CN219390141U - Evaporator and refrigerator - Google Patents
Evaporator and refrigerator Download PDFInfo
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- CN219390141U CN219390141U CN202223456518.5U CN202223456518U CN219390141U CN 219390141 U CN219390141 U CN 219390141U CN 202223456518 U CN202223456518 U CN 202223456518U CN 219390141 U CN219390141 U CN 219390141U
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Abstract
An evaporator provided in a circulation duct, the evaporator having a first flow path through which a refrigerant flows and a plurality of second flow paths which are respectively communicated with the first flow paths and are located on a downstream side of the first flow path, an extending direction of each of the plurality of second flow paths intersecting a wind direction of a circulation wind in the circulation duct; in an operating state of the evaporator, the refrigerant flows from the first flow path into each of the plurality of second flow paths, and circulating wind blows through each of the second flow paths in turn; the evaporator is characterized in that: in the operating state of the evaporator, the plurality of second flow paths are configured such that the flow rate of the refrigerant passing through a second flow path located on the upstream side of the circulating wind is larger than the flow rate of the refrigerant passing through a second flow path located on the downstream side of the circulating wind. Therefore, by adjusting the flow of the refrigerant, the refrigerating benefit is improved, and frosting and icing can be avoided.
Description
Technical Field
The present utility model relates to an evaporator capable of improving refrigerating efficiency and preventing frosting and icing at the tail part, and a refrigerator using the evaporator.
Background
The evaporator is an important part in refrigeration equipment such as a medical refrigerator, and low-temperature refrigerant exchanges heat with the outside air through the evaporator and evaporates to absorb heat, so that the refrigeration effect is achieved. The evaporator typically has a multi-layered distribution of refrigerant lines, with the external circulating air blowing from the upstream side refrigerant line to the downstream side refrigerant line, in turn exchanging heat with the refrigerant in each layer.
In the conventional art, the flow rate of the refrigerant flowing into each layer of the refrigerant lines is uniform, i.e., the flow rate of the refrigerant in the multi-layer refrigerant lines is evenly distributed. Therefore, when the circulating air just blows to the refrigerating pipeline on the upstream side, the temperature difference between the circulating air and the refrigerant is relatively large, so that the heat conduction speed is high, and the heat transfer efficiency is high. However, when the circulating air blows to the refrigerating pipeline at the downstream side, the temperature of the circulating air is greatly reduced, and the temperature difference between the circulating air and the refrigerant is small, so that the heat conduction speed is low and the heat transfer efficiency is low.
In other words, in the case where the heat transfer efficiency is lowered, the refrigerant flowing into the downstream side refrigerant line is still as much as the refrigerant flowing into the upstream side refrigerant line, and this causes waste of the refrigerant amount, resulting in low usage efficiency of the refrigerant.
In addition, the temperature of the circulating air at the downstream side is low, and excessive refrigerant flows in the circulating air, so that the cooling amplitude of the circulating air is too large, the surface of the evaporator at the downstream side, namely the tail part, is easy to frost and freeze, the service life is prolonged, and the refrigerating effect is influenced.
Therefore, in the prior art, the distribution of the refrigerant is optimized, the use benefit of the refrigerant is improved, and the frosting and icing of the tail part of the evaporator are avoided.
Disclosure of Invention
The utility model aims to provide an evaporator capable of improving refrigeration benefits and avoiding frosting and icing at the tail. In order to achieve the above object, an aspect of the present utility model is an evaporator provided in a circulation duct, the evaporator having a first flow path through which a refrigerant flows and a plurality of second flow paths that communicate with the first flow path, respectively, and are located on a downstream side of the first flow path, each of the plurality of second flow paths extending in a direction intersecting with a wind direction of a circulating wind in the circulation duct;
in the operating state of the evaporator, the refrigerant flows from the first flow path into each of the plurality of second flow paths, and the circulating air in the circulating air duct blows through each of the second flow paths in turn;
the evaporator is characterized in that: in the operating state of the evaporator, the plurality of second flow paths are configured such that a flow rate of the refrigerant passing through a second flow path located on an upstream side of the circulating wind is larger than a flow rate of the refrigerant passing through a second flow path located on a downstream side of the circulating wind.
According to the technical scheme, the refrigerant flow in the pipeline which is closer to the downstream side of the circulating wind can be smaller, so that the use benefit of the refrigerating capacity is improved. And the circulating wind at the downstream side can be prevented from being excessively cooled, so that the surface of the evaporator is frosted and frozen.
