CN201392047Y - Multi-machine parallel partial pressure evaporative cooling (hot) water unit - Google Patents
Multi-machine parallel partial pressure evaporative cooling (hot) water unit Download PDFInfo
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 75
- 238000001816 cooling Methods 0.000 title description 5
- 238000001704 evaporation Methods 0.000 claims abstract description 84
- 230000008020 evaporation Effects 0.000 claims abstract description 67
- 239000003507 refrigerant Substances 0.000 claims abstract description 20
- 239000000498 cooling water Substances 0.000 claims 1
- 238000012423 maintenance Methods 0.000 abstract description 3
- 238000005057 refrigeration Methods 0.000 description 19
- 238000000034 method Methods 0.000 description 11
- 230000006835 compression Effects 0.000 description 10
- 238000007906 compression Methods 0.000 description 10
- 238000004378 air conditioning Methods 0.000 description 8
- 238000010586 diagram Methods 0.000 description 8
- 239000007788 liquid Substances 0.000 description 5
- 238000007791 dehumidification Methods 0.000 description 4
- 238000004140 cleaning Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000008014 freezing Effects 0.000 description 2
- 238000007710 freezing Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000004364 calculation method Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
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Abstract
本实用新型涉及一种多机并联分压蒸发冷(热)水机组，它包括冷凝器、两个或两个以上的压缩机、蒸发器冷水进水管、蒸发器冷水出水管、制冷剂管，它还包括与压缩机数量相同的蒸发单元以及与压缩机数量相同的节流阀，所述的多个节流阀、多个蒸发单元、多个压缩机依序连接后与一个冷凝器连接组成一个循环***；多个蒸发单元沿水流方向并排连接组合成蒸发器，前一个蒸发单元的冷水出口管连接后一个蒸发单元的冷水进水管，如此依序连接构成并联的蒸发器。本实用新型具有节能降耗，维修方便等优点。
The utility model relates to a multi-machine parallel partial pressure evaporative cold (hot) water unit, which comprises a condenser, two or more than two compressors, an evaporator cold water inlet pipe, an evaporator cold water outlet pipe, and a refrigerant pipe. It also includes the same number of evaporation units as the number of compressors and the same number of throttle valves as the number of compressors. The multiple throttle valves, multiple evaporation units, and multiple compressors are connected in sequence and connected to a condenser. A circulation system; multiple evaporating units are connected side by side along the water flow direction to form an evaporator, and the cold water outlet pipe of the previous evaporating unit is connected to the cold water inlet pipe of the next evaporating unit, so that they are connected in sequence to form a parallel evaporator. The utility model has the advantages of energy saving, consumption reduction, convenient maintenance and the like.
Description
技术领域： Technical field:
本实用新型涉及一种多机并联分压蒸发冷(热)水机组。The utility model relates to a multi-machine parallel connection partial pressure evaporative cold (hot) water unit.
