is matched with that of the refrigerant medium, the heat exchange sufficiency and the heat exchange efficiency are improved, and the pressure loss of the refrigerant medium is reduced.
Description
Technical Field
The invention relates to the technical field of heat exchange, in particular to a heat exchanger and an air conditioning system.
Background
At present, a common heat pump air conditioning system for an automobile has two basic functions of cooling and heating, which are respectively realized by a condenser and an evaporator, wherein in the condenser, a refrigerant flows through an internal flow channel of the condenser, air flows through the outside of the condenser, the refrigerant releases heat to the air to be cooled, the refrigerant is condensed into a liquid state from a gas state, and the outside air is heated. In the evaporator, a refrigerant flows through an inner flow passage thereof, air flows through an outer portion thereof, the refrigerant absorbs heat in the air to be heated, and is evaporated from a liquid state to a gaseous state, and the outside air is cooled.
The existing condenser and evaporator (collectively called heat exchanger) generally adopt a double-row parallel flow structure, and comprise a front row of heat exchange tubes and a rear row of heat exchange tubes, each row of heat exchange tubes comprises a plurality of refrigerant runners, the design parameters of the two rows of heat exchange tubes are completely consistent (namely the row number, the shape, the number and the size of the refrigerant runners are all the same), and the inlet and the outlet are positioned at the upper part of the side end or at the left and the right of the front end. The difference is that the evaporator contains 4 or 6 passes, while the condenser generally employs two passes (front and rear rows of heat exchange tubes are arranged in one pass, respectively). In this way, it means that in each flow path region, the design features and the heat exchange area of the refrigerant flow channel are basically unchanged, that is, the hydraulic diameter Dh (Dh =4*A/P, a is the cross-sectional area of the flow channel, and P is the wet perimeter of the flow channel) of the heat exchange tube is unchanged.
However, the refrigerant undergoes phase change by heat absorption or heat release during heat exchange, and the state and physical properties, particularly specific volume, of the refrigerant constantly change as the heat exchange progresses. For the evaporator, the refrigerant at the inlet is in a gas-liquid two-phase state, the refrigerant at the outlet is in a superheated gas phase, and the flow rate is changed from slow to fast; for the condenser, the refrigerant at the inlet is a superheated gas phase, the refrigerant at the outlet is a supercooled liquid phase, and the flow rate is changed from fast to slow. The fast flow rate corresponds to large pressure drop and large heat transfer coefficient, and the corresponding hydraulic diameter Dh is also large so as to adapt to the change of the physical property and the heat exchange characteristic of the refrigerant and ensure the sufficient heat exchange. Therefore, the design parameters of the flow channels of all the flows of the existing heat exchanger are the same, the flow channels are not matched with the state and physical property change of the refrigerant medium, and the heat exchange tube is insufficient, so that the heat exchange efficiency is low, and the pressure loss of the refrigerant is large.
Accordingly, there is a need for a heat exchanger and an air conditioning system to solve the above problems.
Disclosure of Invention
The invention aims to provide a heat exchanger and an air conditioning system, which are used for matching the phase change of a refrigerant flow channel and a refrigerant medium, improving the heat exchange sufficiency and the heat exchange efficiency and reducing the pressure loss of the refrigerant medium.
In order to achieve the purpose, the invention adopts the following technical scheme:
a heat exchanger, comprising:
the first heat exchange assembly is provided with a refrigerant inlet and comprises a plurality of rows of first heat exchange tubes arranged in rows;
the second heat exchange assembly is provided with a refrigerant outlet and is fixedly communicated with the first heat exchange assembly, the second heat exchange assembly comprises a plurality of rows of second heat exchange tubes arranged in rows, and the hydraulic diameter of each second heat exchange tube is smaller than that of each first heat exchange tube.
Optionally, the hydraulic diameter of the first heat exchange tube is greater than 1.2 times the hydraulic diameter of the second heat exchange tube.
Optionally, the first heat exchange tube includes a plurality of first refrigerant channels, and the second heat exchange tube includes a plurality of second refrigerant channels;
the sum of the cross sectional areas of the first refrigerant flow channels on each row of the first heat exchange tubes is larger than the sum of the cross sectional areas of the second refrigerant flow channels on each row of the second heat exchange tubes, and the sum of the wetted perimeter of the first refrigerant flow channels on each row of the first heat exchange tubes is not larger than the sum of the wetted perimeter of the second refrigerant flow channels on each row of the second heat exchange tubes.