In a preferred embodiment, the extending direction of the first flow path intersects with the extending direction of each of the plurality of second flow paths, and the cross-sectional area of the first flow path is smaller as the first flow path is closer to the downstream side of the circulating wind.
According to the above-described technical solution, the smaller the pipe cross-sectional area of the first flow path is on the downstream side of the circulating air, the smaller the pipe cross-sectional area of each branch in the second flow path is, and the adjustment of the flow rate of the refrigerant can be achieved without adjusting the cross-sectional area of each branch in the second flow path.
In one preferred embodiment, the plurality of second flow paths are configured such that a flow rate of the refrigerant allowed to pass through, of two adjacent second flow paths, which are located on an upstream side of the circulating wind, is greater than a flow rate of the refrigerant allowed to pass through, of the second flow paths located on a downstream side of the circulating wind.
According to the technical scheme, the pipeline cross section of the first flow path is not changed any more, and the adjustment of the flow rate of the refrigerant is realized by adjusting the cross section of each branch in the second flow path.
In a preferred embodiment, the plurality of second flow paths are substantially parallel, and are multilayer pipes arranged in order along the direction of the circulating wind.
According to the technical scheme, the multi-row pipelines can perform more sufficient heat exchange with circulating air, so that a better cooling effect is achieved.
In addition, another aspect of the utility model is a refrigerator comprising a housing, a compressor, and a circulation duct within the housing;
the refrigerator is characterized in that: the evaporator is also included.
The evaporator provided by the embodiment of the application can avoid excessive waste of refrigerating capacity and improve the use benefit of the refrigerant; the cooling amplitude of circulating air at the downstream side can be reduced, so that the surface temperature distribution of the evaporator is more uniform, the problem that a refrigerant pipeline at the downstream side frosts and freezes is avoided, the service life is prolonged, and the cooling effect is enhanced.
Drawings
In order to more clearly illustrate the present utility model, the following description and the accompanying drawings of the present utility model will be given. It should be apparent that the figures in the following description merely illustrate certain aspects of some exemplary embodiments of the present utility model, and that other figures may be obtained from these figures by one of ordinary skill in the art without undue effort.
Fig. 1 is a schematic view of an evaporator flow path according to the first embodiment.
Fig. 2 is a schematic view of an evaporator flow path according to the second embodiment.
Description of the drawings:
100 evaporator
1 first flow path
2 second flow path
21 first branch
22 second branch
23 third branch
24 fourth branch
3 wind direction
4 small diameter pipeline
Detailed Description
Various exemplary embodiments of the present disclosure are described in detail below with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative, and is in no way intended to limit the disclosure, its application, or uses. The present disclosure may be embodied in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art. It should be noted that: the relative arrangement of parts and steps, numerical expressions and values, etc. set forth in these embodiments are to be construed as illustrative only and not as limiting unless otherwise stated.
The use of the terms "comprising" or "including" and the like in this disclosure means that elements preceding the term encompass the elements recited after the term, and does not exclude the possibility of also encompassing other elements.
All terms (including technical or scientific terms) used in this disclosure have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs, unless specifically defined otherwise. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
Parameters of, and interrelationships between, components, and control circuitry for, components, specific models of components, etc., which are not described in detail in this section, can be considered as techniques, methods, and apparatus known to one of ordinary skill in the relevant art, but are considered as part of the specification where appropriate.
(general structure)
The overall configuration of the evaporator of the present utility model is described below with reference to fig. 1. Fig. 1 is a schematic view of an evaporator flow path according to the first embodiment.
Referring to fig. 1, the evaporator 100 includes a first flow path 1 on the refrigerant inlet side and a second flow path 2 communicating with the first flow path 1 and on the downstream side of the first flow path 1. Wherein the second flow path 2 comprises a plurality of substantially parallel branches. The number of branches of the second flow path 2 is not particularly limited, and for simplicity, only four branches of the first branch 21, the second branch 22, the third branch 23, and the fourth branch 24 shown in fig. 1 will be described as an example.
In a typical example, each of the first flow path 1 and the second flow path 2 is generally a pipe structure. Generally, during the operation of the refrigeration apparatus, the refrigerant is changed into a low-temperature low-pressure liquid after passing through a compressor, a drying device, a capillary tube, etc., and flows into a refrigeration line in the evaporator 100. Specifically, in the present utility model, the low-temperature low-pressure refrigerant enters the first flow path 1 of the evaporator 100, then enters each branch in the second flow path 2, and further exchanges heat with the external environment of the evaporator 100, continuously absorbs heat and rapidly vaporizes, and finally flows out of the evaporator 100 and flows back to the compressor to form a refrigeration cycle.