背景技术： Background technique:
现有的空调用多机压缩冷(热)水机组，由于受早期设计理念的限制，都设计成单蒸发器单压蒸发***以简化其结构及降低成本。其***原理图如图3所示，其工作过程主要为(为叙述方便省略了辅助部件并以制冷过程为例)：制冷剂在蒸发器内蒸发成蒸汽，蒸发时吸收汽化潜热(产生了冷量)而将盘管外的冷水温度降低产生低温冷水。为了使蒸发器中的蒸发过程(制冷过程)能持续不断进行下去，需不断补充制冷剂液体并排走蒸发器内所产生的蒸汽。多个并联的压缩机(吸汽口及排汽口都并联连接)从蒸发器中吸走制冷剂蒸汽并将其压缩而变成了高温高压的制冷剂蒸汽；高温高压的制冷剂蒸汽从压缩机的排汽口排出沿制冷剂管流向冷凝器。在冷凝器中，制冷剂蒸汽在高压下被冷却放出热量，又变成了制冷剂液体以供蒸发器蒸发制冷用。由于蒸发温度与蒸发压力成正比，为了得到冷水所需的低蒸发温度，需用节流装置对制冷剂液体节流降压以产生低压；降压后的制冷剂液体又重新流入蒸发器中蒸发制冷，如此就实现了一个制冷循环。只要压缩机不停止工作，这种制冷循环就会一直进行下去。Due to the limitation of early design concepts, the existing multi-machine compression cold (hot) water units for air conditioners are all designed as single-evaporator single-pressure evaporation systems to simplify their structure and reduce costs. The schematic diagram of the system is shown in Figure 3, and its working process is mainly as follows (the auxiliary components are omitted for the convenience of description and the refrigeration process is taken as an example): the refrigerant evaporates into steam in the evaporator, and absorbs the latent heat of vaporization during evaporation (generating cold amount) to reduce the temperature of the cold water outside the coil to produce low-temperature cold water. In order to make the evaporation process (refrigeration process) in the evaporator continue continuously, it is necessary to continuously replenish the refrigerant liquid and discharge the steam generated in the evaporator. Multiple parallel compressors (steam suction and exhaust ports are connected in parallel) suck the refrigerant vapor from the evaporator and compress it to become a high-temperature and high-pressure refrigerant vapor; the high-temperature and high-pressure refrigerant vapor is compressed from the The exhaust port of the machine is discharged along the refrigerant pipe to the condenser. In the condenser, the refrigerant vapor is cooled under high pressure to release heat, and then becomes a refrigerant liquid for the evaporator to evaporate and refrigerate. Since the evaporating temperature is directly proportional to the evaporating pressure, in order to obtain the low evaporating temperature required by cold water, a throttling device is required to throttle and reduce the pressure of the refrigerant liquid to generate a low pressure; the depressurized refrigerant liquid flows into the evaporator again to evaporate Refrigeration, thus realizing a refrigeration cycle. As long as the compressor does not stop working, this refrigeration cycle will continue.
这种冷(热)水机组的缺点在于：(1)虽然在冷(热)水流过蒸发器的过程中水温是逐步下降(上升)的，但由于制冷***只有一个蒸发器，因而这个蒸发压力只能由温度最低(高)的蒸发器出口水温决定，制冷循环中无法利用冷水降温过程中前端的相对高温，根据制冷原理，蒸发温度(压力)越低，制冷效率就越低；表示其制冷效率与蒸发温度间关系的等效卡诺循环示意图见图5；(2)由于单蒸发器冷(热)水机组蒸发压力下降时效率降低很快，限制了低温冷水和大温差(大的机组冷水进出口温差)技术的利用。提高供回水温差对提高空调***能量利用效率有很大的潜力，降低冷水温出水度对空调***除湿性能有很大的影响，而除湿效率的提高也可显著提高空调***空气处理过程中的能量利用效率；(3)制冷过程中，单蒸发器冷水进出口温差大，出口水温在冰点附近时，蒸发器内易产生因换热死角而导致局部过冷结冰，损坏机组。The disadvantages of this cold (hot) water unit are: (1) Although the water temperature gradually drops (rises) when the cold (hot) water flows through the evaporator, since the refrigeration system has only one evaporator, the evaporation pressure It can only be determined by the water temperature at the outlet of the evaporator with the lowest temperature (highest), and the relatively high temperature at the front end of the cold water cooling process cannot be used in the refrigeration cycle. According to the principle of refrigeration, the lower the evaporation temperature (pressure), the lower the refrigeration efficiency; The equivalent Carnot cycle schematic diagram of the relationship between efficiency and evaporation temperature is shown in Figure 5; (2) Since the efficiency of the single evaporator cold (hot) water unit decreases rapidly when the evaporation pressure drops, the low temperature cold water and the large temperature difference (large unit Cold water inlet and outlet temperature difference) technology utilization. Increasing the temperature difference between supply and return water has a great potential to improve the energy utilization efficiency of the air conditioning system, and reducing the cold water temperature and outlet temperature has a great impact on the dehumidification performance of the air conditioning system, and the improvement of dehumidification efficiency can also significantly improve the air conditioning system in the process of air treatment. Energy utilization efficiency; (3) During the refrigeration process, the temperature difference between the inlet and outlet of the cold water of the single evaporator is large, and when the outlet water temperature is near the freezing point, the evaporator is prone to local overcooling and freezing due to heat exchange dead angles, which will damage the unit.
