TW202407269A - Two-stage refrigeration apparatus - Google Patents
Two-stage refrigeration apparatus Download PDFInfo
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 92
- 239000003507 refrigerant Substances 0.000 claims description 49
- 239000003990 capacitor Substances 0.000 claims description 19
- 230000006870 function Effects 0.000 claims description 15
- 238000001704 evaporation Methods 0.000 claims description 11
- 230000004044 response Effects 0.000 claims description 4
- 230000007423 decrease Effects 0.000 description 14
- 230000004048 modification Effects 0.000 description 12
- 238000012986 modification Methods 0.000 description 12
- 238000001816 cooling Methods 0.000 description 11
- 238000011084 recovery Methods 0.000 description 9
- 230000008020 evaporation Effects 0.000 description 8
- 238000007710 freezing Methods 0.000 description 7
- 230000008014 freezing Effects 0.000 description 7
- 230000005494 condensation Effects 0.000 description 6
- 238000009833 condensation Methods 0.000 description 6
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 4
- CURLTUGMZLYLDI-UHFFFAOYSA-N carbon dioxide Natural products O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 230000007613 environmental effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 235000011089 carbon dioxide Nutrition 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 239000004065 semiconductor Substances 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000010365 information processing Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 229910000069 nitrogen hydride Inorganic materials 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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Abstract
Description
本發明係關於二元冷凍裝置。The present invention relates to a binary refrigeration device.
將低元側冷凍迴圈與高元側冷凍迴圈藉由串聯熱交換器熱性連接之二元冷凍裝置為眾所皆知(例如參照專利文獻1)。在專利文獻1的二元冷凍裝置,在低元側冷凍迴圈,以CO2(二氧化碳)作為低元側冷媒,使用捲動式的低元側壓縮機。專利文獻1的目的為獲得高效率的二元冷凍裝置。
[先前技術文獻]
[專利文獻]
A binary refrigeration device in which a low-side refrigeration cycle and a high-side refrigeration cycle are thermally connected through a series heat exchanger is known (for example, see Patent Document 1). In the binary refrigeration device of
[專利文獻1]日本特開第2012-112615號公報[Patent Document 1] Japanese Patent Application Publication No. 2012-112615
[發明所欲解決之問題][Problem to be solved by the invention]
捲動式或螺旋式這樣的旋轉式低元側壓縮機具有軸承。若以CO2作為低元側冷媒且使用旋轉式的低元側壓縮機,則在軸承上會產生非常高的壓力負載。因此,有無法確保軸承的長使用壽命之虞。Rotary low-side compressors such as scroll type or screw type have bearings. If CO2 is used as the low-side refrigerant and a rotary low-side compressor is used, a very high pressure load will be generated on the bearings. Therefore, there is a risk that the long service life of the bearing cannot be ensured.
本發明係針對以CO2作為低元側冷媒且使用螺旋式低元側壓縮機之二元冷凍裝置,確保低元側壓縮機的軸承之長使用壽命為課題。 [解決問題之技術手段] The present invention is directed to a binary refrigeration device that uses CO2 as the low-side refrigerant and uses a spiral low-side compressor, and ensures a long service life of the bearings of the low-side compressor. [Technical means to solve problems]
本發明提供二元冷凍裝置,其具有: 低元側冷凍迴圈,其具有螺旋式的低元側壓縮機,該低元側壓縮機是將CO2作為低元側冷媒使用並具有藉由軸承可旋轉地支承的螺旋轉子及驅動前述螺旋轉子的低元側電動機,將前述低元側冷媒進行壓縮; 高元側冷凍迴圈,其包含高元側壓縮機,該高元側壓縮機具有高元側電動機且將高元側冷媒進行壓縮; 第1壓力感測器,其測定前述低元側壓縮機的吸入壓力亦即低元側吸入壓力; 第2壓力感測器,其測定前述低元側壓縮機的吐出壓力亦即低元側吐出壓力;及 控制裝置,其從前述第1壓力感測器接收前述低元側吸入壓力並且從前述第2壓力感測器接收前述低元側吐出壓力,算出前述低元側吐出壓力與前述低元側吸入壓力之差量亦即低元側差壓, 前述低元側冷凍迴圈及前述高元側冷凍迴圈共用串聯電容器,該串聯電容器,在前述低元側冷凍迴圈作為使前述低元側冷媒凝結之凝結器發揮功能,並且在前述高元側冷凍迴圈作為使前述高元側冷媒蒸發之蒸發器發揮功能,並在前述低元側冷凍迴圈與前述高元側冷凍迴圈之間進行熱交換, 前述控制裝置係 在前述低元側吸入壓力未滿前述第1下限壓力的情況,使前述低元側電動機的轉速減少,在前述低元側吸入壓力超過第1上限壓力的情況,使前述低元側電動機的轉速增大,在前述低元側吸入壓力為前述第1下限壓力以上且前述第1上限壓力以下的情況,維持前述低元側電動機的轉速,並且執行因應以下的前述低元側差壓之控制,亦即, 在前述低元側差壓未滿第2下限壓力的情況,使前述高元側電動機的轉速減少,在前述低元側差壓超過第2上限壓力的情況,使前述高元側電動機的轉速增大,在前述低元側差壓為前述第2下限壓力以上且前述第2上限壓力以下的情況,維持前述高元側電動機的轉速。 The present invention provides a binary freezing device, which has: The low-side refrigeration cycle has a spiral low-side compressor. The low-side compressor uses CO2 as the low-side refrigerant and has a spiral rotor rotatably supported by a bearing and drives the aforementioned spiral rotor. The low-end side motor compresses the aforementioned low-end side refrigerant; A high-stage side refrigeration cycle, which includes a high-stage side compressor. The high-stage side compressor has a high-stage side motor and compresses the high-stage side refrigerant; a first pressure sensor that measures the suction pressure of the aforementioned low-stage compressor, that is, the low-stage suction pressure; a second pressure sensor that measures the discharge pressure of the low-side compressor, that is, the low-side discharge pressure; and A control device that receives the low-stage suction pressure from the first pressure sensor and the low-stage discharge pressure from the second pressure sensor, and calculates the low-stage discharge pressure and the low-stage suction pressure. The difference is the differential pressure on the low side, The low-stage refrigeration cycle and the high-stage refrigeration cycle share a series capacitor, and the series capacitor functions as a condenser for condensing the low-stage refrigerant in the low-stage refrigeration cycle, and also functions as a condenser for condensing the low-stage refrigerant in the high-stage refrigeration cycle. The side refrigeration cycle functions as an evaporator for evaporating the high-stage refrigerant, and performs heat exchange between the low-stage refrigeration cycle and the high-stage refrigeration cycle. The aforementioned control device system When the low-stage suction pressure is less than the first lower limit pressure, the rotation speed of the low-stage electric motor is reduced. When the low-stage suction pressure exceeds the first upper limit pressure, the rotation speed of the low-stage electric motor is increased. Increase, when the low-stage suction pressure is equal to or greater than the first lower limit pressure and less than the first upper limit pressure, the rotation speed of the low-stage electric motor is maintained, and the following control is performed in response to the low-stage differential pressure, that is, When the low-stage differential pressure is less than the second lower limit pressure, the rotation speed of the high-stage motor is reduced. When the low-stage differential pressure exceeds the second upper limit pressure, the rotation speed of the high-stage motor is increased. When the low-stage differential pressure is greater than the second lower limit pressure and less than the second upper limit pressure, the rotation speed of the high-stage motor is maintained.
