JP6112388B2 - Refrigeration equipment - Google Patents

Description

  The present invention relates to a refrigeration apparatus in which a refrigerant circuit is configured by a compression unit, a gas cooler, a throttling unit, and an evaporator, and a high pressure side is a supercritical pressure.

  Conventionally, this type of refrigeration apparatus has a refrigeration cycle composed of a compression means, a gas cooler, a throttle means, etc., and the refrigerant compressed by the compression means dissipates heat in the gas cooler and is depressurized by the throttle means, and then in an evaporator. The refrigerant was evaporated, and ambient air was cooled by evaporation of the refrigerant at this time. In recent years, chlorofluorocarbon refrigerants cannot be used in this type of refrigeration system due to natural environmental problems. For this reason, the thing using the carbon dioxide which is a natural refrigerant | coolant is developed as a substitute of a fluorocarbon refrigerant | coolant. The carbon dioxide refrigerant is a refrigerant having a high and low pressure difference, and is known to have a low temperature with respect to the critical pressure and to be in a supercritical state on the high pressure side of the refrigerant cycle by compression (for example, see Patent Document 1).

Japanese Patent Publication No. 7-18602 JP 2011-133204 A

  The chlorofluorocarbon refrigerant described above enters the receiver tank after exiting the condenser, and is temporarily stored therein to separate the gas and liquid. The separated liquid refrigerant is stored in the receiver tank, and is used for adjusting the refrigerant amount according to the outside air temperature and the like. On the other hand, when a refrigerant such as carbon dioxide that has a supercritical pressure on the high pressure side is used, when the outside air temperature falls, a saturation cycle is performed, so that the refrigerant is in a gas-liquid mixed state. On the other hand, when the outside air temperature rises to, for example, + 25 ° C. to 30 ° C. or higher, the refrigerant is not liquefied and supercritical cycle operation is performed. Therefore, the amount of circulating refrigerant cannot be adjusted by the receiver tank, and there is a problem that the high-pressure side pressure abnormally increases due to excessive gas refrigerant in the refrigerant circuit.

  Therefore, a high-pressure shut-off device is provided to avoid an abnormal increase in the high-pressure side pressure. This high-pressure shut-off device forces the compression means when the high-pressure side pressure of the refrigerant circuit reaches a predetermined high-pressure shut-off setting value. However, if the compression means is stopped, the cooling by the evaporator is also stopped.

  Therefore, a refrigerant amount adjustment tank is connected to the high pressure side of the refrigerant circuit, and when the high pressure side pressure rises and exceeds a predetermined recovery threshold, the refrigerant is recovered from the high pressure side of the refrigerant circuit, and decreases to a predetermined release. There has also been developed a refrigeration apparatus that prevents the high-pressure side pressure from rising abnormally by releasing the refrigerant into the intermediate pressure region of the refrigerant circuit when it falls below the threshold (see, for example, Patent Document 2). ). In Patent Document 2, a refrigerant amount adjustment tank is built in a refrigerator unit of a refrigeration apparatus that supplies refrigerant from a refrigerator unit to a plurality of showcases (showcase units) installed in a store. Was connected to the high pressure side and the intermediate pressure region of the refrigerant circuit to adjust the amount of circulating refrigerant.

  However, the pressure on the high pressure side of the refrigerant circuit varies greatly due to the influence of opening and closing of the expansion valve (throttle means) on the showcase side. This becomes larger as the number of showcases connected increases in the refrigeration apparatus (a plurality of compressors (compression means) are provided to increase the horsepower of the refrigerator unit).

  Further, since the temperature and pressure at the outlet of the liquid pipe among the pipes connecting the refrigerator unit and each showcase change depending on the change in temperature and operating conditions depending on the season, the amount of refrigerant in the liquid pipe changes greatly. Furthermore, since the length of the pipe connecting this refrigerator unit and each showcase (construction pipe length) varies depending on the scale of the store, it is difficult to define an appropriate refrigerant charging amount.

  For this reason, in the control that recovers the refrigerant in the refrigerant amount adjustment tank when the high-pressure side pressure exceeds the recovery threshold and releases it when the pressure falls below the release threshold, the refrigerant is collected into the refrigerant amount adjustment tank and the refrigerant Since the refrigerant is suddenly released from the volume adjustment tank, the high-pressure side pressure cannot converge, and the refrigeration capacity fluctuates due to fluctuations in the circulating refrigerant amount due to recovery and discharge, and stable cooling performance cannot be obtained. There was a problem.