Optionally, the sum of the wetted perimeter of the first refrigerant flow channel on each row of the first heat exchange tubes is equal to the sum of the wetted perimeter of the second refrigerant flow channel on each row of the second heat exchange tubes, the cross section of the first refrigerant flow channel is circular, and the cross section of the second refrigerant flow channel is rectangular.
Optionally, the cross-sectional shapes of the first refrigerant channel and the second refrigerant channel are both set to be rectangular.
Optionally, the first refrigerant flow channel is provided with a U-shaped protrusion portion, and the U-shaped protrusion portion is protruded toward the inside of the first refrigerant flow channel.
Optionally, two U-shaped protrusions are symmetrically disposed on each of the first coolant channels.
Optionally, the heat exchanger further comprises a first liquid collecting pipe and a second liquid collecting pipe, the number of the first liquid collecting pipes is two, the two first liquid collecting pipes are respectively and fixedly communicated with two ends of the first heat exchange pipe, and the refrigerant inlet is formed in the first liquid collecting pipe positioned at the top of the first heat exchange pipe;
the two second liquid collecting pipes are respectively and fixedly communicated with the two ends of the second heat exchange pipe, the refrigerant outlet is formed in the second liquid collecting pipe positioned at the top of the second heat exchange pipe, and the first liquid collecting pipe is communicated with the second liquid collecting pipe.
Optionally, the heat exchanger further comprises a partition plate, the partition plate is arranged in the first liquid collecting pipe arranged at the top of the first heat exchange pipe and the second liquid collecting pipe arranged at the top of the second heat exchange pipe and used for dividing multiple columns of the first heat exchange pipe into a first heat exchange flow and a second heat exchange flow which are communicated, dividing multiple columns of the second heat exchange pipe into a third heat exchange flow and a fourth heat exchange flow which are communicated, and the tail end of the second heat exchange flow is communicated with the third heat exchange flow through the first liquid collecting pipe and the second liquid collecting pipe along the flowing direction of the refrigerant.
The invention also provides an air conditioning system which comprises the heat exchanger.
The invention has the beneficial effects that:
the invention provides a heat exchanger and an air conditioning system, which comprise a first heat exchange assembly and a second heat exchange assembly, wherein the second heat exchange assembly is fixed and communicated with the first heat exchange assembly; the second heat exchange assembly is provided with a refrigerant outlet and comprises a plurality of rows of second heat exchange tubes, and the hydraulic diameter of each second heat exchange tube is smaller than that of each first heat exchange tube.
Therefore, when heating, refrigerant media enter the first heat exchange tubes from the refrigerant inlets, exchange heat with air flowing through the outside of the heat exchange tubes through the first heat exchange tubes and the second heat exchange tubes and then flow out from the refrigerant outlets, the refrigerant media are converted into gas-liquid two phases or liquid phases from superheated gas phases in the heat exchange process, the flow speed is reduced, and the hydraulic diameter of the reduced second heat exchange tubes is matched with the phase of the refrigerant media with the reduced speed.
During refrigeration and heat exchange, refrigerant enters the second heat exchange tubes from the refrigerant outlets, and flows out from the refrigerant inlets after exchanging heat with air flowing through the outsides of the heat exchange tubes through the second heat exchange tubes and the first heat exchange tubes.
Compared with the prior art, the hydraulic diameter of the second heat exchange tube is smaller than that of the first heat exchange tube, so that the phase change of the heat exchange tube is matched with that of the refrigerant medium, the heat exchange sufficiency and the heat exchange efficiency are improved, and the pressure loss of the refrigerant medium is reduced.
Drawings
Fig. 1 is a schematic overall structural diagram of a heat exchanger according to a first embodiment of the present invention;
FIG. 2 is a schematic diagram of a heat exchanger according to an embodiment of the present invention, partially broken away;
fig. 3 is a schematic structural diagram of a first heat exchange tube in a heat exchanger according to a first embodiment of the present invention;
fig. 4 is a schematic structural diagram of a second heat exchange tube in a heat exchanger according to a first embodiment of the present invention;
fig. 5 is a schematic overall structure diagram of a heat exchanger according to a second embodiment of the present invention;
fig. 6 is a schematic structural diagram of a first heat exchange tube in a heat exchanger according to a third embodiment of the present invention;
fig. 7 is a schematic structural diagram of a first heat exchange tube in a heat exchanger according to a fourth embodiment of the present invention.
