WO2011000137A1

WO2011000137A1 - Microchannel parallel-flow all-aluminum flat-tube weld-type heat exchanger and use of same

Info

Publication number: WO2011000137A1
Application number: PCT/CN2009/001159
Authority: WO
Inventors: 王磊
Original assignee: Wang Lei
Priority date: 2009-06-30
Filing date: 2009-10-19
Publication date: 2011-01-06
Also published as: US20110139420A1; CN101936670B; CN101936670A

Abstract

Provided is a microchannel parallel-flow all-aluminum flat-tube weld-type heat exchanger. A heat exchange part of the heat exchanger is formed by parallel flat tubes (300) made of thin-walled aluminum extrusion profile materials. The heat exchanger can be used in a room air conditioner, a commercial air conditioner and other professional heat exchange systems.

Description

Microchannel, parallel flow, all-aluminum flat tube welded structure heat exchanger and application thereof

The invention relates to a heat exchanger and an application thereof, in particular to a microchannel, parallel flow, all-aluminum flat tube spring-connected structure heat exchanger and application thereof. All the main materials of this new series of heat exchangers are made of aluminum: it is a material that is easy to recycle and has higher corrosion resistance than copper tube aluminum plate heat exchangers. In addition, microchannel flat tubes The design improves the efficiency of the refrigerant side of the heat exchanger, and the advanced design of the parallel flow structure + fins greatly improves the efficiency of the air side of the heat exchanger, thereby greatly improving the overall heat exchanger efficiency. The new series of heat exchangers have the advantages of environmental protection, low refrigerant consumption, pressure resistance, high efficiency, high reliability, low recycling cost, no potential difference and no primary battery effect. Background technique

The heat exchanger in the traditional heat exchanger system mainly adopts the copper tube aluminum tube riser form; the outdoor unit in the conventional heat exchanger system shown in Fig. 1 has the heat exchanger portion 10 as shown in Fig. 3 and Fig. 4 The copper tube 11 is shown with an up-tube structure of the aluminum sheet 12; also in the indoor unit in the conventional heat exchanger system shown in Fig. 2, the heat exchanger 20 is made of a copper tube 21 as shown in Fig. 5. The riser structure of the aluminum sheet 22. This type of conventional heat exchanger system has the following problems:

1. The heat exchange efficiency between the refrigerant in the refrigerant side and the inner wall of the copper pipe is low, and the flow resistance of the refrigerant in the copper pipe of the heat exchanger is large.

2. The heat transfer efficiency of the air piece on the air side is low and the wind resistance is large.

3. The used refrigerant is large and does not meet environmental protection requirements.

4. There is a potential difference between the aluminum sheet and the copper tube, which is easy to corrode and has a short service life.

5. After the thickness of the whole heat exchanger, the weight is heavy and the logistics cost is 4艮.

6. The power of the fan and compressor is large, and the energy consumption is serious.

In 2006, the applicant invented an aluminum extruded thin-walled profile and submitted a utility model patent application to the Chinese State Intellectual Property Office patent and authorized it. The authorization announcement number is CN201007423. The aluminum extruded thin-walled profile is extruded by aluminum ingot smelting and is composed of at least one flat channel tube. The channel tubes are parallel and independent of each other and are laterally connected by the joints to form a multi-channel parallel flow tube of a symmetrical structure or an asymmetric structure. There are at least one hot and cold preparation flow path in the channel tube. And at least a portion of the hot and cold preparation flow passages have a circular or elliptical shape or a polygonal or wavy shape or any combination thereof to suit various product design requirements and different hot and cold preparation requirements. The hot and cold preparation flow passages are arranged in parallel with each other to form a double-flow aluminum extruded thin-walled profile or a multi-channel aluminum extruded thin-walled profile. The fins of each of the hot and cold preparations are separated by fin fins. In place of traditional electrolytic copper tubes, it effectively reduces energy consumption, environmental pollution and improves the efficient use of resources. It has the advantages of low recycling cost and wide utilization of the industry. The applicant also invented a cold heat exchanger using the above-mentioned aluminum extruded thin-walled profile in 2006, and submitted a utility model patent application to the Chinese State Intellectual Property Office patent and authorized it. The authorization announcement number is CN2932273. The heat exchanger includes first and second headers having coupling holes thereon, and a plurality of coupling holes for coupling the first and second headers into the first and second headers of the first and second headers Parallel flat tubes, and outer fins disposed between adjacent flat tubes, each flat tube unit being formed by at least one flat channel tube having a parallel portion between the flat channel tubes. This cold heat exchanger is suitable for parallel flow oil coolers for automotive automatic transmission cooling oils, parallel flow tanks for automotive engine cooling water, and parallel flow heater cores for automotive air conditioning.

At present, the heat exchanger composed of the above-mentioned aluminum extruded thin-walled profile has not been found in a cold medium-sized room and the like for heat exchange by gas-liquid two-phase physical change such as R12, R22, R410A, R407C, R123, HFC134A, etc. Reports on the application of air conditioning systems, refrigeration systems, air conditioning systems for refrigeration and dehumidification, heat pump heating and water cooling/heating air conditioning systems, computer cooling modules in the IT industry, cooling systems in equipment, and other heat exchange systems in other industries. Summary of the invention

The first aspect of the technical problem to be solved by the present invention is to provide a microchannel, a parallel flow, an all-aluminum flat adapted to heat exchange of a refrigerant by assembling the aluminum extruded thin-walled profile and the high-efficiency fin. Pipe welded structural heat exchanger.

The second aspect of the technical problem to be solved by the present invention is to provide an application of the above-described microchannel, parallel flow, all-aluminum flat tube welded structural heat exchanger.

A microchannel, parallel flow, all-aluminum flat tube welded structural heat exchanger according to a first aspect of the present invention, characterized in that: the heat exchange portion of the heat exchanger is a flat tube composed of an extruded aluminum thin-walled profile They are arranged in a parallel arrangement.

In a first preferred embodiment of the heat exchanger of the present invention, the flat tubes are one and are repeatedly bent back and forth in a horizontal direction to constitute a heat exchange portion of the heat exchanger.

In a second preferred embodiment of the heat exchanger of the present invention, the flat tubes are one and are repeatedly bent back and forth in a vertical direction to form a heat exchange portion of the heat exchanger.

In a third preferred embodiment of the heat exchanger according to the present invention, the plurality of flat tubes are two, and are alternately bent back and forth in a horizontal direction or a vertical direction to constitute a heat exchange portion of the heat exchanger.

In the first, second and third preferred embodiments described above, one end of the flat tube is the inlet end of the heat exchange medium, and the other end of the flat tube is the outlet end of the heat exchange medium.

In the fourth preferred embodiment of the heat exchanger of the present invention, the plurality of flat tubes are arranged in two rows at a horizontal interval in parallel; the heat exchanger of the embodiment further includes two or more flat tubes connected to each other. a first header at one end and communicating with said a second header at the other end of the two or more flat tubes.

In a fifth preferred embodiment of the heat exchanger according to the present invention, the plurality of flat tubes are two or more, and are vertically arranged in a row in a parallel manner; the heat exchanger of the embodiment further includes a plurality of flat tubes connected to the two tubes. a first header at one end and a second header connecting the other ends of the two or more tubes.

In a sixth embodiment of the heat exchanger according to the present invention, the plurality of flat tubes are two or more, and are vertically arranged in two rows in a parallel manner; the heat exchanger of the embodiment further includes an end of the first row of flat tubes. a first header, a second header connecting the other end of the first row of flat tubes, a third header connecting one end of the second row of flat tubes, and a fourth header connecting the other end of the second row of flat tubes; The first header and the third header are located in the same direction of the two rows of flat tubes and are parallel to each other and communicate according to the flow direction of the heat exchange medium, and the second header and the fourth header are located in the two rows of flat tubes. The same direction and parallel to each other and communicate according to the flow direction of the heat exchange medium.

In the seventh embodiment of the heat exchanger of the present invention, the plurality of flat tubes are two or more, and are horizontally arranged in two rows in a parallel manner; the heat exchanger of this embodiment further includes a first end connected to the first row of flat tubes. a header, a second header connecting the other end of the first row of flat tubes, a third header connecting one end of the second row of flat tubes, and a fourth header connecting the other end of the second row of flat tubes; The first header and the third header are located in the same direction of the two rows of flat tubes and are parallel to each other and communicate according to the flow direction of the heat exchange medium, and the second header and the fourth header are located in the same row of the two rows of flat tubes Directions and parallel to each other and communicate according to the flow direction of the heat exchange shield.

In the eighth embodiment of the heat exchanger of the present invention, the plurality of flat tubes are arranged in two or more horizontal or vertical intervals in parallel; the heat exchanger of this embodiment further includes a first header connected to one end of the flat tube. And a second header that connects the other end of the flat tube.

In the above embodiment, the flat tube is twisted into a spiral shape, and the spiral helix angle is less than 68.2 degrees, that is, the pitch is 2.5 times the width of the flat tube. The flat tube has a thickness of from 1.0 mm to 2.5 mm, preferably from 1.3 mm to 2.0 mm.

In the ninth embodiment of the heat exchanger of the present invention, the flat tube is two or more U-shaped flat tubes, and each U-shaped flat tube is arranged in a row in a horizontal or vertical interval in a parallel manner, and each U-shaped tube is arranged. The first collecting pipe and the second collecting pipe are respectively connected to each other at both ends of the pipe, and the first collecting pipe and the second collecting pipe are parallel to each other and communicate according to the flow direction of the heat exchange medium.

In the above-described nine-ninth embodiment, the U-shaped flat tube is twisted into a spiral shape, and the spiral helix angle is less than 68.2 degrees, that is, the pitch "2.5 times the width of the flat tube. The flat tube has a thickness of from 1.0 mm to 2.5 mm, preferably from 1.3 mm to 2.0 mm.

In the above embodiment, the inlet end and the outlet end of the heat exchange medium may be respectively disposed at the ends of the header; or may be simultaneously disposed on the tube wall of one header. When the length of the header or the outlet end of the heat exchange medium is set to be >300 mm, the inlet or outlet end of the heat exchange medium is plural, and the inlet end or phase of the adjacent two heat exchange mediums The distance between the exit ends of the adjacent two heat exchange shields is less than 150 mm and the inlet or outlet of all heat exchange media The mouth is equal to the distribution of £.

In the fourth and fifth embodiments described above, the heat exchanger is divided into an odd-circuit single-row parallel flow heat exchanger and an even-circuit single-row parallel flow heat exchanger. For an odd-circuit single-row parallel flow heat exchanger, the inlet end and the outlet end of the heat exchange medium are respectively disposed at the ends of the first header and the second header, and are diagonally distributed. In the even-circuit parallel flow heat exchanger, the inlet and outlet ends are disposed on a first header or a second header. Especially when the fifth embodiment is an odd-circuit single-row parallel flow heat exchanger, it can be used as a condenser or an evaporator, and when used as an evaporator, the inlet end of the heat exchange medium is disposed at the bottom of the heat exchanger. And the outlet end is disposed at the top of the heat exchanger; when used as a condenser, the inlet end of the heat exchange medium is disposed at the top of the heat exchanger, and the outlet end is disposed at the bottom of the heat exchanger. When the fifth embodiment is an even-circuit single-row parallel flow heat exchanger, both the inlet end and the outlet end of the heat exchange medium are located at the bottom of the heat exchanger, whether as a condenser or an evaporator.