若依據此結構,由於可將低元側吸入壓力調整在第1下限壓力與第1上限壓力之間,故,能夠將低元側冷凍迴圈之冷卻量調整為理想的範圍。另外,由於可將低元側差壓調整在第2下限壓力與第2上限壓力之間,故,能夠調整對於軸承之壓力負載,可確保軸承的長使用壽命。若使低元側電動機的轉速增大,則低元側冷凍迴圈之冷卻量增大,冷卻溫度降低。因此,在低元側冷凍迴圈,由於蒸發溫度降低,故,蒸發壓力(亦即低元側吸入壓力)降低。相反地,若使低元側電動機的轉速減少,則蒸發壓力(亦即低元側吸入壓力)上升。如此,低元側吸入壓力可進行調整。另外,若使高元側電動機的轉速增大,則高元側冷凍迴圈之冷卻量增大,冷卻溫度降低。因此,高元側冷凍迴圈之蒸發溫度降低,藉由串聯電容器熱性連接之低元側冷凍迴圈之凝結溫度降低。因此,在低元側冷凍迴圈之凝結壓力(亦即低元側吐出壓力)降低。相反地,若使高元側電動機的轉速減少,則低元側冷凍迴圈之凝結壓力(亦即低元側吐出壓力)上升。如此,低元側吐出壓力可進行調整。因此,可將會影響軸承之低元側差壓調整為理想的範圍。另外,作為低元側冷媒使用的CO2之GWP(地球暖化係數)為1,環境性優異。另外,由於低元側壓縮機為螺旋式,故,即使在CO2因低溫造成固體化(乾冰化)的情況也可藉由螺旋轉子予以破碎,故,比起捲動式等的其他旋轉式,壞影響少。According to this structure, since the low-side suction pressure can be adjusted between the first lower limit pressure and the first upper limit pressure, the cooling amount of the low-side refrigeration cycle can be adjusted to an ideal range. In addition, since the low-side differential pressure can be adjusted between the second lower limit pressure and the second upper limit pressure, the pressure load on the bearing can be adjusted, ensuring a long service life of the bearing. If the rotation speed of the low-side motor is increased, the cooling amount of the low-side refrigeration cycle increases and the cooling temperature decreases. Therefore, in the low-stage refrigeration cycle, since the evaporation temperature decreases, the evaporation pressure (that is, the low-stage suction pressure) decreases. On the contrary, when the rotation speed of the low-stage electric motor is reduced, the evaporation pressure (that is, the low-stage suction pressure) increases. In this way, the low-side suction pressure can be adjusted. In addition, if the rotation speed of the high-stage motor is increased, the cooling amount of the high-stage refrigeration cycle increases and the cooling temperature decreases. Therefore, the evaporation temperature of the high-side refrigeration cycle decreases, and the condensation temperature of the low-side refrigeration cycle thermally connected by the series capacitor decreases. Therefore, the condensation pressure of the low-side refrigeration cycle (that is, the low-side discharge pressure) decreases. On the contrary, if the rotation speed of the high-stage motor is reduced, the condensation pressure of the low-stage refrigeration cycle (that is, the low-stage discharge pressure) increases. In this way, the low-side discharge pressure can be adjusted. Therefore, the low-side differential pressure that affects the bearing can be adjusted to an ideal range. In addition, CO2 used as the low-side refrigerant has a GWP (global warming coefficient) of 1 and has excellent environmental performance. In addition, since the low-side compressor is a spiral type, even if CO2 solidifies (turns into dry ice) due to low temperature, it can be crushed by the spiral rotor. Therefore, compared with other rotary types such as scroll type, Few bad effects.
亦可為前述第2上限壓力與前述第2下限壓力之差量為0.4MPa以下。例如,前述第2下限壓力可為0.6MPa,前述第2上限壓力可為1.0MPa。The difference between the second upper limit pressure and the second lower limit pressure may be 0.4 MPa or less. For example, the second lower limit pressure may be 0.6 MPa, and the second upper limit pressure may be 1.0 MPa.
若依據此結構,可將低元側差壓具體地調整為理想的範圍內,能夠確保軸承的長使用壽命。According to this structure, the low-side differential pressure can be specifically adjusted to an ideal range, ensuring a long service life of the bearing.
亦可為前述高元側冷媒為R1234yf。The aforementioned high-side refrigerant may also be R1234yf.
若依據此結構,作為高元側冷媒使用的R1234yf之GWP為1,環境性優異。Based on this structure, R1234yf used as the high-side refrigerant has a GWP of 1 and has excellent environmental performance.
亦可為前述二元冷凍裝置還具備: 第1溫度感測器,其測定前述低元側電動機的溫度;及 第2溫度感測器,其測定前述高元側電動機的溫度, 前述控制裝置係 從前述第1溫度感測器接收前述低元側電動機的溫度,並且從前述第2溫度感測器接收前述高元側電動機的溫度, 在前述低元側電動機的溫度成為上限值以下之前,待機使前述低元側電動機的轉速增大, 在前述高元側電動機的溫度成為上限值以下之前,待機使前述高元側電動機的轉速增大。 The aforementioned binary refrigeration device may also be equipped with: a first temperature sensor that measures the temperature of the aforementioned low-side motor; and a second temperature sensor that measures the temperature of the aforementioned high-side motor, The aforementioned control device system The temperature of the low-side motor is received from the first temperature sensor, and the temperature of the high-side motor is received from the second temperature sensor, Before the temperature of the low-side motor becomes lower than the upper limit value, the standby operation increases the rotation speed of the low-side motor. The rotation speed of the high-stage motor is increased by waiting until the temperature of the high-stage motor becomes equal to or lower than the upper limit value.
