TWI539126B - Gas - liquid separation refrigeration device - Google Patents
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本發明係關於將以冷凝器凝結之液態冷煤在氣液熱交換器過冷卻以提高冷凍能力之氣液分離型冷凍裝置。The present invention relates to a gas-liquid separation type freezing apparatus which supercools liquid cold coal condensed by a condenser in a gas-liquid heat exchanger to improve freezing ability.
一般而言，冷凍裝置係藉由冷媒配管串聯壓縮機、冷凝器、減壓器、及蒸發器而構成閉環之冷煤循環迴路者，將被壓縮機壓縮之高壓氣體冷煤藉由在冷凝器之放熱而使之液化成為液態冷煤，藉由膨脹閥等減壓器使此高壓液態冷煤膨脹並減壓後，在蒸發器使沸點已降低之低壓液態冷煤蒸發，從庫內等奪取此時之蒸發潛熱，藉此冷卻庫內等。Generally, the refrigerating device is a closed-loop cold coal circulation circuit by a refrigerant piping series compressor, a condenser, a pressure reducer, and an evaporator, and the high-pressure gas cold coal compressed by the compressor is used in the condenser. The heat is liquefied to become liquid cold coal, and the high-pressure liquid cold coal is expanded and depressurized by a pressure reducer such as an expansion valve, and the low-pressure liquid cold coal whose boiling point has been lowered is evaporated in the evaporator, and taken from the inside of the refrigerator. At this time, the latent heat of evaporation is thereby cooled in the chamber.
作為提升此種冷凍裝置之冷凍能力或性能係數(COP)之方法，例如已於專利文獻1提出一種方法，其係設置氣液熱交換器並使以冷凝器液化之高壓液態冷煤與抽出其一部分並使之減壓之低壓氣體冷煤熱交換以將高壓液態冷煤過冷卻。As a method of improving the refrigeration capacity or coefficient of performance (COP) of such a refrigerating apparatus, for example, a method has been proposed in Patent Document 1, which is to provide a gas-liquid heat exchanger and to liquefy a high-pressure liquid cold coal which is liquefied by a condenser. A portion of the low pressure gas cold coal heat exchange for decompression to supercool the high pressure liquid cold coal.
又，於專利文獻2提出之方法，係設置氣液熱交換器(輔助熱交換器)與氣液分離器並使以冷凝器液化之高壓液態冷煤與在氣液分離器分離之低壓氣體冷煤在氣液熱交換器熱交換而將高壓液態冷煤過冷卻。Further, in the method proposed in Patent Document 2, a gas-liquid heat exchanger (auxiliary heat exchanger) and a gas-liquid separator are provided, and a high-pressure liquid cold coal liquefied by a condenser is cooled with a low-pressure gas separated from the gas-liquid separator. The coal is heat exchanged in a gas-liquid heat exchanger to supercool the high-pressure liquid cold coal.
[專利文獻1]日本實開平1-169772號公報[Patent Document 1] Japanese Unexamined Publication No. Hei 1-169972
[專利文獻2]日本特開平11-014167號公報[Patent Document 2] Japanese Patent Laid-Open No. Hei 11-014167
然而，專利文獻1,2中提出之方法中，由於被壓縮機吸入之氣體冷煤會過熱，因此有壓縮機之吐出溫度過度上升而使潤滑壓縮機內之油(冷凍機油)劣化之問題。However, in the method proposed in Patent Documents 1 and 2, since the cold coal gas sucked by the compressor is overheated, there is a problem that the discharge temperature of the compressor excessively rises to deteriorate the oil (refrigerating machine oil) in the lubricating compressor.
本發明係有鑑於上述問題而完成者，其目的在於，提供能藉由抑制高壓液態冷煤之過冷卻與對壓縮機之吸入氣體冷煤之過熱以謀求冷凍能力之提升與油之劣化防止之氣液分離型冷凍裝置。The present invention has been made in view of the above problems, and an object thereof is to provide an improvement in refrigeration ability and deterioration of oil by suppressing supercooling of high-pressure liquid cold coal and overheating of cold coal of a suction gas to a compressor. Gas-liquid separation type freezing device.