For odd-circuit single-row parallel flow heat exchangers and even-circuit single-row parallel flow heat exchangers, when the number of circuits is more than one, the volume of each circuit is distributed according to a certain ratio, for example, for a two-circuit single-row parallel flow In the case of a heat exchanger, the volume of the first loop accounts for 80% of the total volume of the loop, and the volume of the second loop accounts for 20% of the total volume of the loop. For a three-circuit single-row parallel flow heat exchanger, the volume of the first circuit accounts for 55% of the total volume of the circuit, the volume of the second circuit accounts for 30% of the total volume of the circuit, and the volume of the third circuit accounts for 15% of the total volume of the circuit. °/. . For a four-circuit single-row parallel flow heat exchanger, the volume of the first circuit accounts for 40% of the total volume of the circuit, the volume of the second circuit accounts for 27% of the total volume of the circuit, and the volume of the third circuit accounts for 20% of the total volume of the circuit. %, the volume of the fourth circuit accounts for 13% of the total volume of the circuit. For a five-circuit single-row parallel flow heat exchanger, the volume of the first circuit accounts for 34% of the total volume of the circuit, the volume of the second circuit accounts for 24% of the total volume of the circuit, and the volume of the third circuit accounts for 18% of the total volume of the circuit. %, the volume of the fourth circuit accounts for 13% of the total volume of the circuit, and the volume of the fifth circuit accounts for 13% of the total volume of the circuit. For a six-circuit single-row parallel flow heat exchanger, the volume of the first circuit accounts for 30% of the total volume of the circuit, the volume of the second circuit accounts for 20% of the total volume of the circuit, and the volume of the third circuit accounts for 17% of the total volume of the circuit. %, the volume of the fourth circuit accounts for 14% of the total volume of the circuit, the volume of the fifth circuit accounts for 10% of the total volume of the circuit, and the volume of the sixth circuit accounts for 9% of the total volume of the circuit; A manifold or a barrier plate in the second header is separated.

In a sixth embodiment, the length of the heat exchange medium flowing axially in the first header and the third header is greater than the length of the axial flow of the heat exchange medium in the second header and the fourth header And the length of the axial flow in the first header and the third header is as long as possible, and the length of the axial flow in the second and fourth headers is as short as possible. In particular, the length of the heat exchange medium flowing axially in the first header and the third header accounts for the length of the axial flow of the heat exchange medium in the first, second, third and fourth headers 70 More than %, and the length of the axial flow of the heat exchange medium in the second header and the fourth header accounts for the axial flow length of the heat exchange medium in the first, second, third and fourth headers 30% or less. In the sixth embodiment, the first header and the third header are not directly connected to each other, and the portions between the second header and the fourth header are directly in communication with each other. Especially in this embodiment, the axial flow of the heat exchange medium is all completed in the first header and the third header, and the heat exchange medium between the first row of flat tubes and the second row of flat tubes flows. All of the holes are interconnected by the second collecting pipe and the fourth collecting pipe; the heat exchanger is divided into a plurality of circuits by the blocking plate disposed in the collecting pipe, and the circuits are connected in series. In particular, along the direction of flow of the heat exchange medium, the volume of each circuit is gradually increased, but the volume of the last circuit must not be greater than 2.5 times the volume of the first circuit. Preferably, the volume of the latter circuit is greater than 20-60% of the volume of the previous circuit. More preferably, the volume of the latter circuit is greater than 40-50% of the volume of the previous circuit.

In the sixth embodiment, the last two sections of the circuit are provided with replenishment ports for supplementing the heat exchange medium in the last two sections of the circuit, and the replenishment ports can be designed in different shapes, numbers and positions as long as they are controlled and supplemented. The amount of medium does not substantially destroy the flow rate of the original medium; wherein the heat exchange shield supplemented by the last circuit can be 15-20% of the total heat exchange medium weight.

In the sixth embodiment, the inlet end and the outlet end of the heat exchange medium are disposed on the side wall of the first header or the third header.

In the above technical solution, a plurality of orifice plates are arranged at intervals in the header, and each orifice plate has an orifice for turbulence and spraying to solve the problem of gas-liquid separation. The spacing distance between the orifice plates is less than 80 mm, preferably 50 mm.

In the above technical solution, the thickness of the flat tube is 1.0 mm to 2.5 mm, preferably 1.0 mm to 2.0 mm in a single cold condenser, and 1.6 mm to 2.5 mm in a single cold evaporator; The preferred embodiment of the indoor and outdoor heat exchangers is 1.3 mm-2.0 nim, and the preferred cross-sectional area of the single-hole flow path in the porous microchannels inside the flat tubes is preferably 0.36 mm ^{2 -} 1.00 mm ² . In the above technical solution, a warp piece is disposed between the flat tubes, wherein a window angle of 1.5 M/s-2 M/s wind speed warping sheet is 22 degrees to 45 degrees, preferably 27 degrees to 33 degrees. The pitch of 1.5M/s-2M/s wind speed warp is 2.0mm-5.0mm, and the preferred scheme in high efficiency heat exchanger is 2.2mm-2.8mm. The preferred scheme is 2.6mm-3.0 when considering both efficient heat transfer and dehumidification. Mm; The preferred solution is 3.6mm-5.0mm in refrigerated or single dehumidification or dust areas. When the above-mentioned flat tube bending tube heat exchanger is applied to a blowerless heat exchange system, a windowless design is adopted, and the pitch of the warp is equal to the height of the blade.

The above heat exchanger solves the problem of condensed water discharge by using the vertical direction of the flat pipe and the vertical design of the ground. The turbulent river jet action of the orifice plate solves the problem of gas-liquid separation, and the method of changing the loop volume is used to improve the heat exchange efficiency.

The above heat exchanger can solve the problem of gas-liquid separation caused by gravity by using the horizontal flow design of the parallel flow converter, and can solve the problem of condensed water discharge by using the parallel flow heat exchanger fin hydrophilic treatment + gravity action. In the above heat exchanger, at least one or more microchannels extending in the longitudinal direction of the flat tube are disposed in the flat tube. In the above heat exchanger, the cross-sectional shape of the header is a D-type header, which can further reduce the loss of the heat exchange medium in the header.

In order to increase the strength of the header, the reinforcing ribs are spaced apart along the length of the collecting pipe on the three side pipe walls of the D-shaped collecting pipe which are not connected to the flat pipe, and the spacing between the adjacent two reinforcing ribs is 25.4. Mm.

In the above embodiment, the surface of the flat tube is galvanized, and the thickness of the plating layer is 12-18 g/m ² .

The above microchannel, parallel flow, all-aluminum flat tube welded structural heat exchanger can be used in room air conditioners, commercial air conditioners and other professional heat exchange systems. This is especially true for air conditioning systems in rooms and similar applications, refrigeration systems, air conditioning systems for refrigeration and dehumidification, heat pump heating and water cooling/heating air conditioning systems, computer cooling modules in the IT industry, and cooling systems in equipment.

The invention adopts a microchannel flat tube to form an effective heat exchange flow passage and a heat exchange area through a curved tube, and assembles high-efficiency fins between two adjacent flat tubes after the flat tube bending tube, and forms an all-aluminum heat exchange after brazing It can withstand the pressure requirements to the maximum, the product structure is compact, the unit weight is light, the process flow is short, the manufacturing reliability is high, the cost is relatively low, and the special design can make the windward area of the product to be better than 0.2m ² for better heat exchange efficiency.杲, the performance is higher than the traditional copper tube + aluminum sheet structure 20%.

Since the above technical solution is adopted, the present invention has the following advantages over the prior art:

1. The heat exchange efficiency of the refrigerant and the inner wall of the flat tube is increased by 40%, and the flow resistance of the refrigerant in the heat exchanger is reduced by 40%.

2. The fin heat exchange efficiency on the air side is increased by 40%, and the air resistance of the air side heat exchanger is reduced by 40%.

3. The heat transfer performance of the entire heat exchanger is increased by 40%.

4. 30% less refrigerant consumption than conventional technology

5. Comparison of all-aluminum structure and copper-aluminum structure: no copper - aluminum potential difference, longer life

The invention adopts the flat tube to withstand high pressure, compact product structure, light unit weight, short process flow, high manufacturing reliability and relatively low cost. DRAWINGS

The invention will be further described in detail below with reference to the drawings and specific embodiments.

Figure 1 is a schematic view showing the structure of an outdoor unit in a conventional heat exchanger system.

Figure 2 is a schematic view showing the structure of an indoor unit in a conventional heat exchanger system.

Figure 3 is a schematic view showing the structure of a copper tube aluminum piece riser type heat exchanger in an outdoor unit in a conventional heat exchanger system.

Figure 4 is a left side view of Figure 3. Fig. 5 is a structural schematic view showing the use of a copper tube aluminum piece riser type heat exchanger in an indoor unit in a conventional heat exchanger system. Figure 6 is a schematic view showing the principle of Embodiment 1 of the heat exchanger of the present invention.

Figure 7 is a schematic view showing the principle of Embodiment 2 of the heat exchanger of the present invention.

Figure 8 is a schematic view showing the principle of Embodiment 3 of the heat exchanger of the present invention.

Fig. 9 is a thermographic image showing the performance test of the embodiment 3 of the present invention.

Figure 10 is a schematic view showing the principle of Embodiment 4 of the heat exchanger of the present invention.

Figure 11 is a schematic view showing the structure of a heat exchanger according to a fifth embodiment of the present invention.

Figure 12 is a bottom view of Figure 11.

Figure 13 is a left side view of Figure 11.

Figure 14 is a view showing the connection relationship between the flat tube and the splayed piece of Example 5.

Figure 15 is a view taken along the line A in Figure 14.

Figure 16 is a schematic view showing the structure of a heat exchanger according to a sixth embodiment of the present invention.

Figure 17 is a schematic view showing the structure of a heat exchanger according to a seventh embodiment of the present invention.

Figure 18 is a schematic view showing the structure of a heat exchanger according to a sixth embodiment of the present invention.

Figure 19 is a schematic view showing the structure of a heat exchanger according to a ninth embodiment of the present invention.

Figure 20 is a bottom view of Figure 19.

Figure 21 is a left side view of Figure 19.

Figure 22 is a schematic view showing the structure of a heat exchanger according to a tenth embodiment of the present invention.

Figure 23 is a schematic view showing the structure of a heat exchanger according to Embodiment 11 of the present invention.

Figure 24 is a plan view of Figure 23.

Figure 25 is a left side view of Figure 23.

Figure 26 is a schematic view showing the structure of a heat exchanger according to Embodiment 12 of the present invention.

Figure 27 is a schematic view showing the structure of a heat exchanger according to a thirteenth embodiment of the present invention.

Figure 28 is a bottom view of Figure 27.

Figure 29 is a left side view of Figure 27.

Figure 30 is a schematic view showing the structure of a heat exchanger according to Embodiment 14 of the present invention.

Figure 31 is a schematic view showing the structure of a heat exchanger according to a fifteenth embodiment of the present invention.

Figure 32 is a plan view of Figure 31.