In the figure:
1. a first heat exchange assembly; 11. a refrigerant inlet; 12. a first heat exchange tube; 121. a first refrigerant channel; 1211. a U-shaped boss;
2. a second heat exchange assembly; 21. a refrigerant outlet; 22. a second heat exchange tube; 221. a second refrigerant channel;
3. a first liquid collecting pipe;
4. a second liquid collecting pipe;
5. a fin;
6. a sideboard;
7. a separator.
Detailed Description
In order to make the technical problems solved, technical solutions adopted and technical effects achieved by the present invention clearer, the technical solutions of the embodiments of the present invention will be described in further detail below with reference to the accompanying drawings, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all embodiments. All other embodiments, which can be obtained by a person skilled in the art without making any creative effort based on the embodiments in the present invention, belong to the protection scope of the present invention.
In the description of the present invention, unless expressly stated or limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, e.g., as meaning permanently connected, removably connected, or integral to one another; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present invention, unless expressly stated or limited otherwise, the recitation of a first feature "on" or "under" a second feature may include the recitation of the first and second features being in direct contact, and may also include the recitation that the first and second features are not in direct contact, but are in contact via another feature between them. 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 technical scheme of the invention is further explained by the specific implementation mode in combination with the attached drawings.
Example one
The embodiment of the invention discloses a heat exchanger, which comprises a first heat exchange assembly 1 and a second heat exchange assembly 2, wherein the first heat exchange assembly 1 and the second heat exchange assembly 2 are fixed and communicated, as shown in figures 1-4. Optionally, the first heat exchange assembly 1 is provided with a refrigerant inlet 11, and the first heat exchange assembly 1 comprises a plurality of rows of first heat exchange tubes 12. The second heat exchange assembly 2 is provided with a refrigerant outlet 21, the second heat exchange assembly 2 comprises a plurality of rows of second heat exchange tubes 22, and the hydraulic diameter of the second heat exchange tubes 22 is smaller than that of the first heat exchange tubes 12.
Therefore, during heating, the refrigerant enters the first heat exchange tubes 12 from the refrigerant inlets 11, exchanges heat with air flowing through the outside of the heat exchange tubes through the first heat exchange tubes 12 and the second heat exchange tubes 22 and then flows out from the refrigerant outlets 21, the refrigerant medium is converted into a gas-liquid two-phase or a liquid-phase from an overheated gas phase in the heat exchange process, the flow speed is reduced, and the hydraulic diameter of the reduced second heat exchange tubes 22 is matched with the phase of the refrigerant medium with the reduced speed.
During refrigeration and heat exchange, a refrigerant enters the second heat exchange tubes 22 from the refrigerant outlet 21, the refrigerant flows out from the refrigerant inlet 11 after exchanging heat with air flowing through the outside of the heat exchange tubes through the second heat exchange tubes 22 and the first heat exchange tubes 12, the refrigerant is converted into a superheated gas phase from a gas-liquid phase or a liquid phase in the heat exchange process, the flow rate is increased, and the hydraulic diameter of the increased first heat exchange tubes 12 is matched with the phase of the refrigerant with the increased speed.
Overall, compared with the prior art, the hydraulic diameter of the second heat exchange tube 22 is smaller than that of the first heat exchange tube 12, so that the heat exchange tubes are matched with the refrigerant medium in phase change, the heat exchange sufficiency and the heat exchange efficiency are improved, and the pressure loss of the refrigerant medium is reduced.
Alternatively, the hydraulic diameter of the first heat exchange pipe 12 is larger than 1.2 times of the hydraulic diameter of the second heat exchange pipe 22, so that the heat exchanger obtains better heat exchange effect.
