TW201809555A - Dehumidifier - Google Patents
Dehumidifier Download PDFInfo
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- TW201809555A TW201809555A TW106114773A TW106114773A TW201809555A TW 201809555 A TW201809555 A TW 201809555A TW 106114773 A TW106114773 A TW 106114773A TW 106114773 A TW106114773 A TW 106114773A TW 201809555 A TW201809555 A TW 201809555A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
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- Central Air Conditioning (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
本發明係有關於一種除濕裝置，尤其係有關於一種利用冷凍循環之除濕裝置。 The present invention relates to a dehumidifier, and more particularly to a dehumidifier using a refrigeration cycle.
在以往之利用冷凍循環的除濕裝置，在蒸發器對除濕裝置內所取入之空氣以蒸發器冷卻並除濕，在凝結器對在蒸發器所冷卻除濕的空氣進行加溫。 In the conventional dehumidifier using a refrigeration cycle, the air taken in the dehumidifier was cooled and dehumidified by the evaporator in the evaporator, and the air cooled and dehumidified in the evaporator was heated in the condenser.
作為表示除濕機之除濕性能的指標，已知表示每1kWh之除濕量L的EF值。除濕裝置係EF值愈高可愈減少耗電量。作為提高除濕裝置之EF值的方法，想到降低冷媒之凝結溫度，使凝結壓力與蒸發壓力之差變小，藉此，減少壓縮機的負載。 As an index indicating the dehumidification performance of a dehumidifier, an EF value indicating a dehumidification amount L per 1 kWh is known. The higher the EF value of the dehumidifier, the more power consumption can be reduced. As a method for increasing the EF value of the dehumidifier, it is thought to reduce the condensation temperature of the refrigerant so that the difference between the condensation pressure and the evaporation pressure becomes smaller, thereby reducing the load on the compressor.
以往之除濕裝置係因為在凝結器過熱氣體狀態的冷媒、氣液二相狀態的冷媒以及過冷卻液狀態的冷媒與已在蒸發器進行熱交換的空氣進行熱交換，所以無法使凝結溫度充分地降低。 In the conventional dehumidifier, the refrigerant in the superheated gas state of the condenser, the refrigerant in the gas-liquid two-phase state, and the refrigerant in the supercooled state exchanged heat with the air that had been heat-exchanged in the evaporator, so the condensation temperature could not be sufficiently reduce.
又，在特開平5-87417號公報(專利文獻1)，揭示一種除濕裝置，該除濕裝置係將凝結器的一部分形成於在蒸發器被進行熱交換之空氣的風路上，且將凝結器的剩下部分形成於在蒸發器未被進行熱交換之空氣的風路上。 In addition, Japanese Patent Application Laid-Open No. 5-87417 (Patent Document 1) discloses a dehumidifying device that forms a part of a condenser on an air path of air that is heat-exchanged in an evaporator, and decompresses the condenser. The remaining part is formed in the wind path of the air where the evaporator is not heat-exchanged.
[專利文獻1]特開平5-87417號公報 [Patent Document 1] Japanese Unexamined Patent Publication No. 5-87417
可是，在該專利文獻1所記載之除濕裝置，因為在凝結器之冷媒的出口被形成於在蒸發器未被進行熱交換之空氣的風路上，所以在凝結器無法充分地得到過冷卻度。結果，在該公報所記載之除濕裝置，因為難得到大的除濕量，所以難比以往之除濕裝置充分地提高EF值。 However, in the dehumidifier described in Patent Document 1, the outlet of the refrigerant in the condenser is formed on the air path of the air where the evaporator is not heat-exchanged, so the degree of subcooling cannot be sufficiently obtained in the condenser. As a result, it is difficult to obtain a large dehumidification amount in the dehumidifier described in this publication, and therefore it is difficult to sufficiently increase the EF value compared with the conventional dehumidifier.
本發明係為了解決如上述所示之課題而開發的，其目的在於提供一種EF值比以往之除濕裝置更高的的除濕裝置。 The present invention was developed to solve the problems as described above, and an object thereof is to provide a dehumidifier having an EF value higher than that of a conventional dehumidifier.
本發明之除濕裝置包括：冷媒迴路，係包含壓縮機、第1凝結器、第2凝結器、降壓裝置以及蒸發器；及框體，係將該冷媒迴路收容於內部。在冷媒迴路，冷媒係在壓縮機、第1凝結器、第2凝結器、降壓裝置以及蒸發器依序流通。框體係包含將第1風路與第2風路分離的隔開部，該第1風路係從框體的外部被取入內部之空氣的一部分通過第1凝結器，該第2風路係從框體的外部被取入內部之空氣的剩下部分依序通過蒸發器、第2凝結器。構成為在第1凝結器在過熱氣體狀態之冷媒與第1風路內的空氣之間進行熱交換，在第2凝結器在過冷卻液狀態之冷媒與第2風路內之通過蒸發器的空氣之間進行熱交換。 The dehumidifier according to the present invention includes a refrigerant circuit including a compressor, a first condenser, a second condenser, a pressure reducing device, and an evaporator; and a frame that houses the refrigerant circuit inside. In the refrigerant circuit, the refrigerant flows through the compressor, the first condenser, the second condenser, the pressure reducing device, and the evaporator in this order. The frame system includes a partition that separates the first air path from the second air path. The first air path is a part of the air taken in from the outside of the frame and passes through the first condenser. The second air path is The remainder of the air taken in from the outside of the casing passes through the evaporator and the second condenser in order. It is configured to perform heat exchange between the refrigerant in the supercondensed gas state of the first condenser and the air in the first air path, and the refrigerant in the supercooled liquid state of the second condenser and the evaporator passing through the second air path. Heat is exchanged between the air.
若依據本發明，可提供一種EF值比以往之除濕裝置更高的除濕裝置。 According to the present invention, a dehumidifier having an EF value higher than that of a conventional dehumidifier can be provided.
1‧‧‧壓縮機 1‧‧‧compressor
2‧‧‧第1凝結器 2‧‧‧The first condenser
3‧‧‧第2凝結器 3‧‧‧ 2nd condenser
4‧‧‧膨脹閥(減壓裝置) 4‧‧‧Expansion valve (decompression device)
5‧‧‧蒸發器 5‧‧‧Evaporator
6‧‧‧隔開部 6‧‧‧ partition
10‧‧‧框體 10‧‧‧Frame
11‧‧‧第1風路 11‧‧‧ the first wind road
12‧‧‧第2風路 12‧‧‧Second Wind Road
13‧‧‧第1開口部 13‧‧‧The first opening
14‧‧‧第2開口部 14‧‧‧The second opening
15‧‧‧送風部 15‧‧‧Air Supply Department
16‧‧‧調整部 16‧‧‧ Adjustment Department
17‧‧‧第3風路 17‧‧‧ 3rd wind road
100、101、102、103‧‧‧除濕裝置 100, 101, 102, 103‧‧‧ dehumidifier
第1圖係表示第1實施形態之除濕裝置的圖。 Fig. 1 is a diagram showing a dehumidifier according to a first embodiment.
第2圖係表示第1實施形態的除濕裝置之在第1凝結器及第2凝結器的冷媒與空氣之溫度變化的圖形。 Fig. 2 is a graph showing changes in temperature of the refrigerant and air in the first condenser and the second condenser of the dehumidifier according to the first embodiment.
第3圖係表示以往之除濕裝置的圖。 Fig. 3 is a diagram showing a conventional dehumidifier.
第4圖係表示第3圖所示的除濕裝置之在凝結器的冷媒與空氣之溫度變化的圖形。 Fig. 4 is a graph showing the temperature change of the refrigerant and air in the condenser of the dehumidifier shown in Fig. 3.
第5圖係表示第2實施形態之除濕裝置的圖。 Fig. 5 is a diagram showing a dehumidifier according to a second embodiment.