Figure 33 is a left side view of Figure 31. Figure 34 is a schematic view showing the working principle of the heat exchanger according to the fifteenth embodiment of the present invention.

Figure 35 is an enlarged schematic view of the portion I of Figure 34.

Figure 36 is a thermographic image of the embodiment 15 during cooling operation.

Figure 37 is a schematic view showing the working principle of the heat exchanger of the heat exchanger of the present invention.

Figure 38 is an enlarged schematic view of the portion I of Figure 37.

Figure 39 is a thermographic image of Example 15 during heating operation.

Figure 40 is a schematic view showing the structure of a heat exchanger embodiment 16 of the present invention.

Figure 41 is a plan view of Figure 40.

Figure 42 is a left side view of Figure 40.

Figure 43 is a schematic view showing the structure of a heat exchanger according to a seventh embodiment of the present invention.

Figure 44 is a plan view of Figure 43.

Figure 45 is a left side view of Figure 43.

Figure 46 is a schematic view showing the principle of Embodiment 18 of the heat exchanger of the present invention.

Figure 47 is a schematic view showing the principle of Embodiment 19 of the heat exchanger of the present invention.

Figure 48 is a schematic view showing the principle of the embodiment 20 of the heat exchanger of the present invention.

Figure 49 is a schematic view showing the principle of Embodiment 21 of the heat exchanger of the present invention.

Figure 50 is a schematic view showing the connection relationship between a circular header and a flat tube in a conventional structure.

Figure 51 is a schematic view showing the flow resistance in a dome-shaped header in a conventional structure.

Figure 52 is a schematic view showing the connection relationship between the D-type header and the flat tube of the present invention.

Figure 53 is a schematic view showing the flow resistance in the D-type header of the present invention.

Figure 54 is a schematic view showing the structure of a D-type header of the present invention;

Figure 55 is a structural schematic view of a reinforcing rib in a D-type header of the present invention. detailed description

In order to make the technical means, the authoring features, the achievement of the object and the effect of the present invention easy to understand, the present invention will be further described below in conjunction with the embodiments.

Example 1

The microchannel, parallel flow, all-aluminum flat tube welded structure heat exchanger of this embodiment is a double-circuit single-row parallel flow heat exchanger, which is used for heating of a heat pump type indoor heat exchanger. Referring to FIG. 6, the heat exchanger includes a first header 100 and a second current collector. a tube 200 and a plurality of flat tubes ³ 00 connected between the first header 100 and the second header 200. The flat tube 300 is composed of an extruded aluminum thin-walled profile, and the thickness of the flat tube 300 is 1.3 mm-2.0 mm. .

In this embodiment, a plurality of flat tubes 300 are vertically arranged in a row in a parallel arrangement, the first header 100 is located at the top of the entire heat exchanger, and the second header 200 is at the bottom of the entire heat exchanger, the heat exchange medium The inlet end 400 is located at the left end of the first header 100, and the outlet end 500 is located at the right end of the first header 100. Blocking plates 110, 210 are respectively disposed in the first header 100 and the second header 200, and the blocking plates 110, 210 divide the entire heat exchanger into a first loop 610 and a second loop 620, and the first loop 610 The volume accounts for 80% of the total volume of the circuit, and the volume of the second circuit 620 accounts for 20% of the total volume of the circuit. . Three orifice plates 700 are disposed in the second header 200, and each orifice plate 700 has an orifice 710 for turbulence and spraying, and between each orifice plate 700 The separation distance is less than 80 mm, and the optimum is 50 mm. The working principle of this embodiment is: a heat exchange medium, such as a refrigerant entering from the inlet end 400 of the left end of the first header 100, flowing vertically through the flat tube of the first circuit 610 to the second header 200 is installed The side of the throttle J1 anti-700 is throttled by the orifice plate 700, and flows to the second header 200 without the side of the throttle 5L reverse 700, and then the flat tube of the second loop 620 is vertically upward. It flows into the first header 100 and flows out of the outlet end 500.

Example 2

The microchannel, parallel flow, all-aluminum flat tube welded structural heat exchanger of this embodiment is a dual-circuit single-row parallel flow heat exchanger, which is used for heat pump type indoor heat exchanger refrigeration. Referring to Fig. 7, the structure is the same as that of the embodiment 1, except that the inlet end 400 and the outlet end 500 of the heat exchange medium are at different positions. In this embodiment, the inlet end 400 of the heat exchange medium is located at the right end of the header manifold 100. The outlet end 500 is located at the left end of the first header 100.

The working principle of this embodiment is: heat exchange, such as heating agent from the inlet end 400 of the right end of the first header 100, and the flat tube of the second circuit 620 flowing vertically downward to the second header 200 The side of the orifice plate 700 is not installed, and flows to the side where the orifice plate 700 is attached to the second header 200. After throttling through the orifice plate 700, the manifold passing through the first return path 610 flows vertically upward into the first header 100 and exits from the outlet end 500.

Example 3

The microchannel, parallel flow, all-aluminum flat tube welded structure heat exchanger of this embodiment is a three-circuit single-row parallel flow heat exchanger, and the refrigerant flow direction is designed so that the heat pump type indoor heat exchanger is used for heating. . Referring to FIG. 8, the heat exchanger includes a first header 100, a second header 200, and a plurality of flat tubes 300 connected between the first header 100 and the second header 200. The flat tube 300 is composed of The aluminum extruded thin wall profile is composed of a flat tube 300 having a thickness of 1.3 mm to 2.0 mm.

In this embodiment, a plurality of flat tubes 300 are vertically arranged in a row in a parallel arrangement, the first header 100 is located at the top of the entire heat exchanger, and the second header 200 is at the bottom of the entire heat exchanger, the heat exchange medium The inlet end 400 is located first The left end of the header 100, the outlet end 500 is located at the right end of the second header 200, and the inlet end 400 and the outlet end 500 are diagonally distributed. Blocking plates 110, 120, 210 220 are respectively disposed in the first header 100 and the second header ²⁰⁰ , and the blocking plates 110, 120, 210, 220 divide the entire heat exchanger into the first loop 610, The second circuit 620 and the third circuit 630, the volume of the first circuit 610 accounts for 55% of the total circuit volume, the volume of the second circuit 620 accounts for 30% of the total circuit volume, and the volume of the third circuit 630 accounts for 15% of the total circuit volume. . Three orifice plates 700 are disposed in the second header 200, and each of the channels 700 has an orifice 710 for turbulence and jetting, and between each orifice plate 700 The spacing distance is less than 80 mm, preferably 50 mm. The working principle of this embodiment is: a heat exchange medium, such as a refrigerant entering from the inlet end 400 of the left end of the first header 100, flowing vertically through the flat tube of the first circuit 610 to the second header 200 is installed One side of the orifice plate 700 is throttled by the orifice plate 700, flows to the second header tube 200 without the intermediate side of the orifice plate 700, and then passes through the flat tube of the second circuit 620 vertically upward. Flowing into the first header 100, then flowing vertically downward from the flat tube of the third circuit 630 through the first header 100 to the other side of the second header 200 without the orifice plate 700 installed, The outlet end 500 flows out.

Referring to Figure 9, in this embodiment, the thermal distribution of the refrigerant inside the microchannel parallel flow heat exchanger is reasonable in each circuit, the subcooling control is effective, and the heat exchange efficiency is high.

Example 4

The microchannel, parallel flow, all-aluminum flat tube welded structure heat exchanger of this embodiment is a three-circuit single-row parallel flow heat exchanger whose refrigerant flow direction is designed to be used for heat pump type indoor heat exchanger refrigeration. Referring to FIG. 10, the heat exchanger includes a first header 100, a second header 200, and a plurality of flat tubes 300 connected between the first header and the second header 200. The flat tube 300 is composed of The aluminum extruded thin wall profile is composed of a flat tube 300 having a thickness of 1.3 mm to 2.0 mm.

In this embodiment, a plurality of flat tubes 300 are vertically arranged in a row in a parallel arrangement, the first header 100 is located at the top of the entire heat exchanger, and the second header 200 is at the bottom of the entire heat exchanger, the heat exchange medium The inlet end 400 is located at the right end of the second header 200, the outlet end 500 is located at the left end of the first header 100, and the inlet end 400 and the outlet end 500 are diagonally distributed. Blocking plates 110, 120, 210, 220 are respectively disposed in the first header 100 and the second header 200, and the blocking plates 110, 120, 210, 220 divide the entire heat exchanger into a first loop 610, The second circuit 620 and the third circuit 630, the volume of the first circuit 610 accounts for 55% of the total circuit volume, the volume of the second circuit 620 accounts for 30% of the total circuit volume, and the volume of the third circuit 630 accounts for 15% of the total circuit volume. . Three orifice plates 700 are disposed in the second header 200, and each orifice plate 700 has an orifice 710 for turbulence and spraying, and between each orifice plate 700 The spacing distance is less than 80 mm, preferably 50 mm. The working principle of this embodiment is: a heat exchange medium, such as a refrigerant entering from the inlet end 400 of the right end of the second header 200, flowing vertically upward through the flat tube of the third circuit 630 to the first header 100 Side, through the middle-side first header 100 and a second loop ⁶²⁰ flows to the second current side of the intermediate tube 200, then the refrigerant flows to the second header 200 is attached to a throttle ^ ^ One side of the reverse 700 is throttled by the orifice plate 700, and then flows vertically through the flat tube of the first circuit 610 into the first header 100, and flows out from the outlet end 500.

Example 5

The microchannel, parallel flow, all-aluminum flat tube welded structure heat exchanger of this embodiment is a double-circuit single-row parallel flow heat exchanger, which is used for cooling and heating of a heat pump type indoor heat exchanger. Referring to FIG. 11 to FIG. 13 , the heat exchanger includes a first header 100 , a second header 200 , and a plurality of flat tubes 300 connected between the first header 100 and the second header 200 . The tube 300 is composed of an extruded aluminum thin-walled profile, and the flat tube 300 has a thickness of 1.3 mm to 2.0 mm.

In this embodiment, a plurality of flat tubes 300 are vertically spaced in a row in a parallel arrangement, the first header 100 is located at the top of the entire heat exchanger, and the second header 200 is at the bottom of the entire heat exchanger, the heat exchange shield The inlet end 400 and the outlet end 500 are located on the second header 200. The second header 200 is respectively provided with a blocking plate 210. The blocking plate 210 divides the entire heat exchanger into a first circuit 610 and a second circuit. 620, the volume of the first circuit 610 accounts for 80% of the total circuit volume, and the volume of the second circuit 620 accounts for 20% of the total circuit volume.

The working principle of this embodiment is: a heat exchange medium, such as a refrigerant entering from the inlet end 400 on the left side of the second header 200, flowing vertically upward through the flat tube of the first circuit 610 to the first header 100 The side flows to the other side of the first header 100, and then flows vertically upward through the flat tube of the second circuit 620 to the other side of the second header 100, and flows out of the outlet end 500.

Referring to FIG. 14 and FIG. 15, a warping piece 800 is disposed between two adjacent flat tubes 300, and the rocking piece 800 has a serpentine folded shape, wherein the window angle of the 2M/s wind speed warping piece is 22 degrees - 45 degrees, preferably 27 degrees. -33 degrees. The pitch of the 1.5M/s-2M/s wind speed blade is 2.0 mm - 5.0 mm, preferably 2.2 mm - 3.6 mm. When the above heat exchanger is used in a blowerless heat exchange system, a windowless design is adopted, and the pitch of the warp 800 is equal to the height of the warp 800.