Illustratively, the first heat exchange tube 12 comprises a plurality of first refrigerant channels 121, the second heat exchange tube 22 comprises a plurality of second refrigerant channels 221, the sum of the cross-sectional areas of the first refrigerant channels 121 on each row of the first heat exchange tube 12 is greater than the sum of the cross-sectional areas of the second refrigerant channels 221 on each row of the second heat exchange tube 22, and the sum of the wetted perimeters of the first refrigerant channels 121 on each row of the first heat exchange tube 12 is not greater than the sum of the wetted perimeters of the second refrigerant channels 221 on each row of the second heat exchange tube 22. According to the setting, the calculation formula according to the hydraulic diameter Dh is as follows: dh = (4*A)/P, wherein: a is the cross-sectional area of the refrigerant flow channel, and P is the wetted perimeter of the refrigerant flow channel. In order to ensure the efficient heat exchange of the heat exchanger and reduce the refrigerant resistance loss, the hydraulic diameter Dh of the flow channel is adapted to the state and the heat exchange characteristic of the refrigerant medium. In this embodiment, by optimally designing the first refrigerant flow channel 121 and the second refrigerant flow channel 221, the cross-sectional area of the first refrigerant flow channel 121 is larger than that of the second refrigerant flow channel 221, the sum of the wetted perimeter of the first refrigerant flow channel 121 is not larger than that of the wetted perimeter of the second refrigerant flow channel 221, and the hydraulic diameter of the first heat exchange tube 12 is larger than that of the second heat exchange tube 22 according to a calculation formula of the hydraulic diameter, so that the phase change in the heat exchange process of the refrigerant medium is better adapted, and the heat exchange efficiency is improved.
In the present embodiment, as shown in fig. 3 and 4, the cross-sectional areas of the first refrigerant flow channel 121 and the second refrigerant flow channel 221 are both set to be rectangular, the rectangular shape of the first refrigerant flow channel 121 is larger than the rectangular shape of the second refrigerant flow channel 221, and the number of the first refrigerant flow channels 121 is smaller than the number of the second refrigerant flow channels 221 in comparison with each of the first heat exchange tubes 12 and each of the second heat exchange tubes 22. In general, the sum of the cross-sectional areas of the first refrigerant channel 121 is greater than the sum of the cross-sectional areas of the second refrigerant channel 221, but the sum of the perimeters (wetted perimeters) of the respective cross-sectional rectangles of the first refrigerant channel 121 is less than the sum of the perimeters (wetted perimeters) of the respective cross-sectional rectangles of the second refrigerant channel 221. Of course, in other embodiments, the cross-sectional shapes of the first refrigerant channel 121 and the second refrigerant channel 221 may be set according to the needs, and are not limited to this embodiment.
Optionally, the heat exchanger further comprises a first liquid collecting pipe 3 and a second liquid collecting pipe 4, the number of the first liquid collecting pipes 3 is two, the first liquid collecting pipes are respectively and fixedly communicated with two ends of the first heat exchange pipe 12, and the refrigerant inlet 11 is arranged on the first liquid collecting pipe 3 located at the top of the first heat exchange pipe 12. During heating, the refrigerant flows into the first liquid collecting pipe 3 from the refrigerant inlet 11, flows into the first heat exchange pipe 12 through the first liquid collecting pipe 3 and exchanges heat with the external air; during cooling, the refrigerant medium flows from the first header pipe 3 to the refrigerant inlet 11 and is discharged. Illustratively, the refrigerant inlet 11 is provided at a middle portion of the first header pipe 3.
Correspondingly, the number of the second liquid collecting pipes 4 is two, the two second liquid collecting pipes are respectively and fixedly communicated with the two ends of the second heat exchange pipe 22, the refrigerant outlet 21 is arranged on the second liquid collecting pipe 4 positioned at the top of the second heat exchange pipe 22, and the first liquid collecting pipe 3 is communicated with the second liquid collecting pipe 4. In the arrangement, during heating, the refrigerant flowing out of the first heat exchange tube 12 flows into the second heat exchange tube 22 through the first liquid collecting tube 3 and the second liquid collecting tube 4 to exchange heat with the outside air, and the refrigerant after heat exchange flows out of the refrigerant outlet 21 through the second liquid collecting tube 4 positioned at the top of the second heat exchange tube 22; during refrigeration, the refrigerant medium flows into the second liquid collecting pipe 4 from the refrigerant outlet 21, flows into the second heat exchange pipe 22 through the second liquid collecting pipe 4 to exchange heat with the outside air, and finally flows into the first heat exchange pipe 12 through the second liquid collecting pipe 4 and the first liquid collecting pipe 3 and flows out through the refrigerant inlet 11. Illustratively, the refrigerant outlet 21 is provided at a middle portion of the second header pipe 4.