实用新型内容： Utility model content:
本实用新型的目的在于提供一种节能降耗的多机并联分压蒸发冷(热)水机组。The purpose of the utility model is to provide an energy-saving and consumption-reducing multi-machine parallel partial pressure evaporative cold (hot) water unit.
本实用新型包括它包括冷凝器、两台或两台以上的压缩机、蒸发器冷水进水管、蒸发器冷水出水管、制冷剂管，其特征在于：它还包括与压缩机数量相同的蒸发单元以及与压缩机数量相同的节流阀，由多个节流阀、多个蒸发单元、多个压缩机依序连接后与一个冷凝器连接组成一个循环***；多个蒸发单元沿水流方向串联连接组合成蒸发器，前一个蒸发单元的冷水出口连接后一个蒸发单元的冷水进水口，如此依序串联连接构成组合式蒸发器，蒸发器冷水进水管从蒸发器的一侧接入，蒸发器冷水出水管从蒸发器的另一侧导出。The utility model includes a condenser, two or more compressors, an evaporator cold water inlet pipe, an evaporator cold water outlet pipe, and a refrigerant pipe, and is characterized in that it also includes an evaporation unit with the same number as the compressor As well as the same number of throttle valves as the number of compressors, multiple throttle valves, multiple evaporation units, multiple compressors are connected in sequence and then connected to a condenser to form a circulation system; multiple evaporation units are connected in series along the direction of water flow Combined into an evaporator, the cold water outlet of the previous evaporator unit is connected to the cold water inlet of the next evaporator unit, so that they are connected in series to form a combined evaporator. The cold water inlet pipe of the evaporator is connected from one side of the evaporator, and the cold water of the evaporator The outlet pipe leads from the other side of the evaporator.
本实用新型具有下述优点：(1)由于对每台压缩机设置了独立的蒸发单元并将蒸发单元按水流方向顺序排列，蒸发单元两端不封闭，机组运行时各蒸发单元内的的制冷剂液体可在不同的压力下进行蒸发。机组运行时蒸发器进出口水温存在温差，各级蒸发单元的蒸发温度是逐步下降而不是由蒸发器出口水温决定，因而提高了机组的平均蒸发温度，提高了机组的能效比。(2)可更安全更高效地产生更低温度的冷水，减缓了因机组冷(热)水出口温度下降(或升高)而引起的效率降低，提高机组的综合能效比。更低温的冷水冷源在空调***的空气处理过程中有更高的除湿效率及更大的节能潜力。(3)可更高效地实现大温差供回水，而大温差冷源有利于中央空调***高效地实现空调负荷的“分质”处理，这是以前的空调***中是难以实现的。(4)蒸发单元可按蒸发量范围分成有限的几个系列，同系列不同蒸发量的蒸发单元采取标准接口，不同压缩机所匹配的蒸发单元只是厚度(长度)不同，因而可方便地组合成任意所需的蒸发器；(5)组装式蒸发器更便于维修，更换和内部清洗；(6)由蒸发单元组合成的蒸发器有利于蒸发器标准化流水线生产以降低成本。The utility model has the following advantages: (1) Since each compressor is provided with an independent evaporation unit and the evaporation units are arranged in sequence according to the direction of water flow, the two ends of the evaporation unit are not closed, and the refrigeration in each evaporation unit when the unit is running The agent liquid can be evaporated under different pressures. When the unit is running, there is a temperature difference between the inlet and outlet water temperatures of the evaporator, and the evaporation temperature of the evaporation units at each level is gradually reduced rather than determined by the outlet water temperature of the evaporator, thus increasing the average evaporation temperature of the unit and improving the energy efficiency ratio of the unit. (2) It can produce cold water at a lower temperature more safely and efficiently, slow down the efficiency reduction caused by the temperature drop (or rise) of the cold (hot) water outlet of the unit, and improve the overall energy efficiency ratio of the unit. The lower temperature cold water cooling source has higher dehumidification efficiency and greater energy saving potential in the air treatment process of the air conditioning system. (3) Water supply and return with a large temperature difference can be realized more efficiently, and the cold source with a large temperature difference is beneficial to the central air-conditioning system to efficiently realize the "quality-based" processing of the air-conditioning load, which was difficult to achieve in the previous air-conditioning system. (4) Evaporation units can be divided into several limited series according to the evaporation range. Evaporation units of the same series with different evaporation rates adopt standard interfaces. Evaporation units matched with different compressors are only different in thickness (length), so they can be easily combined into Any required evaporator; (5) The assembled evaporator is more convenient for maintenance, replacement and internal cleaning; (6) The evaporator composed of evaporation units is conducive to the standardized assembly line production of the evaporator to reduce costs.