若依據此結構,可分別將低元側電動機及高元側電動機的溫度抑制在上限值以下。因此,可將施加於低元側電動機及高元側電動機的負載抑制在一定以下。According to this structure, the temperatures of the low-side motor and the high-side motor can be suppressed below the upper limit value. Therefore, the load applied to the low-side motor and the high-side motor can be suppressed below a certain level.
亦可為前述二元冷凍裝置還具備: 第1電流感測器,其測定前述低元側電動機的電流;及 第2電流感測器,其測定前述高元側電動機的電流, 前述控制裝置係 從前述第1電流感測器接收前述低元側電動機的電流,並且從前述第2電流感測器接收前述高元側電動機的電流, 在前述低元側電動機的電流成為上限值以下之前,待機使前述低元側電動機的轉速增大, 在前述高元側電動機的溫度成為上限值以下之前,待機使前述高元側電動機的轉速增大。 The aforementioned binary refrigeration device may also be equipped with: a first current sensor that measures the current of the aforementioned low-side motor; and a second current sensor that measures the current of the aforementioned high-voltage side motor, The aforementioned control device system The current of the low-side motor is received from the first current sensor, and the current of the high-side motor is received from the second current sensor, Before the current of the low-side motor becomes below the upper limit value, the standby increases the rotation speed of the low-side motor, The rotation speed of the high-stage motor is increased by waiting until the temperature of the high-stage motor becomes equal to or lower than the upper limit value.
若依據此結構,可分別將低元側電動機及高元側電動機的電流抑制在上限值以下。因此,可將施加於低元側電動機及高元側電動機的負載抑制在一定以下。According to this structure, the currents of the low-side motor and the high-side motor can be suppressed below the upper limit value. Therefore, the load applied to the low-side motor and the high-side motor can be suppressed below a certain level.
亦可為前述二元冷凍裝置還具備: 第1轉速感測器,其測定前述低元側電動機的轉速;及 第2轉速感測器,其測定前述高元側電動機的轉速, 前述控制裝置係 從前述第1轉速感測器接收前述低元側電動機的轉速,並且從前述第2轉速感測器接收前述高元側電動機的轉速, 在前述低元側電動機的轉速成為上限值以下之前,待機使前述低元側電動機的轉速增大, 在前述高元側電動機的轉速成為上限值以下之前,待機使前述高元側電動機的轉速增大。 The aforementioned binary refrigeration device may also be equipped with: a first rotational speed sensor, which measures the rotational speed of the aforementioned low-side motor; and a second rotational speed sensor that measures the rotational speed of the aforementioned high-end motor, The aforementioned control device system The rotation speed of the low-side motor is received from the first rotation speed sensor, and the rotation speed of the high-side motor is received from the second rotation speed sensor, Before the rotation speed of the low-side motor becomes below the upper limit value, the standby operation increases the rotation speed of the low-side motor, The rotation speed of the high-stage motor is increased by waiting until the rotation speed of the high-stage motor becomes equal to or lower than the upper limit value.
若依據此結構,可分別將低元側電動機及高元側電動機的轉速抑制在上限值以下。因此,可將施加於低元側電動機及高元側電動機的負載抑制在一定以下。 [發明效果] According to this structure, the rotation speeds of the low-side motor and the high-side motor can be suppressed below the upper limit value. Therefore, the load applied to the low-side motor and the high-side motor can be suppressed below a certain level. [Effects of the invention]
若依據本發明,針對以CO2作為低元側冷媒且使用螺旋式低元側壓縮機之二元冷凍裝置,能確保低元側壓縮機的軸承之長使用壽命。According to the present invention, for a binary refrigeration device using CO2 as the low-side refrigerant and using a spiral low-side compressor, the long service life of the bearings of the low-side compressor can be ensured.