  The present invention has been made in order to solve the conventional technical problems. The high pressure side is a critical pressure, and the cooling refrigerant amount in the refrigerant circuit is appropriately maintained to achieve stable cooling performance. A refrigeration apparatus that can be realized is provided.

The refrigeration apparatus of the invention of claim 1 is a refrigerant connected to the refrigerant circuit in a refrigeration apparatus in which a refrigerant circuit is constituted by a compression means, a gas cooler, a throttling means, and an evaporator, and the high pressure side is at a supercritical pressure. An amount adjustment tank, a first communication circuit communicating the refrigerant amount adjustment tank and the high pressure side of the refrigerant circuit, a lower portion of the refrigerant amount adjustment tank, an intermediate pressure region of the refrigerant circuit, or a low pressure side. A second communication circuit that communicates, a third communication circuit that communicates an upper portion of the refrigerant amount adjustment tank and an intermediate pressure region of the refrigerant circuit, and a throttling function provided in the first communication circuit. 1, a second valve device provided in the second communication circuit, a third valve device provided in the third communication circuit, and circulating refrigerant on the high-pressure side of the refrigerant circuit. Collected in the refrigerant quantity adjustment tank, the refrigerant quantity adjustment tank Intermediate pressure region of the refrigerant circuit collected refrigerant, or, and a control means for releasing the low pressure side, wherein the control means of the refrigerant circuit based on the evaporation temperature of the refrigerant in the outdoor air temperature and the evaporator When the target value of the high pressure side pressure is determined and the high pressure side pressure of the refrigerant circuit is higher than the target value of the high pressure side pressure, the third valve device is opened and the valve opening of the first valve device is opened. To change the refrigerant recovery rate to the refrigerant amount adjustment tank, and when the high-pressure side pressure of the refrigerant circuit is lower than the target value of the high-pressure side pressure, with the first valve device slightly opened, The refrigerant is gradually released from the refrigerant quantity adjustment tank according to the opening time of the second valve device .

According to a second aspect of the present invention, in the refrigeration apparatus according to the present invention, the control means controls the valve opening of the first valve device to gradually open as the high-pressure side pressure of the refrigerant circuit increases. It is characterized by .

According to a third aspect of the present invention, in the refrigeration apparatus according to the present invention, the control means opens the second valve device for a predetermined time as the high-pressure side pressure of the refrigerant circuit decreases, thereby adjusting the refrigerant amount adjustment tank. The refrigerant is gradually discharged from the tank .

A refrigeration apparatus according to a fourth aspect of the invention is characterized in that, in the invention, carbon dioxide is used as the refrigerant .