In this embodiment, the first header 3 at the bottom of the first heat exchange tube 12 is communicated with the second header 4 at the bottom of the second heat exchange tube 22. With this arrangement, the heat exchanger in the present embodiment has two heat exchange flow paths, that is, the first heat exchange tube 12 and the second heat exchange tube 22 are respectively arranged to form one heat exchange flow path. In other embodiments, the heat exchange tubes in the heat exchanger may be divided into corresponding heat exchange flows according to needs, which is not limited to this embodiment.
Further, the heat exchanger further comprises a plurality of fins 5, and the fins 5 are arranged between two adjacent rows of the first heat exchange tubes 12 and between two adjacent rows of the second heat exchange tubes 22 so as to equalize the flow of the external heat exchange air and enhance the heat exchange effect.
Optionally, the heat exchanger further comprises two side plates 6, the two side plates 6 are arranged on two sides of the first heat exchange assembly 1 and the second heat exchange assembly 2 respectively, so that heat exchange air on two sides of the heat exchanger is blocked, leakage of the heat exchange air from two sides is avoided, and heat exchange reliability is improved. Further, the side plates 6 are fixedly connected with the first liquid collecting pipe 3 and the second liquid collecting pipe 4, so that the side plates 6 are fixedly connected.
The embodiment of the invention also provides an air conditioning system which comprises the heat exchanger.
To sum up, the embodiment of the present invention provides a heat exchanger and an air conditioning system, and as a whole, the hydraulic diameter of the second heat exchange tube 22 is smaller than the hydraulic diameter of the first heat exchange tube 12, so that the heat exchange tubes are matched with the phase change of the refrigerant medium, thereby improving the heat exchange sufficiency and the heat exchange efficiency, and reducing the pressure loss of the refrigerant medium.
Example two
In this embodiment, the same portions as those in the first embodiment are given the same reference numerals, and the same description thereof is omitted.
Fig. 5 is a schematic view of the overall structure of a heat exchanger according to a second embodiment of the present invention. As shown in fig. 5, compared with the first embodiment, the heat exchanger provided by the present embodiment further includes a partition plate 7, where the partition plate 7 is disposed in the first header pipe 3 located at the top of the first heat exchange pipe 12 and the second header pipe 4 located at the top of the second heat exchange pipe 22, and is used to divide the multiple rows of the first heat exchange pipe 12 into a first heat exchange flow and a second heat exchange flow which are communicated, and divide the multiple rows of the second heat exchange pipe 22 into a third heat exchange flow and a fourth heat exchange flow which are communicated, and along the flow direction of the refrigerant, the end of the second heat exchange flow is communicated with the third heat exchange flow through the first header pipe 3 and the second header pipe 4.
According to the arrangement, the heat exchanger in the embodiment has four heat exchange processes, namely, the multiple rows of the first heat exchange tubes 12 are divided into the first heat exchange process and the second heat exchange process by the partition plate 7, the multiple rows of the second heat exchange tubes 22 are divided into the third heat exchange process and the fourth heat exchange process by the partition plate 7, the refrigerant inlet 11 is communicated with the first heat exchange process, and the refrigerant outlet 21 is communicated with the fourth heat exchange process. During heating, the refrigerant flows into the first heat exchange process from the refrigerant inlet 11, and flows out from the refrigerant outlet 21 through the second heat exchange process, the third heat exchange process and the fourth heat exchange process; during refrigeration, the refrigerant flows into the fourth heat exchange flow from the refrigerant outlet 21, and flows out from the refrigerant inlet 11 through the third heat exchange flow, the second heat exchange flow and the first heat exchange flow, so that heat exchange with outside air is realized. Compare in embodiment one, this embodiment has prolonged the heat transfer route of refrigerant medium, has further improved heat exchange efficiency, ensures that the heat transfer is abundant.
In this embodiment, fins 5 are also disposed between the side plate 6 and the first heat exchange tube 12 and between the side plate 6 and the second heat exchange tube 22, so as to equalize the flow of the external heat exchange air.
Of course, in other embodiments, the partition 7 may also be used to divide the heat exchange tubes in the heat exchanger into six, eight or more heat exchange flows as needed, which is not limited to this embodiment.