第6圖係表示第3實施形態之除濕裝置的圖。 Fig. 6 is a diagram showing a dehumidifier according to a third embodiment.
第7圖係表示第4實施形態的除濕裝置之第2風路的風量之對第1風路與第2風路之總風量的百分比和EF值之關係的圖形。 Fig. 7 is a graph showing the relationship between the air volume of the second air passage of the dehumidifier of the fourth embodiment and the percentage of the total air volume of the first air passage and the second air passage and the EF value.
第8圖係表示第5實施形態的除濕裝置之第2凝結器的導熱面積之對第1凝結器與第2凝結器之總導熱面積的百分比和EF值之關係的圖形。 Fig. 8 is a graph showing the relationship between the percentage of the heat transfer area of the second condenser of the dehumidifier of the fifth embodiment to the total heat transfer area of the first condenser and the second condenser and the EF value.
第9圖係表示第6實施形態之除濕裝置的圖。 Fig. 9 is a diagram showing a dehumidifier according to a sixth embodiment.
第10圖係表示第6實施形態的除濕裝置之在第1凝結器及第2凝結器之冷媒與空氣之溫度變化的圖形。 Fig. 10 is a graph showing temperature changes of the refrigerant and air in the first condenser and the second condenser of the dehumidifier according to the sixth embodiment.
以下，參照圖面，說明本發明之實施形態。在以 下的圖面，對相同或相當之部分附加相同的參照編號，其說明係不重複。 Hereinafter, embodiments of the present invention will be described with reference to the drawings. At In the drawings below, the same or corresponding parts are denoted by the same reference numerals, and descriptions thereof are not repeated.
(第1實施形態) (First Embodiment)
參照第1圖，第1實施形態之除濕裝置100包括：冷媒迴路，係包含壓縮機1、第1凝結器2、第2凝結器3、作為降壓裝置之膨脹閥4以及蒸發器5；及框體10，係將冷媒迴路收容於內部。第1凝結器2、第2凝結器3以及蒸發器5係在冷媒與空氣之間進行熱交換的熱交換器。各個第1凝結器2、第2凝結器3以及蒸發器5具有冷媒之入口與出口、及空氣之入口與出口。框體10係除濕裝置100面向作為除濕對象之外部空氣(起居室內空間)。 Referring to FIG. 1, the dehumidifier 100 according to the first embodiment includes a refrigerant circuit including a compressor 1, a first condenser 2, a second condenser 3, an expansion valve 4 as a pressure reducing device, and an evaporator 5; and The casing 10 houses the refrigerant circuit therein. The first condenser 2, the second condenser 3, and the evaporator 5 are heat exchangers that perform heat exchange between the refrigerant and the air. Each of the first condenser 2, the second condenser 3, and the evaporator 5 has an inlet and an outlet of a refrigerant, and an inlet and an outlet of air. The housing 10 is a dehumidifier 100 that faces outside air (a living room space) as a dehumidification target.
首先，說明除濕裝置100的冷媒迴路。除濕裝置100的冷媒迴路係在框體10內構成冷凍循環。在冷媒迴路，冷媒係依序在壓縮機1、第1凝結器2、第2凝結器3、膨脹閥4以及蒸發器5流通。具體而言，壓縮機1具有排出口與吸入口。各個第1凝結器2、第2凝結器3、膨脹閥4以及蒸發器5具有冷媒入口及冷媒出口。第1凝結器2之冷媒入口係與壓縮機1的排出口連接。第2凝結器3之冷媒入口係與第1凝結器2的冷媒出口連接。膨脹閥4之冷媒入口係與第2凝結器3的冷媒出口連接。蒸發器5之冷媒入口係與膨脹閥4的冷媒出口連接。壓縮機1的吸入口係與蒸發器5的冷媒出口連接。此外，降壓裝置係不是被限定為膨脹閥4，例如亦可是毛細管。 First, the refrigerant circuit of the dehumidifier 100 will be described. The refrigerant circuit of the dehumidifier 100 constitutes a refrigeration cycle in the casing 10. In the refrigerant circuit, the refrigerant system flows through the compressor 1, the first condenser 2, the second condenser 3, the expansion valve 4, and the evaporator 5 in this order. Specifically, the compressor 1 includes a discharge port and a suction port. Each of the first condenser 2, the second condenser 3, the expansion valve 4, and the evaporator 5 has a refrigerant inlet and a refrigerant outlet. The refrigerant inlet of the first condenser 2 is connected to the discharge outlet of the compressor 1. The refrigerant inlet of the second condenser 3 is connected to the refrigerant outlet of the first condenser 2. The refrigerant inlet of the expansion valve 4 is connected to the refrigerant outlet of the second condenser 3. The refrigerant inlet of the evaporator 5 is connected to the refrigerant outlet of the expansion valve 4. The suction inlet of the compressor 1 is connected to the refrigerant outlet of the evaporator 5. The pressure reducing device is not limited to the expansion valve 4 and may be, for example, a capillary tube.
第1凝結器2的導熱面積(在第1凝結器2與冷媒接觸之導熱管之表面積的總和)係以在第1凝結器2被進行熱 交換之空氣的溫度成為冷媒之凝結溫度以上的方式所形成。第2凝結器3的導熱面積(在第2凝結器3與冷媒接觸之導熱管之表面積的總和)係對第1凝結器2之導熱面積及第2凝結器3之導熱面積的和是25%以上較佳。 The heat-conducting area of the first condenser 2 (the total surface area of the heat-conducting tube in contact with the refrigerant in the first condenser 2) is such that the heat is conducted in the first condenser 2 The temperature of the exchanged air is formed such that the condensation temperature of the refrigerant is higher than the condensation temperature of the refrigerant. The heat transfer area of the second condenser 3 (the total surface area of the heat transfer tube in contact with the refrigerant in the second condenser 3) is the sum of the heat transfer area of the first condenser 2 and the heat transfer area of the second condenser 3 is 25% The above is better.
其次，說明除濕裝置100之空氣的流路(風路)。在框體10的內部，至少形成第1風路11與第2風路12之2條風路。在第1風路11內，至少被配置第1凝結器2。在第2風路12內，至少被配置第2凝結器3及蒸發器5。在第1風路11，從框體10的外部被取入內部之空氣的一部分通過第1凝結器2。在第2風路12，從框體10的外部被取入內部之空氣的剩下部分依序通過蒸發器5、第2凝結器3。第1風路11內之空氣的流通方向係例如與第2風路12內之空氣的流通方向平行。 Next, a flow path (air path) of air in the dehumidifier 100 will be described. Inside the housing 10, at least two air paths of the first air path 11 and the second air path 12 are formed. At least the first condenser 2 is arranged in the first air path 11. In the second air path 12, at least a second condenser 3 and an evaporator 5 are arranged. In the first air path 11, a part of the air taken in from the outside of the casing 10 passes through the first condenser 2. In the second air path 12, the remainder of the air taken in from the outside of the casing 10 passes through the evaporator 5 and the second condenser 3 in this order. The flow direction of the air in the first air path 11 is, for example, parallel to the flow direction of the air in the second air path 12.
具體而言，第1風路11係至少形成於從第1凝結器2的空氣入口至空氣出口之間。第2風路12係至少形成於從蒸發器5的空氣入口至第2凝結器3的空氣出口之間。第2風路12係與第1風路11分離。即，第1風路11及第2風路12係防止在兩者之間之直接性之空氣的出入。第2風路12係例如在第2風路12內之空氣的流通方向經由位於比蒸發器5的空氣入口更上游側的空間與第1風路11連接。第1風路11係在該流通方向經由位於比第2凝結器3的空氣出口更下游側的空間與第2風路12連接。 Specifically, the first air path 11 is formed at least from the air inlet to the air outlet of the first condenser 2. The second air path 12 is formed at least between the air inlet of the evaporator 5 and the air outlet of the second condenser 3. The second air path 12 is separated from the first air path 11. That is, the first air path 11 and the second air path 12 prevent direct air from entering and exiting therebetween. The second air path 12 is, for example, connected to the first air path 11 through a space located more upstream than the air inlet of the evaporator 5 in the air flow direction in the second air path 12. The first air path 11 is connected to the second air path 12 in the flow direction through a space located further downstream than the air outlet of the second condenser 3.