In a refrigeration system with supercritical pressure on the high pressure side, if the outside air temperature exceeds a predetermined temperature range, supercritical cycle operation that does not liquefy in the refrigerant circuit is performed, so the liquid volume is adjusted by a conventional receiver tank. However, according to the present invention, the refrigerant amount adjustment tank is connected to the refrigerant circuit, so that excess refrigerant in the refrigerant circuit is recovered from the high pressure side to the refrigerant amount adjustment tank, and the refrigerant amount It is possible to appropriately maintain the circulating refrigerant amount in the refrigerant circuit by discharging the refrigerant from the adjustment tank to the intermediate pressure region of the refrigerant circuit or to the low pressure side. Thereby, it is possible to eliminate the disadvantage that the high pressure side in the refrigerant circuit becomes abnormally high pressure, and it is possible to prevent the overload operation of the compression means due to the high pressure abnormality.
In particular, in the first aspect of the invention, the control means releases the refrigerant while collecting the refrigerant in the refrigerant quantity adjustment tank, and controls the circulating refrigerant quantity by adjusting the degree of collection and release based on the target value of the high pressure side pressure. Thus, it is possible to prevent sudden fluctuations in the circulating refrigerant amount accompanying the recovery of the refrigerant to the refrigerant quantity adjustment tank and the release of the refrigerant from the refrigerant quantity adjustment tank.
Further, the control means determines the target value of the high-pressure side pressure of the refrigerant circuit based on the outside air temperature and the evaporation temperature of the refrigerant in the evaporator. In consideration of this, it is possible to achieve a suitable high-pressure side pressure based on the evaporation temperature, and high-efficiency operation is possible.
When the high pressure side pressure of the refrigerant circuit is higher than the target value of the high pressure side pressure, the control device opens the third valve device and sets the refrigerant recovery rate to the refrigerant amount adjustment tank by the valve opening degree of the first valve device. By changing the above, by opening the third valve device, the pressure in the refrigerant quantity adjustment tank can be released to the outside of the tank. As a result, the pressure in the refrigerant quantity adjustment tank decreases and the refrigerant in the refrigerant quantity adjustment tank liquefies and accumulates, so that the refrigerant in the refrigerant circuit can be smoothly collected in the refrigerant quantity adjustment tank. . At this time, since the upper part of the refrigerant amount adjustment tank and the intermediate pressure region of the refrigerant circuit are communicated with each other, unlike the case where the refrigerant circuit is communicated with the low pressure side region of the refrigerant circuit, a decrease in cooling efficiency due to an increase in the low pressure side pressure is avoided. It becomes possible to do.
Further, the control means changes the refrigerant recovery rate to the refrigerant amount adjustment tank according to the valve opening degree of the first valve device, thereby setting the degree of discharge of the refrigerant recovery to the refrigerant amount adjustment tank of the first valve device. It becomes possible to accurately control the valve opening. If the refrigerant is gradually released from the refrigerant amount adjustment tank as the high-pressure side pressure of the refrigerant circuit decreases, the rapid fluctuation of the circulating refrigerant amount accompanying the release of the refrigerant from the refrigerant amount adjustment tank is similarly achieved. Can also be prevented.
When the high pressure side pressure of the refrigerant circuit is lower than the target value of the high pressure side pressure, the control device makes the refrigerant from the refrigerant amount adjustment tank according to the opening time of the second valve device with the first valve device opened slightly. Is gradually released, and the degree of refrigerant recovery to the refrigerant quantity adjustment tank and the release of refrigerant from the refrigerant quantity adjustment tank are accurately determined by the valve opening degree of the first valve device and the opening time of the second valve device. Can be controlled.
Thereby, the degree of refrigerant recovery and release can be controlled based on the high-pressure side pressure, and high-pressure protection and overload operation can be prevented accurately. Thereby, the cooling performance of the refrigeration apparatus can be ensured, and the COP can be optimized.

In the invention of claim 2 , the control means increases the high-pressure side pressure by controlling the valve opening of the first valve device to gradually open as the high-pressure side pressure of the refrigerant circuit increases. Accordingly, by increasing the refrigerant recovery rate, it becomes possible to prevent excessive refrigerant recovery in advance, and similarly, the rapid fluctuation of the circulating refrigerant amount accompanying the recovery of the refrigerant to the refrigerant amount adjustment tank can be prevented. It becomes possible to prevent.

Furthermore, in the invention of claim 3, the control means opens the second valve device for a predetermined time and gradually releases the refrigerant from the refrigerant amount adjustment tank as the high-pressure side pressure of the refrigerant circuit decreases. Thus, similarly, it is possible to prevent sudden fluctuations in the circulating refrigerant amount accompanying the release of the refrigerant from the refrigerant quantity adjusting tank.

  Thus, according to the invention of the present application, it is possible to appropriately maintain and manage the circulating refrigerant amount in the refrigerant circuit of the refrigeration apparatus in which the high pressure side becomes the critical pressure, and to realize stable cooling performance.

In the supercritical refrigerant circuit (supercritical refrigeration cycle) using carbon dioxide as the refrigerant as in the invention of claim 4 , the above inventions are particularly effective.

It is a refrigerant circuit figure of the freezing apparatus in a present Example. It is a block diagram of the control apparatus of the freezing apparatus of FIG. It is a figure which shows the tendency of the target high pressure THP determined from external temperature and evaporation temperature. It is a figure explaining the collection | recovery of refrigerant | coolant to the refrigerant | coolant amount adjustment tank by the control apparatus of FIG. 2, and discharge | release control of the refrigerant | coolant from a refrigerant | coolant amount adjustment tank.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a refrigerant circuit diagram of a refrigeration apparatus R according to an embodiment of the present invention. The refrigeration apparatus R in the present embodiment is composed of a refrigeration unit 3 and a plurality of showcase units 5, and the refrigeration unit 3 and each showcase unit 5 include a refrigerant pipe 7 (liquid pipe) and a refrigerant pipe. 9 are connected to form a predetermined refrigerant circuit 1.

