CN212902102U - Heat exchanger and refrigerating and heating system with same - Google Patents

Abstract

The utility model discloses a heat exchanger and refrigeration heating system who has this heat exchanger. The heat exchanger includes: a first header and a second header; and a plurality of flat tubes arranged at intervals along the length direction of the first header, each flat tube having a first end and a second end in the length direction thereof, the first end of each flat tube being connected to the first header, and the second end of each flat tube being connected to the second header, wherein the plurality of flat tubes constitute a plurality of flat tube groups, each flat tube group including at least one flat tube, and the flow area of each flat tube of the downstream flat tube group is smaller than the flow area of each flat tube of the upstream flat tube group. According to the utility model discloses the heat exchanger has advantages such as heat exchange efficiency is high, the refrigerant pressure drop is little.

Description

Heat exchanger and refrigerating and heating system with same

Technical Field

The utility model relates to a refrigeration field specifically relates to the heat exchanger, still relates to the refrigeration heating system who has this heat exchanger.

Background

The heat exchanger has the advantages of high heat exchange efficiency and compact structure, and the manufacturing cost of the heat exchanger is more advantageous than that of a common copper tube heat exchanger. When the heat exchanger is used as a condenser of a heat pump water heater, the arrangement mode of the flat pipe is different from that of a common heat exchanger. Specifically, when the heat exchanger is used as a condenser of a heat pump water heater, the flat pipe is vertically placed and is connected without fins, the flat pipe is tightly wound on the outer surface of the water tank, and a refrigerant transfers heat into the water tank through the flat pipe.

SUMMERY OF THE UTILITY MODEL

The present invention is made based on the discovery and recognition by the inventors of the following facts and problems: when the heat exchanger is used as a condenser of a heat pump water heater, the refrigerant is in a high-pressure gaseous state in an inlet area of the heat exchanger, and the heat exchange efficiency of the refrigerant is high but the flow resistance is large. As the condensation process progresses, the dryness of the refrigerant gradually decreases, and the refrigerant has become completely liquid as it approaches the outlet of the heat exchanger. At this time, the volume of the refrigerant is reduced, the flow rate is reduced, and the heat exchange efficiency is reduced.

The flat tubes of the heat exchangers of the related art are uniformly sized from upstream to downstream, and this design does not match the variation in the dryness of the refrigerant during condensation well.

The present invention aims at solving at least one of the technical problems in the related art to a certain extent. Therefore, the utility model provides a heat exchanger and have this heat exchanger's refrigeration heating system.

According to the utility model discloses a heat exchanger includes: a first header and a second header; and a plurality of flat tubes arranged at intervals along the length direction of the first header, each flat tube having a first end and a second end in the length direction thereof, the first end of each flat tube being connected to the first header, and the second end of each flat tube being connected to the second header, wherein the plurality of flat tubes constitute a plurality of flat tube groups, each flat tube group including at least one flat tube, and the flow area of each flat tube of the downstream flat tube group is smaller than the flow area of each flat tube of the upstream flat tube group.

According to the utility model discloses a heat exchanger has the advantage that heat exchange efficiency is high.

Optionally, a plurality of flat pipe constitutes first flat nest of tubes and second flat nest of tubes, first flat nest of tubes includes a plurality of flat pipe, the second flat nest of tubes includes a plurality of flat pipe, wherein first flat nest of tubes is located the upper reaches of second flat nest of tubes.

Optionally, the flow area of each flat tube of the first flat tube group is 7 mm to 13 mm.

Optionally, the flow area of each of the flat tubes of the first flat tube group is 9.1 square millimeters to 12.2 square millimeters.

Optionally, the thickness of each flat tube of the first flat tube group is 1.2 mm to 1.4 mm, and the width of each flat tube of the first flat tube group is 16 mm to 20 mm.

Optionally, the flow area of each flat tube of the second flat tube group is 3 mm to 8 mm.

Optionally, the flow area of each of the flat tubes of the second flat tube group is 4 mm to 7 mm.

Optionally, the thickness of each flat tube of the second flat tube group is 1.2 mm to 1.4 mm, and the width of each flat tube of the second flat tube group is 8 mm to 12 mm.

Optionally, the first header includes an upper section and a lower section which are arranged at a distance or a partition plate is provided in the first header so as to divide the first header into the upper section and the lower section, each of the upper section, the lower section and the second header is arranged vertically, each of the flat tubes is arranged horizontally, wherein a plurality of the flat tubes constitute an upper flat tube group including a plurality of the flat tubes and a lower flat tube group including a plurality of the flat tubes, the first end portion of each of the flat tubes of the upper flat tube group is connected to the upper section, the first end portion of each of the flat tubes of the lower flat tube group is connected to the lower section, and the flow area of each of the flat tubes of the lower flat tube group is smaller than the flow area of each of the flat tubes of the upper flat tube group.