The flat tube 300 adopts the A ^Q design to guide the heat exchanger condensate in the direction of the wind, wherein 30 ^G A ^G 60 ^Q ; the fin window 800 window length is used to prevent the formation of condensed water, B 0.3 mm, the optimum value is 0.10-0.15mm.

Example 6

The microchannel, parallel flow, all aluminum flat tube spliced structural heat exchanger of this embodiment is a single circuit single row parallel flow heat exchanger that is used as an evaporator or condenser in a water cooling system. Referring to FIG. 16, the heat exchanger includes a first header 100, a second header 200, and a plurality of flat tubes 300 connected between the first header 100 and the second header 200. The flat tube 300 is composed of The aluminum extruded thin wall profile is composed of a flat tube 300 having a thickness of 1.6 mm to 2.0 mm.

In this embodiment, a plurality of flat tubes 300 are vertically spaced in a parallel arrangement in a row, and the first header 100 is located The top of the entire heat exchanger, the bottom of the entire heat exchanger of the second header 200. The inlet end 400 of the heat exchange medium is located at the left end of the first header 100, and the outlet end 500 is located at the right end of the second header 200. The inlet end 400 and the outlet end 500 are distributed diagonally. The flat tube 300 is twisted into a spiral shape having a spiral helix angle of 68.2 degrees or less and a pitch of 2.5 times the width of the flat tube 300.

The working principle of this embodiment is: a heat exchange shield, such as refrigerant entering from the inlet end 400 on the left side of the first header 100, flowing vertically downward through the flat tube 300 to the second header 200, from the outlet end 500 Flow out.

Example 7

The microchannel, parallel flow, all aluminum flat tube welded structural heat exchanger of this embodiment is a single circuit single row parallel flow heat exchanger that is used as an evaporator or condenser in a water cooling system. Referring to FIG. 16, the heat exchanger includes a first header 100, a second header 200, and a plurality of flat tubes 300 connected between the first header 100 and the second header 200. The flat tube 300 is composed of The aluminum extruded thin wall profile is composed of a flat tube 300 having a thickness of 1.6 mm to 2.0 mm.

In this embodiment, a plurality of flat tubes 300 are horizontally arranged in a row in a parallel manner, the first header 100 is located on one side of the entire heat exchanger, and the second header 200 is on the other side of the entire heat exchanger. The inlet end 400 of the heat exchange medium is located at the lower end of the first header 100, the outlet end 500 is located at the upper end of the second header 200, and the inlet end 400 and the outlet end 500 are distributed diagonally. The flat tube 300 is twisted into a spiral shape having a spiral helix angle of 68.2 degrees or less and a pitch of 2.5 times the width of the flat tube 300.

The working principle of this embodiment is that a heat exchange medium, such as a refrigerant, enters from the inlet end 400 of the lower end of the first header 100, flows horizontally through the flat tube 300 to the second header 200, and flows out of the outlet end 500.

Example 8

The microchannel and all-aluminum single flat tube of the embodiment form an effective refrigerant flow path and a heat exchange space through the elbow, and is welded to the high-efficiency heat exchange fin as a single-circuit single-row microchannel heat exchanger, which is single-cooled. The evaporator in the system is used. Referring to FIG. 18, the heat exchanger is repeatedly bent back and forth in a vertical direction by a flat tube 300 to form a heat exchange portion of the heat exchanger, and a warping piece 800 is disposed between the adjacent two flat tubes 300. The serpentine folded shape, with reference to Figs. 14 and 15, in which the 2M/s wind speed window angle A is 22 degrees - 45 degrees, preferably 27 degrees - 33 degrees. The pitch of the 2M/s wind speed blade is 2.0 mm - 5.0 mm, preferably 2.2 mm - 3.6 mm. When the above heat exchanger is used in a blowerless heat exchange system, the windowless design is adopted, and the pitch of the warp 800 is equal to the height of the warp 800.

One end of the flat tube 300 is the inlet end 400 of the heat exchange medium, and the other end of the flat tube 300 is the outlet end of the heat exchange medium.

500.

The working principle of this embodiment is: a heat exchange medium, such as a refrigerant entering the flat tube 300 from the inlet end 400, passing through the flat tube 300 heat exchange, flowing out of the outlet end 500.

Example 9

The microchannel, all-aluminum single flat tube welded structural heat exchanger of this embodiment is a single circuit single row heat exchanger which is used as an evaporator in a water cooling system. Referring to FIG. 19 to FIG. 21, the heat exchanger is repeatedly bent back and forth in a vertical direction by a flat tube 300 to form a heat exchange portion of the heat exchanger. One end of the flat tube 300 is an inlet end 400 of the heat exchange medium, and the flat tube The other end of 300 is the outlet end 500 of the heat exchange medium. The flat tube 300 is twisted into a spiral shape having a spiral helix angle of 68.2 degrees or less and a pitch of 2.5 times the width of the flat tube 300.

The working principle of this embodiment is that a heat exchange medium, such as refrigerant, enters the flat tube 300 from the inlet end 400, is heat exchanged through the flat tube 300, and flows out from the outlet end 500.

Example 10

The microchannel, parallel flow, all aluminum flat tube welded structural heat exchanger of this embodiment is a dual circuit single row parallel flow heat exchanger that is used as a room or commercial condenser. Referring to FIG. 22, the heat exchanger includes a first header 100, a second header 200, and a plurality of flat tubes 300 connected between the first header 100 and the second header 200. The flat tube 300 is composed of The aluminum extruded thin wall profile is composed of a flat tube 300 having a thickness of 1.0 mm to 2.0 mm.

In this embodiment, a plurality of tubes 300 are horizontally spaced in a row in a parallel arrangement, the first header 100 is located on one side of the entire heat exchanger, and the second header 200 is on the other side of the entire heat exchanger. The inlet end 400 and the outlet end 500 of the heat exchange shield are located at the upper and lower ends of the first header 100.

The working principle of this embodiment is: a heat exchange shield, such as a refrigerant entering the upper side of the first header 100 from the inlet end 400, and then flowing through the flat tube 300 of the upper portion of the entire heat exchanger to the second header 200 In the upper side, then flowing down the second header 200, the flat tube 300 passing through the lower portion of the entire heat exchanger returns to the lower side of the first header 100 and flows out from the outlet end 500.

Example 11

The microchannel and all-aluminum single flat tube of the embodiment form an effective refrigerant flow path and a heat exchange space through the elbow, and is welded to the high-efficiency heat exchange fin as a single-circuit single-row microchannel heat exchanger, which is single-cooled. The condenser in the system is used. Referring to FIG. 23 to FIG. 24, the heat exchanger is repeatedly bent back and forth in a horizontal direction by a flat tube 300 to form a heat exchange portion of the heat exchanger, and a warping piece 800 is disposed between the adjacent two flat tubes 300. The sheet 800 is in the form of a serpentine fold, with reference to Figures 14 and 15, wherein the 2M/s wind speed window angle A is 22 degrees - 45 degrees, preferably 27 degrees - 33 degrees. The pitch of the 2M/s wind speed blade is 2.0 mm - 5.0 mm, preferably 2.2 mm - 3.6 mm. When the above heat exchanger is used in a blowerless heat exchange system, a windowless design is adopted, and the pitch of the warp 800 is equal to the height of the warp 800.

One end of the flat tube 300 is the inlet end 400 of the heat exchange medium, and the other end of the flat tube 300 is the outlet end of the heat exchange shield. 500.

Example 12

The microchannel, all-aluminum single flat tube splicing structure heat exchanger of this embodiment is a single-circuit single-row heat exchanger, which is used as a condenser in a water-cooling system. Referring to FIG. 26, the heat exchanger is repeatedly bent back and forth in a horizontal direction by a flat tube 300 to form a heat exchange portion of the heat exchanger. One end of the flat tube 300 is an inlet end 400 of the heat exchange medium, and the flat tube 300 is another. One end is the outlet end 500 of the heat exchange medium. The flat tube 300 is twisted into a spiral shape having a spiral helix angle of 68.2 degrees or less and a pitch of 2.5 times the width of the flat tube 300.

Example 13

The microchannel, all-aluminum flat tube welded structural heat exchanger of this embodiment is a parallel-connected single-circuit single-row heat exchanger, which is used as an evaporator. Referring to FIG. 27 to FIG. 29, the heat exchanger is composed of two flat tubes 300 which are bent back and forth in multiple parallel and vertical directions to form a heat exchange portion of the heat exchanger, and a warp sheet is disposed between the adjacent two flat tubes 300. 800, the warp piece 800 has a serpentine folded shape, with reference to Figs. 14 and 15, wherein the 2M/s wind speed warping window angle A is 22 degrees - 45 degrees, preferably 27 degrees - 33 degrees. The pitch of the 2M7s wind speed warp sheet is 2.0 mm - 5.0 mm, preferably 2.2 mm - 3.6 mm. When the above heat exchanger is used in a blowerless heat exchange system, the windowless design is used, and the pitch of the warp 800 is equal to the height of the warp 800. One end of the two flat tubes 300 is joined as the inlet end 400 of the heat exchange medium, and the other end of the two flat tubes 300 is joined as the outlet end 500 of the heat exchange medium.

The working principle of this embodiment is that a heat exchange medium, such as a refrigerant, enters two flat tubes 300 from the inlet end 400, is heat exchanged through the two flat tubes 300, and flows out from the outlet end 500.

Example 14

The microchannel, all-aluminum flat tube welded structural heat exchanger of this embodiment is a co-parallel single-circuit single-row heat exchanger, which is used as a condenser. Referring to FIG. 30, the heat exchanger is formed by two flat tubes 300 which are mutually parallel and horizontally bent back and forth to form a heat exchange portion of the heat exchanger, and a warping piece 800 is disposed between the adjacent two flat tubes 300. The sheet 800 is in the form of a serpentine fold, with reference to Figures 14 and 15, wherein the 2M/s wind speed window angle A is 22 degrees - 45 degrees, preferably 27 degrees - 33 degrees. The 2M/s wind speed blade pitch H is 2.0 mm to 5.0 mm, preferably 2.2 mm to 3.6 mm. When the above heat exchanger is applied to a blowerless heat exchange system, a windowless design is adopted, and the pitch 800 of the slab is equal to the height of the sheet 800. One end of the two flat tubes 300 is joined as the inlet end 400 of the heat exchange medium, and the other end of the two flat tubes 300 is joined as the outlet end 500 of the heat exchange medium.