第1風路11與第2風路12係只要根據任意的方法分離即可，例如藉隔開部6分離。各個第1風路11及第2風路12係例如藉框體10及隔開部6所形成。在第2風路12 之空氣的流通方向，位於隔開部6之上游側的一端(上游端部)係至少形成於比蒸發器5之空氣出口更上游側，例如形成於比連接蒸發器5之冷媒出口與壓縮機1之吸入口的冷媒配管更上游側。隔開部6的該一端係例如形成於比蒸發器5之空氣入口更上游側。在該流通方向，位於隔開部6之下游側的另一端(下游端部)係至少形成於比第1凝結器2之空氣入口及第2凝結器3之空氣入口更下游側，例如形成於比連接第1凝結器2之冷媒出口與第2凝結器3之冷媒入口的冷媒配管更上游側。隔開部6的該另一端係例如形成於比第1凝結器2之空氣入口及第2凝結器3之空氣出口更下游側。隔開部6係具備任意的構成即可，例如形成為平板狀。隔開部6係被固定於框體10的內部。隔開部6係以任意的材料構成即可。 The first air path 11 and the second air path 12 may be separated by any method, for example, by the partition 6. Each of the first air path 11 and the second air path 12 is formed by, for example, the frame 10 and the partition 6. On the second wind road 12 The flow direction of the air is at least one end (upstream end) located on the upstream side of the partition 6 formed at least upstream than the air outlet of the evaporator 5. For example, it is formed more than the refrigerant outlet connected to the evaporator 5 and the compressor. The refrigerant pipe of the suction port of 1 is further upstream. The one end of the partition 6 is formed, for example, on the upstream side from the air inlet of the evaporator 5. In this flow direction, the other end (downstream end portion) located on the downstream side of the partition 6 is formed at least further downstream than the air inlet of the first condenser 2 and the air inlet of the second condenser 3, and is formed, for example, on It is further upstream than the refrigerant pipe connecting the refrigerant outlet of the first condenser 2 and the refrigerant inlet of the second condenser 3. The other end of the partition 6 is formed, for example, on the downstream side from the air inlet of the first condenser 2 and the air outlet of the second condenser 3. The partition 6 may have any configuration, and may be formed in a flat plate shape, for example. The partition 6 is fixed to the inside of the housing 10. The partition 6 may be made of any material.
在框體10，形成：第1開口部13，係用以從作為除濕對象之外部空間(起居室內空間)將空氣送入框體10的內部；及第2開口部14，係用以從內部將空氣送出至該外部空間。第1風路11及第2風路12係並列地形成於第1開口部13與第2開口部14之間。第1風路11之空氣的流通方向及第2風路12之空氣的流通方向係從第1開口部13往第2開口部14的方向。第1開口部13係在第1風路11之空氣的流通方向，形成於比第1風路11內之第1凝結器2的空氣入口更上游側，且比第2風路12內之蒸發器5的空氣入口更上游側。第2開口部14係在該流通方向，形成於比第1風路11內之第1凝結器2的空氣流出側更下游側，且比第2風路12之第2凝結器3的空氣流出側更下游側。 In the frame body 10, a first opening portion 13 is formed to send air into the frame body 10 from an external space (living room space) as a dehumidification target, and a second opening portion 14 is formed to receive air from the inside. Send air to the outside space. The first air passage 11 and the second air passage 12 are formed in parallel between the first opening portion 13 and the second opening portion 14. The air flow direction of the first air path 11 and the air flow direction of the second air path 12 are directions from the first opening portion 13 to the second opening portion 14. The first opening 13 is formed in the air flow direction of the first air path 11 and is formed on the upstream side of the air inlet of the first condenser 2 in the first air path 11 and evaporates more than the air in the second air path 12 The air inlet of the device 5 is further upstream. The second opening portion 14 is formed in this flow direction, and is formed on the downstream side from the air outflow side of the first condenser 2 in the first air path 11, and flows out of the air from the second condenser 3 of the second air path 12. More downstream side.
此外，在除濕裝置100，亦可在第1風路11內，除了被配置於第2風路12內的第2凝結器3及蒸發器5以外，配置構成冷媒迴路之任意的構件。例如，亦可在第1風路11內，配置壓縮機1。又，亦可在第2風路12內，除了被配置於第1風路內的第1凝結器2以外，配置構成冷媒迴路之任意的構件。例如，亦可在第2風路12內，配置膨脹閥4。 In addition, in the dehumidifying apparatus 100, in the first air path 11, in addition to the second condenser 3 and the evaporator 5 disposed in the second air path 12, arbitrary members constituting a refrigerant circuit may be disposed. For example, the compressor 1 may be arranged in the first air passage 11. In addition, in the second air path 12, any member constituting the refrigerant circuit may be disposed in addition to the first condenser 2 disposed in the first air path. For example, the expansion valve 4 may be arranged in the second air passage 12.
其次，參照第1圖及第2圖，說明除濕裝置100之除濕運轉時的動作。第2圖係表示除濕裝置100之在第1凝結器2及第2凝結器3的冷媒與空氣之溫度變化的圖形。第2圖之縱軸表示冷媒及空氣的溫度，橫軸下表示冷媒之流路，橫軸上表示空氣之流路。在第2圖，以In2與Out2表示第1凝結器2之冷媒入口及冷媒出口，以In3與Out3表示第2凝結器3之冷媒入口及冷媒出口。在第2圖，以In2’與Out2’表示第1凝結器2之空氣入口及空氣出口，以In3’與Out3’表示第2凝結器3之空氣入口及空氣出口。 Next, an operation during the dehumidifying operation of the dehumidifying device 100 will be described with reference to FIGS. 1 and 2. Fig. 2 is a graph showing changes in the temperature of the refrigerant and air in the first condenser 2 and the second condenser 3 of the dehumidifier 100. In FIG. 2, the vertical axis indicates the temperature of the refrigerant and air, the horizontal axis indicates the refrigerant flow path, and the horizontal axis indicates the air flow path. In FIG. 2, the refrigerant inlet and the refrigerant outlet of the first condenser 2 are represented by In2 and Out2, and the refrigerant inlet and the refrigerant outlet of the second condenser 3 are represented by In3 and Out3. In Fig. 2, the air inlet and air outlet of the first condenser 2 are shown by In2 'and Out2', and the air inlet and air outlet of the second condenser 3 are shown by In3 'and Out3'.
從壓縮機1所排出之過熱氣體狀態的冷媒係流入被配置於第1風路11內的第1凝結器2。流入第1凝結器2之溫度T1之過熱氣體狀態的冷媒係藉由與經由第1開口部13從外部空間被取入第1風路11內之溫度T6的空氣進行熱交換而被冷卻，成為凝結溫度T2之氣液二相狀態的冷媒。凝結溫度T2係溫度T6以上。 The refrigerant in the superheated gas state discharged from the compressor 1 flows into the first condenser 2 arranged in the first air passage 11. The refrigerant in the state of superheated gas at the temperature T1 flowing into the first condenser 2 is cooled by heat exchange with air having a temperature T6 taken into the first air passage 11 from the external space through the first opening 13 and becomes Gas-liquid two-phase refrigerant at condensation temperature T2. The coagulation temperature T2 is higher than the temperature T6.