According to the utility model discloses a refrigeration heating system is including consecutive compressor, condenser, flow controller and evaporimeter, the condenser is according to the utility model discloses a heat exchanger.

According to the utility model discloses a refrigeration heating system has the advantage that heat exchange efficiency is high.

Drawings

Fig. 1 is a schematic structural diagram of a heat exchanger according to an embodiment of the present invention;

fig. 2 is according to the utility model discloses the structural schematic of flat pipe of heat exchanger.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings. The embodiments described below with reference to the drawings are exemplary and intended to be used for explaining the present invention, and should not be construed as limiting the present invention.

The heat exchanger 100 according to an embodiment of the present invention is described below with reference to the drawings. As shown in fig. 1 and 2, a heat exchanger 100 according to an embodiment of the present invention includes a first header 21, a second header 22, and a plurality of flat tubes 1.

The flat tubes 1 are arranged at intervals in the longitudinal direction of the first header 21, that is, the flat tubes 1 are arranged at intervals in the longitudinal direction of the second header 22. The first end 11 of each flat tube 1 is connected to a first header 21, and the second end 12 of each flat tube 1 is connected to a second header 22. The flat tubes 1 form a plurality of flat tube groups, each flat tube group comprises at least one flat tube 1, and the flow area of each flat tube 1 of the flat tube group positioned at the downstream is smaller than that of each flat tube 1 of the flat tube group positioned at the upstream.

Wherein "upstream" and "downstream" are determined according to the flow direction of the refrigerant in the heat exchanger 100, and the refrigerant enters the heat exchanger 100 and flows through the flat tube group located upstream and then flows through the flat tube group located downstream. That is, the flat tube group near the refrigerant inlet of the heat exchanger 100 is "upstream", and the flat tube group near the refrigerant outlet of the heat exchanger 100 is "downstream".

According to the utility model discloses heat exchanger 100 is according to the characteristics of the condensation process of refrigerant, the dryness factor situation of change according to the flow in-process of refrigerant in heat exchanger 100 promptly, the great flat pipe 1 of flow area is adopted in overheated or the great region of dryness factor, so that reduce the pressure drop loss of refrigerant when guaranteeing the heat exchange efficiency, and in supercooling or the less region of dryness factor, adopt the less flat pipe 1 of flow area, so that promote the flow rate of refrigerant in flat pipe 1 as far as possible, thereby promote the heat transfer coefficient of the refrigerant side in this region. Therefore, the heat exchanger 100 according to the embodiment of the present invention is a heat exchanger with a variable flat tube size.

According to the utility model discloses heat exchanger 100 is less than the flow area of every flat pipe 1 of this flat pipe group that is located the upper reaches through the flow area that makes every flat pipe 1 of this flat pipe group that is located the lower reaches to can combine the quality of refrigerant change, compromise the heat transfer coefficient who promotes the refrigerant side simultaneously and reduce the pressure drop of refrigerant in heat exchanger 100.

Therefore, according to the utility model discloses heat exchanger 100 has advantages such as heat exchange efficiency is high, the refrigerant pressure drop is little.

As shown in fig. 1 and 2, the heat exchanger 100 includes a first header 21, a second header 22, and a plurality of flat tubes 1. The flat tubes 1 are arranged at intervals along the length direction of the first header 21, the first end 11 of each flat tube 1 is connected with the first header 21, and the second end 12 of each flat tube 1 is connected with the second header 22.

Optionally, a plurality of flat pipes 1 constitute first flat pipe group and second flat pipe group, and this first flat pipe group includes a plurality of flat pipes 1, and this second flat pipe group includes a plurality of flat pipes 1, and this first flat pipe group is located the upper reaches of this second flat pipe group. Therefore, the flow area of each flat tube 1 of the second flat tube group is smaller than the flow area of each flat tube 1 of the first flat tube group. As shown in fig. 2, the flat tube 1 includes a plurality of refrigerant flow holes 11, and the flow area of the flat tube 1 is equal to the sum of the cross-sectional areas of the plurality of refrigerant flow holes 11 of the flat tube 1.