Example 15

The microchannel, parallel flow, all aluminum flat tube welded structural heat exchanger of this embodiment is a double row double exchange parallel flow heat exchanger which is used as a heat pump type evaporator or condenser. Referring to FIG. 31 to FIG. 33, the heat exchanger includes a first header 100, a second header 200, a third header 100a, a fourth header 200a, and a plurality of flat tubes 300. Aluminum extruded thin-walled profile, the thickness of the flat tube 300 is preferably 1.3mm-2.0mm in the heat pump type heat exchanger, and the preferred solution for the single-hole flow path in the porous microchannel inside the flat tube is 0.36mm. ² -1.00mm ² . The plurality of flat tubes 300 are vertically spaced in a parallel arrangement in two rows, the upper end of the row of flat tubes 300 is in communication with the first header 100, and the lower end of the first row of tubes 300 is in communication with the second header 200. The upper end of the second row of flat tubes 300 is in communication with the third header tube 100a, the lower end of the second row of flat tubes 300 is in communication with the fourth header tube 200a, and the first header tube 100 and the third header tube 100a are located in two rows of flat tubes. The tubes 300 are in the same direction and parallel to each other and are located at the top of the entire heat exchanger, and the two do not communicate directly, but communicate through the flat tubes 300 according to the flow direction of the heat exchange medium. The first header tube 200 and the fourth header tube 200a are located in the same direction of the two rows of the flat tubes 300 and are parallel to each other, and are located at the bottom of the entire heat exchanger, and communicate directly according to the flow direction of the heat exchange medium.

A warping piece 800 is disposed between the adjacent two flat tubes 300, and the rocking piece 800 has a serpentine folded shape. Referring to FIG. 14 and FIG. 15, wherein the wind angle of the 1.5M/s-2M/s wind speed window is 22 degrees. -45 degrees, preferably 27 degrees - 33 degrees. The pitch of the 2M/s wind speed is 2.0mm-5.0mm, and the preferred scheme in the high-efficiency heat exchanger is 2.2mm-2.8mm. The preferred solution is 2.6mm-3.0mm when considering both efficient heat exchange and dehumidification; The preferred solution for refrigeration or single dehumidification or dust areas is 3.6 mm to 5.0 mm. When the above heat exchanger is used in a blowerless heat exchange system, the windowless design is adopted, and the pitch of the warp 800 is equal to the height of the warp 800.

Referring to Figures 34 and 35, when the heat exchanger of this embodiment is applied to a refrigeration application, the inlet end 400 of the heat exchange medium is two, disposed on the right side of the first header 100. The heat exchange medium has three outlet ends 500, which are arranged on the left side of the first header 100 and are equidistantly distributed. A blocking plate 110 is disposed between the right side and the left side of the first header 100, and a orifice plate 700 is disposed between the right side and the left side of the second collecting tube 200, and the orifice plate 700 is disposed on the orifice plate 700. There is an orifice 710, and a blocking plate 210a is disposed between the left side and the right side of the fourth header 200a. The blocking plate 210a, the orifice plate 700, and the blocking plate 110 are located on the same plane. The right side of the second header 200 is in direct communication with the right side of the fourth header 200a, such as through a small hole (not shown), and the left and fourth currents of the second header 200 The left side of the tube 200a is directly connected, Directly connected through small holes (not shown). When cooling, the working principle of this embodiment is: the heat exchange medium enters the right side of the first header 100 from the two inlet ends 400, and then flows down the part of the flat tube 300 to the right of the second header 200. On the side, a part of the liquid phase flowing into the right side of the second header 200 flows into the left side of the second header 200 through the orifice 710 on the orifice plate 700 to balance the left side of the second header 200. The gas-liquid two phases, the other portion of the liquid phase flow laterally to the right side of the fourth header 200a. The liquid phase entering the right side of the fourth header 200a flows upward along a portion of the flat tube 300 to the right side of the third header 100a, and the liquid phase entering the right side of the third header 100a passes through the third header. 100a flows axially to the left side of the third header 100a, and then flows down the part of the flat tube 300 to the left side of the fourth header 200a, at which time the heat exchange medium flowing to the left side of the fourth header 200a It is already a gas-liquid two phase, because the gas-liquid two phases are not easy to stratify due to gravity. The gas-liquid two phases then flow laterally into the left side of the second header 200, mixed with the liquid phase passing through the orifice plate 700, and then flowed upward along the portion to the left side of the first header 100. And then flow out from the three outlet ends 500. Since the orifice plate 700 is disposed in the second header 200, the degree of superheat of the entire heat exchanger is small relative to the prior art (see FIG. 36), and is only close to the outlet end 500-small. The block area enables efficient conversion of energy in the parallel flow heat exchanger in the system.

Referring to Figures 37 and 38, when the heat exchanger of this embodiment is applied to a heating environment, the heat exchange medium has three inlet ends 400 which are disposed on the left side of the first header 100 and are equidistantly distributed. The outlet end 500 of the heat exchange medium is two, disposed on the right side of the first header 100. A blocking plate 110 is disposed between the right side and the left side of the first collecting pipe 100, and a orifice plate 700 is disposed between the right side and the left side of the second collecting pipe 200, and the orifice plate 700 is disposed on the orifice plate 700. There is an orifice 710, and a blocking plate 210a is disposed between the left side and the right side of the fourth header 200a. The blocking plate 210a, the orifice plate 700, and the blocking plate 110 are located on the same plane. The right side of the second header 200 is in direct communication with the right side of the fourth header 200a, such as through a small hole (not shown), and the left and fourth currents of the second header 200 The left side of the tube 200a is in direct communication, such as through a small aperture (not shown). When heating, the working principle of this embodiment is: the heat exchange medium enters the left side of the first header 100 from the three inlet ends 400, and then flows down the part of the flat tube 300 to the second header 200. On the left side, a part of the gas phase flowing into the right side of the second header 200 flows into the right side of the second header 200 through the orifice 710 on the orifice plate 700 to balance the right side of the second header 200. The gas-liquid two phases, and the other portion of the gas phase flow laterally to the left side of the fourth header 200a. The gas phase entering the left side of the fourth header 200a flows upward along the part of the flat tube 300 to the left side of the third header 100a, and the gas phase entering the left side of the third header 100a passes through the third header 100a. Flowing to the right side of the third header 100a, then flowing down the part of the flat tube 300 to the right side of the fourth header 200a, at which time the heat exchange medium flowing to the left side of the fourth header 200a is already Gas-liquid two phases, because of the gravity, the gas-liquid two phases are not easy to stratify. The gas-liquid two phases then flow laterally into the right side of the second header 200, mixing with the gas phase passing through the orifice plate 700. After that, a part of the flat tube flows upward to the right side of the first header 100, and then flows out from the two outlet ends ⁵⁰⁰ . Since the orifice plate 700 is disposed in the second header 200, the degree of supercooling of the entire heat exchanger is small relative to the prior art (see FIG. 37), and only close to the outlet end 500. In the small area, the energy conversion of the parallel flow heat exchanger in the system is realized.

The heat exchanger can also be placed horizontally: the plane composed of the collecting pipe, the flat pipe and the fin is placed parallel to the ground during system installation, and the design solves the problem of gas-liquid separation caused by gravity in the heat exchanger, and Parallel flow heat exchanger fins hydrophilic treatment + condensate self gravity can be used to solve the problem of condensed water discharge.

Example 16

The microchannel, parallel flow, all aluminum flat tube welded structural heat exchanger of this embodiment is a silent double exchange parallel flow heat exchanger, which is used as an evaporator. Referring to Figures 40 to 41, the heat exchanger includes a first header 100, a second header 200, and a plurality of flat tubes 300 having a thickness of 1.6 mm to 2.0 mm. Each flat tube 300 is bent into a U shape, and each U-shaped flat tube is vertically arranged in a row in a parallel manner. > Both ends of each U-shaped flat tube are respectively a first header 100 and a second header 200 In communication, the first header 100 and the second header 200 are parallel to each other and are positioned at the top of the entire heat exchanger. The first header 100 and the second header 200 are not in direct communication, but are communicated by the flat tube 300 in accordance with the flow direction of the heat exchange medium. A warping piece 800 is disposed between the adjacent two flat tubes 300, and the rocking piece 800 has a serpentine folding shape. Referring to FIG. 14 and FIG. 15, wherein the 2M/s wind speed chopping window angle A is 22 degrees to 45 degrees, preferably It is 27 degrees - 33 degrees. The pitch of the 2M/s wind speed blade is 2.0 mm - 5.0 mm, preferably 2.2 mm - 3.6 mm. When the above heat exchanger is used in a blowerless heat exchange system, a windowless design is adopted, and the pitch of the warp 800 is equal to the height of the warp 800. An inlet end 400 and an outlet end 500 of the heat exchange medium are disposed on the first header 100 at intervals.

The heat exchanger of this embodiment works as follows: The heat exchange medium enters the left side of the first header 100 from the inlet end 400, and flows into the second header 200 from the flat tube 300 on the left side of the entire heat exchanger. On the left side; the heat exchange medium flowing into the second header 200 flows axially along the second header 200 to the right side of the second header 200, and then passes through the flat tube 300 on the right side of the entire heat exchanger. It flows into the right side of the first header 100 and exits from the outlet end 500. '

Example 17

The heat exchanger structure of this embodiment is substantially the same as that of the embodiment 16, referring to Figs. 43 to 45, except that the flat tube 300 is twisted into a spiral shape, the spiral helix angle is equal to or greater than 68.2 degrees, and the width of the pitch flat tube 300 is 2.5. Times. There is no sheet 800 between the adjacent two flat tubes 300.

Example 18

The microchannel, parallel flow, all aluminum flat tube welded structural heat exchanger of this embodiment is a silent double exchange parallel flow heat exchanger, It is used as an evaporator or condenser. Referring to Figure 46, the heat exchanger includes a first manifold 100, second manifold ^200, third header 100a, 200a and a plurality of fourth header root flat tubes 300, ³⁰⁰ by a flat aluminum tube The extruded thin-walled profile is constructed, and the thickness of the flat tube 300 is 1.6 mm - 2.5 n. The plurality of fan tubes 300 are vertically arranged in two rows in a parallel manner. The upper end of the row of flat tubes 300 is in communication with the first header tube 100, and the lower end of the row of flat tubes 300 is connected to the second header tube 200. The upper end of the second row of flat tubes 300 is in communication with the third header tube 100a, the lower end of the second row of flat tubes 300 is in communication with the fourth header tube 200a, and the first header tube 100 and the third header tube 100a are located in two rows of flat tubes. The tubes 300 are in the same direction and parallel to each other, and are located at the top of the entire heat exchanger. The second header 200 and the fourth header 200a are located in the same direction of the two rows of the flat tubes 300 and are parallel to each other, and are located at the bottom of the entire heat exchanger. . The outlet end is disposed at one end of the third header 100a, and the inlet end 400 and the outlet end 500 are located on the same side of the entire heat exchanger. Blocking plates 110, 110a are respectively disposed in the middle of the first header 100 and the third header 100a, and an inlet end 400 of the heat exchange medium is disposed at one end of the first header 100, the blocking plate 110, 110a divides the flow path of the entire heat exchanger into a first circuit 610, a second circuit 620, a third circuit 630, and a fourth circuit 640. The first header 100 and the third header 100a are away from the inlet end 400 and the outlet. One side of the end 500 is directly communicated through the small hole 900, and the second header 200 is not in direct communication with the fourth header 200a.