另一方面，第1風路11內所取入之溫度T6的空氣係藉由在第1凝結器2與超過溫度T2且溫度T1以下之過熱氣體狀態的冷媒或溫度T2的氣液二相狀態與冷媒進行熱交換 而被加熱。藉此，已通過第1風路11之第1凝結器2之空氣的溫度T7係可變成該冷媒之凝結溫度T2以上。 On the other hand, the air taken in at the temperature T6 in the first air passage 11 is in the first condenser 2 and the refrigerant in a superheated gas state exceeding the temperature T2 and below the temperature T1 or a gas-liquid two-phase state at the temperature T2 Heat exchange with refrigerant While being heated. As a result, the temperature T7 of the air that has passed through the first condenser 2 of the first air path 11 can be equal to or higher than the condensation temperature T2 of the refrigerant.
從第1凝結器2所流出之溫度T2之氣液二相狀態的冷媒流入被配置於第2風路12內的第2凝結器3。流入第2凝結器3之溫度T2之氣液二相狀態的冷媒係與在第2風路12內已通過蒸發器5之溫度T4的空氣進行熱交換，進一步被冷卻，成為溫度T3之過冷卻液狀態的冷媒。從第2凝結器3所流出之過冷卻液狀態的冷媒係藉由通過膨脹閥4而被降壓，成為氣液二相狀態的冷媒後，流入被配置於第2風路12內的蒸發器5。流入蒸發器5之氣液二相狀態的冷媒係與經由第1開口部13從外部空間被取入第2風路12內的空氣進行熱交換而被加熱，成為過熱氣體狀態的冷媒。 The refrigerant in a gas-liquid two-phase state at a temperature T2 flowing from the first condenser 2 flows into the second condenser 3 disposed in the second air path 12. The refrigerant flowing into the gas-liquid two-phase state at the temperature T2 of the second condenser 3 exchanges heat with the air that has passed through the temperature T4 of the evaporator 5 in the second air path 12 and is further cooled to become supercooled at the temperature T3. Liquid refrigerant. The refrigerant in the supercooled liquid state flowing out of the second condenser 3 is depressurized by the expansion valve 4 to become a gas-liquid two-phase refrigerant, and then flows into the evaporator disposed in the second air path 12 5. The refrigerant in the gas-liquid two-phase state flowing into the evaporator 5 exchanges heat with the air taken into the second air passage 12 from the external space through the first opening 13 to be heated, and becomes a refrigerant in a superheated gas state.
另一方面，第2風路12內所取入之空氣係首先，藉由在蒸發器5被冷卻至空氣之露點以下的溫度而被除濕。被冷卻並除濕之空氣係藉由在第2凝結器3與氣液二相狀態之冷媒或過冷卻液狀態之冷媒進行熱交換而被加熱。藉此，已通過第2風路12之空氣的溫度係超過空氣之露點，可變成該冷媒之凝結溫度以下。溫度T5及溫度T7係被設定成外部空間的氣溫不會因已通過第1風路11之空氣及已通過第2風路12之空氣而降低。 On the other hand, the air taken in the second air path 12 is first dehumidified by being cooled by the evaporator 5 to a temperature below the dew point of the air. The cooled and dehumidified air is heated by heat exchange between the second condenser 3 and the gas-liquid two-phase refrigerant or the supercooled liquid refrigerant. As a result, the temperature of the air that has passed through the second air path 12 exceeds the dew point of the air, and may become lower than the condensation temperature of the refrigerant. The temperature T5 and the temperature T7 are set such that the temperature of the external space is not lowered by the air that has passed through the first air path 11 and the air that has passed through the second air path 12.
其次，說明除濕裝置100的作用效果。除濕裝置100包括：冷媒迴路，係包含壓縮機1、第1凝結器2、第2凝結器3、降壓裝置4以及蒸發器5；及框體10，係將冷媒迴路收容於內部。在冷媒迴路，冷媒係在壓縮機1、第1凝結器 2、第2凝結器3、降壓裝置4以及蒸發器5依序流通。在框體10的內部，形成：第1風路11，係從框體10的外部被取入內部之空氣的一部分依序通過蒸發器5、第2凝結器3；及第2風路12，係與第1風路11分離，且從框體10的外部被取入內部之空氣的剩下部分通過第1凝結器2。除濕裝置100構成為在第1凝結器，在過熱氣體狀態之冷媒與第2風路內的空氣之間進行熱交換，而在第2凝結器，在過冷卻液狀態之冷媒與第1風路內之已通過蒸發器的空氣之間進行熱交換。 Next, functions and effects of the dehumidifier 100 will be described. The dehumidifier 100 includes a refrigerant circuit including a compressor 1, a first condenser 2, a second condenser 3, a pressure reducing device 4, and an evaporator 5; and a frame 10 that houses the refrigerant circuit therein. In the refrigerant circuit, the refrigerant is connected to the compressor 1 and the first condenser. 2. The second condenser 3, the pressure reducing device 4, and the evaporator 5 flow in sequence. Inside the casing 10, a first air path 11 is formed, and a part of the air taken in from the outside of the casing 10 passes through the evaporator 5 and the second condenser 3 in sequence; and the second air path 12, The system is separated from the first air path 11 and the remainder of the air taken in from the outside of the casing 10 passes through the first condenser 2. The dehumidifier 100 is configured to exchange heat between the refrigerant in the superheated gas state and the air in the second air path in the first condenser, and in the second condenser, the refrigerant in the supercooled liquid state and the first air path Heat is exchanged between the air that has passed through the evaporator.
若依此方式，除濕裝置100係在第2凝結器3在過冷卻液狀態之冷媒與已通過蒸發器5的空氣之間進行熱交換。因此，除濕裝置100係在凝結器過冷卻液狀態的冷媒與未通過蒸發器的空氣之間進行熱交換之在該專利文獻1所記載的除濕裝置相比，可充分地取得過冷卻度，而可得到大的除濕量。結果，與在該專利文獻1所記載的除濕裝置相比，表示除濕性能的EF值高。 In this way, the dehumidifier 100 performs heat exchange between the refrigerant in the supercooled liquid state of the second condenser 3 and the air that has passed through the evaporator 5. Therefore, the dehumidifier 100 is capable of sufficiently obtaining a degree of subcooling compared with the dehumidifier described in the Patent Document 1 in which the refrigerant in the condenser supercooled liquid state exchanges heat with the air that has not passed through the evaporator, and A large amount of dehumidification can be obtained. As a result, compared with the dehumidifier described in this patent document 1, the EF value which shows a dehumidification performance is high.
又，除濕裝置100係在第1風路11內，在第1凝結器2過熱氣體狀態或氣液二相狀態的冷媒與未通過蒸發器5的空氣之間進行熱交換。因此，除濕裝置100係與在凝結器過熱氣體狀態的冷媒與已通過蒸發器的空氣之間進行熱交換之以往的除濕裝置相比，可在不會降低從除濕裝置100所流出之空氣的溫度下，降低冷媒的凝結溫度。結果，除濕裝置100係與以往之除濕裝置相比，可降低凝結溫度且使凝結壓力與蒸發壓力之差變小，而可實現成為高EF值之除濕運轉。 In addition, the dehumidifier 100 is disposed in the first air path 11, and performs heat exchange between the refrigerant in the superheated gas state or the gas-liquid two-phase state of the first condenser 2 and the air that has not passed through the evaporator 5. Therefore, the dehumidifying device 100 can reduce the temperature of the air flowing out of the dehumidifying device 100 compared with the conventional dehumidifying device that exchanges heat between the refrigerant in the condenser superheated gas state and the air that has passed through the evaporator. Lower the condensation temperature of the refrigerant. As a result, the dehumidifier 100 is capable of lowering the condensation temperature and reducing the difference between the condensation pressure and the evaporation pressure compared with conventional dehumidifiers, and can realize a dehumidification operation with a high EF value.