為達成上述目的，申請專利範圍第1項記載之發明為一種氣液分離型冷凍裝置，係藉由冷媒配管串聯至少壓縮機、冷凝器、減壓器、氣液分離器及蒸發器而構成閉環之冷煤循環迴路，其特徵在於：設有氣液熱交換器，係使從前述冷凝器流向前述減壓器之液態冷煤，藉由該液態冷煤之噴射及與被前述氣液分離器分離之氣體冷煤及來自前述蒸發器之氣體冷煤之熱交換而過冷卻。In order to achieve the above object, the invention described in claim 1 is a gas-liquid separation type refrigerating apparatus which is formed by a refrigerant piping in series with at least a compressor, a condenser, a pressure reducer, a gas-liquid separator, and an evaporator to form a closed loop. The cold coal circulation circuit is characterized in that: a gas-liquid heat exchanger is provided, wherein the liquid cold coal flowing from the condenser to the pressure reducer is sprayed by the liquid cold coal and the gas-liquid separator is used The heat exchange of the separated gas cold coal and the gas cold coal from the aforementioned evaporator is supercooled.
申請專利範圍第2項記載之發明，係申請專利範圍第1項之發明中，於前述氣液熱交換器設置使從前述冷凝器流向前述減壓器之液態冷煤流通之液側通路、與使被噴射之液態冷煤與被前述氣液分離器分離之氣體冷煤及來自前述蒸發器之氣體冷煤混合並流通之氣體側通路，將該氣體側流路連接於前述壓縮機之吸入側。According to a second aspect of the invention, in the first aspect of the invention, the liquid-liquid heat exchanger is provided with a liquid-side passage for circulating liquid cold coal flowing from the condenser to the pressure reducer, and a gas side passage in which the injected liquid cold coal is mixed with the gas cold coal separated by the gas-liquid separator and the gas cold coal from the evaporator, and the gas side passage is connected to the suction side of the compressor .
申請專利範圍第3項記載之發明，係申請專利範圍第1或2項之發明中，於前述冷煤配管之隔著前述壓縮機其上游側與下游側分別設置蓄壓器與油分離器，將從前述油分離器延伸之油返回管連接於冷煤配管之前述蓄壓器之上游側。The invention according to claim 3, wherein the cold coal pipe is provided with an accumulator and an oil separator on an upstream side and a downstream side of the compressor, respectively. An oil return pipe extending from the oil separator is connected to an upstream side of the aforementioned accumulator of the cold coal pipe.
根據本發明，從冷凝器流向減壓器之高壓液態冷煤，由於藉由在氣液熱交換器被噴射之液態冷煤與被氣液分離器分離之低壓氣體冷煤及以蒸發器蒸發之低壓氣體冷煤之熱交換而被過冷卻，因此能與其過冷卻量之熱量對應地使在蒸發器之蒸發潛熱變大而提高冷凍能力。According to the present invention, the high-pressure liquid cold coal flowing from the condenser to the pressure reducer is cooled by the low-pressure gas cooled by the liquid cold coal injected in the gas-liquid heat exchanger and separated by the evaporator. Since the low-pressure gas cold coal is supercooled by heat exchange, the latent heat of vaporization in the evaporator can be increased to increase the refrigeration capacity in accordance with the amount of heat of the supercooling.
又，氣液熱交換器中供高壓液態冷煤之過冷卻之低壓氣體冷煤，由於藉由與高壓液態冷煤之熱交換而溫度變高，因此即使壓縮機之負荷變動亦不會凝結，不會產生於壓縮機吸入液態冷煤而該壓縮機之負荷增大等之問題。其中，氣液熱交換器中供高壓液態冷煤之過冷卻而溫度變高之氣體冷煤，由於藉由被噴射至氣液熱交換器之液態冷煤之蒸發而被冷卻，因此可抑制被壓縮機吸入之氣體冷煤之過熱。因此，可抑制壓縮機之吐出溫度之上升而防止壓縮機內之油劣化。Moreover, in the low-pressure gas cold coal which is supercooled by the high-pressure liquid cold coal in the gas-liquid heat exchanger, since the temperature is increased by heat exchange with the high-pressure liquid cold coal, the compressor does not condense even if the load of the compressor fluctuates. There is no problem that the compressor draws in liquid cold coal and the load on the compressor increases. Among them, the gas-cold coal in which the temperature of the high-pressure liquid cold coal is supercooled and the temperature is increased in the gas-liquid heat exchanger is cooled by evaporation of the liquid cold coal injected into the gas-liquid heat exchanger, thereby suppressing being suppressed Overheating of the gas cold coal inhaled by the compressor. Therefore, it is possible to suppress an increase in the discharge temperature of the compressor and prevent deterioration of the oil in the compressor.
