CN103075846B - Condenser for forcibly transferring heat by reboiling - Google Patents
Condenser for forcibly transferring heat by reboiling Download PDFInfo
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- 239000003507 refrigerant Substances 0.000 abstract description 21
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- 238000005516 engineering process Methods 0.000 description 3
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Abstract
Description
技术领域 technical field
本发明涉及一种冷凝器强化传热技术，尤其是一种再沸腾强化传热的冷凝器。 The invention relates to a condenser heat transfer enhancement technology, in particular to a reboiling condenser heat transfer enhancement.
背景技术 Background technique
冷凝器是制冷系统中的重要部件，提高冷凝器传热系数对提高制冷系统性能、降低制冷设备体积和成本具有重要作用。在中小型制冷设备中，冷凝器一般管内通制冷剂，管外为冷却介质。 The condenser is an important part in the refrigeration system. Improving the heat transfer coefficient of the condenser plays an important role in improving the performance of the refrigeration system and reducing the volume and cost of refrigeration equipment. In small and medium-sized refrigeration equipment, the condenser generally has a refrigerant inside the tube and a cooling medium outside the tube.
目前，冷凝器管内强化传热的方法主要是针对制冷剂管内凝结换热进行设计，采用的方法主要为扩展表面法和流体旋转法。实际上制冷系统中制冷剂在冷凝器管内冷却经过三个过程，第一过程为过热蒸汽冷却过程，此过程的换热方式为气体强制对流，第二过程为气液两相凝结过程，此过程换热方式为凝结换热，第三过程为液体过冷过程，此过程换热方式为液体强制对流。在这三个过程中，过热蒸汽冷却过程的换热量约占冷凝器总换热量的1/3，换热面积约占总换热面积的1/2，此过程管内换热系数较小，仅为凝结换热系数的1/10～1/50；气液两相凝结过程换热量约占冷凝器总换热量的2/3，换热面积约占总换热面积的1/2，此过程管内换热系数最大；液体过冷过程换热量较少。显然，提高冷凝器的传热系数，其重点不仅仅是提高气液两相凝结过程的换热系数，对过热蒸汽冷却过程也需要采取有效的改善措施。 At present, the method of enhancing heat transfer in the condenser tube is mainly designed for the condensation heat transfer in the refrigerant tube, and the methods used are mainly the extended surface method and the fluid rotation method. In fact, in the refrigeration system, the refrigerant is cooled in the condenser tube through three processes. The first process is the superheated steam cooling process. The heat exchange method of this process is gas forced convection. The second process is the gas-liquid two-phase condensation process. The heat transfer method is condensation heat transfer, and the third process is liquid subcooling process, and the heat transfer method of this process is liquid forced convection. Among these three processes, the heat transfer of the superheated steam cooling process accounts for about 1/3 of the total heat transfer of the condenser, and the heat transfer area accounts for about 1/2 of the total heat transfer area. The heat transfer coefficient in the tube is relatively small in this process , which is only 1/10 to 1/50 of the condensation heat transfer coefficient; the gas-liquid two-phase condensation process accounts for about 2/3 of the total heat transfer heat of the condenser, and the heat transfer area accounts for about 1/ of the total heat transfer area 2. In this process, the heat transfer coefficient in the tube is the largest; the liquid supercooling process has less heat transfer. Obviously, the focus of improving the heat transfer coefficient of the condenser is not only to improve the heat transfer coefficient of the gas-liquid two-phase condensation process, but also to take effective improvement measures for the superheated steam cooling process.
发明内容 Contents of the invention
本发明的目的是克服现有技术的不足提供一种再沸腾强化传热的冷凝器，可以使制冷剂换热更多的在换热系数较大的气液两相区进行，同时重点对气液两相区凝结换热进行强化，从整体上提高冷凝器换热系数。 The purpose of the present invention is to overcome the deficiencies of the prior art and provide a condenser with reboiling enhanced heat transfer, which can make the refrigerant heat exchange more in the gas-liquid two-phase region with a larger heat transfer coefficient, and focus on the gas-liquid two-phase region. The condensation heat transfer in the liquid two-phase area is strengthened, and the heat transfer coefficient of the condenser is improved as a whole.