以下,參照圖面說明本發明的實施形態。Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(第1實施形態)
參照圖1,第1實施形態之二元冷凍裝置1具備:低元側冷凍迴圈10、高元側冷凍迴圈20及控制裝置30。
(First Embodiment)
Referring to FIG. 1 , a
在低元側冷凍迴圈10,使用CO2(二氧化碳)作為低元側冷媒。低元側冷凍迴圈10包含:低元側壓縮機11、油回收器12、串聯電容器5、膨脹閥13及蒸發器14。In the low-
同時參照圖2,低元側壓縮機11為螺旋式,用以壓縮低元側冷媒。低元側壓縮機11具有:螺旋轉子11a;驅動螺旋轉子11a之低元側電動機11b;及收等該等構件的外殼11c。螺旋轉子11a藉由軸承(滾動軸承)11d可旋轉地支承,經由連結器11e與低元側電動機11b機械性連接。Referring to Figure 2 at the same time, the low-
低元側電動機11b具有:固定於外殼11c之固定件11b1;及配置於固定子11b1的內側,並且藉由軸承(滾動軸承)11f可旋轉地支承之旋轉件11b2。低元側電動機11b藉由反相器11g可調整轉速。The low-
在本實施形態,低元側壓縮機11為油冷式。在螺旋轉子11a與低元側電動機11b之間,與連結器11e相鄰地設有軸封裝置11h。軸封裝置11h防止油通過。In this embodiment, the low-
低元側壓縮機11將低元側冷媒(CO2)從吸入口11i吸入,在內部進行壓縮,再從吐出口11j吐出。被吐出的CO2含有油,被送至油回收器12而將油回收。被回收的油供給至低元側壓縮機11,亦即循環利用。在油回收器12將油分離後的CO2輸送至串聯冷凝器5。The low-
串聯電容器5由低元側冷凍迴圈10及高元側冷凍迴圈20共有。在串聯電容器5,在低元側冷凍迴圈10與高元側冷凍迴圈20之間執行熱交換。串聯電容器5在低元側冷凍迴圈10作為將低元側冷媒冷卻並凝結之凝結器發揮功能。The
以串聯電容器5所凝結的低元側冷媒通過膨脹閥13而膨脹,並被輸送至蒸發器14。膨脹閥13為例如壓力調整閥。The low-side refrigerant condensed in the
在蒸發器14,通過膨脹閥13而膨脹的低元側冷媒蒸發,蒸發後的低元側冷媒被輸送至低元側壓縮機11。In the
在低元側冷凍迴圈10,設有測定低元側壓縮機11吸入壓力亦即低元側吸入壓力之第1壓力感測器15a、及測定低元側壓縮機11吐出壓力亦即低元側吐出壓力之第2壓力感測器15b。The low-
在高元側冷凍迴圈20,例如將HFO(氫氟烯烴)、HFC(氫氟碳化物)、或NH3(氨)作為高元側冷媒使用。在本實施形態,將HFO的一種之R1234yf作為高元側冷媒使用。高元側冷凍迴圈20包含:高元側壓縮機21、油回收器22、凝結器23、膨脹閥24及串聯電容器5。In the high-
高元側壓縮機21壓縮高元側冷媒。高元側壓縮機21可為例如螺旋式、捲動式、或往復式等。高元側壓縮機21具有成為驅動源之高元側電動機21a。高元側電動機21a藉由反相器21b可調整轉速。The high-
高元側壓縮機21將高元側冷媒從吸入口21c吸入,在內部進行壓縮,再從吐出口21d吐出。被吐出的高元側冷媒含有油,被送至油回收器22而將油回收。被回收的油供給至高元側壓縮機21,亦即循環利用。被油回收器22分離油後的高元側冷媒輸送至凝結器23。The high-
在凝結器23,高元側冷媒被冷卻而凝結。以凝結器23所凝結的高元側冷媒通過膨脹閥24而膨脹,並被輸送至串聯電容器5。膨脹閥24為例如壓力調整閥。In the
串聯電容器5在高元側冷凍迴圈20作為將高元側冷媒冷卻並凝結之蒸發器發揮功能。在串聯電容器5,通過膨脹閥24而膨脹的高元側冷媒蒸發,蒸發後的高元側冷媒被輸送至高元側壓縮機21。The
控制裝置30進行運算處理及裝置全體的控制。控制裝置30,包含例如與軟體協調作用而達到預定的功能之CPU(Central Processing Unit)或MPU(Micro Processing Unit)。控制裝置30,可由設計為實現預定的功能的專用電子電路或可重構的電子電路等之硬體電路構成,亦可由各種半導體積體電路構成。作為各種的半導體積體電路,例如除了CPU、MPU以外,可舉出微電腦、DSP(Digital Signal Processor)、FPGA(Field Programmable Gate Array)、及ASIC(Application Specific Integrated Circuit)等。另外,控制裝置30亦可包含RAM(Random Access Memory)及ROM (Read Only Memory)等的記憶裝置。具體而言,控制裝置30能以例如桌上型電腦、筆記型電腦、工件站、或平板終端這樣的資訊處理裝置或具有相同功能的印刷基板等構成。The
控制裝置30讀出被儲存的數據、程式等再進行各種的運算處理,藉此實現預定的功能。藉由控制裝置30所執行的程式,可利用依據預定的通訊標準而進行通訊之通訊部等,從外部提供,亦可儲存在具有可移動性的記錄媒體。The
參照圖3,控制裝置30具有接收部31、運算部32、低元側轉速控制部33、及高元側轉速控制部34,作為功能性結構。該等可藉由前述硬體及軟體的協調作用而實現。另外,該等分別可理解為對應的電路(circuitry)。Referring to FIG. 3 , the
接收部31從第1壓力感測器15a接收低元側吸入壓力,並且從第2壓力感測器15b接收低元側吐出壓力。The receiving
運算部32算出低元側吐出壓力與低元側吸入壓力之差量亦即低元側差壓。The
低元側轉速控制部33依據圖4~6的流程圖,經由反相器11g控制低元側電動機11b的轉速。同樣地,高元側轉速控制部34依據圖4~6的流程圖,經由反相器21b控制高元側電動機21a的轉速。The low-side rotation
參照圖4,控制裝置30開始二元冷凍裝置1的運轉,起動高元側壓縮機21(步驟S4-1),起動低元側壓縮機11(步驟S4-2)。然後,控制低元側電動機11b的轉速(步驟S4-3),控制高元側電動機21a的轉速(步驟S4-4)。亦即,低元側電動機11b的轉速控制(步驟S4-3)及高元側電動機21a的轉速控制(步驟S4-4),並非再高元側壓縮機21及低元側壓縮機11起動時(亦即運轉開始時)進行,而是在高元側壓縮機21及低元側壓縮機11起動後進行。Referring to Fig. 4 , the
參照圖5,在低元側電動機11b的轉速控制(圖4的步驟S4-3),執行關於低元側吸入壓力P1之判定(步驟S5-1)。在低元側吸入壓力P1未滿第1下限壓力P11的情況(A:步驟S5-1),使低元側電動機11b的轉速減少(步驟S5-2)。然後,再次執行關於低元側吸入壓力P1之判定(步驟S5-1)。另外,低元側吸入壓力P1超過第1上限壓力P12的情況(B:步驟S5-1),使低元側電動機11b的轉速增大(步驟S5-3)。然後,再次執行關於低元側吸入壓力P1之判定(步驟S5-1)。另外,在低元側吸入壓力P1為第1下限壓力P1以上且第1上限壓力P12以下的情況(C:步驟S5-1),維持低元側電動機11b的轉速(步驟S5-4)。然後,結束低元側電動機11b的轉速控制(圖4的步驟S4-3)。Referring to FIG. 5 , during the rotation speed control of the low-stage