以下，參照附圖說明本發明之實施形態。Hereinafter, embodiments of the present invention will be described with reference to the drawings.
圖1係本發明之氣液分離型冷凍裝置之冷煤迴路圖，圖2係該氣液分離型冷凍裝置之氣液熱交換器之剖面圖。1 is a cold coal circuit diagram of a gas-liquid separation type refrigerating apparatus of the present invention, and FIG. 2 is a cross-sectional view of the gas-liquid heat exchanger of the gas-liquid separation type refrigerating apparatus.
本發明之氣液分離型冷凍裝置，如圖1所示，基本上係藉由冷媒配管L1,L2,L3,L4,L5連接壓縮機1、冷凝器2、氣液熱交換器3、作為減壓器之膨脹閥4、氣液分離器5、蒸發器6等主要機器而構成。As shown in Fig. 1, the gas-liquid separation type refrigerating apparatus of the present invention basically connects the compressor 1, the condenser 2, and the gas-liquid heat exchanger 3 by the refrigerant pipes L1, L2, L3, L4, and L5. It is composed of a main machine such as an expansion valve 4 of the pressure device, a gas-liquid separator 5, and an evaporator 6.
又，於上述冷煤配管L1連接有油分離器7與電磁開閉閥V1，於冷煤配管L2連接有電磁開閉閥V2、接受器槽8、乾燥機(D)9、窺鏡(S.G)10及電磁開閉閥V3。又，於冷煤配管L5連接有吸入壓調整閥(ZSP閥)V4與蓄壓器11，從前述油分離器7延伸之油返回管L6連接於冷煤配管L5之前述吸入壓調整閥V4與蓄壓器11之間，於其途中設有流量控制用之毛細管12。Further, an oil separator 7 and an electromagnetic opening and closing valve V1 are connected to the cold coal pipe L1, and an electromagnetic opening and closing valve V2, a receiver tank 8, a dryer (D) 9, and a sight glass (SG) 10 are connected to the cold coal pipe L2. And electromagnetic opening and closing valve V3. Further, a suction pressure regulating valve (ZSP valve) V4 and an accumulator 11 are connected to the cold coal pipe L5, and the oil return pipe L6 extending from the oil separator 7 is connected to the suction pressure regulating valve V4 of the cold coal pipe L5. Between the accumulators 11, a capillary tube 12 for flow control is provided on the way.
又，從前述冷煤配管L2之窺鏡10與電磁開閉閥V3之間分歧出噴射配管L7，此噴射配管L7連接於前述氣液熱交換器3，於其途中設有電磁開閉閥V5與流量控制用之毛細管13。Further, an injection pipe L7 is branched from the sight glass 10 of the cold coal pipe L2 and the electromagnetic opening and closing valve V3. The injection pipe L7 is connected to the gas-liquid heat exchanger 3, and an electromagnetic opening and closing valve V5 and a flow rate are provided in the middle. Capillary tube 13 for control.
再者，從前述氣液分離器5之上部延伸之冷煤配管L8與從前述蒸發器6延伸之前述冷煤配管L5連接於前述氣液熱交換器3，冷煤配管L5從氣液熱交換器3導出而連接於前述壓縮機1之吸入側。Further, the cold coal pipe L8 extending from the upper portion of the gas-liquid separator 5 and the cold coal pipe L5 extending from the evaporator 6 are connected to the gas-liquid heat exchanger 3, and the cold coal pipe L5 is exchanged from gas-liquid heat. The device 3 is led out and connected to the suction side of the compressor 1.
此處，根據圖2說明氣液熱交換器3之內部構造。Here, the internal structure of the gas-liquid heat exchanger 3 will be described based on Fig. 2 .
於氣液熱交換器3之軸中心部貫通有構成氣體側通路之粗圓管狀之前述冷煤配管L5，於氣液熱交換器3內之冷煤配管L5周圍形成有圓筒狀之空間S。又，於冷煤配管L5之外周，螺旋狀地捲繞有構成液側通路之前述冷煤配管L2。又，在形成於氣液熱交換器3內之前述空間S分別開口有前述噴射配管L7與從氣液分離器5延伸之前述冷煤配管L8。The cold coal pipe L5 constituting the thick-circular tubular shape forming the gas side passage is penetrated in the axial center portion of the gas-liquid heat exchanger 3, and a cylindrical space S is formed around the cold coal pipe L5 in the gas-liquid heat exchanger 3. . Further, the cold coal pipe L2 constituting the liquid side passage is spirally wound around the outer circumference of the cold coal pipe L5. Further, in the space S formed in the gas-liquid heat exchanger 3, the injection pipe L7 and the cold coal pipe L8 extending from the gas-liquid separator 5 are respectively opened.