此處，參照第1圖~第4圖，更詳細地說明除濕裝 置100與以往之除濕裝置的相異。第3圖係表示上述之以往的除濕裝置200。以往的除濕裝置200包括：冷媒迴路，係冷媒在壓縮機201、凝結器202、膨脹裝置204以及蒸發器205依序通過；及框體210，係將冷媒迴路收容於內部。在以往的除濕裝置200，僅形成其內部所取入之空氣依序通過蒸發器205、凝結器202的風路211。第4圖係表示除濕裝置200之在凝結器202的冷媒與空氣之溫度變化的圖形。第4圖之縱軸表示冷媒及空氣的溫度，橫軸下表示冷媒之流路，橫軸上表示空氣之流路。在第4圖，以In與Out表示凝結器202之冷媒入口及冷媒出口，以In’與Out’表示凝結器202之空氣入口及空氣出口。參照第2圖及第4圖，比較在第1圖所示之除濕裝置100及第3圖所示之以往的除濕裝置200之在凝結器之冷媒與空氣的溫度變化。 Here, the dehumidifying device will be described in more detail with reference to FIGS. 1 to 4. The setting 100 is different from the conventional dehumidifier. FIG. 3 shows the conventional dehumidifier 200 described above. The conventional dehumidifier 200 includes a refrigerant circuit, which passes through the compressor 201, the condenser 202, the expansion device 204, and the evaporator 205 in order; and a frame 210, which houses the refrigerant circuit inside. In the conventional dehumidifier 200, only the air path 211 in which the air taken in from the inside sequentially passes through the evaporator 205 and the condenser 202 is formed. FIG. 4 is a graph showing changes in the temperature of the refrigerant and the air in the condenser 202 of the dehumidifier 200. In FIG. 4, the vertical axis indicates the temperature of the refrigerant and air, the horizontal axis indicates the refrigerant flow path, and the horizontal axis indicates the air flow path. In Fig. 4, the refrigerant inlet and the refrigerant outlet of the condenser 202 are shown by In and Out, and the air inlet and the air outlet of the condenser 202 are shown by In 'and Out'. Referring to FIG. 2 and FIG. 4, temperature changes of the refrigerant in the condenser and the air of the dehumidifier 100 shown in FIG. 1 and the conventional dehumidifier 200 shown in FIG. 3 are compared.
如第3圖及第4圖所示，在除濕裝置200，從壓縮機201所排出之過熱氣體狀態的冷媒係流入凝結器202。流入凝結器202之溫度T1之過熱氣體狀態的冷媒係藉由與從外部空間被取入除濕裝置200內並在通過蒸發器205時被冷卻之溫度T12的空氣進行熱交換而被冷卻。冷媒係成為凝結溫度T10之氣液二相狀態，進而被冷卻，成為溫度T11之過冷卻液狀態。凝結溫度T10及溫度T11係溫度T12以上。 As shown in FIGS. 3 and 4, in the dehumidifier 200, the refrigerant in the superheated gas state discharged from the compressor 201 flows into the condenser 202. The refrigerant in a superheated gas state at a temperature T1 flowing into the condenser 202 is cooled by heat exchange with air at a temperature T12 that is taken into the dehumidifier 200 from an external space and cooled when passing through the evaporator 205. The refrigerant system is in a gas-liquid two-phase state at a condensation temperature T10, and is further cooled to a supercooled liquid state at a temperature T11. The coagulation temperature T10 and the temperature T11 are above the temperature T12.
另一方面，溫度T12的空氣係藉由在凝結器202與超過溫度T10且溫度T1以下之過熱氣體狀態的冷媒、溫度T10之氣液二相狀態與冷媒、或溫度T11之過冷卻液狀態的冷媒進行熱交換而被加熱。具體而言，溫度T12的空氣係藉由在 凝結器202與溫度T11之過冷卻液狀態的冷媒或溫度T10之氣液二相狀態與冷媒進行熱交換，被加熱至溫度T20，進而藉由在凝結器20與超過溫度T10且溫度T1以下之過熱氣體狀態的冷媒進行熱交換，被加熱至溫度T13。藉此，依序通過蒸發器205及凝結器202之空氣的溫度T13係可變成該冷媒之凝結溫度T10以上。溫度T13係被設定成與除濕裝置200之外部空間的氣溫同程度。因此，在除濕裝置200，凝結溫度T10、與和凝結溫度T10之位於氣液二相狀態的冷媒進行熱交換之空氣的溫度之最高值T20的差變小。結果，在除濕裝置200，無法使凝結溫度T10充分地降低，而難提高EF值。 On the other hand, the air at temperature T12 passes through condenser 202 and the refrigerant in a superheated gas state exceeding temperature T10 and below temperature T1, the gas-liquid two-phase state at temperature T10 and the refrigerant, or the supercooled liquid state at temperature T11. The refrigerant is heated by heat exchange. Specifically, the air at temperature T12 is The condenser 202 and the refrigerant in the supercooled liquid state at temperature T11 or the gas-liquid two-phase state in temperature T10 exchange heat with the refrigerant, and are heated to the temperature T20, and then pass through the condenser 20 and exceed the temperature T10 and the temperature T1 or less. The refrigerant in a superheated gas state undergoes heat exchange and is heated to a temperature T13. As a result, the temperature T13 of the air passing through the evaporator 205 and the condenser 202 in sequence can become the condensation temperature T10 of the refrigerant or more. The temperature T13 is set to the same degree as the temperature of the outer space of the dehumidifier 200. Therefore, in the dehumidifier 200, the difference between the condensation temperature T10 and the highest value T20 of the temperature of the air that performs heat exchange with the refrigerant in the gas-liquid two-phase state and the condensation temperature T10 becomes smaller. As a result, in the dehumidifier 200, the condensation temperature T10 cannot be sufficiently reduced, and it is difficult to increase the EF value.
相對地，在除濕裝置100，在第1凝結器2在過熱氣體狀態或氣液二相狀態的冷媒、與是比通過第2凝結器3之溫度T7的空氣更低溫之溫度T6的空氣之間進行熱交換。因此，若依據除濕裝置100，在若將除濕運轉時之設定溫度設定成與除濕裝置200相等的情況，可使凝結溫度T2與和凝結溫度T2之位於氣液二相狀態的冷媒進行熱交換之空氣之溫度的最高值T20之差，比和除濕裝置200之凝結溫度T10之位於氣液二相狀態的冷媒進行熱交換之空氣之溫度的最高值T20之差更大。結果，除濕裝置100係即使降低凝結溫度T2，亦因為可使凝結溫度T2與該溫度T20之差成為與除濕裝置200同等以上，所以可使凝結溫度T2比除濕裝置200更降低，而可提高EF值。 In contrast, in the dehumidifier 100, between the refrigerant in the supercondensed gas state or the gas-liquid two-phase state of the first condenser 2 and the air at a temperature T6 which is lower than the air passing the temperature T7 of the second condenser 3 Perform heat exchange. Therefore, according to the dehumidification device 100, if the set temperature during the dehumidification operation is set equal to the dehumidification device 200, the condensation temperature T2 and the refrigerant in the gas-liquid two-phase state with the condensation temperature T2 can be heat-exchanged The difference between the highest value T20 of the temperature of the air is greater than the difference between the highest value T20 of the temperature of the air that performs heat exchange with the refrigerant in the gas-liquid two-phase state at the condensation temperature T10 of the dehumidifier 200. As a result, even if the dehumidification device 100 system reduces the condensation temperature T2, the difference between the condensation temperature T2 and the temperature T20 can be made equal to or more than that of the dehumidification device 200. Therefore, the condensation temperature T2 can be lowered than the dehumidification device 200, and EF can be improved value.
(第2實施形態) (Second Embodiment)
其次，參照第5圖，說明第2實施形態之除濕裝 置101。除濕裝置101係基本上具備與第1實施形態之除濕裝置100一樣的構成，但是在第1風路11及第2風路12更具備用以將框體10之外部的空氣取入第2風路12的送風部15上相異。 Next, a dehumidifying device according to a second embodiment will be described with reference to FIG. 5. Set 101. The dehumidifying device 101 basically has the same structure as the dehumidifying device 100 of the first embodiment, but the first air path 11 and the second air path 12 are further provided with air for taking outside air of the casing 10 into the second air. The air supply section 15 of the road 12 is different.