The evaporator 100 is typically disposed within a circulating air duct within a refrigeration appliance, such as a medical refrigerator, with the initial temperature of the circulating air being the same as the ambient temperature outside the evaporator 100, having a higher temperature than the refrigerant within the evaporator 100. In the process of blowing through the evaporator 100, the circulating air exchanges heat with the refrigerant in the evaporator 100, becomes cold air with relatively low temperature, and continuously blows into the internal space of the refrigeration equipment, thereby achieving the purpose of cooling.
With continued reference to fig. 1, in general, the direction of extension of the individual branches in the second flow path 2 intersects the direction 3 of the circulating wind so that the circulating wind blows through each branch in turn. Preferably, each branch in the second flow path 2 extends in a direction substantially perpendicular to the wind direction 3 of the circulating wind, so that the refrigerant inside each branch is in more sufficient contact and heat exchange with the circulating wind. Meanwhile, each branch in the second flow path 2 is sequentially arranged along the direction of the wind direction 3 to form a multi-row pipeline structure, so that circulating wind sequentially blows through the first branch 21, the second branch 22, the third branch 23 and the fourth branch 24, and finally enters the internal space of the refrigeration and heating equipment after being changed into cold wind.
In the conventional art, the flow rates of the refrigerant entering the first branch 21, the second branch 22, the third branch 23, and the fourth branch 24 are uniform. At this time, when the circulating wind just blows to the first branch 21, the temperature difference between the circulating wind which has not been cooled and the refrigerant in the first branch 21 is relatively large, and it is known from the fourier heat conduction law that the larger the temperature gradient, the faster the heat conduction, and the higher the heat conduction efficiency.
Specifically, the temperature is a reaction indicating the degree of cold or heat of an object macroscopically, but is microscopically the degree of intense thermal movement of molecules inside the object, and the higher the temperature is, the more intense the thermal movement of molecules is. The heat transfer between the objects is essentially the transfer of energy by impact from thermal motion between molecules. The larger the temperature difference between the two objects, the larger the probability of collision of molecules on both sides, the better the interaction effect with each other, the more energy is transferred through collision, and the faster the heat transfer speed.
However, when the circulating wind blows to a branch on the downstream side, for example, the fourth branch 24, the circulating wind passes through the heat exchange of the preceding several branches, and the temperature is already greatly reduced, while the flow rate and temperature of the refrigerant in the fourth branch 24 are still consistent with those of the refrigerant in the first branch 21, at which time the heat transfer rate between the circulating wind at a relatively low temperature and the refrigerant in the fourth branch 24 inevitably becomes slow, and the heat exchange efficiency therebetween inevitably decreases. In other words, the fourth branch 24 uses as much refrigerant as the first branch 21, but the refrigerating effect of the first branch 21 is not achieved, and the refrigerating efficiency is greatly reduced.
Thus, the evaporator 100 of the conventional art faces the following technical problems: on the one hand, since the refrigerating efficiency of the refrigerant located at the downstream side of the wind direction 3 is lowered, the waste of the refrigerating capacity at the downstream side is caused to some extent, in other words, the flow rate of each layer of the refrigerant is uniformly distributed in the multi-layer pipeline, which inevitably results in a deterioration of the overall use efficiency of the refrigerant. On the other hand, too much refrigerant is distributed in the pipes located downstream of the wind direction 3, which tends to cause excessive decrease in the temperature of the circulating wind on the downstream side, and thus frost and ice are formed on the surfaces of the cooling pipes on the downstream side, affecting the service life and cooling effect of the evaporator 100.
In order to solve the above technical problem, in the present utility model, in the operating state of the evaporator 100, the single branch located on the upstream side of the wind direction 3 in the second flow path 2 passes a larger flow rate of the refrigerant than the single branch located on the downstream side of the wind direction 3. Specifically, as shown in fig. 1, the flow rates of the refrigerant flowing into the first branch 21, the second branch 22, the third branch 23, and the fourth branch 24 are sequentially reduced, so that the flow rate distribution of the refrigerant is optimized, and the uniformity of the surface temperature of the evaporator 100 and the use efficiency of the refrigerant are improved.