參照圖6,在高元側電動機21a的轉速控制(圖4的步驟S4-4),執行關於低元側差壓P2之判定(步驟S6-1)。在低元側差壓P2未滿第2下限壓力P21的情況(A:步驟S6-1),使高元側電動機21a的轉速減少(步驟S6-2)。然後,再次執行關於低元側差壓P2之判定(步驟S6-1)。另外,低元側差壓P2超過第2上限壓力P22的情況(B:步驟S6-1),使高元側電動機21a的轉速增大(步驟S6-3)。然後,再次執行關於低元側差壓P2之判定(步驟S6-1)。另外,在低元側差壓P2為第2下限壓力P21以上且第2上限壓力P22以下的情況(C:步驟S6-1),維持高元側電動機21a的轉速(步驟S6-4)。然後,結束高元側電動機21a的轉速控制(圖4的步驟S4-4)。Referring to FIG. 6 , during the rotation speed control of the high-
若依據本實施形態的二元冷凍裝置1,由於可將低元側吸入壓力P1調整在第1下限壓力P11與第1上限壓力P12之間,故,能夠將低元側冷凍迴圈10之冷卻量調整為理想的範圍。另外,由於可將低元側差壓P2調整在第2下限壓力P21與第2上限壓力P22之間,故,能夠調整對於軸承11d之壓力負載,可確保軸承11d的長使用壽命。若使低元側電動機11b的轉速增大,則低元側冷凍迴圈10之冷卻量增大,冷卻溫度降低。因此,在低元側冷凍迴圈10,由於蒸發溫度降低,故,蒸發壓力(亦即低元側吸入壓力P1)降低。相反地,若使低元側電動機11b的轉速減少,則蒸發壓力(亦即低元側吸入壓力P1)上升。如此,低元側吸入壓力P1可進行調整。另外,若使高元側電動機21a的轉速增大,則高元側冷凍迴圈20之冷卻量增大,冷卻溫度降低。因此,高元側冷凍迴圈20之蒸發溫度降低,藉由串聯電容器5熱性連接之低元側冷凍迴圈10之凝結溫度降低。因此,在低元側冷凍迴圈10之凝結壓力(亦即低元側吐出壓力)降低。相反地,若使高元側電動機21a的轉速減少,則低元側冷凍迴圈10之凝結壓力(亦即低元側吐出壓力)上升。如此,低元側吐出壓力可進行調整。因此,可將會影響軸承之低元側差壓P2調整為理想的範圍。另外,作為低元側冷媒使用的CO2之GWP(地球暖化係數)為1,環境性優異。另外,由於低元側壓縮機11為螺旋式,故,即使在CO2因低溫造成固體化(乾冰化)的情況也可藉由螺旋轉子11a予以破碎,故,比起捲動式等的其他旋轉式,壞影響少。According to the
另外,作為高元側冷媒使用的R1234yf之GWP為1,環境性優異。In addition, R1234yf used as the high-side refrigerant has a GWP of 1 and has excellent environmental performance.
理想為第2上限壓力P21與第2下限壓力P22之差量是0.4MPa以下。例如,第2下限壓力P21為0.6MPa,第2上限壓力P22為1.0MPa。若低元側差壓為0.6MPa以上,則形成為軸承11d的必要最小負載以上,可迴避軸承11d的擦傷,能夠確保長使用壽命。若低元側差壓為1.0MPa以內,則可迴避對於軸承11d之過負載,能夠確保長使用壽命。藉此,可將低元側差壓P2具體地調整為理想的範圍內,能夠確保軸承11d的長使用壽命。Ideally, the difference between the second upper limit pressure P21 and the second lower limit pressure P22 is 0.4 MPa or less. For example, the second lower limit pressure P21 is 0.6MPa, and the second upper limit pressure P22 is 1.0MPa. If the differential pressure on the low-end side is 0.6 MPa or more, the load on the
(第2實施形態)
圖7所示的第2實施形態之二元冷凍裝置1,關於第1溫度感測器15c、第2溫度感測器15d、及控制裝置30之結構與第1實施形態。關於這些以外的部分,實質上與第1實施形態相同。因此,關於在第1實施形態所示的部分,有省略其說明的情況。
(Second Embodiment)
The
在本實施形態,在於低元側冷凍迴圈10,設有測定低元側電動機11b的溫度(例如線圈溫度)的第1溫度感測器15c、及測定高元側電動機21a的溫度(例如線圈溫度)的第2溫度感測器15d。In this embodiment, the low-
參照圖8,在本實施形態,控制裝置30的接收部31,不僅如第1實施形態接收低元側吸入壓力及低元側吐出壓力,另外,還從第1溫度感測器15c接收低元側電動機11b的溫度及從第2溫度感測器15d接收高元側電動機21a的溫度。Referring to FIG. 8 , in this embodiment, the receiving
在本實施形態,控制裝置30的控制是與第1實施形態的圖4相同,但將第1實施形態的圖5、6的流程圖分別置換為圖9、10的流程圖。In this embodiment, the control performed by the
參照圖9,在低元側電動機11b的轉速控制(圖4的步驟S4-3),執行關於低元側吸入壓力P1之判定(步驟S9-1)。在低元側吸入壓力P1未滿第1下限壓力P11的情況(A:步驟S9-1),使低元側電動機11b的轉速減少(步驟S9-2)。然後,再次執行關於低元側吸入壓力P1之判定(步驟S9-1)。另外,低元側吸入壓力P1超過第1上限壓力P12的情況(B:步驟S9-1),執行關於低元側電動機11b的溫度之判定(步驟S9-3)。在低元側電動機11b的溫度為上限值以下的情況下(Y:步驟S9-3),增大低元側電動機11b的轉速(步驟S9-4),再次執行關於低元側吸入壓力P1的判定(步驟S9-1)。在低元側電動機11b的溫度為非上限值以下的情況下(N:步驟S9-3),減少低元側電動機11b的轉速(步驟S9-2),再次執行關於低元側吸入壓力P1的判定(步驟S9-1)。另外,在低元側吸入壓力P1為第1下限壓力P1以上且第1上限壓力P12以下的情況(C:步驟S9-1),執行關於低元側電動機11b的溫度之判定(步驟S9-5)。在低元側電動機11b的溫度為非上限值以下的情況下(N:步驟S9-5),減少低元側電動機11b的轉速(步驟S9-2),再次執行關於低元側吸入壓力P1的判定(步驟S9-1)。在低元側電動機11b的溫度為上限值以下的情況(Y:步驟S9-5),維持低元側電動機11b的轉速(步驟S9-6),結束低元側電動機11b的轉速控制(圖4的步驟S4-3)。Referring to FIG. 9 , during the rotation speed control of the low-stage