送風部15係形成於框體10內。送風部15係在各個第1風路11及第2風路12，被設置成可對框體10之外部的空氣送風。亦可送風部15係例如由一台送風機所構成。送風部15係形成為可調整第1風路11與第2風路12之風量較佳。送風部15係例如由被設置成可送風至第1風路11的送風機、與被設置成可送風至第2風路12的送風機所構成較佳。 The air blowing part 15 is formed in the housing 10. The air blowing unit 15 is provided in each of the first air path 11 and the second air path 12, and is provided so as to be able to blow air to the outside of the casing 10. The blower unit 15 may be constituted by, for example, a single blower. The air supply unit 15 is preferably formed so that the air volume of the first air path 11 and the second air path 12 can be adjusted. The air blowing unit 15 is preferably composed of, for example, a blower provided to the first air path 11 and a blower provided to the second air path 12.
若依據這種除濕裝置101，可藉送風部15增加第1風路11及第2風路12的風量。尤其，除濕裝置101係與除濕裝置100相比，第1風路11之風量可增加，而可使冷媒之凝結溫度充分地降低。這種除濕裝置101係與除濕裝置100相比，EF值提高。 According to such a dehumidifying device 101, the air volume of the first air path 11 and the second air path 12 can be increased by the air sending section 15. In particular, compared with the dehumidifying apparatus 100, the dehumidifying apparatus 101 can increase the amount of air in the first air passage 11, and can sufficiently reduce the condensation temperature of the refrigerant. The dehumidifier 101 has an EF value higher than that of the dehumidifier 100.
(第3實施形態) (Third Embodiment)
其次，參照第6圖，說明第3實施形態之除濕裝置102。除濕裝置102係基本上具備與第1實施形態之除濕裝置100一樣的構成，但是在更具備調整第1風路11內之風量與第2風路12內之風量的百分比之調整部16上相異。 Next, a dehumidifier 102 according to a third embodiment will be described with reference to FIG. 6. The dehumidifying device 102 basically has the same structure as the dehumidifying device 100 of the first embodiment, but is equipped with an adjustment unit 16 that further includes a percentage of the air volume in the first air path 11 and the air volume in the second air path 12. different.
調整部16係形成於框體10內。調整部16係只要在可調整第1風路11內之風量與第2風路12內之風量的範圍，具備任意的構成即可。調整部16係例如形成於第1風路11內，並可調整與第1風路11之空氣的流通方向垂直之第1 風路11之截面積(開口大小)的風擋。調整部16係例如在第1風路11內形成於比第1凝結器2更上游側。 The adjustment portion 16 is formed in the housing 10. The adjustment unit 16 may have any configuration as long as it can adjust the air volume in the first air path 11 and the air volume in the second air path 12. The adjustment unit 16 is formed in the first air path 11, for example, and can adjust the first vertical direction perpendicular to the air flow direction of the first air path 11. A windshield with a cross-sectional area (opening size) of the wind path 11. The adjustment unit 16 is formed, for example, on the upstream side of the first condenser 2 in the first air passage 11.
被配置第1凝結器2之第1風路11係與被配第2凝結器3和蒸發器5的第2風路12相比，對空氣成為阻力體之構造少。因此，在例如不藉第5圖所示之送風部15等來調整第1風路11與第2風路12之風量的情況，第1風路11之風量比第2風路12之風量更多，而無法使凝結溫度充分地降低。相對地，除濕裝置102係藉調整部16調整第1風路11與第2風路12之風量，而可限制第1風路11之風量。因此，除濕裝置102係與未具備調整部16之除濕裝置相比，可使凝結溫度充分地降低，而EF值高。 The first air path 11 in which the first condenser 2 is disposed has less structure than the second air path 12 in which the second condenser 3 and the evaporator 5 are disposed as a resistance body. Therefore, for example, when the air volume of the first air path 11 and the second air path 12 is not adjusted by the air supply unit 15 shown in FIG. 5, the air volume of the first air path 11 is greater than that of the second air path 12. Too much, and the coagulation temperature cannot be sufficiently reduced. In contrast, the dehumidifier 102 adjusts the air volume of the first air path 11 and the second air path 12 by the adjusting unit 16, and can limit the air volume of the first air path 11. Therefore, the dehumidifier 102 can reduce the condensation temperature sufficiently compared with a dehumidifier without the adjustment unit 16, and the EF value is high.
除濕裝置102係更具備如第4圖所示之送風部15較佳。在此情況，送風部15係由一台送風機所構成，亦可送風部15本身構成為無法調整第1風路11與第2風路12的風量。若依此方式，因為除濕裝置102係可藉送風部15增加第1風路11及第2風路12的風量，且可藉調整部16調整各風量，所以與未具備送風部15及調整部16的除濕裝置相比，可使凝結溫度充分地降低，而EF值高。 It is preferable that the dehumidifier 102 further includes an air blowing unit 15 as shown in FIG. 4. In this case, the air supply unit 15 is composed of a single blower, and the air supply unit 15 itself may be configured so that the air volume of the first air path 11 and the second air path 12 cannot be adjusted. In this way, because the dehumidification device 102 can increase the air volume of the first air path 11 and the second air path 12 by the air supply section 15, and each air volume can be adjusted by the adjustment section 16, it is the same as without the air supply section 15 and the adjustment section. Compared with the 16 dehumidifier, the condensation temperature can be sufficiently reduced, and the EF value is high.
(第4實施形態) (Fourth Embodiment)
其次，說明第4實施形態之除濕裝置。第4實施形態之除濕裝置係基本上具備與第1實施形態之除濕裝置100一樣的構成，但是在將第2風路12的風量被特定是第1風路11及第2風路12之總風量的30%以上且68%以下上相異。 Next, a dehumidifier according to a fourth embodiment will be described. The dehumidifying device of the fourth embodiment basically has the same configuration as the dehumidifying device 100 of the first embodiment, but the air volume of the second air path 12 is specified as the total of the first air path 11 and the second air path 12 The air volume varies from 30% to 68%.
第7圖係表示藉模擬所算出之第2風路12的風量 之對第1風路11及第2風路12之總風量的百分比和除濕裝置100之EF值之關係的圖形。第5圖之橫軸表示第2風路12的風量之對第1風路11及第2風路12之總風量的百分比(單位：%)。第7圖之縱軸表示圖3所示之除濕裝置100的EF值對以往的除濕裝置200的EF值的百分比(單位：%)。如第7圖所示，在第2風路12的風量之對第1風路11及第2風路12之總風量的百分比為30%、50%、68%時，EF值之該百分比是110%、118%、116%。 FIG. 7 shows the air volume of the second air path 12 calculated by simulation. A graph showing the relationship between the percentage of the total air volume of the first air path 11 and the second air path 12 and the EF value of the dehumidifier 100. The horizontal axis of FIG. 5 represents the percentage of the air volume of the second air path 12 to the total air volume of the first air path 11 and the second air path 12 (unit:%). The vertical axis of FIG. 7 represents the percentage (unit:%) of the EF value of the dehumidifier 100 shown in FIG. 3 to the EF value of the conventional dehumidifier 200. As shown in Fig. 7, when the percentage of the air volume of the second air path 12 to the total air volume of the first air path 11 and the second air path 12 is 30%, 50%, and 68%, the percentage of the EF value is 110%, 118%, 116%.
第2風路12之風量的該百分比是30%以上且68%以下之除濕裝置係與以往之除濕裝置相比，因為在第2凝結器3與通過蒸發器5之空氣的熱交換量多，所以可充分地降低凝結溫度，而EF值比以往之除濕裝置提高。 The percentage of the air volume of the second air path 12 is 30% or more and 68% or less. Compared with conventional dehumidifiers, the second condenser 3 has a larger heat exchange amount with the air passing through the evaporator 5, Therefore, the condensation temperature can be sufficiently reduced, and the EF value is higher than that of conventional dehumidifiers.