附图说明： Description of drawings:
图1为本实用新型的结构示意图。Fig. 1 is the structural representation of the utility model.
图2为本实用新型中蒸发单元构成的蒸发器的结构示意图。Fig. 2 is a structural schematic diagram of an evaporator composed of an evaporating unit in the present invention.
图3为现在技术的结构示意图。Fig. 3 is a schematic structural diagram of the current technology.
图4为本实用新型的制冷效率与蒸发温度间关系的等效卡诺循环示意图。Fig. 4 is a schematic diagram of an equivalent Carnot cycle of the relationship between refrigeration efficiency and evaporation temperature of the present invention.
图5为现有技术的制冷效率与蒸发温度间关系的等效卡诺循环示意图。FIG. 5 is a schematic diagram of an equivalent Carnot cycle of the relationship between refrigeration efficiency and evaporation temperature in the prior art.
标号说明：1压缩机、2冷凝器、3节流阀；4蒸发器；5蒸发器冷水进水管、6蒸发器冷水出水管；7制冷剂管、8蒸发单元、81蒸发盘管、82外壳、83法兰、9蒸发器端盖、10、蒸发器。Explanation of symbols: 1 compressor, 2 condenser, 3 throttle valve; 4 evaporator; 5 cold water inlet pipe of evaporator, 6 cold water outlet pipe of evaporator; 7 refrigerant pipe, 8 evaporation unit, 81 evaporation coil, 82 shell , 83 flange, 9 evaporator end cover, 10, evaporator.
具体实施方式： Detailed ways:
如图1所示，本实用新型包括冷凝器2、两个或两个以上的压缩机1、蒸发器冷水进水管5、蒸发器冷水出水管6、制冷剂管7、与压缩机数量相同的蒸发单元8以及与压缩机数量相同的节流阀3，由一个压缩机与一个蒸发单元和一个节流阀依序连接组成一个单元，多个单元之间并联排列后与一个冷凝器串联连接组成一个循环***。As shown in Figure 1, the utility model includes a
多个蒸发单元沿水流方向串联连接组合成蒸发器，前一个蒸发单元的冷水出口连接后一个蒸发单元的冷水进口，如此依序连接构成串联组合的蒸发器8。蒸发器冷水进水管5从蒸发器的一侧接入，蒸发器冷水出水管6从蒸发器的另一侧导出。由于对每台压缩机设置了独立蒸发单元，并将蒸发单元按水流方向顺序排列，蒸发单元两端不封闭，机组运行时各单元式蒸发可在不同的压力下进行。机组运行时蒸发器进出口水温存在温差，各级蒸发单元的蒸发温度是逐步下降而不是由蒸发器出口水温决定，因而提高了机组的平均蒸发温度，提高了机组的能效比。同时可更安全更高效地产生更低温度的冷水，减缓了机组冷水出口温度下降(或升高)而引起的效率降低，提高机组的综合能效比。更低温的冷水冷源在空调***的空气处理过程中有更高的除湿效率及更大的节能潜力。A plurality of evaporating units are connected in series along the water flow direction to form an evaporator, and the cold water outlet of the previous evaporating unit is connected to the cold water inlet of the following evaporating unit, so that the evaporators 8 are connected in series to form a series combination. The evaporator cold
如图2所示，蒸发单元分为蒸发盘管81与外壳82两部分，外壳82为筒状，外壳内设有蒸发盘管81，两端不封闭且设有法兰83，蒸发器两端设有蒸发器端盖9。通过设置法兰，可以使蒸发单元两两连接，并使蒸发器两端的蒸发单元与蒸发器端盖相连。As shown in Figure 2, the evaporating unit is divided into two parts: an