为了达到上述目的，本发明的一种技术是这样实现的，其是一种再沸腾强化传热的冷凝器，其特征在于包括: In order to achieve the above object, a technology of the present invention is achieved in that it is a condenser for reboiling enhanced heat transfer, which is characterized in that it comprises:
连接管，所述连接管的一端与压缩机的排气口联通； A connecting pipe, one end of the connecting pipe communicates with the exhaust port of the compressor;
分流器，所述分流器的一端与所述连接管的另一端联通； A flow divider, one end of the flow divider communicates with the other end of the connecting pipe;
第一分流管及第二分流管，所述第一分流管及第二分流管的一端分别与分流器的另一端联通；和 a first shunt pipe and a second shunt pipe, one end of the first shunt pipe and the second shunt pipe communicate with the other end of the shunt respectively; and
换热器，所述第一分流管的另一端与换热器的入口联通，所述第二分流管的另一端与换热器联通，第二分流管与换热器的联通位置离换热器的入口距离为换热器的总长度的0.3-0.62倍。 heat exchanger, the other end of the first shunt pipe communicates with the inlet of the heat exchanger, the other end of the second shunt pipe communicates with the heat exchanger, and the communication position between the second shunt pipe and the heat exchanger is away from the heat exchange The inlet distance of the heat exchanger is 0.3-0.62 times the total length of the heat exchanger.
为了达到上述目的，本发明的另一种技术是这样实现的，其是一种再沸腾强化传热的冷凝器，其特征在于包括: In order to achieve the above object, another technology of the present invention is achieved in that it is a condenser for reboiling enhanced heat transfer, which is characterized in that it comprises:
连接管，所述连接管的一端与压缩机的排气口联通； A connecting pipe, one end of the connecting pipe communicates with the exhaust port of the compressor;
分流器，所述分流器的一端与所述连接管的另一端联通； A flow divider, one end of the flow divider communicates with the other end of the connecting pipe;
第一分流管、第二分流管及第三分流管，所述第一分流管、第二分流管 The first shunt pipe, the second shunt pipe and the third shunt pipe, the first shunt pipe, the second shunt pipe
及第三分流管的一端分别与分流器的另一端联通；和 and one end of the third shunt pipe communicates with the other end of the shunt respectively; and
换热器，所述第一分流管的另一端与换热器的入口联通；所述第二分流管的另一端与换热器联通，第二分流管与换热器的联通位置离换热器的入口距离为换热器的总长度的0.2-0.5倍；所述第三分流管的另一端与换热器联通，第三分流管与换热器的联通位置离换热器的入口距离为换热器的总长度的0.5-0.8倍。 heat exchanger, the other end of the first shunt pipe communicates with the inlet of the heat exchanger; the other end of the second shunt pipe communicates with the heat exchanger, and the communication position between the second shunt pipe and the heat exchanger is away from the heat exchange The inlet distance of the heat exchanger is 0.2-0.5 times of the total length of the heat exchanger; the other end of the third shunt pipe communicates with the heat exchanger, and the communication position of the third shunt pipe and the heat exchanger is at a distance from the inlet of the heat exchanger It is 0.5-0.8 times of the total length of the heat exchanger.
本发明相对现有技术具有以下优点： The present invention has the following advantages relative to the prior art:
1）过热蒸汽冷却区的过热蒸汽冷却热负荷减少，大部分过热蒸汽冷却热负荷转移到换热系数较高的气液两相区，平均换热系数提高； 1) The superheated steam cooling heat load in the superheated steam cooling zone is reduced, and most of the superheated steam cooling heat load is transferred to the gas-liquid two-phase zone with a higher heat transfer coefficient, and the average heat transfer coefficient is increased;
2）在气液两相凝结换热过程加入制冷剂过热蒸汽，使部分液态制冷剂再次沸腾，凝结换热得到强化，换热系数进一步提高； 2) Add refrigerant superheated steam in the gas-liquid two-phase condensation heat transfer process, so that part of the liquid refrigerant boils again, the condensation heat transfer is strengthened, and the heat transfer coefficient is further improved;
3）气液两相凝结换热过程大部分在换热最佳的干度范围进行，换热系数得到提高。 3) Most of the gas-liquid two-phase condensation heat transfer process is carried out in the dryness range with the best heat transfer, and the heat transfer coefficient is improved.