As shown in fig. 1, each of the first header 21 and the second header 22 is vertically disposed, and each flat tube 1 is horizontally disposed. Flat nest of tubes 1 constitutes last flat nest of tubes 1a and lower flat nest of tubes 1b, goes up flat nest of tubes 1a and includes a plurality of flat pipes 1, and lower flat nest of tubes 1b includes a plurality of flat pipes 1. The flow area of each flat tube 1 of the lower flat tube group 1b is smaller than the flow area of each flat tube 1 of the upper flat tube group 1 a.

A partition plate 3 is provided in the first header 21 so as to partition the first header 21 into an upper section 211 and a lower section 212. Alternatively, the first header 21 includes an upper section 211 and a lower section 212 that are spaced apart. Each of the upper section 211 and the lower section 212 is vertically disposed. The first end 11 of each flat tube 1 of the upper flat tube group 1a is connected to the upper section 211, and the first end 11 of each flat tube 1 of the lower flat tube group is connected to the lower section 212. Thereby making the structure of the heat exchanger 100 more rational. The vertical direction is shown by an arrow a in fig. 1.

Alternatively, each flat tube 1 of the first flat tube group (upper flat tube group 1a) has a flow area of 7 mm to 13 mm. Alternatively, each flat tube 1 of the first flat tube group (upper flat tube group 1a) has a flow area of 9.1 mm square to 12.2 mm square. That is, the flow area of each flat tube 1 of the first flat tube group (upper flat tube group 1a) is 9.1 mm square or more and 12.2 mm square or less.

Each flat tube 1 of the first flat tube group (upper flat tube group 1a) has a thickness of 1.2 mm to 1.4 mm, and each flat tube 1 of the first flat tube group (upper flat tube group 1a) has a width of 16 mm to 20 mm. The width direction of the flat tube 1 is shown by an arrow B in fig. 2, and the thickness direction of the flat tube 1 is shown by an arrow C in fig. 2.

The flow area of each flat tube 1 of the second flat tube group (lower flat tube group 1b) is 3 mm to 8 mm. Alternatively, each flat tube 1 of the second flat tube group (lower flat tube group 1b) has a flow area of 4 mm to 7 mm.

Each flat tube 1 of the second flat tube group (lower flat tube group 1b) has a thickness of 1.2 mm to 1.4 mm, and each flat tube 1 of the second flat tube group (lower flat tube group 1b) has a width of 8 mm to 12 mm.

When the refrigerant enters the heat exchanger 100 from the inlet, the refrigerant is in a high-pressure gaseous state, and the refrigerant has a large volume and a high flow rate. Therefore, the first flat tube group (upper flat tube group 1a) can select the flat tubes 1 with larger size so as to reduce the flow velocity of the gaseous refrigerant and make the flow of the refrigerant smoother, and the design has less influence on the heat exchange efficiency, but can obviously reduce the pressure drop loss of the refrigerant.

The flat tubes 1 of the first flat tube group (upper flat tube group 1a) have a small variation range, although the amount of heat exchange inside the flat tubes 1 increases as the flow area of the flat tubes 1 decreases. However, the pressure drop of the refrigerant increases significantly as the flow area of the flat tubes 1 decreases. In view of the combination of the heat exchange amount and the pressure drop, the flow area of each flat tube 1 of the first flat tube group (upper flat tube group 1a) is 9.1 mm to 12.2 mm, the thickness of each flat tube 1 of the first flat tube group (upper flat tube group 1a) is 1.2 mm to 1.4 mm, and the width of each flat tube 1 of the first flat tube group (upper flat tube group 1a) is 16 mm to 20 mm.

When the refrigerant passes through the first flat tube group (the upper flat tube group 1a), the dryness of the refrigerant is reduced (generally reduced to below 0.3), most of the refrigerant changes from a gaseous state to a liquid state, the volume of the refrigerant is reduced, and the flow speed is reduced, so that the heat exchange coefficient is reduced. Therefore, the second flat tube group (lower flat tube group 1b) can select the flat tubes 1 having a smaller size so as to reduce the flow area of the refrigerant, thereby increasing the flow rate of the refrigerant in the flat tubes 1 and increasing the heat exchange coefficient on the refrigerant side in this region.

For the flat tubes 1 of the second flat tube group (lower flat tube group 1b), the pressure drop increases with the decrease in the flow area of the flat tubes 1, but the variation range is not large, and the amount of heat exchange inside the tubes of the flat tubes 1 increases significantly with the decrease in the flow area of the flat tubes 1. In view of the heat exchange amount and the pressure drop in combination, each flat tube 1 of the second flat tube group (lower flat tube group 1b) has a flow area of 4 mm to 7 mm, each flat tube 1 of the second flat tube group (lower flat tube group 1b) has a thickness of 1.2 mm to 1.4 mm, and each flat tube 1 of the second flat tube group (lower flat tube group 1b) has a width of 8 mm to 12 mm.