In the operation process, when the circulating air just blows to the first branch 21, the temperature difference between the circulating air which is not cooled and the refrigerant in the first branch 21 is relatively large, heat conduction between the circulating air and the refrigerant is relatively quick, heat conduction efficiency is relatively high, and at the moment, the first branch 21 has relatively large refrigerant flow, so that the maximization of refrigeration benefit can be realized. However, when the circulating wind blows to the branch on the downstream side, for example, the fourth branch 24, the circulating wind passes through the heat exchange of the previous branches, the temperature is greatly reduced, and the flow rate of the refrigerant in the fourth branch 24 is also reduced compared with the flow rate of the refrigerant in the previous branches, so that the waste of the refrigerating capacity is avoided, and the excessive cooling of the circulating wind on the downstream side is also avoided.
Accordingly, on one hand, the flow of the refrigerant is reduced layer by layer along the direction of the wind direction 3 by reasonably adjusting the flow distribution of the refrigerant, so that the use benefit of the refrigerant is improved; on the other hand, the temperature reduction range of the circulating air at the downstream side is reduced, so that the surface temperature distribution of the evaporator 100 is more uniform, the problem of frosting and icing of a refrigerating pipeline at the downstream side is avoided, the service life is prolonged, and the temperature reduction effect is ensured.
Example one
Next, a specific description of the first embodiment will be continued with reference to fig. 1.
As an example, as shown in fig. 1, the first flow path 1 extends substantially in the direction of the wind direction 3 of the circulating wind, and the cross-sectional area of the first flow path 1 decreases as it approaches the downstream side of the wind direction 3. That is, the first flow path 1 gradually decreases in cross-sectional area in the direction from the first branch 21 to the fourth branch 24, and the flow resistance of the refrigerant gradually increases.
Thus, the flow rate of the refrigerant is sequentially reduced while flowing from the first flow path 1 into the first branch 21, the second branch 22, the third branch 23, and the fourth branch 24, respectively. It will be appreciated that the magnitude of the variation in the refrigerant flow in the different branches can be achieved by adjusting the gradient of the variation in the cross-sectional area of the first flow path 1. In other words, by the variation in the sectional area of the first flow path 1, the distribution adjustment of the refrigerant flow rate in the branches of different stages is achieved.
The first flow path 1 is not limited to extending in the direction of the wind direction 3, and the extending direction of the first flow path 1 may be intersecting with the extending direction of the first branch 21, the second branch 22, the third branch 23, and the fourth branch 24, and is not particularly limited.
According to the technical scheme of the embodiment, on the premise of not changing the pipeline sectional areas of the first branch 21, the second branch 22, the third branch 23 and the fourth branch 24, the optimized distribution of the refrigerant flow can be realized by only changing the pipeline sectional area of the first flow path 1, so that the use benefit of the refrigerant is improved, the surface temperature distribution of the evaporator 100 is more uniform, the structure is simple, the processing is convenient, and excessive cost is not increased.
Example two
Next, a second embodiment will be specifically described with reference to fig. 2. Fig. 2 is a schematic view of an evaporator flow path according to the second embodiment.
As another embodiment, as shown in fig. 2, the cross-sectional areas of the first branch 21, the second branch 22, the third branch 23 and the fourth branch 24, which are communicated with the first flow path 1, become smaller in sequence, that is, the pipelines from the first branch 21 to the second branch 22 to the third branch 23 to the fourth branch 24 become thinner gradually, and each branch is intersected with the wind direction 3 of the circulating wind. Accordingly, from the upstream side to the downstream side of the wind direction 3, the flow rate of the refrigerant allowed to pass through in the different branch paths also becomes gradually smaller, and the flow resistance of the refrigerant in the different branch paths becomes gradually larger.
According to the aspect of this embodiment, the sectional area of the first flow path 1 can be kept constant, and the flow rate of the refrigerant can be adjusted by adjusting the thickness of each branch from the upstream side to the downstream side of the wind direction 3. The magnitude of the variation of the refrigerant flow in the different branches can be realized by adjusting the cross-sectional area of the different branches.
It will of course be appreciated that the lines of the first flow path 1 may also taper in the direction of the wind direction 3 and co-act with the branches of the second flow path 2 to achieve a better flow regulation.
In this embodiment, the first flow path 1 is not limited to extend in the direction of the wind direction 3, and may extend in a direction substantially perpendicular to the wind direction 3, and may branch into four paths at the connection point with the second flow path 2, and may communicate with the first branch 21, the second branch 22, the third branch 23, and the fourth branch 24, respectively, and is not particularly limited herein.