The working principle of this embodiment is: the heat exchange medium enters the first header 100 near the inlet end 400 through the inlet end 400, and the heat exchange medium will follow the first loop 610 due to the action of the blocking plate 110. The tube 300 flows downward into the side of the second manifold 200. The heat exchange medium flowing into the side of the second header 200 flows axially along the second header 200 to the other side of the second header 200, and then flows upward through the flat tube 300 in the second circuit 620. The first header 100 is located away from the inlet end 400 side. The heat exchange medium flowing into the first header 100 away from the inlet end 400 flows through the small hole 900 into the third header 100a away from the outlet end 500 side, and enters the third current collection due to the blocking of the blocking plate 110a. The heat exchange medium in the side of the tube 100a away from the outlet end 500 flows downward into the side of the fourth header 200a along the flat tube 300 in the third circuit 630, and flows into the heat in the side of the fourth header 200a. The exchange medium flows axially along the fourth header (200a) to the other side of the fourth header 200a, and then flows upward through the flat tube 300 in the fourth circuit 640 to the third header 100a near the outlet end 400. Inside the side, it flows out through the outlet end 400.

Example 19

The £channel, parallel flow, all-aluminum flat tube welded structural heat exchanger of this embodiment is a double row double exchange parallel flow heat exchanger that is used as an evaporator or condenser. Referring to FIG. 47, the heat exchanger of this embodiment includes a first header 100, a second header 200, The third header 100a, the fourth header 200a, and the thousands of tubes 300 are formed of an extruded aluminum thin-walled profile, and the thickness of the flat tube 300 is 1.6 mm to 2.0 mm. The plurality of flat tubes 300 are vertically arranged in two rows in a parallel manner. The upper end of the first row of flat tubes 300 is in communication with the first header tube 100, and the lower end of the first row of flat tubes 300 is connected to the second header tube 200. two rows of flat tubes communicating an upper end 300 of the third header 100a, and the lower end of the second flat tube row the fourth header 300 ² 00a communicates the first header and the third header 100 located in two rows 100a The flat tubes 300 are in the same direction and parallel to each other, and are located at the top of the entire heat exchanger. The second headers 200 and the fourth headers 200a are located in the same direction of the two rows of the flat tubes 300 and are parallel to each other, and are located in the entire heat exchanger. bottom. The outlet end is disposed at one end of the third header 100a, and the inlet end 400 and the outlet end 500 are located on the same side of the entire heat exchanger. Blocking plates 110, 110a are respectively disposed in the middle of the first header 100 and the third header 100a, and an inlet end 400 of the heat exchange medium is disposed at one end of the first header 100, the blocking plate 110, 110a divides the flow path of the entire heat exchanger into a first circuit 610, a second circuit 620, a third circuit 630, and a fourth circuit 640. The first header 100 and the third header 100a are away from the inlet end 400, One side of the outlet end 500 is directly communicated through the small hole 900, and the second header 200 is not in direct communication with the fourth header 200a. Three orifice plates 700 are disposed in the second header 200 and the fourth header 200a, and an orifice 710 is disposed in each orifice plate 700.

The working principle of this embodiment is: the heat exchange medium enters the first header 100 near the inlet end 400 through the inlet end 400, and the heat exchange medium will follow the first loop 610 due to the action of the blocking plate 110. The tube 300 flows downward into the side of the second header 200. The heat exchange medium flowing into the side of the second header 200 is axially along the second header 200, and is throttled by the three orifice plates 700 in the second header 200 to flow to the second set. The other side of the flow tube 200 then flows upward through the flat tube 300 in the second circuit 620 to the side of the first header 100 away from the inlet end 400. The heat exchange medium flowing into the side of the first header 100 away from the inlet end 400 flows through the small hole 900 into the side of the third header 100a away from the outlet end 500, and enters the third current collection due to the blocking of the blocking plate 110a. The heat exchange medium in the side of the tube 100a away from the outlet end 500 flows downward into the side of the fourth header 200a along the flat tube 300 in the third circuit 630, and flows into the heat in the side of the fourth header 200a. The exchange medium flows along the axial direction of the fourth header 200a, and is throttled by the three orifice plates 700 in the fourth header 200a, and then flows into the other side of the fourth header 200a, and then passes through the fourth The flat tube 300 in the circuit 640 flows upward into the side of the third header (100a) near the outlet end 400, and flows out through the outlet end 400.

Example 20

The microchannel, parallel flow, all aluminum flat tube welded structural heat exchanger of this embodiment is a double row double exchange parallel flow heat exchanger, It is used as an evaporator or condenser. Referring to FIG. 48, the heat exchanger includes a first header, a second header 200, a third header 100a, a fourth header 200a, and a plurality of flat tubes 300. The flat tubes 300 are made of aluminum. The thin-walled profile is extruded, and the thickness of the flat tube 300 is 1.6 mm - 2.5 n) m. The plurality of flat tubes 300 are vertically spaced in a parallel arrangement in two rows, the upper end of the row of flat tubes 300 is in communication with the first header 100, and the lower end of the first row of tubes 300 is in communication with the second header 200. two rows of flat pipe 300 communicates an upper end of third header 100a, and the lower end of the second flat tube row the fourth header 300 ² 00a communicates the first header and the third header 100 located in two rows 100a The flat tubes 300 are in the same direction and parallel to each other, and are located at the top of the entire heat exchanger. The second headers 200 and the fourth headers 200a are located in the same direction of the two rows of the flat tubes 300 and are parallel to each other, and are located in the entire heat exchanger. bottom.

The first header tube 100 and the third header tube 100a are not directly connected to each other, and the second header tube 200 and the fourth header tube 200a are directly in direct communication with each other, such that the first header tube 100, the second The header 200, the third header 100a, the fourth header 200a, and the flat tube 300 constitute the entire heat exchange flow path of this embodiment. The heat exchange interface of the entire heat exchange passage: the inlet end 400 and the outlet end 500 are disposed on the side wall of the first header 100.

A blocking plate 110 and 210 are disposed in each of the first header 100 and the second header 200, wherein the blocking plates 110 and 210 are flat tubes between the first header 100 and the second header 200 The 300 is divided into an N1 exhaust passage and a 2+N3 exhaust passage, and the blocking plates 110 and 210 are located on the same plane.

A blocking plate 210a is disposed in the fourth header 210a, and an orifice plate 700 is disposed in the third header 110a, wherein the blocking plate 210a and the orifice plate 700 will be the third header 100a, The flat tube 300 between the fourth headers 200a is divided into N1+N2 drains and N3 drains. The N1 drain channel in the second header 200 and the N1+N2 drain channel in the fourth header 210a communicate through the small hole 910 between the second header 200 and the fourth header 210a. The N2+N3 discharge channel in the second header 200 and the N3 discharge channel in the fourth header 210a communicate through the small hole 920 between the second header 200 and the fourth header 210a, first The manifold 300 of the N1 exhaust channel between the header 100 and the second header 200 constitutes a first loop 610, and the N1+N2 drain of the third header 100a and the fourth header 200a is flattened. The tube 300 constitutes a second circuit 620, and the flat tube 300 of the N3 discharge channel between the third header 100a and the fourth header 200a constitutes a third circuit 630, the first header 100 and the second header 200 The flat tube 300 between the N2+N3 drains constitutes a fourth loop 640.

The flow direction of the refrigerant in the entire flow channel is: entering the N1 discharge channel of the first header 100 from the inlet end 400, flowing down the flat tube 130 of the first circuit to the N1 discharge channel of the second header 200 Then, the small hole 910 flows into the N1+N2 discharge channel of the fourth header 200a laterally, and then rises along the flat tube 300 of the second circuit to the N1+N2 discharge channel of the third header 100a. The refrigerant entering the N1+N2 discharge passage of the third header 100a flows through the orifice plate 700 in the axial direction of the third header 100a to the N3 discharge passage of the third header 100a, and then Flat tube of the third circuit 630 300 is lowered into the N3 chute of the fourth header 200a. Then, it flows laterally into the N2+N3 discharge channel of the second header 200 through the small hole 920. The N2+N3 discharge passage that flows into the second header 200 rises along the flat tube 300 in the fourth circuit 640 to the N2+N3 discharge passage of the first header 100, and flows out from the outlet end 500.

The entire refrigerant passes through four circuits in the flow process, namely, the first circuit ⁶ 10, the second circuit ⁶² 0 , the third circuit 6 ³ 0 , and the fourth circuit 640 . During the flow of the refrigerant, the volume of the four circuits is gradually increased, that is, the volume of each flow channel is: First circuit 610 <Second circuit 620 < Third circuit 630 < Fourth circuit ⁶⁴ 0, Second circuit The volume of ⁶² 0 is greater than 40-50% of the volume of the first circuit 610, the volume of the third circuit 630 is greater than 40-50% of the volume of the second circuit 620, and the volume of the fourth circuit 640 is greater than 40-50 of the volume of the third circuit 630. %, the volume of the fourth loop 640 is 2.5 times the volume of the first loop 610.

As can be seen from Fig. 48, the length of the refrigerant flowing axially along the fourth header 200a in the fourth header 200a is at most N1 + N2, and the length of the axial flow in the third header 110a. For N2+N3, since the length of N3 is greater than N1, the length of the refrigerant flowing axially along the third header 100a in the third header 100a is greater than the axial direction of the fourth header 200a along the fourth header 200a. The length of the flow.

When disposed, the length of the refrigerant flowing axially in the third header 110a may be as long as possible, occupying the refrigerant along the first header 100 along the first header 100 and the third header 100a. The length of the axial flow of the third header 100a and the length of the axial flow of the second header and the fourth header 200a along the second header 200 and the fourth header 200a are 70 %, while the length of the fourth collector pipe 200a flowing axially along the fourth header 200a is only likely to be short, accounting for the refrigerant along the first header 100 and the third header 100a along the first header The length of the axial flow of the 100 and the third header 100a is the sum of the lengths of the second header 200 and the fourth header 200a flowing axially along the second header 200 and the fourth header 200a. 30%.

Example 21

The microchannel, parallel flow, all aluminum flat tube splicing structure heat exchanger of this embodiment is a double row double exchange parallel flow heat exchanger which is used as an evaporator or a condenser. Referring to FIG. 49, the heat exchanger includes a first header 100, a second header 200, a third header 100a, a fourth header 200a, and a plurality of flat tubes 300. The flat tubes 300 are extruded from aluminum. The thin wall profile is formed, and the thickness of the flat tube 300 is 1.6 mm to 2.5 mm. The plurality of flat tubes 300 are vertically arranged in two rows in a parallel manner. The upper end of the first row of flat tubes 300 is in communication with the first header tube 100, and the lower end of the first row of flat tubes 300 is connected to the second header tube 200. Two The upper end of the flattening tube 300 is in communication with the third header 100a, the lower end of the second row of flat tubes 300 is in communication with the fourth header 200a, and the first header 100 and the third header 100a are located in two rows of flat tubes The same direction of 300 and parallel to each other, located at the top of the entire heat exchanger, the second header 200 and the fourth header 200a are located in the same direction of the two rows of flat tubes 300 and are parallel to each other, at the bottom of the entire heat exchanger.

The first header 100 and the third header 100a are not in direct communication, and the second header 200 and the fourth header 200a are directly in direct communication with each other, such that the first header 100, the second The header 200, the third header 100a, the fourth header 200a, and the flat tube 300 constitute the entire heat exchange flow path of this embodiment. The inlet end 400 of the heat exchange medium of the entire heat exchange passage is disposed at one end of the third header 100a, and the outlet end 500 is disposed at one end of the first header 100.