又，於構成氣體側通路之冷煤配管L5之一部分安裝有合流用孔口14，冷煤配管L5內部之氣體通路與空間S透過合流用孔口14而互相連通。Further, a merged orifice 14 is attached to one of the cold coal pipes L5 constituting the gas side passage, and the gas passage and the space S inside the cold coal pipe L5 pass through the joining orifice 14 to communicate with each other.
其次，以下使用圖3所示之莫利爾線圖(P-i線圖)說明如以上構成之氣液分離型冷凍裝置之作用。Next, the action of the gas-liquid separation type freezing apparatus constructed as above will be described below using the Mollier diagram (P-i diagram) shown in FIG.
在壓縮機1被驅動源即未圖示電動馬達驅動後，處於圖3之a所示之狀態(壓力P1，焓i1)之氣體冷煤被壓縮機1壓縮而成為於圖3以b所示之狀態(壓力P2，焓i2)之高溫高壓之氣體冷煤(壓縮步驟)，此氣體冷煤通過冷煤配管L1被往冷凝器2導入。此外，此時之壓縮機1之壓縮動力W(熱量換算)係以(i2-i1)表示。After the compressor 1 is driven by an electric motor, which is not shown, the gas cold coal in the state shown in a of FIG. 3 (pressure P 1 , 焓i 1 ) is compressed by the compressor 1 and becomes as shown in FIG. In the state shown (pressure P 2 , 焓i 2 ), the high temperature and high pressure gas cold coal (compression step) is introduced into the condenser 2 through the cold coal pipe L1. Further, the compression power W (heat conversion) of the compressor 1 at this time is represented by (i 2 - i 1 ).
冷凝器2中，高溫高壓之氣體冷煤係往外氣放出凝結熱Q2，而以圖3之b→c之方式狀態變化(相變化)而液化(凝結步驟)，成為於圖3以c所示之狀態(壓力P2，焓i3)之高壓液態冷煤。此外，此時之放熱量(凝結熱)Q2係以(i2-i3)表示。In the condenser 2, the high-temperature and high-pressure gas-cold coal releases the condensing heat Q 2 to the outside air, and is liquefied (coagulation step) by the state change (phase change) in the manner of b→c in Fig. 3, and becomes the c in Fig. 3 High pressure liquid cold coal in the state shown (pressure P 2 , 焓i 3 ). Further, the amount of heat generation (condensation heat) Q 2 at this time is represented by (i 2 - i 3 ).
接著，如上所述在冷凝器2液化之高壓液態冷煤，其一部分雖通過噴射配管L7而被噴射至氣液熱交換器3之空間S，但此液態冷煤係被減壓而絕熱膨脹(等焓膨脹)，成為於圖3以d所示之狀態(壓力P1，焓i3)，其一部分係氣體化。Then, a part of the high-pressure liquid cold coal liquefied in the condenser 2 as described above is injected into the space S of the gas-liquid heat exchanger 3 through the injection pipe L7, but the liquid cold coal is decompressed and adiabatically expanded ( In the state shown by d in FIG. 3 (pressure P 1 , 焓i 3 ), a part thereof is gasified.