EXAMPLE III
In this embodiment, the same portions as those in the first embodiment are given the same reference numerals, and the same description is omitted.
Fig. 6 is a schematic structural diagram of a first heat exchange tube 12 in a heat exchanger according to a third embodiment of the present invention. As shown in fig. 6, compared to the first embodiment, the heat exchanger provided in the present embodiment has the following differences that the first refrigerant flow channel 121 is provided with a U-shaped protrusion 1211, the U-shaped protrusion 1211 protrudes toward the inside of the first refrigerant flow channel 121, and each first refrigerant flow channel 121 is symmetrically provided with two U-shaped protrusions 1211. The U-shaped protrusion 1211 further increases a contact area between the refrigerant medium in the first refrigerant flow channel 121 and the external heat exchange air, and improves heat exchange efficiency. Of course, in other embodiments, the U-shaped projection 1211 may be replaced with a V-shape, a W-shape, or the like, and may also function in the present embodiment, and is not limited to the present embodiment.
Example four
In this embodiment, the same portions as those in the first embodiment are given the same reference numerals, and the same description is omitted.
Fig. 7 is a schematic structural diagram of a first heat exchange tube 12 in a heat exchanger according to a fourth embodiment of the present invention. As shown in fig. 7, compared to the first embodiment, the heat exchanger provided in the present embodiment has the difference that the sum of the wetted perimeter of the first refrigerant channel 121 of each row of the first heat exchange tubes 12 is equal to the sum of the wetted perimeter of the second refrigerant channel 221 of each row of the second heat exchange tubes 22, the cross-sectional shape of the first refrigerant channel 121 is circular, and the cross-sectional shape of the second refrigerant channel 221 is rectangular. With this arrangement, under the condition of the same perimeter, the cross-sectional area of the circular first refrigerant channel 121 is larger than that of the rectangular second refrigerant channel 221, and the hydraulic diameter of the first heat exchange tube 12 is larger than that of the second heat exchange tube 22, so as to adapt to the phase change characteristic of the refrigerant medium.
It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention, and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.
Claims (9)
1. A heat exchanger, comprising:
the heat exchanger comprises a first heat exchange assembly (1) and a second heat exchange assembly (1), wherein the first heat exchange assembly (1) is provided with a refrigerant inlet (11), and the first heat exchange assembly (1) comprises a plurality of rows of first heat exchange tubes (12) arranged in rows;
the second heat exchange assembly (2) is provided with a refrigerant outlet (21), the second heat exchange assembly (2) is fixed with and communicated with the first heat exchange assembly (1), the second heat exchange assembly (2) comprises a plurality of rows of second heat exchange tubes (22) arranged in rows, and the hydraulic diameter of each second heat exchange tube (22) is smaller than that of the first heat exchange tube (12);
the first heat exchange assembly (1) and the second heat exchange assembly (2) are arranged in parallel;
the first heat exchange tube (12) comprises a plurality of first refrigerant flow channels (121), and the second heat exchange tube (22) comprises a plurality of second refrigerant flow channels (221);
the sum of the wetted perimeter of the first refrigerant flow channel (121) on each row of the first heat exchange tubes (12) is equal to the sum of the wetted perimeter of the second refrigerant flow channel (221) on each row of the second heat exchange tubes (22), the cross section of the first refrigerant flow channel (121) is circular, and the cross section of the second refrigerant flow channel (221) is rectangular.
2. Heat exchanger according to claim 1, wherein the hydraulic diameter of the first heat exchange tube (12) is greater than 1.2 times the hydraulic diameter of the second heat exchange tube (22).
3. The heat exchanger as recited in claim 1 wherein the sum of the cross sectional areas of the first refrigerant flow channels (121) in each row of the first heat exchange tubes (12) is greater than the sum of the cross sectional areas of the second refrigerant flow channels (221) in each row of the second heat exchange tubes (22), and the sum of the wetted perimeters of the first refrigerant flow channels (121) in each row of the first heat exchange tubes (12) is no greater than the sum of the wetted perimeters of the second refrigerant flow channels (221) in each row of the second heat exchange tubes (22).
4. The heat exchanger as claimed in claim 1, wherein the cross-sectional shapes of the first refrigerant flow channel (121) and the second refrigerant flow channel (221) are both rectangular.