Two blocking plates 210 and 220 are disposed in the second header 200. The two blocking plates 210 and 220 divide the second collecting tube 200 into N1 exhaust channels, N2 exhaust channels, and N3+N4 drains. In the first header 100, a blocking plate 110 and an orifice plate 700 are disposed. The blocking plate 110 and the orifice plate 700 divide the first header 100 into N1 rows and N2 rows. The runner and the N3+N4 drain.

Two blocking plates 210 and 220 are disposed in the fourth header 200a. The two blocking plates 210 and 220 divide the fourth header 200a into N1 exhaust channels, N2+N3 exhaust channels, and N4 drains. A third blocking tube 100a is provided with a blocking plate 110a and an orifice plate 700. The blocking plate 110a and the orifice plate 700 divide the third header 100a into N1 exhaust channels, N2+. N3 exhaust channel, N4 drain channel. The draft tube 410 is inserted into the third header 100a, the inlet is connected to the inlet end 400, and the outlet is located in the N1 discharge channel in the third header 100a.

The N1 exhaust channel in the second header 200 communicates with the N1 exhaust channel in the fourth header 200a through the small hole 910 between the second header 200 and the fourth header 200a. The N2 discharge channel in the second header 200 communicates with the N2+N3 discharge channel in the fourth header 200a through the small hole 920 between the second header 200 and the fourth header 200a, second The N3+N4 discharge passages in the header 200 and the N4 discharge passages in the fourth header 200a communicate through the small holes 930 between the second headers 200 and the fourth headers 200a.

The flat tube 300 of the N1 discharge channel between the third header tube 100a and the fourth header tube 200a constitutes a first loop 610, and the flattening of the N1 drain channel between the second header tube 200 and the first header tube 100 The tube 300 constitutes a second circuit 620, and the flat tube 300 of the N2 discharge channel between the first header 100 and the second header 200 constitutes a third circuit 630, a fourth header 200a and a third header 100a The flat tube 300 between the N2+N3 discharge passages constitutes a fourth circuit 640, and the flat tube 300 of the N4 discharge channel between the third header tube 100a and the fourth header tube 200a constitutes a fifth circuit 650, the second current collection The flat tube 300 of the N4 discharge passage between the tube 200 and the first header 100 constitutes a sixth loop 660. The flow direction of the refrigerant in the entire flow path is: from the inlet end 400 into the draft tube 410, from the draft tube 410 into the N1 discharge channel of the third header 100a, along the flat tube of the first circuit 610 2 ³ 0 flows down to the N1 discharge channel of the fourth header ² 00a, and then flows into the N1 discharge channel of the second header 200 laterally from the small hole 122, and then rises along the flat tube 130 of the second circuit 620. To the N1 exhaust channel of the first header 100. The refrigerant entering the N1 discharge passage of the first header 100 flows axially along the first header 100, and flows through the orifice plate 700 to the N ² discharge passage of the first header 100.

The refrigerant flowing into the N2 discharge channel of the first header 100 flows along the flat tube 300 of the third circuit 630 to the N2 discharge channel of the second header 200, and then flows laterally from the small hole 123 to the fourth set. The flow tube 200a is in the N2+N3 discharge channel. The refrigerant entering the N2+N3 discharge passage of the fourth header 200a flows upward along the flat tube 300 of the fourth circuit 640 to the N2+N3 discharge passage of the third header 100a.

The refrigerant entering the N2+N3 discharge channel of the third header 100a flows along the axial direction of the third header 100a, flows through the orifice plate 700 to the N4 discharge channel of the third header 100a, and then The flat tube 300 of the fifth circuit 650 flows down into the N4 discharge channel of the fourth header 200a. The refrigerant entering the N4 discharge passage of the fourth header (200a) flows laterally into the N4 discharge passage of the second header 200 through the small hole 935, and then rises to the first current along the flat tube 300 of the sixth circuit 660. The N3+N4 discharge channel of the tube 100 flows out of the outlet end 500.

The entire refrigerant passes through six circuits in the flow process, that is, the first circuit 610, the second circuit 620, the third circuit 630, the fourth circuit 640, the fifth circuit 650, and the six circuit 660, the refrigerant is in the process of flowing, The volume of the first loop 610 to the sixth loop 660 is gradually increased, that is, the volume of each loop is: 笫 first loop 610 <second loop 620 <third loop 630 < fourth loop 640 < fifth loop 650 < sixth In loop 660, the volume of the second loop 620 is greater than 40-50% of the volume of the first loop 610, the volume of the third loop 630 is greater than 40-50% of the volume of the second loop 620, and the volume of the fourth loop 640 is greater than the third loop 630. 40-50% of the volume, the volume of the fifth circuit 650 is greater than 40-50% of the volume of the fourth circuit 640, the volume of the sixth circuit 660 is greater than 40-50% of the volume of the fifth circuit 650, and the volume of the sixth circuit 660 is The first loop 610 is 2.5 times the volume.

As can be seen from Fig. 49, the refrigerant has almost no axial flow in the fourth header 200a and the second header 200, and in the third header 100a along the third header 100a. The length of the flow direction is N4+N3+N2+N1+N2+N3+N4, and the length of the axial flow along the first header 100 in the first header 100 is N1+N2+N4, and thus is much larger than The length of the refrigerant flowing axially in the fourth header 200a and in the second header 200.

At the time of setting, the length of the refrigerant flowing in the axial direction of the third header 100a along the third header 100a can be made and The length of a header 100 flowing axially along the first header 100 is as long as possible, accounting for the refrigerant in the first header 100 and the third header 100a along the first header 100 and the third set The length of the axial flow of the flow tube 100a is 70% of the sum of the lengths of the second collector tube 200 and the fourth header 200a flowing axially along the second header 200 and the fourth header 200a. The length of the second header tube 200 and the fourth header tube 200a flowing axially along the second header tube 200 and the fourth header tube 200a is only likely to be short, accounting for the refrigerant in the first header 100 and the third The length of the header 100a flowing along the first header 100 and the third header 100a and the second header and the fourth header 200 and the fourth header 200a along the second header 200 and the fourth current collector 200a The tube 200a has a length of 30% or less of the axial flow.

In order to prevent the overheating phenomenon, a hole is formed in the section of the N3 exhaust channel and the N4 exhaust channel in the third header 100a, and the hole is passed through the hole to the N3 channel in the third header 100a. The refrigerant is replenished with the four-row flow passage, wherein the refrigerant supplemented to the N4 discharge passage accounts for 15-20% of the total refrigerant.

The heat exchanger can also be placed horizontally: the plane composed of the collecting pipe, the flat pipe and the fin is placed parallel to the ground during system installation. The design solves the problem of gas-liquid separation caused by gravity in the heat exchanger. The parallel flow heat exchanger fin hydrophilic treatment + condensed water gravity can be used to solve the problem of condensed water discharge.

Referring to Fig. 50, the existing header a is a circular tube structure, and when connected to the flat tube 300, the flow resistance is large (see Fig. 51). However, the header used in the above embodiment of the present invention is a D-type header b, and when connected to the flat tube 300, the loss of the heat exchange medium in the header can be further reduced (see Fig. 53).

Referring to FIG. 54 and FIG. 55, in order to increase the strength of the collecting pipe, a reinforcing rib bl is disposed along the length of the collecting pipe on the three side pipe walls of the D-shaped header b which are not connected to the flat pipe, and two adjacent ribs are adjacent. The distance between the ribs bl is 25.4 mm, the rib bl is a semi-circular concave rib, the depth is lmm, and the radius is Rl.

The flat tubes in the specific embodiment are all galvanized, and the thickness of the galvanized layer is 12-18 g/m ² , which can extend the service life of the flat tubes.

The basic principles and main features of the present invention and the advantages of the present invention are shown and described above. It should be understood by those skilled in the art that the present invention is not limited by the foregoing embodiments, and that the present invention is only described in the foregoing embodiments and the description of the present invention, without departing from the spirit and scope of the invention. Various changes and modifications are intended to fall within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and their equivalents.

Claims

Rights request

A microchannel, parallel flow, all-aluminum flat tube welded structural heat exchanger, characterized in that the heat exchange portion of the heat exchanger is formed by a flat tube composed of an extruded aluminum thin wall profile arranged in parallel.

The heat exchanger according to claim 1, wherein the flat tubes are one and are bent back and forth in a horizontal direction to form a heat exchange portion of the heat exchanger.

The heat exchanger according to claim 1, wherein the flat tubes are one and are bent back and forth in a plurality of directions in a vertical direction to constitute a heat exchange portion of the heat exchanger.

The heat exchanger according to claim 1, wherein the plurality of flat tubes are two, and are alternately bent back and forth in a horizontal direction to form a heat exchange portion of the heat exchanger.

The heat exchanger according to claim 1, wherein the two flat tubes are two, and are repeatedly bent back and forth in parallel with each other in a vertical direction to constitute a heat exchange portion of the heat exchanger.

The heat exchanger according to claim 1, wherein the plurality of flat tubes are two or more, arranged horizontally in a row in a parallel manner; and further comprising a first set connecting one ends of the two or more flat tubes a flow tube and a second header connecting the other ends of the two or more flat tubes.

The heat exchanger according to claim 1, wherein the plurality of flat tubes are two or more, arranged vertically in a row in a parallel manner, and further comprising a first end connecting the ends of the flat tubes above the two tubes a header and a second header connecting the other ends of the two or more flat tubes.

The heat exchanger according to claim 1, wherein the plurality of flat tubes are two or more, and are vertically arranged in a parallel arrangement in two rows, and the heat exchangers can be arranged vertically or horizontally or It is placed at an angle of 15 ^Q ~ 25 ^G with the horizontal; it also includes a first header connecting one end of the first row of flat tubes, a second header connecting the other end of the row of flat tubes, and one end of the second row of flat tubes a third header, a fourth header connected to the other end of the second row of flat tubes; wherein the first header and the third header are located in the same direction of the two rows of flat tubes and are parallel to each other and according to the heat exchange medium The flow direction is communicated, and the second header and the fourth header are located in the same direction of the two rows of flat tubes and are parallel to each other and communicate according to the flow direction of the heat exchange medium.

The heat exchanger according to claim 1, wherein the plurality of flat tubes are two or more, and are horizontally arranged in two rows in a parallel manner, and the heat exchangers or the horizontal or horizontal tubes can be formed after being arranged. Or placed at an angle of 15 ^Q - 25 ^D with the horizontal; further comprising a manifold connected to one end of the first row of flat tubes, a second header connecting the other end of the first row of flat tubes, and a second tube connected to the second row a third header at one end, a fourth header connected to the other end of the second row of flat tubes; wherein the first header and the third header are located in the same direction of the two rows of flat tubes and are parallel to each other and according to heat exchange The flow direction of the medium communicates, and the second header and the fourth header are located in the same direction of the two rows of flat tubes and are parallel to each other and communicate according to the flow direction of the heat exchange medium.

10. The heat exchanger according to claim 1, wherein the flat tubes are two or more, arranged horizontally or vertically in a parallel manner; and further comprising a first header and a connecting flat connecting one end of the flat tube The second header at the other end of the tube.