附图说明 Description of drawings
图1是本发明实施例一的结构示意图； Fig. 1 is a schematic structural view of Embodiment 1 of the present invention;
图2是本发明实施二的结构示意图。 Fig. 2 is a schematic structural diagram of Embodiment 2 of the present invention.
具体实施方式 Detailed ways
下面详细描述本发明的实施例，所述实施例的示例在附图中示出，图中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，仅用于解释发明，而不能理解为对本发明的限制。 Embodiments of the present invention are described in detail below, examples of which are shown in the drawings, in which the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions. The embodiments described below by referring to the figures are exemplary only for explaining the invention and should not be construed as limiting the invention.
在本发明的描述中，术语“第一”、“第二”及“第三”仅用于描述目的，而不能理解为指示或暗示相对重要性。 In the description of the present invention, the terms "first", "second" and "third" are used for descriptive purposes only, and should not be understood as indicating or implying relative importance.
实施例一 Embodiment one
如图1所示，其是一种再沸腾强化传热的冷凝器，包括: As shown in Figure 1, it is a kind of condenser with reboiling enhanced heat transfer, comprising:
连接管1，所述连接管的一端与压缩机的排气口联通； Connecting pipe 1, one end of the connecting pipe communicates with the exhaust port of the compressor;
分流器2，所述分流器2的一端与所述连接管1的另一端联通； A flow divider 2, one end of the flow divider 2 communicates with the other end of the connecting pipe 1;
第一分流管3及第二分流管4，所述第一分流管3及第二分流管4的一端分别与分流器2的另一端联通；和 The first shunt pipe 3 and the second shunt pipe 4, one end of the first shunt pipe 3 and the second shunt pipe 4 communicate with the other end of the shunt 2 respectively; and
换热器5，所述第一分流管3的另一端与换热器5的入口联通，所述第二分流管4的另一端与换热器5联通，第二分流管4与换热器5的联通位置离换热器5的入口距离为换热器5的总长度的0.3-0.62倍。在本实施例中，第二分流管4与换热器5的联通位置离换热器5的入口距离为换热器5的总长度的0.52倍，也可以根据换热器5内制冷剂干度计算及排气温度和排气压力的变化来确定第二分流管4与换热器5的联通位置。 Heat exchanger 5, the other end of the first shunt pipe 3 communicates with the inlet of the heat exchanger 5, the other end of the second shunt pipe 4 communicates with the heat exchanger 5, and the second shunt pipe 4 communicates with the heat exchanger The distance between the communicating position of 5 and the inlet of heat exchanger 5 is 0.3-0.62 times of the total length of heat exchanger 5 . In this embodiment, the distance between the communication position between the second branch pipe 4 and the heat exchanger 5 and the entrance of the heat exchanger 5 is 0.52 times the total length of the heat exchanger 5, and it can also be determined according to the dryness of the refrigerant in the heat exchanger 5. The communication position between the second branch pipe 4 and the heat exchanger 5 is determined by temperature calculation and the change of exhaust temperature and exhaust pressure.
工作时，制冷系统压缩机排出的高温制冷剂过热蒸汽经连接管1进入分流器2分成两路，一路经第一分流管3从换热器5的入口进入换热管内，在过热蒸汽区进行强制对流换热，此部分高温制冷剂在过热蒸汽区内被逐步冷却到干蒸汽饱和温度并进入气液两相凝结区，进行凝结换热，随着凝结换热的进行，气液两相制冷剂干度从连接管1开始逐渐下降并进入换热最佳的干度范围，随着干度的进一步下降，开始偏离最佳换热干度区，此时，另一路高温制冷剂过热蒸汽经第二分流管4在距离换热器5的换热管入口距离为总长度的0.52倍范围内进入换热器5的两相凝结区，与两相区内的制冷剂进行混合，两相区内的部分液态制冷剂再次沸腾，使凝结换热得到进一步强化,最后经过过冷区后流出。 During operation, the high-temperature refrigerant superheated steam discharged from the compressor of the refrigeration system enters the flow divider 2 through the connecting pipe 1 and is divided into two paths, and one path passes through the first flow pipe 3 and enters the heat exchange tube from the entrance of the heat exchanger 5, and is carried out in the superheated steam area. Forced convection heat exchange, this part of the high-temperature refrigerant is gradually cooled to the saturation temperature of dry steam in the superheated steam area and enters the gas-liquid two-phase condensation area for condensation heat exchange. As the condensation heat exchange proceeds, the gas-liquid two-phase refrigeration The refrigerant dryness gradually decreases from the connecting pipe 1 and enters the optimum heat exchange dryness range. As the dryness further decreases, it begins to deviate from the optimum heat exchange dryness area. At this time, another high-temperature refrigerant superheated steam passes through The second branch pipe 4 enters the two-phase condensation zone of the heat exchanger 5 within a distance of 0.52 times the total length from the heat exchange tube inlet of the heat exchanger 5, and mixes with the refrigerant in the two-phase zone, and the two-phase zone Part of the liquid refrigerant inside boils again, which further strengthens the condensation heat transfer, and finally flows out after passing through the subcooling zone.