Moreover, the larger the number of the flat tube groups formed by the plurality of flat tubes 1 is, the better the refrigerant quality change can be adapted to, and the better the improvement of the heat exchange coefficient on the refrigerant side and the reduction of the pressure drop of the refrigerant in the heat exchanger 100 can be achieved.

Compare with the heat exchanger among the relevant art (the flow area of flat pipe keeps unchangeable), according to the utility model discloses heat exchanger 100 can obviously improve the heat transfer volume under the basically unanimous condition of pressure drop.

The utility model discloses still provide refrigeration heating system. According to the utility model discloses refrigeration heating system is including consecutive compressor, condenser, flow controller and evaporimeter, and this condenser is according to the utility model discloses heat exchanger 100.

Therefore, according to the utility model discloses refrigeration heating system has advantages such as heat exchange efficiency is high, the refrigerant pressure drop is little.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", and the like, indicate the orientation or positional relationship indicated based on the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the present invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally formed; may be mechanically coupled, may be electrically coupled or may be in communication with each other; they may be directly connected or indirectly connected through intervening media, or they may be connected internally or in any other suitable relationship, unless expressly stated otherwise. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

In the present application, unless expressly stated or limited otherwise, the first feature may be directly on or directly under the second feature or indirectly via intermediate members. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

In the present disclosure, the terms "one embodiment," "some embodiments," "an example," "a specific example," or "some examples" or the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present disclosure. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

Although embodiments of the present invention have been shown and described, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art without departing from the scope of the present invention.

Claims (10)

1. A heat exchanger, comprising:

a first header and a second header; and

a plurality of flat tubes, the plurality of flat tubes being arranged at intervals along the length direction of the first header, each flat tube having a first end and a second end in the length direction thereof, the first end of each flat tube being connected to the first header, and the second end of each flat tube being connected to the second header, wherein the plurality of flat tubes constitute a plurality of flat tube groups, each flat tube group including at least one flat tube, and the flow area of each flat tube of the downstream flat tube group being smaller than the flow area of each flat tube of the upstream flat tube group.

2. The heat exchanger of claim 1, wherein a plurality of the flat tubes comprise a first flat tube bank comprising a plurality of the flat tubes and a second flat tube bank comprising a plurality of the flat tubes, wherein the first flat tube bank is upstream of the second flat tube bank.

3. The heat exchanger of claim 2, wherein each of the flat tubes of the first bank has a flow area of 7-13 square millimeters.

4. The heat exchanger of claim 3, wherein each of the flat tubes of the first bank has a flow area in the range of 9.1 square millimeters to 12.2 square millimeters.

5. The heat exchanger of claim 4, wherein each of the flat tubes of the first bank has a thickness of 1.2 mm to 1.4 mm and each of the flat tubes of the first bank has a width of 16 mm to 20 mm.

6. The heat exchanger of claim 2, wherein each of the flat tubes of the second bank has a flow area of 3-8 square millimeters.

7. The heat exchanger of claim 6, wherein each of the flat tubes of the second bank of flat tubes has a flow area of 4-7 square millimeters.

8. The heat exchanger of claim 7, wherein each of said flat tubes of said second bank has a thickness of 1.2 mm to 1.4 mm and each of said flat tubes of said second bank has a width of 8 mm to 12 mm.

9. The heat exchanger of claim 1, wherein the first header includes upper and lower sections that are spaced apart or a baffle is provided within the first header to separate the first header into the upper and lower sections, each of the upper section, the lower section, and the second header being vertically disposed, each of the flat tubes being horizontally disposed, wherein a plurality of flat tubes form an upper flat tube group and a lower flat tube group, the upper flat tube group comprises a plurality of flat tubes, the lower flat tube group comprises a plurality of flat tubes, the first end of each flat tube of the upper flat tube group is connected with the upper section, the first end part of each flat pipe of the lower flat pipe group is connected with the lower section, and the flow area of each flat pipe of the lower flat pipe group is smaller than that of each flat pipe of the upper flat pipe group.

10. A refrigerating and heating system, which is characterized by comprising a compressor, a condenser, a restrictor and an evaporator which are connected in sequence, wherein the condenser is a heat exchanger according to any one of claims 1 to 9.

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