(第5實施形態) (Fifth Embodiment)
其次，說明第5實施形態之除濕裝置。第5實施形態之除濕裝置係基本上具備與第1實施形態之除濕裝置100一樣的構成，但是在構成隔開部6的材料被特定成導熱率比在第1凝結器2構成冷媒所流通之導熱管(未圖示)的材料更低的材料上相異。 Next, a dehumidifier according to a fifth embodiment will be described. The dehumidifier device according to the fifth embodiment basically has the same structure as the dehumidifier device 100 according to the first embodiment, but the material constituting the partition 6 is specified to have a higher thermal conductivity than that of the refrigerant flowing through the first condenser 2. The material of the heat transfer tube (not shown) differs from the lower material.
構成隔開部6的材料係只要是導熱率比在第1凝結器2構成冷媒所流通之導熱管(未圖示)的材料更低的材料即可，例如是從樹脂、陶瓷、紙以及橡膠等所構成之群所選擇的至少一種。 The material constituting the partition 6 may be a material having a lower thermal conductivity than a material constituting a heat transfer tube (not shown) through which the refrigerant flows in the first condenser 2, and may be, for example, resin, ceramic, paper, or rubber. At least one selected by the group formed by waiting.
若依此方式，可抑制第1風路11內之空氣與第2風路12內之空氣經由隔開部6進行熱交換。因此，可抑制在 第1風路11內流通至第1凝結器2之空氣的溫度降低，又，可抑制在第2風路12內通過蒸發器5之空氣的溫度上升。結果，若依據第5實施形態之除濕裝置，與構成隔開部6的材料是具有與在第1凝結器2構成冷媒所流通之導熱管的材料同等之導熱率的材料的情況相比，EF值高。 In this way, it is possible to suppress the heat exchange between the air in the first air path 11 and the air in the second air path 12 via the partition 6. Therefore, it can be suppressed The temperature of the air flowing through the first air path 11 to the first condenser 2 decreases, and the temperature of the air passing through the evaporator 5 in the second air path 12 can be suppressed from increasing. As a result, if the dehumidifier according to the fifth embodiment has a material having the same thermal conductivity as that of the material constituting the partitioning portion 6 and having the same thermal conductivity as the material constituting the heat transfer tube through which the refrigerant flows in the first condenser 2, EF The value is high.
(第6實施形態) (Sixth embodiment)
其次，說明第6實施形態之除濕裝置。第6實施形態之除濕裝置係基本上具備與第1實施形態之除濕裝置100一樣的構成，但是在第1凝結器2之導熱面積被特定為比第2凝結器3之導熱面積更大上相異。 Next, a dehumidifier according to a sixth embodiment will be described. The dehumidifier device according to the sixth embodiment basically has the same configuration as the dehumidifier device 100 according to the first embodiment, but the heat transfer area of the first condenser 2 is specified to be larger than that of the second condenser 3 different.
第8圖係表示藉模擬所算出之第2凝結器3的導熱面積對第1凝結器2之導熱面積及第2凝結器3之導熱面積的和之百分比、與除濕裝置100之EF值之關係的圖形。第8圖之橫軸表示第2凝結器3的導熱面積對第1凝結器2之導熱面積及第2凝結器3之導熱面積的和之百分比(單位：%)。第8圖之縱軸表示除濕裝置100之EF值對第3圖所示之以往的除濕裝置200的EF值之百分比(單位：%)。如第8圖所示，第2凝結器3的導熱面積對第1凝結器2之導熱面積及第2凝結器3之導熱面積的和之百分比是32%以上。除濕裝置係EF值之該百分比是105%以上，EF值比以往之除濕裝置提高。尤其，第2凝結器3的導熱面積對第1凝結器2之導熱面積及第2凝結器3之導熱面積的和之百分比是50%以上的除濕裝置係EF值之該百分比是115%以上，EF值比以往之除濕裝置提高。 Figure 8 shows the relationship between the heat transfer area of the second condenser 3 and the sum of the heat transfer area of the first condenser 2 and the heat transfer area of the second condenser 3 calculated by simulation, and the relationship between the EF value of the dehumidifier 100 Graphics. The horizontal axis of FIG. 8 indicates the percentage (unit:%) of the heat conduction area of the second condenser 3 to the sum of the heat conduction area of the first condenser 2 and the heat conduction area of the second condenser 3. The vertical axis of FIG. 8 represents the percentage (unit:%) of the EF value of the dehumidifier 100 to the EF value of the conventional dehumidifier 200 shown in FIG. 3. As shown in FIG. 8, the percentage of the heat transfer area of the second condenser 3 to the sum of the heat transfer area of the first condenser 2 and the heat transfer area of the second condenser 3 is 32% or more. The percentage of the EF value of the dehumidifier is more than 105%, and the EF value is higher than that of the conventional dehumidifier. In particular, the percentage of the heat transfer area of the second condenser 3 to the sum of the heat transfer area of the first condenser 2 and the heat transfer area of the second condenser 3 is 50% or more. The percentage of the EF value of the dehumidifier is 115% or more. The EF value is higher than conventional dehumidifiers.
(第7實施形態) (Seventh embodiment)
其次，參照第9圖及第10圖，說明第7實施形態之除濕裝置103。除濕裝置103係基本上具備與第1實施形態之除濕裝置100一樣的構成，但是在框體10的內部，更形成與第2風路12串列地連接，且通過第2凝結器3之空氣通過第1凝結器2的第3風路17上相異。 Next, a dehumidifier 103 according to a seventh embodiment will be described with reference to Figs. 9 and 10. The dehumidifying device 103 basically has the same structure as the dehumidifying device 100 of the first embodiment, but inside the housing 10, it is connected in series with the second air path 12 and passes through the air of the second condenser 3. The third air path 17 passing through the first condenser 2 is different.
第1凝結器2具有：第1熱交換部，係過熱氣體狀態之冷媒與未通過蒸發器5之空氣進行熱交換；及第2熱交換部(在冷媒的流通方向位於比第1熱交換部更下游側的熱交換部)，係氣液二相狀態之冷媒依序與通過蒸發器5、第2凝結器3之空氣進行熱交換。 The first condenser 2 includes: a first heat exchange unit that performs heat exchange between a refrigerant in a superheated gas state and air that has not passed through the evaporator 5; and a second heat exchange unit (located in a direction in which the refrigerant flows is higher than the first heat exchange unit). Further downstream heat exchange section), the refrigerant in the gas-liquid two-phase state sequentially exchanges heat with the air passing through the evaporator 5 and the second condenser 3.
第2風路12形成於蒸發器5之空氣入口與第2凝結器3的空氣出口之間。第3風路17形成於第2凝結器3之空氣出口與第1凝結器2之該第2熱交換部的空氣出口之間。第1風路11係例如藉隔開部6與第2風路12及第3風路分離。隔開部6的下游端部係例如與第1凝結器2的空氣入口連接成將第1凝結器2分離成該第1熱交換部與該第2熱交換部。 The second air path 12 is formed between the air inlet of the evaporator 5 and the air outlet of the second condenser 3. The third air path 17 is formed between the air outlet of the second condenser 3 and the air outlet of the second heat exchange section of the first condenser 2. The first air path 11 is separated from the second air path 12 and the third air path by the partition 6, for example. The downstream end of the partition 6 is connected to, for example, the air inlet of the first condenser 2 to separate the first condenser 2 into the first heat exchange unit and the second heat exchange unit.