亦即,在本實施形態,控制裝置30除了第1實施形態的控制之外,在低元側電動機11b的溫度成為上限值以下之前,待機使低元側電動機11b的轉速增大。That is, in this embodiment, in addition to the control of the first embodiment, the
參照圖10,在高元側電動機21a的轉速控制(圖4的步驟S4-4),執行關於低元側差壓P2之判定(步驟S10-1)。在低元側差壓P2未滿第2下限壓力P21的情況(A:步驟S10-1),使高元側電動機21a的轉速減少(步驟S10-2)。然後,再次執行關於低元側差壓P2之判定(步驟S10-1)。另外,低元側差壓力P2超過第2上限壓力P22的情況(B:步驟S10-1),執行關於高元側電動機21a的溫度之判定(步驟S10-3)。在高元側電動機21a的溫度為上限值以下的情況下(Y:步驟S10-3),增大高元側電動機21a的轉速(步驟S10-4)。然後,再次執行關於低元側差壓P2之判定(步驟S10-1)。在高元側電動機21a的溫度為非上限值以下的情況下(Y:步驟S10-3),減少高元側電動機21a的轉速(步驟S10-2)。然後,再次執行關於低元側差壓P2之判定(步驟S10-1)。另外,在低元側差壓P2為第2下限壓力P21以上且第2上限壓力P22以下的情況(C:步驟S10-1),執行高元側電動機21a的溫度之判定(步驟S10-4)。在高元側電動機21a的溫度為非上限值以下的情況下(N:步驟S10-5),減少高元側電動機21a的轉速(步驟S10-2)。然後,再次執行關於低元側差壓P2之判定(步驟S10-1)。在高元側電動機21a的溫度為上限值以下的情況下(Y:步驟S10-5),維持高元側電動機21a的轉速(步驟S10-6),結束高元側電動機21a的轉速控制(圖4的步驟S4-4)。Referring to FIG. 10 , during the rotation speed control of the high-stage
亦即,在本實施形態,控制裝置30除了第1實施形態的控制之外,在高元側電動機21a的溫度達到上限值以下之前,待機使高元側電動機21a的轉速增大。That is, in this embodiment, in addition to the control in the first embodiment, the
低元側電動機11b的溫度的上限值及高元側電動機21a的溫度的上限值可根據電動機的種類不同。例如,亦可為F種的上限值設定為155℃,B種的上限值設定為130℃,E種的上限值設定為120℃。The upper limit value of the temperature of the low-
若依據本實施形態,可分別將低元側電動機11b及高元側電動機21a的溫度抑制在上限值以下。因此,可將施加於低元側電動機11b及高元側電動機21a的負載抑制在一定以下。According to this embodiment, the temperatures of the low-
針對因應前述低元側電動機11b的溫度及高元側電動機21a的溫度之控制,可考量各種變形例。Various modifications can be considered for the control in response to the temperature of the low-
參照圖7、8,作為第1變形例,第1溫度感測器15c亦可變更為測定低元側電動機11b的電流之第1電流感測器15e。同樣地,第2溫度感測器15d亦可變更為測定高元側電動機21a的電流之第2電流感測器15f。Referring to FIGS. 7 and 8 , as a first modification, the
參照圖11、12,前述低元側電動機11b的溫度亦可變更為低元側電動機11b的電流(步驟S11-3、S11-5)。同樣地,高元側電動機21a的溫度亦可變更為高元側電動機21a的電流(步驟S12-3、S12-5)。亦即,在本變形例,控制裝置30除了第1實施形態的控制之外,在低元側電動機11b的電流成為上限值以下之前,待機使低元側電動機11b的轉速增大,在高元側電動機21a的電流成為上限值以下之前,待機使高元側電動機21a的轉速增大。Referring to FIGS. 11 and 12 , the temperature of the low-
低元側電動機11b的電流的上限值及高元側電動機21a的電流的上限值設定為電動機所規定之額定電流値。The upper limit value of the current of the low-
若依據第1變形例,可分別將低元側電動機11b及高元側電動機21a的電流抑制在上限值以下。因此,可將施加於低元側電動機11b及高元側電動機21a的負載抑制在一定以下。According to the first modification, the currents of the low-
參照圖7、8,作為第2變形例,第1溫度感測器15c亦可變更為測定低元側電動機11b的轉速之第1轉速感測器15g。同樣地,第2溫度感測器15d亦可變更為測定高元側電動機21a的轉速之第2轉速感測器15h。Referring to FIGS. 7 and 8 , as a second modification, the
參照圖13、14,前述低元側電動機11b的溫度亦可變更為低元側電動機11b的轉速(步驟S13-3、S13-5)。同樣地,高元側電動機21a的溫度亦可分別變更為高元側電動機21a的轉速(步驟S14-3、S14-5)。亦即,在本變形例,控制裝置30除了第1實施形態的控制之外,在低元側電動機11b的電流成為上限值以下之前,待機使低元側電動機11b的轉速增大,在高元側電動機21a的電流成為上限值以下之前,待機使高元側電動機21a的轉速增大。Referring to FIGS. 13 and 14 , the temperature of the low-
低元側電動機11b的轉速的上限值及高元側電動機21a的轉速的上限值可以考量電動機中所使用的旋轉件及軸承的容許轉速來設定。例如,可將該上限值設定為6000rpm。The upper limit of the rotation speed of the low-
若依據第2變形例,可分別將低元側電動機11b及高元側電動機21a的轉速抑制在上限值以下。因此,可將施加於低元側電動機及高元側電動機的負載抑制在一定以下。According to the second modification, the rotation speeds of the low-
如以上所記載,針對本發明的具體實施形態及變形例進行說明,但,本發明不限於前述形態,在不超出本發明的範圍內可進行各種變更並實施。例如,亦可將各個實施形態的內容適宜組合者作為本發明的一實施形態。As described above, the specific embodiments and modifications of the present invention are described. However, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the present invention. For example, the content of each embodiment may be appropriately combined as an embodiment of the present invention.