蒸发单元按蒸发量范围分成有限的几个等级，不同等级的蒸发单元的接口相同。由于不同压缩机所匹配的蒸发单元只是厚度(长度)不同，因而可方便地串联组合成任意所需的蒸发器；采用组合式蒸发器更便于维修、更换和内部清洗；同时由蒸发单元串联所组成的蒸发器有利于蒸发器标准化流水线生产以降低成本。Evaporation units are divided into several limited grades according to the evaporation range, and the interfaces of different grades of evaporation units are the same. Since the evaporator units matched by different compressors are only different in thickness (length), they can be conveniently combined in series to form any desired evaporator; the use of combined evaporators is more convenient for maintenance, replacement and internal cleaning; The composed evaporator is conducive to the standardized assembly line production of the evaporator to reduce the cost.
下面结合图4图5对本实用新型与现有技术进行对比分析。Below in conjunction with Fig. 4 Fig. 5, the utility model and the prior art are comparatively analyzed.
如图5所示，图中：W为制冷所消耗的压缩功；TK为冷凝器中制冷剂蒸汽的冷凝温度；TO蒸发器中制冷剂的蒸发温度；As shown in Figure 5, in the figure: W is the compression work consumed by refrigeration; TK is the condensation temperature of the refrigerant vapor in the condenser; the evaporation temperature of the refrigerant in the TO evaporator;
即蒸发器中制冷剂的蒸发温度越低，面积越大，制冷所消耗的压缩功也越大，现有技术的制冷***中只有一个蒸发器，因而这个蒸发温度只能由温度最低的蒸发器出口水温决定，制冷循环中无法利用冷水降温过程中前端的相对高温，所以现有技术存在着不足之处。That is, the lower the evaporation temperature of the refrigerant in the evaporator, the larger the area, and the greater the compression work consumed by refrigeration. There is only one evaporator in the refrigeration system of the prior art, so the evaporation temperature can only be determined by the evaporator with the lowest temperature. The outlet water temperature is determined, and the relatively high temperature at the front end of the cold water cooling process cannot be used in the refrigeration cycle, so there are deficiencies in the prior art.
如图4所示，它是采用了3组压缩机的制冷效率与蒸发温度间关系的等效卡诺循环示意图，图中：W1第一台压缩机所消耗的压缩功；W2第二台压缩机所消耗的压缩功；W3第三台压缩机所消耗的压缩功；W1、W2下的阴影面积为本实用新型所节约的压缩功。As shown in Figure 4, it is a schematic diagram of the equivalent Carnot cycle using the relationship between the refrigeration efficiency of three compressors and the evaporation temperature. In the figure: the compression work consumed by the first compressor of W1; the compression work consumed by the second compressor of W2 The compression work consumed by the compressor; the compression work consumed by the third compressor of W3; the shadow area under W1 and W2 is the compression work saved by the utility model.