  In this refrigeration cycle, carbon dioxide whose refrigerant pressure (high pressure) on the high pressure side is equal to or higher than its critical pressure (supercritical) is used as the refrigerant. This carbon dioxide refrigerant is a natural refrigerant that is friendly to the global environment and takes into consideration flammability and toxicity. As the lubricating oil, existing oils such as mineral oil (mineral oil), alkylbenzene oil, ether oil, ester oil, and PAG (polyalkyl glycol) are used.

  The refrigerator unit 3 of an Example is provided with the two compressors 11 as a compression means arrange | positioned in parallel. In this embodiment, the compressor 11 is an internal intermediate pressure type multistage compression rotary compressor, and includes a cylindrical sealed container 12 made of a steel plate, and an electric element (not shown) arranged and housed in the sealed container 12. ) And a first rotary compression element (low-stage side first compression element) 18 and a second rotary compression element (high-stage side second compression element) 20 driven by the electric element. It consists of a mechanism part.

  The first rotary compression element 18 compresses the low-pressure refrigerant sucked into the compressor 11 from the low-pressure side of the refrigerant circuit 1 through the refrigerant pipe 9, boosts it to an intermediate pressure, and discharges it. Further sucks in the intermediate pressure refrigerant compressed and discharged by the first rotary compression element 18, compresses it to a high pressure, and discharges it to the high pressure side of the refrigerant circuit 1. The compressor 11 is a variable frequency compressor, and the rotational speed of the first rotary compression element 18 and the second rotary compression element 20 can be controlled by changing the operating frequency of the electric element.

  On the side surface of the hermetic container 12 of the compressor 11, a low-stage suction port 22 and a low-stage discharge port 24 that communicate with the first rotary compression element 18, and a high-stage side that communicates with the second rotary compression element 20. A suction port 26 and a high-stage discharge port 28 are formed. Refrigerant introduction pipes 30 are connected to the low-stage side suction ports 22 of the respective compressors 11, and merge at the respective upstream sides and connected to the refrigerant pipe 9.

  Low-pressure (LP: about 2.6 MPa in a normal operation state) refrigerant gas sucked into the low-pressure portion of the first rotary compression element 18 by the low-stage suction port 22 is intermediate pressure by the first rotary compression element 18. The pressure is increased to (MP: about 5.5 MPa in a normal operation state) and discharged into the sealed container 12. Thereby, the inside of the airtight container 12 becomes an intermediate pressure (MP).

  Then, intermediate pressure discharge pipes 36 are connected to the low-stage discharge ports 24 of the compressors 11 from which the refrigerant gas of intermediate pressure in the hermetic container 12 is discharged. 38 is connected to one end of 38. The intercooler 38 cools the intermediate pressure refrigerant discharged from the first rotary compression element 18 by air, and an intermediate pressure suction pipe 40 is connected to the other end of the intercooler 38. The suction pipe 40 is branched into two and then connected to the high-stage suction port 26 of each compressor 11.

  The medium pressure (MP) refrigerant gas sucked into the intermediate pressure portion of the second rotary compression element 20 by the high-stage suction port 26 is compressed in the second stage by the second rotary compression element 20. It becomes a refrigerant gas of high temperature and pressure (HP: supercritical pressure of about 9 MPa in a normal operation state). The high-stage discharge port 28 provided on the high-pressure chamber side of the second rotary compression element 20 of each compressor 11 is connected to a high-pressure discharge pipe 42, and merges at each downstream side, and an oil separator 44, the gas cooler 46, and details are connected to the refrigerant pipe 7 via an intermediate heat exchanger 80 constituting a split cycle, which will be described later.

  The gas cooler 46 cools the high-pressure discharged refrigerant discharged from the compressor 11, and a gas cooler blower 47 for air-cooling the gas cooler 46 is disposed in the vicinity of the gas cooler 46. In this embodiment, the gas cooler 46 is juxtaposed with the above-described intercooler 38 and an oil cooler 74 described later in detail, and these are arranged in the same air passage 45. The air passage 45 is provided with an outside air temperature sensor (outside air temperature detecting means) 56 for detecting the outside air temperature where the refrigerator unit 3 is disposed. Further, a high-pressure sensor (high-pressure detector) 48 for detecting the discharge pressure (high-pressure pressure HP) of the refrigerant discharged from the second rotary compression element 20 and a discharge are provided at the high-stage discharge ports 28 and 28. A discharge temperature sensor (discharge temperature detecting means) 50 for detecting the refrigerant temperature is provided.