其他大部分之高壓液態冷煤，雖於冷煤配管L2朝向膨脹閥4流動之過程中通過氣液熱交換器3，但如後所述，在氣液分離器5被分離之狀態d’(壓力P1，焓i3’)之低壓氣體冷煤從冷煤配管L8被導入氣液熱交換器3內之空間S(參照圖2)，且在蒸發器6蒸發而氣化之狀態a’(壓力P1，焓i1’)之低壓氣體冷煤在氣液熱交換器3內之冷煤配管L5流動。此時，被噴射至氣液熱交換器3之空間S而氣體化之氣體冷煤與在氣液分離器5被分離而導入空間S之氣體冷煤，通過合流用孔口14流入冷煤配管L5內之氣體側通路並合流，三個氣體冷煤在被混合之狀態下流動於冷煤配管L5，在其過程中在與流動於螺旋狀冷煤配管L2之高壓液態冷煤之間進行熱交換而將該高壓液態冷煤過冷卻。亦即從冷凝器2流向膨脹閥4之高壓液態冷煤藉由通過氣液熱交換器3而被過冷卻，以成為圖3之c→c’之狀態(壓力P2，焓i3’)之方式狀態變化，而被過冷卻圖示之△Q2(=i3-i3’)之量。Most of the other high-pressure liquid cold coal passes through the gas-liquid heat exchanger 3 during the flow of the cold coal pipe L2 toward the expansion valve 4, but as described later, the gas-liquid separator 5 is separated in the state d' ( The low-pressure gas cold coal of the pressure P 1 , 焓i 3 ') is introduced into the space S (refer to FIG. 2) in the gas-liquid heat exchanger 3 from the cold coal pipe L8, and is vaporized and vaporized in the evaporator 6 a' The low-pressure gas cold coal (pressure P 1 , 焓i 1 ') flows in the cold coal pipe L5 in the gas-liquid heat exchanger 3. At this time, the gas cold coal which is injected into the space S of the gas-liquid heat exchanger 3 and gasified is separated from the gas cold coal which is separated into the space S by the gas-liquid separator 5, and flows into the cold coal pipe through the joining orifice 14 The gas side passages in L5 merge and flow, and the three gas cold coals flow to the cold coal pipe L5 while being mixed, and heat is generated between the high pressure liquid cold coal flowing in the spiral cold coal pipe L2 in the process. The high pressure liquid cold coal is supercooled by exchange. That is, the high-pressure liquid cold coal flowing from the condenser 2 to the expansion valve 4 is supercooled by passing through the gas-liquid heat exchanger 3 to become the state of c→c' of FIG. 3 (pressure P 2 , 焓i 3 ') The mode changes and the amount of ΔQ 2 (=i 3 -i 3 ') is overcooled.
如此，在氣液熱交換器3被過冷卻之高壓液態冷煤係藉由通過膨脹閥4被減壓而絕熱膨脹(等焓膨脹)(膨脹步驟)，以成為圖3之c’→d’之狀態(壓力P1，焓i3’)之方式狀態變化，其一部分氣體化。接著，一部分氣體化之冷煤通過冷煤配管L3被導入氣液分離器5而被氣液分離，低壓氣體冷煤係如前所述從冷煤配管L8被導入氣液熱交換器3以供在該處流動之高壓液態冷煤之過冷卻。In this way, the high-pressure liquid cold coal which is supercooled in the gas-liquid heat exchanger 3 is adiabatically expanded (equal expansion) by being decompressed by the expansion valve 4 (expansion step) to become c'→d' of FIG. The state (pressure P 1 , 焓i 3 ') changes state, and a part thereof is gasified. Then, a part of the gasified cold coal is introduced into the gas-liquid separator 5 through the cold coal pipe L3 to be gas-liquid separated, and the low-pressure gas cold coal is introduced into the gas-liquid heat exchanger 3 from the cold coal pipe L8 as described above. The high pressure liquid cold coal flowing there is supercooled.
又，狀態d’(壓力P1，焓i3’)之低壓液態冷煤通過冷煤配管L4而被導入蒸發器6，在通過該蒸發器6之過程中從周圍被奪取蒸發熱Q1，以圖3之d’→a’(壓力P1，焓i1’)之方式狀態變化而蒸發(蒸發步驟)，成為狀態a’之氣體冷煤。此時之蒸發熱量(蒸發潛熱)Q1雖係以(i1’-i3’)表示，但如前所述，由於在氣液熱交換器3將高壓液態冷煤過冷卻△Q2(=i3-i3’)之量，因此能與此過冷卻量之熱量△Q1對應地增大蒸發熱量Q1，而對應其量提高冷凍能力。Further, the low-pressure liquid cold coal of the state d' (pressure P 1 , 焓i 3 ') is introduced into the evaporator 6 through the cold coal pipe L4, and the heat of vaporization Q 1 is taken from the surroundings during the passage of the evaporator 6. The state is changed by d'→a' (pressure P 1 , 焓i 1 ') in FIG. 3 and evaporated (evaporation step) to become gas cold coal in state a'. At this time, the heat of vaporization (latent heat of vaporization) Q 1 is represented by (i 1 '-i 3 '), but as described above, since the high-pressure liquid cold coal is supercooled in the gas-liquid heat exchanger 3, ΔQ 2 ( = i 3 -i 3 ') of the amount, it is possible to this amount of subcooling heat △ Q 1 is increased to correspond to the heat of evaporation Q 1, an amount corresponding to the increase refrigerating capacity.