第10圖係表示除濕裝置103之在第1凝結器2及第2凝結器3之冷媒與空氣之溫度變化的圖形。第10圖之縱軸表示冷媒及空氣的溫度，橫軸下表示冷媒之流路，橫軸上表示空氣之流路。在第10圖，以In2與Out2表示第1凝結器2之冷媒入口及冷媒出口，以In3與Out3表示第2凝結器3之冷媒入口及冷媒出口。在第3圖，以In2’a與Out2’a表示第1凝結器2之第1熱交換部的空氣入口及空氣出口，以In2’b與Out2’b表示第1凝結器2之第2熱交換部的空氣入口及空氣出口，以 In3’與Out3’表示第2凝結器3之空氣入口及空氣出口。 Fig. 10 is a graph showing changes in the temperature of the refrigerant and air in the first condenser 2 and the second condenser 3 of the dehumidifier 103. In Fig. 10, the vertical axis indicates the temperature of the refrigerant and air, the horizontal axis indicates the refrigerant flow path, and the horizontal axis indicates the air flow path. In FIG. 10, the refrigerant inlet and the refrigerant outlet of the first condenser 2 are shown by In2 and Out2, and the refrigerant inlet and the refrigerant outlet of the second condenser 3 are shown by In3 and Out3. In Fig. 3, In2'a and Out2'a represent the air inlet and air outlet of the first heat exchange section of the first condenser 2, and In2'b and Out2'b represent the second heat of the first condenser 2. The air inlet and air outlet of the exchange department In3 'and Out3' indicate the air inlet and air outlet of the second condenser 3.
不論如何，都如第9圖及第10圖所示，因為在第2凝結器3的第2熱交換部在過冷卻液狀態之冷媒與通過蒸發器5的空氣之間進行熱交換，所以除濕裝置103係與在凝結器在過冷卻液狀態之冷媒與未通過蒸發器的空氣之間進行熱交換之在該專利文獻1所記載的除濕裝置相比，可充分地取得過冷卻度，而可得到大的除濕量。 In any case, as shown in Figs. 9 and 10, the second heat exchange section of the second condenser 3 performs dehumidification because the heat exchange is performed between the refrigerant in the supercooled liquid state and the air passing through the evaporator 5. The device 103 is capable of obtaining a sufficient degree of subcooling as compared with the dehumidifying device described in the Patent Document 1 in which heat is exchanged between the refrigerant in the supercooled state of the condenser and the air that has not passed through the evaporator. A large amount of dehumidification is obtained.
又，這種除濕裝置103係與除濕裝置100相比，因為通過第2凝結器3之空氣的量增加，所以提高凝結性能。進而，如第10圖所示，除濕裝置103係因為接近通過第2凝結器3之冷媒的過冷卻溫度之溫度T8的空氣可在第1凝結器2與氣液二相狀態之冷媒進行熱交換，所以比除濕裝置100提高凝結性能。 In addition, the dehumidifying device 103 has a higher amount of air passing through the second condenser 3 than the dehumidifying device 100, thereby improving the condensation performance. Further, as shown in FIG. 10, the dehumidifier 103 is capable of performing heat exchange between the first condenser 2 and the gas-liquid two-phase refrigerant because air having a temperature T8 close to the subcooling temperature of the refrigerant passing through the second condenser 3 is used. Therefore, the coagulation performance is improved as compared with the dehumidification device 100.
此外，在除濕裝置103，只要第1風路11與第2風路12分離，亦可第1風路11與第3風路17係未分離。如第10圖所示，通過第2風路12之空氣的溫度T8係例如可成為與在第1風路所取入之空氣的溫度T6同等程度。因此，即使在第1風路11通過第2風路12並在第3風路17內流通的空氣混入，亦可具有與該除濕裝置103相同之效果。 In addition, in the dehumidifier 103, as long as the first air path 11 and the second air path 12 are separated, the first air path 11 and the third air path 17 may not be separated. As shown in FIG. 10, the temperature T8 of the air passing through the second air path 12 may be, for example, approximately the same as the temperature T6 of the air taken in the first air path. Therefore, even if the air flowing through the first air path 11 through the second air path 12 and flowing in the third air path 17 is mixed, the same effect as that of the dehumidifying device 103 can be obtained.
應認為這次所揭示之實施形態係在所有的事項上是舉例表示，不是用以限制的。本發明的範圍係不是根據上述之說明，而是根據申請專利範圍所表示，圖謀包含與申請專利範圍同等之意義及在範圍內之所有的變更。 It should be considered that the embodiments disclosed this time are examples on all matters and are not intended to be limiting. The scope of the present invention is not based on the above description, but is expressed according to the scope of the patent application. The intention is to include all changes within the meaning and scope of the scope of the patent application.
1‧‧‧壓縮機 1‧‧‧compressor
2‧‧‧第1凝結器 2‧‧‧The first condenser
3‧‧‧第2凝結器 3‧‧‧ 2nd condenser
4‧‧‧膨脹閥 4‧‧‧ Expansion Valve
5‧‧‧蒸發器 5‧‧‧Evaporator
6‧‧‧隔開部 6‧‧‧ partition
10‧‧‧框體 10‧‧‧Frame
11‧‧‧第1風路 11‧‧‧ the first wind road
12‧‧‧第2風路 12‧‧‧Second Wind Road
13‧‧‧第1開口部 13‧‧‧The first opening
14‧‧‧第2開口部 14‧‧‧The second opening
100‧‧‧除濕裝置 100‧‧‧ Dehumidifier
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| ??PCT/JP2016/068528 | 2016-06-22 | ||
| PCT/JP2016/068528 WO2017221351A1 (en) | 2016-06-22 | 2016-06-22 | Dehumidifier |
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| TWI753323B (en) * | 2019-05-27 | 2022-01-21 | 日商三菱電機股份有限公司 | Dehumidifier |
| TWI784343B (en) * | 2020-06-05 | 2022-11-21 | 日商三菱電機股份有限公司 | Dehumidifier |
| TWI830175B (en) * | 2021-04-22 | 2024-01-21 | 日商三菱電機股份有限公司 | Dehumidifying device |
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| JP7308975B2 (en) * | 2019-12-12 | 2023-07-14 | 三菱電機株式会社 | dehumidifier |
| WO2022264375A1 (en) * | 2021-06-17 | 2022-12-22 | 三菱電機株式会社 | Dehumidifying device |
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| JPS52135354U (en) * | 1976-04-09 | 1977-10-14 | ||
| JPS5919255Y2 (en) * | 1979-12-18 | 1984-06-04 | ダイキン工業株式会社 | air conditioner |
| JPH0587417A (en) * | 1991-09-26 | 1993-04-06 | Hitachi Air Conditioning & Refrig Co Ltd | Dehumidifying device |
| JP2003172557A (en) * | 2001-12-06 | 2003-06-20 | Daikin Ind Ltd | Air-conditioner |
| JP5046685B2 (en) * | 2007-03-01 | 2012-10-10 | 三菱電機株式会社 | Dehumidifier |
| EP2562017B1 (en) * | 2010-04-23 | 2016-02-10 | Panasonic Intellectual Property Management Co., Ltd. | Vehicle air conditioning device |
| US9631834B2 (en) * | 2011-11-21 | 2017-04-25 | Lennox Industries Inc. | Dehumidifier having split condenser configuration |
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| TWI753323B (en) * | 2019-05-27 | 2022-01-21 | 日商三菱電機股份有限公司 | Dehumidifier |
| TWI784343B (en) * | 2020-06-05 | 2022-11-21 | 日商三菱電機股份有限公司 | Dehumidifier |
| TWI830175B (en) * | 2021-04-22 | 2024-01-21 | 日商三菱電機股份有限公司 | Dehumidifying device |
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| CN109312968A (en) | 2019-02-05 |
| JPWO2017221351A1 (en) | 2019-03-22 |
| JP6676163B2 (en) | 2020-04-08 |
| WO2017221351A9 (en) | 2018-03-08 |
| CN109312968B (en) | 2020-11-06 |
| WO2017221351A1 (en) | 2017-12-28 |
| TWI654398B (en) | 2019-03-21 |
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