In summary, the evaporator 100 of the present utility model is located at the upstream side of the wind direction 3 of the circulating wind, the temperature of the circulating wind is higher, and the heat exchange efficiency between the circulating wind and the refrigerant is also relatively higher, so that the refrigerating efficiency is improved by inputting a larger flow rate of the refrigerant, and a better cooling effect is achieved.
The closer to the downstream side of the wind direction 3, the lower the heat exchange efficiency between the circulating wind and the refrigerant, and at this time, the waste of the cooling capacity is avoided by inputting a smaller flow rate of the refrigerant. On one hand, the distribution of the refrigerant can be more scientific, and the use benefit of the refrigerant is improved. On the other hand, the circulating wind at the downstream side of the wind direction 3 can be prevented from being cooled too much, so that the surface of the evaporator 100 is frosted and frozen, and the service life of the equipment is prolonged.
As an example, as shown in fig. 1, a small-diameter pipe 4 is further connected to the inlet end of the first flow path 1, and the small-diameter pipe 4 has an inner diameter smaller than that of the first flow path 1. As a preferable mode, the connection between the small-diameter pipeline 4 and the first flow path 1 is in a gradually-expanding structure like a horn mouth, and the inner diameter is larger at a position closer to the first flow path 1, namely, the connection between the small-diameter pipeline 4 and the first flow path 1 is in a gradually-expanding structure.
Accordingly, when the refrigerant flows from the thin small diameter pipe 4 into the thick first flow path 1, the flow velocity of the refrigerant gradually decreases due to the gradual increase of the inner diameter, and unnecessary collision with the pipe wall is reduced, thereby reducing noise generated by rapid flow of the refrigerant. In this case, the evaporator 100 is a so-called roll-to-roll evaporator.
It should be understood that the above embodiments are only for explaining the present utility model, the protection scope of the present utility model is not limited thereto, and any person skilled in the art should be able to modify, replace and combine the technical solution and concept according to the present utility model within the scope of the present utility model.
Claims (5)
1. An evaporator provided in a circulation duct, the evaporator having a first flow path through which a refrigerant flows and a plurality of second flow paths that communicate with the first flow path, respectively, and that are located on a downstream side of the first flow path, each of the plurality of second flow paths extending in a direction intersecting with a direction of a circulation wind in the circulation duct;
in the operating state of the evaporator, the refrigerant flows from the first flow path into each of the plurality of second flow paths, and the circulating air in the circulating air duct blows through each of the second flow paths in turn;
the method is characterized in that:
in the operating state of the evaporator, the plurality of second flow paths are configured such that a flow rate of the refrigerant passing through a second flow path located on an upstream side of the circulating wind is larger than a flow rate of the refrigerant passing through a second flow path located on a downstream side of the circulating wind.
2. The evaporator according to claim 1, wherein:
the extending direction of the first flow path intersects with the extending direction of each of the plurality of second flow paths, and the cross-sectional area of the first flow path is smaller as the first flow path is closer to the downstream side of the circulating wind.
3. The evaporator according to claim 1, wherein:
the plurality of second flow paths are configured such that, of two adjacent second flow paths, a second flow path located on an upstream side of the circulating wind has a larger flow rate of the refrigerant allowed to pass therethrough than a second flow path located on a downstream side of the circulating wind has a larger flow rate of the refrigerant allowed to pass therethrough.
4. A vaporizer according to claim 3, wherein:
the plurality of second flow paths are substantially parallel and are multilayer pipes arranged in sequence along the wind direction of the circulating wind.
5. A refrigerator, comprising a refrigerator body, a compressor and a circulating air duct positioned in the refrigerator body;
the method is characterized in that:
further comprising the evaporator of any one of claims 1-4.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223456518.5U CN219390141U (en) | 2022-12-23 | 2022-12-23 | Evaporator and refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202223456518.5U CN219390141U (en) | 2022-12-23 | 2022-12-23 | Evaporator and refrigerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN219390141U true CN219390141U (en) | 2023-07-21 |
Family
ID=87200241
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202223456518.5U Active CN219390141U (en) | 2022-12-23 | 2022-12-23 | Evaporator and refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN219390141U (en) |
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2022
- 2022-12-23 CN CN202223456518.5U patent/CN219390141U/en active Active
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