5. The heat exchanger as claimed in claim 4, wherein the first refrigerant flow channel (121) is provided with a U-shaped protrusion (1211), and the U-shaped protrusion (1211) protrudes towards the inside of the first refrigerant flow channel (121).
6. The heat exchanger as claimed in claim 5, wherein two U-shaped protrusions (1211) are symmetrically disposed on each of the first refrigerant channels (121).
7. The heat exchanger according to claim 1, further comprising a first header pipe (3) and a second header pipe (4), wherein two first header pipes (3) are provided and are respectively fixedly communicated with two ends of the first heat exchange pipe (12), and the refrigerant inlet (11) is provided on the first header pipe (3) at the top of the first heat exchange pipe (12);
the two second liquid collecting pipes (4) are respectively and fixedly communicated with the two ends of the second heat exchange pipe (22), the refrigerant outlet (21) is formed in the second liquid collecting pipe (4) positioned at the top of the second heat exchange pipe (22), and the first liquid collecting pipe (3) is communicated with the second liquid collecting pipe (4).
8. The heat exchanger according to claim 7, further comprising a partition plate (7), wherein the partition plate (7) is arranged in the first header pipe (3) positioned at the top of the first heat exchange pipe (12) and the second header pipe (4) positioned at the top of the second heat exchange pipe (22) and is used for dividing a plurality of rows of the first heat exchange pipe (12) into a first heat exchange flow and a second heat exchange flow which are communicated, and dividing a plurality of rows of the second heat exchange pipe (22) into a third heat exchange flow and a fourth heat exchange flow which are communicated, and the tail end of the second heat exchange flow is communicated with the third heat exchange flow through the first header pipe (3) and the second header pipe (4) along the flow direction of the refrigerant medium.
9. An air conditioning system comprising a heat exchanger according to any one of claims 1 to 8.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011552414.7A CN112629077B (en) | 2020-12-24 | 2020-12-24 | Heat exchanger and air conditioning system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011552414.7A CN112629077B (en) | 2020-12-24 | 2020-12-24 | Heat exchanger and air conditioning system |
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| CN112629077B true CN112629077B (en) | 2022-11-15 |
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| CN113188273A (en) * | 2021-05-24 | 2021-07-30 | 浙江酷灵信息技术有限公司 | Evaporator with a heat exchanger |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US10047984B2 (en) * | 2010-06-11 | 2018-08-14 | Keihin Thermal Technology Corporation | Evaporator |
| CN102889713B (en) * | 2012-09-20 | 2015-04-08 | 上海加冷松芝汽车空调股份有限公司 | Parallel flow heat exchanger special for bus air conditioner |
| EP3173138B1 (en) * | 2014-07-23 | 2018-12-05 | Ibiden Co., Ltd. | Honeycomb filter |
| JP6578938B2 (en) * | 2015-12-25 | 2019-09-25 | 株式会社デンソー | Exhaust gas filter |
| CN107664459A (en) * | 2016-07-30 | 2018-02-06 | 高诗白 | The design and manufacturing process of a kind of heat exchange ultramicropore pipe |
| CN111780459B (en) * | 2019-04-03 | 2022-04-01 | 浙江三花智能控制股份有限公司 | Heat exchanger and heat exchange system |
| CN210664082U (en) * | 2019-05-08 | 2020-06-02 | 阿特拉斯·科普柯(无锡)压缩机有限公司 | Cooler and air compressor unit with same |
| CN210486167U (en) * | 2019-08-30 | 2020-05-08 | 杭州三花微通道换热器有限公司 | Heat exchanger and heat pump water heater system with same |
| CN211876833U (en) * | 2020-01-09 | 2020-11-06 | 安徽威灵汽车部件有限公司 | Heat exchange tube, heat exchanger, heat exchange system, household appliance and vehicle |
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Effective date of registration: 20210705 Address after: 201108 Room 101, building 1, 888 Shenfu Road, Minhang District, Shanghai Applicant after: SUPERCOOL (SHANGHAI) REFRIGERATION EQUIPMENT Co.,Ltd. Address before: 201108 Shanghai Huaning Minhang District Industrial Zone Xhenzhuang Road No. 4999 Applicant before: SONGZ AUTOMOBILE AIR CONDITIONING Co.,Ltd. |
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