其後，在蒸發器6蒸發之低壓氣體冷煤，由於如前所述在流動於氣液熱交換器3之過程中供流動於冷煤配管L2之高壓液態冷煤之過冷卻，因此溫度上升，在被吸入壓縮機1之階段下狀態以圖3所示之a’→a(壓力P1，焓i1)之方式變化，而過熱圖示之熱量△Q1(=i1-i1’)。接著，此氣體冷煤被壓縮機1再度壓縮，其後亦反覆相同之狀態變化(冷凍循環)，但從壓縮機1吐出之高壓氣體冷煤所含之油係藉由油分離器7而與冷煤分離，被分離之油，從油返回配管L6往冷煤配管L5返回，在蓄壓器11與氣體冷煤混合而被壓縮機1吸引，以供壓縮機1內之各部之潤滑。Thereafter, the low-pressure gas cold coal evaporated in the evaporator 6 is heated by the supercooling of the high-pressure liquid cold coal flowing through the cold coal pipe L2 during the flow of the gas-liquid heat exchanger 3 as described above. The state of being sucked into the compressor 1 is changed in the manner of a'→a (pressure P 1 , 焓i 1 ) shown in FIG. 3, and the heat of the overheating diagram ΔQ 1 (=i 1 -i 1 ) '). Then, the gas cold coal is recompressed by the compressor 1 and thereafter reversed to the same state change (refrigeration cycle), but the oil contained in the high pressure gas cold coal discharged from the compressor 1 is supplied by the oil separator 7 The cold coal is separated, and the separated oil is returned from the oil return pipe L6 to the cold coal pipe L5, and is mixed with the gas cold coal by the accumulator 11 and sucked by the compressor 1 to lubricate the respective portions in the compressor 1.
進而，本發明之氣液分離型冷凍裝置，雖係反覆以上說明之冷凍循環而藉由在蒸發器6之低壓液態冷煤之蒸發所伴隨之吸熱來進行所需之冷凍，但根據本發明之氣液分離型冷凍裝置能得到如以下之效果。Further, in the gas-liquid separation type refrigerating apparatus of the present invention, the desired freezing is performed by the endothermic heat accompanying the evaporation of the low-pressure liquid cold coal in the evaporator 6 in accordance with the refrigeration cycle described above, but according to the present invention, The gas-liquid separation type freezing apparatus can obtain the following effects.
亦即，從冷凝器2流向膨脹閥4之高壓液態冷煤，由於藉由在氣液熱交換器3被噴射之高壓液態冷煤與被氣液分離器5分離之低壓氣體冷煤及以蒸發器6蒸發之低壓氣體冷煤之熱交換而被過冷卻，因此能與其過冷卻量之熱量對應地使在蒸發器6之蒸發潛熱變大而提高冷凍能力。That is, the high-pressure liquid cold coal flowing from the condenser 2 to the expansion valve 4 is cooled by the low-pressure gas separated by the high-pressure liquid cold coal injected in the gas-liquid heat exchanger 3 and separated by the gas-liquid separator 5. The heat exchange of the low-pressure gas cold coal evaporated by the device 6 is supercooled, so that the latent heat of vaporization in the evaporator 6 can be increased in accordance with the amount of heat of the supercooling amount to increase the refrigeration capacity.