由于在第1组压缩机所对应的蒸发单元的出口处的水温较高，即制冷剂的蒸发温度高，故所消耗的压缩功较小，依此类推，最后一组蒸发单元的出口处的水温最低，制冷剂的蒸发温度低，故所消耗的压缩功最大。机组运行时蒸发器进出口水温存在温差，各级蒸发单元的蒸发温度是逐步下降而不是由蒸发器出口水温决定，因而提高了机组的平均蒸发温度，提高了机组的能效比，其等效卡诺循环示意图见图4。在假定冷凝温度都为40℃，蒸发器最终出水温度都为7℃，蒸发器进出口水温差都为5℃时，各压缩机均为同型号压缩机前提下，经计算，本实用新型在理论上比现有的冷水机组一般可提高制冷效率5％以上，而且蒸发器进出口水温差越大节能效果越好。Since the water temperature at the outlet of the evaporating unit corresponding to the first group of compressors is high, that is, the evaporation temperature of the refrigerant is high, the compression work consumed is small, and so on, the water at the outlet of the last group of evaporating units The water temperature is the lowest, and the evaporation temperature of the refrigerant is low, so the compression work consumed is the largest. When the unit is running, there is a temperature difference between the inlet and outlet water temperatures of the evaporator, and the evaporation temperature of the evaporation units at each level is gradually reduced rather than determined by the outlet water temperature of the evaporator, thus increasing the average evaporation temperature of the unit, improving the energy efficiency ratio of the unit, and its equivalent card A schematic diagram of the Noah cycle is shown in Figure 4. Assuming that the condensing temperature is 40°C, the final outlet water temperature of the evaporator is 7°C, and the water temperature difference between the inlet and outlet of the evaporator is 5°C, and all compressors are of the same type, after calculation, the utility model has a theoretical Generally, the refrigeration efficiency can be increased by more than 5% compared with the existing chillers, and the greater the water temperature difference between the inlet and outlet of the evaporator, the better the energy-saving effect.
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| CN200920137840U Expired - Fee Related CN201392047Y (en) | 2009-04-27 | 2009-04-27 | Multi-machine parallel partial pressure evaporative cooling (hot) water unit |
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| Country | Link |
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| CN (1) | CN201392047Y (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103217310A (en) * | 2013-04-28 | 2013-07-24 | 宁波沃弗圣龙环境技术有限公司 | Food freezer performance test device |
| CN105865066A (en) * | 2016-06-29 | 2016-08-17 | 湖南亚华乳业有限公司 | Combined-type raw milk fast cooling system based on non-azeotropic mixtures |
| CN106482372A (en) * | 2016-10-18 | 2017-03-08 | 章晓晓 | A kind of dehumidifier |
| CN111043782A (en) * | 2019-12-25 | 2020-04-21 | 中船重工（邯郸）派瑞特种气体有限公司 | Large-scale modularization refrigerating fluid refrigerating system |
| CN114111076A (en) * | 2021-11-08 | 2022-03-01 | 清华大学 | A modular non-azeotropic working medium relay evaporative refrigeration system and its control method |
-
2009
- 2009-04-27 CN CN200920137840U patent/CN201392047Y/en not_active Expired - Fee Related
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103217310A (en) * | 2013-04-28 | 2013-07-24 | 宁波沃弗圣龙环境技术有限公司 | Food freezer performance test device |
| CN103217310B (en) * | 2013-04-28 | 2016-05-25 | 南京师范大学 | A kind of food refrigerator performance testing device |
| CN105865066A (en) * | 2016-06-29 | 2016-08-17 | 湖南亚华乳业有限公司 | Combined-type raw milk fast cooling system based on non-azeotropic mixtures |
| CN106482372A (en) * | 2016-10-18 | 2017-03-08 | 章晓晓 | A kind of dehumidifier |
| CN106482372B (en) * | 2016-10-18 | 2019-01-01 | 章晓晓 | A kind of dehumidifier |
| CN111043782A (en) * | 2019-12-25 | 2020-04-21 | 中船重工（邯郸）派瑞特种气体有限公司 | Large-scale modularization refrigerating fluid refrigerating system |
| CN114111076A (en) * | 2021-11-08 | 2022-03-01 | 清华大学 | A modular non-azeotropic working medium relay evaporative refrigeration system and its control method |
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