如图2所示，其是一种再沸腾强化传热的冷凝器，包括:连接管1，所述连接管的一端与压缩机的排气口联通； As shown in Figure 2, it is a kind of condenser that reboiling strengthens heat transfer, comprises: connecting pipe 1, and one end of described connecting pipe communicates with the exhaust port of compressor;
分流器2，所述分流器2的一端与所述连接管1的另一端联通；第一分流管3、第二分流管4及第三分流管6，所述第一分流管3、第二分流管4及第三分流管6的一端分别与分流器2的另一端联通；和换热器5，所述第一分流管3的另一端与换热器5的入口联通； A flow divider 2, one end of the flow divider 2 communicates with the other end of the connecting pipe 1; a first flow pipe 3, a second flow pipe 4 and a third flow pipe 6, the first flow pipe 3, the second flow pipe One end of the shunt pipe 4 and the third shunt pipe 6 communicate with the other end of the flow divider 2 respectively; and the heat exchanger 5, the other end of the first shunt pipe 3 communicates with the inlet of the heat exchanger 5;
所述第二分流管4的另一端与换热器5联通，第二分流管4与换热器5的联通位置离换热器5的入口距离为换热器5的总长度的0.2-0.5倍，在本实施例中，第二分流管4与换热器5的联通位置离换热器5的入口距离为换热器5的总长度的0.48，也可以根据换热器5内制冷剂干度计算及排气温度和排气压力的变化来确定第二分流管4与换热器5的联通位置；所述第三分流管6的另一端与换热器5联通，第三分流管6与换热器5的联通位置离换热器5的入口距离为换热器5的总长度的0.5-0.8倍，在本实施例中，第三分流管6与换热器5的联通位置离换热器5的入口距离为换热器5的总长度的0.7倍，也可以根据换热器5内制冷剂干度计算及排气温度和排气压力的变化来确定第三分流管6与换热器5的联通位置。 The other end of the second shunt pipe 4 communicates with the heat exchanger 5, and the distance between the second shunt pipe 4 and the heat exchanger 5 and the entrance distance of the heat exchanger 5 is 0.2-0.5 of the total length of the heat exchanger 5. times, in this embodiment, the distance between the communication position of the second branch pipe 4 and the heat exchanger 5 and the entrance of the heat exchanger 5 is 0.48 of the total length of the heat exchanger 5. Dryness calculation and changes in exhaust temperature and exhaust pressure to determine the communication position of the second branch pipe 4 and the heat exchanger 5; the other end of the third branch pipe 6 communicates with the heat exchanger 5, and the third branch pipe The distance between the communication position of 6 and the heat exchanger 5 and the entrance of the heat exchanger 5 is 0.5-0.8 times the total length of the heat exchanger 5. In this embodiment, the communication position of the third branch pipe 6 and the heat exchanger 5 The distance from the inlet of the heat exchanger 5 is 0.7 times the total length of the heat exchanger 5, and the third branch pipe 6 can also be determined according to the calculation of the refrigerant dryness in the heat exchanger 5 and the change of the exhaust temperature and exhaust pressure. The communication position with the heat exchanger 5.