本發明係揭示有以下的態樣。
(態樣1)
低元側冷凍迴圈,其具有螺旋式的低元側壓縮機,該低元側壓縮機是將CO2作為低元側冷媒使用並具有藉由軸承可旋轉地支承的螺旋轉子及驅動前述螺旋轉子的低元側電動機,將前述低元側冷媒進行壓縮;
高元側冷凍迴圈,其包含高元側壓縮機,該高元側壓縮機具有高元側電動機且將高元側冷媒進行壓縮;
第1壓力感測器,其測定前述低元側壓縮機的吸入壓力亦即低元側吸入壓力;
第2壓力感測器,其測定前述低元側壓縮機的吐出壓力亦即低元側吐出壓力;及
控制裝置,其從前述第1壓力感測器接收前述低元側吸入壓力,並且從前述第2壓力感測器接收前述低元側吐出壓力,算出前述低元側吐出壓力與前述低元側吸入壓力之差量亦即低元側差壓,
前述低元側冷凍迴圈及前述高元側冷凍迴圈共用串聯電容器,該串聯電容器,在前述低元側冷凍迴圈作為使前述低元側冷媒凝結之凝結器發揮功能,並且在前述高元側冷凍迴圈作為使前述高元側冷媒蒸發之蒸發器發揮功能,並在前述低元側冷凍迴圈與前述高元側冷凍迴圈之間進行熱交換,
前述控制裝置係
在前述低元側吸入壓力未滿前述第1下限壓力的情況,使前述低元側電動機的轉速減少,在前述低元側吸入壓力超過第1上限壓力的情況,使前述低元側電動機的轉速增大,在前述低元側吸入壓力為前述第1下限壓力以上且前述第1上限壓力以下的情況,維持前述低元側電動機的轉速,並且執行因應以下的前述低元側差壓之控制,
在前述低元側差壓未滿第2下限壓力的情況,使前述高元側電動機的轉速減少,在前述低元側差壓超過第2上限壓力的情況,使前述高元側電動機的轉速增大,在前述低元側差壓為前述第2下限壓力以上且前述第2上限壓力以下的情況,維持前述高元側電動機的轉速。
(態樣2)
如態樣1的二元冷凍裝置,其中,前述第2上限壓力與前述第2下限壓力之差量為0.4MPa以下。
(態樣3)
如態樣2的二元冷凍裝置,其中,前述第2下限壓力為0.6MPa,
前述第2上限壓力為1.0MPa。
(態樣4)
如態樣1至3中任一態樣的二元冷凍裝置,其中,前述高元側冷媒為R1234yf。
(態樣5)
如態樣1至4中任一態樣的二元冷凍裝置,其中,還具備:第1溫度感測器,其測定前述低元側電動機的溫度;及
第2溫度感測器,其測定前述高元側電動機的溫度,
前述控制裝置係
從前述第1溫度感測器接收前述低元側電動機的溫度,並且從前述第2溫度感測器接收前述高元側電動機的溫度,
在前述低元側電動機的溫度成為上限值以下之前,待機使前述低元側電動機的轉速增大,
在前述高元側電動機的溫度成為上限值以下之前,待機使前述高元側電動機的轉速增大。
(態樣6)
如態樣1至5中任一態樣的二元冷凍裝置,其中,第1電流感測器,其測定前述低元側電動機的電流;及
第2電流感測器,其測定前述高元側電動機的電流,
前述控制裝置係
從前述第1電流感測器接收前述低元側電動機的電流,並且從前述第2電流感測器接收前述高元側電動機的電流,
在前述低元側電動機的電流成為上限值以下之前,待機使前述低元側電動機的轉速增大,
在前述高元側電動機的溫度成為上限值以下之前,待機使前述高元側電動機的轉速增大。
(態樣7)
如態樣1至6中任一態樣的二元冷凍裝置,其中,第1轉速感測器,其測定前述低元側電動機的轉速;及
第2轉速感測器,其測定前述高元側電動機的轉速,
前述控制裝置係
從前述第1轉速感測器接收前述低元側電動機的轉速,並且從前述第2轉速感測器接收前述高元側電動機的轉速,
在前述低元側電動機的轉速成為上限值以下之前,待機使前述低元側電動機的轉速增大,
在前述高元側電動機的轉速成為上限值以下之前,待機使前述高元側電動機的轉速增大。
The present invention discloses the following aspects.
(Pattern 1)
The low-side refrigeration cycle has a spiral low-side compressor. The low-side compressor uses CO2 as the low-side refrigerant and has a spiral rotor rotatably supported by a bearing and drives the aforementioned spiral rotor. The low-end side motor compresses the aforementioned low-end side refrigerant;
A high-stage side refrigeration cycle, which includes a high-stage side compressor. The high-stage side compressor has a high-stage side motor and compresses the high-stage side refrigerant;
a first pressure sensor that measures the suction pressure of the aforementioned low-stage compressor, that is, the low-stage suction pressure;
a second pressure sensor that measures the discharge pressure of the low-side compressor, that is, the low-side discharge pressure; and
A control device that receives the low-stage suction pressure from the first pressure sensor, receives the low-stage discharge pressure from the second pressure sensor, and calculates the low-stage discharge pressure and the low-stage suction pressure. The difference in pressure is the differential pressure on the low side,
The low-stage refrigeration cycle and the high-stage refrigeration cycle share a series capacitor. The series capacitor functions as a condenser for condensing the low-stage refrigerant in the low-stage refrigeration cycle, and also functions as a condenser for condensing the low-stage refrigerant in the high-stage refrigeration cycle. The side refrigeration cycle functions as an evaporator for evaporating the high-stage refrigerant, and performs heat exchange between the low-stage refrigeration cycle and the high-stage refrigeration cycle.
The aforementioned control device system
When the low-stage suction pressure is less than the first lower limit pressure, the rotation speed of the low-stage electric motor is reduced. When the low-stage suction pressure exceeds the first upper limit pressure, the rotation speed of the low-stage electric motor is increased. Increase, when the low-stage suction pressure is equal to or greater than the first lower limit pressure and less than the first upper limit pressure, the rotation speed of the low-stage electric motor is maintained, and the following control is performed in response to the low-stage differential pressure,
When the low-stage differential pressure is less than the second lower limit pressure, the rotation speed of the high-stage motor is reduced. When the low-stage differential pressure exceeds the second upper limit pressure, the rotation speed of the high-stage motor is increased. If the low-stage differential pressure is greater than the second lower limit pressure and less than the second upper limit pressure, the rotation speed of the high-stage motor is maintained.
(Pattern 2)
In the binary refrigeration device of
本案主張申請日為2022年6月2日的日本國專利申請之日本特願第2022-090252號為基礎申請的優先權。參照日本特願第2022-090252號而併入本說明書。This case claims the priority of the basic application of Japanese Patent Application No. 2022-090252, which has a filing date of June 2, 2022. It is incorporated into this specification with reference to Japanese Patent Application No. 2022-090252.