The heat exchanger according to claim 1, wherein the flat tube is two or more U-shaped flat tubes, each of which

The U-shaped flat tubes are arranged in a row in a horizontal or vertical interval in a parallel manner, and the first collecting tube and the second collecting tube are respectively connected at both ends of each u-shaped flat tube, the first collecting tube and the second collecting unit The flow tubes are parallel to each other and communicate according to the flow direction of the heat exchange medium.

The heat exchanger according to any one of claims 2 to 5, wherein one end of the tube is an inlet end of a heat exchange medium, and the other end of the flat tube is a heat exchange medium. Export end.

The heat exchanger according to any one of claims 1 to 11, wherein the flat tube has a thickness of 1.0 mm to 2.5 mm.

14. A heat exchanger according to any one of claims 1 to 11, wherein the thickness of the flat tube is from 1.0 mm to 2.0 mm in a single cold condenser.

The heat exchanger according to any one of claims 1 to 11, wherein the thickness of the flat tube is 1.6 min - 2.5 mm in a single cold evaporator.

The heat exchanger according to any one of claims 1 to 11, wherein the thickness of the flat tube is 1.3 mm - 2.0 mm in a heat pump type indoor and outdoor heat exchanger,

The heat exchanger according to any one of claims 1 to 11, wherein the thickness of the flat tube is such that the flat tube is twisted into a spiral shape, and the spiral spiral angle is equal to or less than 68.2 Degree, the pitch < 2.5 times the width of the flat tube 300.

The heat exchanger according to any one of claims 1 to 11, characterized in that the flat tube is provided with at least one microchannel extending in the longitudinal direction of the flat tube.

19. A heat exchanger according to claim 18, wherein said single microchannel orifice flow path cross-sectional area between 0.36mm ^² -1.00mm ^2.

The heat exchanger according to any one of claims 6 to 11, wherein the inlet end and the outlet end of the heat exchange medium are respectively disposed at ends of the header.

The heat exchanger according to any one of claims 6 to 11, wherein the inlet end and the outlet end of the heat exchange medium are simultaneously disposed on a pipe wall of a header.

22. The heat exchanger according to claim 21, wherein an inlet end or an outlet of the heat exchange medium is provided when a length of a header provided at an inlet end or an outlet end of the heat exchange medium is > 300 mm There are multiple ends, and the distance between the inlet end of two adjacent heat exchange shields or the exit end of two adjacent heat exchange shields is less than 150 mm, and all the heat exchange media The inlet or outlet ends are equidistantly distributed.

23. The heat exchanger according to claim 6 or 7, wherein the heat exchanger is divided into an odd-circuit single-row parallel flow heat exchanger and an even-circuit single-row parallel flow heat exchanger.

24. The heat exchanger according to claim 23, wherein, for the odd-circuit single-row parallel flow heat exchanger, the inlet end and the outlet end of the heat exchange medium are respectively disposed at the first header and the second The ends of the header are distributed diagonally.

25. The heat exchanger according to claim 23, wherein in the even-circuit parallel flow heat exchanger, the inlet and outlet ends are disposed on the first header or the second header.

26. The heat exchanger according to claim 24, wherein, when acting as an evaporator, the inlet end of the heat exchange shield is disposed at the bottom of the heat exchanger, and the outlet end is disposed at the top of the heat exchanger.

27. The heat exchanger according to claim 24, wherein when used as a condenser, the inlet end of the heat exchange medium is disposed at the top of the heat exchanger, and the outlet end is disposed at the bottom of the heat exchanger.

28. The heat exchanger of claim 25 wherein the inlet and outlet ends of the heat exchange medium are both located at the bottom of the heat exchanger.

The heat exchanger according to claim 6 or 7, wherein when the number of circuits is one or more, the volume of each circuit is distributed in a certain ratio.

30. The heat exchanger of claim 29 wherein said heat exchanger is a dual circuit, single row parallel flow heat exchanger wherein the volume of the first circuit is 80 of the total volume of the circuit. / ₀ , the volume of the second circuit accounts for 20% of the total volume of the circuit.

The heat exchanger according to claim 29, wherein the heat exchanger is a three-circuit single-row parallel flow heat exchanger, wherein the volume of the first circuit accounts for 55% of the total volume of the circuit, and the second circuit The volume accounts for 30% of the total volume of the circuit, and the volume of the third circuit accounts for 15% of the total volume of the circuit.

The heat exchanger according to claim 29, wherein the heat exchanger is a four-circuit single-row parallel flow heat exchanger, wherein the volume of the first circuit accounts for 40% of the total volume of the circuit, and the second circuit The volume accounts for 27% of the total volume of the circuit, the volume of the third circuit accounts for 20% of the total volume of the circuit, and the volume of the fourth circuit accounts for 13% of the total volume of the circuit.

33. The heat exchanger according to claim 29, wherein the heat exchanger is a five-circuit single-row parallel flow heat exchanger, wherein the volume of the first circuit accounts for 34% of the total volume of the circuit, and the second circuit The volume accounts for 24% of the total volume of the circuit, the volume of the third circuit accounts for only 18% of the total circuit, the volume of the fourth circuit accounts for 13% of the total volume of the circuit, and the volume of the fifth circuit accounts for 13% of the total volume of the circuit.

The heat exchanger according to claim 29, wherein the heat exchanger is a six-circuit single-row parallel flow heat exchanger, wherein the volume of the first circuit accounts for 30% of the total volume of the circuit, and the second circuit The volume accounts for 20% of the total volume of the loop, the third loop The volume accounts for 17% of the total volume of the circuit, the volume of the fourth circuit accounts for 14% of the total volume of the circuit, the volume of the fifth circuit accounts for 10% of the total volume of the circuit, and the volume of the sixth circuit accounts for 9% of the total volume of the circuit.

35. The heat exchanger according to claim 33, wherein the respective circuits are separated by a barrier plate disposed in the first header or the second header.

36. The heat exchanger according to claim 8, wherein a length of the heat exchange medium axially flowing in the first header and the third header is greater than a heat exchange medium in the second header and The length of the axial flow in the fourth header, and the length of the axial flow in the first header and the third header is as long as possible, and the inner shaft in the second header and the fourth header The length of the flow is only possible short.

37. The heat exchanger according to claim 36, wherein a length of the heat exchange medium axially flowing in the first header and the third header accounts for the heat exchange medium at the first, second, The length of the axial flow in the third and fourth headers is more than 70%, and the length of the axial flow of the heat exchange shield in the second header and the fourth header accounts for the heat exchange medium in the first, the first 2. The length of the axial flow in the third and fourth headers is less than 30%.

38. The heat exchanger according to claim 8, wherein the first header and the third header are not in direct communication, and the second header and the fourth header are in communication Some are directly connected to each other.

39. The heat exchanger according to claim 38, wherein the axial flow of the heat exchange medium is all completed in the first header and the third header, and the first row of tubes and the second row are flat The flow of heat exchange medium between the tubes is completely completed by the interconnection of the holes between the second header and the fourth header.

40. The heat exchanger according to claim 39, wherein the heat exchanger is divided into a plurality of circuits by a blocking plate disposed in the header, and the circuits are connected in series.

41. The heat exchanger according to claim 40, wherein the volume of each circuit is gradually increased along the flow direction of the heat exchange medium, but the volume of the last circuit is not more than 2.5 times the volume of the first circuit.

42. The heat exchanger according to claim 41, wherein the volume of the latter circuit is greater than 20-60% of the volume of the previous circuit along the flow direction of the heat exchange medium.

43. The heat exchanger according to claim 41, wherein the volume of the latter circuit is greater than 40-50% of the volume of the previous circuit along the flow direction of the heat exchange medium.

44. The heat exchanger according to claim 39, wherein the last two sections of the circuit are provided with a replenishment port that supplements the heat exchange shield in the last two sections of the circuit, wherein the last circuit supplements the heat exchange The medium is 15-20% by weight of the total heat exchange medium.

45. The heat exchanger according to claim 8, wherein the inlet end and the outlet end of the heat exchange medium are disposed On the side wall of the first header or the third header.

The heat exchanger according to any one of claims 6 to 11, wherein a plurality of orifice plates are arranged at intervals in the header, and each section of the orifice plate has a section Flow hole.

47. The heat exchanger of claim 46, wherein the orifice plates are spaced apart by a distance of less than 80 mm.

48. The heat exchanger of claim 46, wherein the orifice plates are spaced apart by a distance of 50 mm.

The heat exchanger according to any one of claims 2 to 11, wherein a warping piece is disposed between the flat tubes.

50. The heat exchanger according to claim 49, wherein the height of the blade is 6 mm to 16 mm.

The heat exchanger according to claim 49, wherein the height of the ridge piece is 6 mm to 10 mm.

52. The heat exchanger according to claim 49, wherein the 1.5 M/s-2 M/s wind speed blade window angle is 22 degrees to 45 degrees.

53. The heat exchanger according to claim 49, wherein the 1.5 M/s-2 M/s wind speed blade window angle is 27 degrees to 33 degrees.

54. The heat exchanger according to claim 49, wherein the 1.5 M/s to 2 M s wind speed blade pitch is 2.0 mm to 5.0 mm.

55. The heat exchanger according to claim 49, wherein the 1.5 M/S-2 M/S wind speed blade pitch is 2.2 mm to 2.8 mm in the high efficiency heat exchanger.

The heat exchanger according to claim 49, wherein the 1.5 M/s to 2 M/s wind speed blade pitch is 2.6 mm to 3.0 mm in consideration of efficient heat exchange and dehumidification.

57. The heat exchanger according to claim 49, wherein the 1.5 M/s-2 M/s wind speed blade pitch is preferably 3.6 mm-5.0 in a refrigerated or single dehumidification or dust area. Mm.

58. The heat exchanger of claim 49 wherein when the heat exchanger is applied to a blowerless heat exchange system, the windowless design is employed and the pitch of the blade is equal to the height of the blade.

59. The heat exchanger according to claim 49, wherein the warp window length B is 0.3 mm.

60. The heat exchanger according to claim 49, wherein the warp window length B is 0.10 to 0.15 mm.

61. The heat exchanger according to claim 49, wherein the flat tube adopts an ^AQ design to guide the heat exchanger condensate in a wind direction, wherein 30° A ⁰ < 60 ⁰ .

The heat exchanger according to any one of claims 6 to 11, wherein the header has a cross-sectional shape of a D-type header.

63. The heat exchanger according to claim 62, wherein a reinforcing rib is disposed along a length of the header of the three-side tube wall of the D-type header that is not connected to the flat tube, The spacing between two adjacent stiffeners is 25.4 mm.

64. Use of a microchannel, parallel flow, all aluminum flat tube welded structural heat exchanger according to the preceding claims in room air conditioning, commercial air conditioning and other specialized heat exchange systems.

65. The use of claim 64 is in an air conditioning system.

66. The use of claim 64 in an application in a refrigerated refrigeration system.

67. The use according to claim 64, which is an application in an air conditioning system for refrigeration and dehumidification.

68. The use of claim 64 in an application in a heat pump heating system.

69. The use of claim 64 in an application in a water cooling/heating air conditioning system.

70. The application of claim 64, which is an application in a computer cooling module in the IT industry.

71. An application as claimed in claim 64, which is an application in a device cooling system.