工作时，制冷系统压缩机排出的高温制冷剂过热蒸汽经连接管1进入分流器2分成两路，一路经第一分流管3从换热器5的入口进入换热管内，在过热蒸汽区进行强制对流换热，此部分高温制冷剂在过热蒸汽区内被逐步冷却到干蒸汽饱和温度并进入气液两相凝结区，进行凝结换热，随着凝结换热的进行，气液两相制冷剂干度从连接管1开始逐渐下降并进入换热最佳的干度范围，随着干度的进一步下降，开始偏离最佳换热干度区，此时，另一路高温制冷剂过热蒸汽经第二分流管4在距离换热器5的换热管入口距离为换热器5的总长度的0.48倍范围内进入换热器5的两相凝结区，与两相区内的制冷剂进行混合，两相区内的部分液态制冷剂再次沸腾，使凝结换热得到进一步强化, 随之干度又下降，此时又一路高温制冷剂过热蒸汽经第三分流管6在距离换热器5的换热管入口距离为换热器5的总长度的0.7倍范围内再次进入换热器5的两相凝结区，使凝结换热得到强化,从而达到最佳的干度,最后经过过冷区后流出。 During operation, the high-temperature refrigerant superheated steam discharged from the compressor of the refrigeration system enters the flow divider 2 through the connecting pipe 1 and is divided into two paths, and one path passes through the first flow pipe 3 and enters the heat exchange tube from the entrance of the heat exchanger 5, and is carried out in the superheated steam area. Forced convection heat exchange, this part of the high-temperature refrigerant is gradually cooled to the saturation temperature of dry steam in the superheated steam area and enters the gas-liquid two-phase condensation area for condensation heat exchange. As the condensation heat exchange proceeds, the gas-liquid two-phase refrigeration The refrigerant dryness gradually decreases from the connecting pipe 1 and enters the optimum heat exchange dryness range. As the dryness further decreases, it begins to deviate from the optimum heat exchange dryness area. At this time, another high-temperature refrigerant superheated steam passes through The second branch pipe 4 enters the two-phase condensation zone of the heat exchanger 5 within a distance of 0.48 times the total length of the heat exchanger 5 from the entrance of the heat exchange tube of the heat exchanger 5, and conducts with the refrigerant in the two-phase zone. Mixing, part of the liquid refrigerant in the two-phase region boils again, which further strengthens the condensation heat transfer, and then the dryness decreases. The inlet distance of the heat exchange tube is 0.7 times the total length of the heat exchanger 5 and enters the two-phase condensation zone of the heat exchanger 5 again, so that the condensation heat transfer is strengthened, so as to achieve the best dryness, and finally after supercooling Area outflow.
尽管已经示出和描述了本发明的实施例，本领域的普通技术人员可以理解：在不脱离本发明的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换及变形，本发明的范围由权利要求及其等同物限定。 Although the embodiments of the present invention have been shown and described, those skilled in the art can understand that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principle and spirit of the present invention. The scope of the invention is defined by the claims and their equivalents.
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| CN110094902A (en) * | 2019-05-29 | 2019-08-06 | 珠海格力电器股份有限公司 | Refrigerant flow path and design method thereof |
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| JPH10111029A (en) * | 1996-10-04 | 1998-04-28 | Sanyo Electric Co Ltd | Vapor compression refrigerator |
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| JP2010261642A (en) * | 2009-05-01 | 2010-11-18 | Ｓ−Ｓｐｅｃ株式会社 | Condenser and air conditioner equipped with the same |
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| JPH094941A (en) * | 1995-06-21 | 1997-01-10 | Sanyo Electric Co Ltd | Refrigerating device |
| JPH10103796A (en) * | 1996-09-30 | 1998-04-21 | Sanyo Electric Co Ltd | Steam compression type refrigerating device |
| JPH10111029A (en) * | 1996-10-04 | 1998-04-28 | Sanyo Electric Co Ltd | Vapor compression refrigerator |
| JPH10238894A (en) * | 1997-02-26 | 1998-09-08 | Sanyo Electric Co Ltd | Heat exchanger |
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| JP2010261642A (en) * | 2009-05-01 | 2010-11-18 | Ｓ−Ｓｐｅｃ株式会社 | Condenser and air conditioner equipped with the same |
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| CN103075846A (en) | 2013-05-01 |
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