1:二元冷凍裝置
5:串聯電容器
10:低元側冷凍迴圈
11:低元側壓縮機
11a:螺旋轉子
11b:低元側電動機
11b1:固定件
11b2:旋轉件
11c:外殼
11d:軸承
11e:連結器
11f:軸承
11g:反相器
11h:軸封裝置
11i:吸入口
11j:吐出口
12:油回收器
13:膨脹閥
14:蒸發器
15a:第1壓力感應器
15b:第2壓力感應器
15c:第1溫度感測器
15d:第2溫度感測器
15e:第1電流感測器
15f:第2電流感測器
15g:第1轉速感測器
15h:第2轉速感測器
20:高元側冷凍迴圈
21:高元側壓縮機
21a:高元側電動機
21b:反相器
21c:吸入口
21d:吐出口
22:油回收器
23:凝結器
24:膨脹閥
30:控制裝置
31:接收部
32:運算部
33:低元側轉速控制部
34:高元側轉速控制部
1: Binary freezing device
5: Series capacitor
10: Low side freezing cycle
11:
[圖1]係本發明的第1實施形態之二元冷凍裝置的冷媒迴路圖。 [圖2]係顯示低元側壓縮機的內部之剖面圖。 [圖3]係第1實施形態之控制裝置的方塊圖。 [圖4]係顯示藉由控制裝置之控制的流程圖。 [圖5]係與圖4的步驟S4-3相對應的第1實施形態之低元側電動機的轉速控制之流程圖。 [圖6]係與圖4的步驟S4-4相對應的第1實施形態之高元側電動機的轉速控制之流程圖。 [圖7]係本發明的第2實施形態之二元冷凍裝置的冷媒迴路圖。 [圖8]係第2實施形態之控制裝置的方塊圖。 [圖9]係與圖4的步驟S4-3相對應的第2實施形態之低元側電動機的轉速控制之流程圖。 [圖10]係與圖4的步驟S4-4相對應的第2實施形態之高元側電動機的轉速控制之流程圖。 [圖11]係與圖4的步驟S4-3相對應的第2實施形態的第1變形例之低元側電動機的轉速控制之流程圖。 [圖12]係與圖4的步驟S4-4相對應的第2實施形態的第1變形例之高元側電動機的轉速控制之流程圖。 [圖13]係與圖4的步驟S4-3相對應的第2實施形態的第2變形例之低元側電動機的轉速控制之流程圖。 [圖14]係與圖4的步驟S4-4相對應的第2實施形態的第2變形例之高元側電動機的轉速控制之流程圖。 [Fig. 1] is a refrigerant circuit diagram of the binary refrigeration device according to the first embodiment of the present invention. [Fig. 2] is a cross-sectional view showing the inside of the low-stage compressor. [Fig. 3] is a block diagram of the control device of the first embodiment. [Fig. 4] is a flowchart showing control by the control device. [Fig. 5] is a flowchart corresponding to step S4-3 of Fig. 4 of the rotation speed control of the low-side electric motor in the first embodiment. [Fig. 6] is a flowchart corresponding to step S4-4 of Fig. 4 of the rotation speed control of the high-level motor in the first embodiment. [Fig. 7] is a refrigerant circuit diagram of the binary refrigeration device according to the second embodiment of the present invention. [Fig. 8] is a block diagram of the control device of the second embodiment. [Fig. 9] is a flowchart corresponding to step S4-3 of Fig. 4 of the rotation speed control of the low-side electric motor in the second embodiment. [Fig. 10] It is a flowchart corresponding to step S4-4 of Fig. 4 of the rotation speed control of the high-level motor in the second embodiment. [Fig. 11] A flowchart of rotation speed control of the low-side electric motor in the first modification of the second embodiment corresponding to step S4-3 in Fig. 4. [Fig. [Fig. 12] A flowchart of the rotation speed control of the high-stage motor in the first modified example of the second embodiment corresponding to step S4-4 in Fig. 4. [Fig. [Fig. 13] A flowchart of rotation speed control of the low-side electric motor in the second modification of the second embodiment corresponding to step S4-3 in Fig. 4. [Fig. [Fig. 14] A flowchart of rotation speed control of a high-level motor in a second modification of the second embodiment corresponding to step S4-4 in Fig. 4. [Fig.
1:二元冷凍裝置 1: Binary freezing device
5:串聯電容器 5: Series capacitor
10:低元側冷凍迴圈 10: Low side freezing cycle
11:低元側壓縮機 11: Low side compressor
11b:低元側電動機 11b: Low side motor
11g:反相器 11g:Inverter
11i:吸入口 11i: suction port
11j:吐出口 11j: spit out
12:油回收器 12:Oil recovery device
13:膨脹閥 13:Expansion valve
14:蒸發器 14:Evaporator
15a:第1壓力感應器 15a: 1st pressure sensor
15b:第2壓力感應器 15b: 2nd pressure sensor
20:高元側冷凍迴圈 20: High-end side freezing cycle
21:高元側壓縮機 21:High-end side compressor
21a:高元側電動機 21a:High side motor
21b:反相器 21b:Inverter
21c:吸入口 21c: Suction port
21d:吐出口 21d: spit out
22:油回收器 22:Oil recovery device
23:凝結器 23:Condenser
24:膨脹閥 24:Expansion valve
30:控制裝置 30:Control device
Claims (7)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2022090252A JP2023177526A (en) | 2022-06-02 | 2022-06-02 | Binary refrigeration device |
JP2022-090252 | 2022-06-02 |
Publications (1)
Publication Number | Publication Date |
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TW202407269A true TW202407269A (en) | 2024-02-16 |
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Application Number | Title | Priority Date | Filing Date |
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TW112118286A TW202407269A (en) | 2022-06-02 | 2023-05-17 | Two-stage refrigeration apparatus |
Country Status (3)
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JP (1) | JP2023177526A (en) |
TW (1) | TW202407269A (en) |
WO (1) | WO2023233937A1 (en) |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2002364937A (en) * | 2001-06-11 | 2002-12-18 | Mitsubishi Electric Corp | Refrigerator |
JP4804396B2 (en) * | 2007-03-29 | 2011-11-02 | 三菱電機株式会社 | Refrigeration air conditioner |
JP5717584B2 (en) * | 2011-08-10 | 2015-05-13 | 三菱電機株式会社 | Refrigeration cycle equipment |
JP5409747B2 (en) * | 2011-10-20 | 2014-02-05 | 三菱電機株式会社 | Dual refrigeration equipment |
EP3121541B1 (en) * | 2014-03-17 | 2021-11-10 | Mitsubishi Electric Corporation | Refrigerating device and refrigerating device control method |
CN205937114U (en) * | 2016-08-02 | 2017-02-08 | 江森自控空调冷冻设备(无锡)有限公司 | Male rotor symmetrical arrangement's helical -lobe compressor |
CN210512229U (en) * | 2019-07-15 | 2020-05-12 | 中国建筑科学研究院有限公司 | Cascade high-temperature heat pump unit |
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