又，氣液熱交換器3中供高壓液態冷煤之過冷卻之低壓氣體冷煤，由於藉由與高壓液態冷煤之熱交換而溫度變高，因此成為過熱狀態，即使壓縮機1之負荷變動亦不會凝結，不會產生於壓縮機1吸入液態冷煤而該壓縮機1之負荷增大等之問題。其中，氣液熱交換器3中供高壓液態冷煤之過冷卻而溫度變高之氣體冷煤，由於藉由被噴射至氣液熱交換器3之液態冷煤之蒸發而被冷卻，因此可抑制被壓縮機1吸入之氣體冷煤之過熱。因此，可抑制壓縮機1之吐出溫度之上升而防止壓縮機1內之油劣化。Further, in the low-pressure gas cold coal in which the high-pressure liquid cold coal is supercooled in the gas-liquid heat exchanger 3, the temperature is increased by heat exchange with the high-pressure liquid cold coal, so that it is in an overheated state, even if the load of the compressor 1 is high. The change does not condense and does not cause a problem that the compressor 1 draws in liquid cold coal and the load of the compressor 1 increases. The gas cold coal in the gas-liquid heat exchanger 3 for supercooling the high-pressure liquid cold coal and having a high temperature is cooled by evaporation of the liquid cold coal injected into the gas-liquid heat exchanger 3, thereby The superheat of the cold coal of the gas sucked by the compressor 1 is suppressed. Therefore, it is possible to suppress an increase in the discharge temperature of the compressor 1 and prevent deterioration of the oil in the compressor 1.
此外，本實施形態中，雖使用膨脹閥作為減壓器，但亦能使用毛細管或渦管等其他任意者來作為減壓器。Further, in the present embodiment, an expansion valve is used as the pressure reducer, but any other person such as a capillary tube or a scroll tube may be used as the pressure reducer.
1．．．壓縮機1. . . compressor
2．．．冷凝器2. . . Condenser
3．．．氣液熱交換器3. . . Gas liquid heat exchanger
4．．．膨脹閥4. . . Expansion valve
5．．．氣液分離器5. . . Gas-liquid separator
6．．．蒸發器6. . . Evaporator
7．．．油分離器7. . . Oil separator
8．．．接受器槽8. . . Receiver slot
9．．．乾燥機9. . . Dryer
10．．．窺鏡10. . . Speculum
11．．．蓄壓器11. . . Accumulator
12,13．．．毛細管12,13. . . Capillary
14．．．合流用孔口14. . . Confluence orifice
L1～L5．．．冷煤配管L1～L5. . . Cold coal piping
L6．．．油返回管L6. . . Oil return pipe
L7．．．噴射配管L7. . . Injection piping
L8．．．冷煤配管L8. . . Cold coal piping
S．．．空間S. . . space
V1～V3．．．電磁開閉閥V1 ~ V3. . . Electromagnetic on-off valve
V4．．．吸入壓調整閥V4. . . Suction pressure regulating valve
V5．．．電磁開閉閥V5. . . Electromagnetic on-off valve
圖1係本發明之氣液分離型冷凍裝置之冷煤迴路圖。BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view showing a cold coal circuit of a gas-liquid separation type refrigerating apparatus of the present invention.
圖2係本發明之氣液分離型冷凍裝置之氣液熱交換器之剖面圖。Fig. 2 is a cross-sectional view showing a gas-liquid heat exchanger of the gas-liquid separation type refrigerating apparatus of the present invention.
圖3係顯示冷煤之狀態變化之莫利爾線圖。Figure 3 is a Molier diagram showing the state change of cold coal.
1．．．壓縮機1. . . compressor
2．．．冷凝器2. . . Condenser
3．．．氣液熱交換器3. . . Gas liquid heat exchanger
4．．．膨脹閥4. . . Expansion valve
5．．．氣液分離器5. . . Gas-liquid separator
6．．．蒸發器6. . . Evaporator
7．．．油分離器7. . . Oil separator
8．．．接受器槽8. . . Receiver slot
9．．．乾燥機9. . . Dryer
10．．．窺鏡10. . . Speculum
11．．．蓄壓器11. . . Accumulator
12,13．．．毛細管12,13. . . Capillary
L1～L5．．．冷煤配管L1～L5. . . Cold coal piping
L6．．．油返回管L6. . . Oil return pipe
L7．．．噴射配管L7. . . Injection piping
L8．．．冷煤配管L8. . . Cold coal piping
V1～V3．．．電磁開閉閥V1 ~ V3. . . Electromagnetic on-off valve
V4．．．吸入壓調整閥V4. . . Suction pressure regulating valve
V5．．．電磁開閉閥V5. . . Electromagnetic on-off valve
Claims (3)
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| TW100125418A TWI539126B (en) | 2011-07-19 | 2011-07-19 | Gas - liquid separation refrigeration device |
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| TW100125418A TWI539126B (en) | 2011-07-19 | 2011-07-19 | Gas - liquid separation refrigeration device |
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| TWI539126B true TWI539126B (en) | 2016-06-21 |
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