  On the other hand, each showcase unit 5 is installed in a store or the like, and is connected in parallel to the refrigerant pipes 7 and 9, respectively. Each showcase unit 5 has a case-side refrigerant pipe 60 that connects the refrigerant pipe 7 and the refrigerant pipe 9, and each case-side refrigerant pipe 60 has a main throttle means 62 (main expansion valve) as a throttle means. And the evaporator 63 are sequentially connected. Each evaporator 63 is adjacent to an unillustrated cool air circulation blower that blows air to the evaporator 63. The refrigerant pipe 9 is connected to the low-stage suction port 22 that communicates with the first rotary compression element 18 of each compressor 11 via the refrigerant introduction pipe 30 as described above. Thereby, the refrigerant circuit 1 of the refrigeration apparatus R in the present embodiment is configured.

  The refrigeration apparatus R includes a control device (control means) C configured by a general-purpose microcomputer in the electric box B. The control device C has various sensors connected to the input side as shown in FIG. 2, and various valve devices and the electric element 11M (compressor motor) of the compressor 11 on the output side. ) The fan motor 47M of the gas cooler blower 47 is connected. The control device C is actually a control device on the refrigerator unit 3 side, a control device on the showcase unit 5 side (not shown), and a control device on the additional refrigerant amount adjusting device 111 side (to be described later). 1) and a centralized control device, etc., but here it is simplified and shown by the control device C, and details thereof will be described later according to each control.

(A) Adjustment control of circulating refrigerant amount Next, the adjustment control of the circulating refrigerant amount of the refrigerant circuit 1 of the refrigeration apparatus R in the present embodiment will be described. A refrigerant quantity adjustment tank 100 is connected via a first communication circuit 101 to the high pressure side that is the supercritical pressure of the refrigerant circuit 1, that is, downstream of the intermediate heat exchanger 80 of the refrigerator unit 3 in this embodiment. Yes. The refrigerant amount adjustment tank 100 is built in the refrigerator unit 3 together with the compressor 11 and the gas cooler 46 and has a predetermined volume, and a first communication circuit 101 is connected to the upper part of the tank 100. ing. The first communication circuit 101 is provided with an electric expansion valve 102 as a first valve device having a throttling function.

  The valve device having the throttle function is not limited to this, and the first communication circuit 101 includes, for example, a plurality of capillary tubes having different resistance values and solenoid valves (valve devices) as throttle means. May be.

  The refrigerant amount adjustment tank 100 is connected to a third communication circuit 103 that communicates the upper part of the tank 100 with the intermediate pressure region of the refrigerant circuit 1. In the present embodiment, the other end of the third communication circuit 103 is connected to an intermediate pressure suction pipe 40 on the outlet side of the intercooler 38 of the refrigerant circuit 1 as an example of the intermediate pressure region. The third communication circuit 103 is provided with an electromagnetic valve 104 as a third valve device.

  In addition, a second communication circuit 105 that connects the lower portion of the tank 100 and the intermediate pressure region of the refrigerant circuit 1 is connected to the refrigerant amount adjustment tank 100. In the present embodiment, the other end of the second communication circuit 105 is communicated with an inlet of a first flow path 80A of an intermediate heat exchanger 80 (described later) communicated with the intermediate pressure suction pipe 40 as an example of an intermediate pressure region. . The second communication circuit 105 is provided with an electromagnetic valve 106 as a second valve device and a capillary tube 107 as a pressure reducing means.

(A-0) Additional refrigerant amount adjusting device Further, an additional refrigerant amount adjusting device 111 is connected to the refrigeration apparatus R of the embodiment. The additional refrigerant amount adjusting device 111 is a refrigerator in order to add an additional refrigerant amount adjusting tank 116 (also a refrigerant amount adjusting tank in the present invention) to the refrigerant amount adjusting tank 100 according to the scale of the refrigeration apparatus R. The unit 3 is optionally attached, provided outside the refrigerator unit 3 (addition), and detachably connected to the refrigerant circuit 1. In this case, the additional refrigerant amount adjusting device 111 includes an additional refrigerant amount adjusting tank 116 having a predetermined capacity inside an exterior case (not shown), and a first extension having a throttling function above the additional refrigerant amount adjusting tank 116. A third service port (service valve) 118 that communicates via an electric expansion valve 117 as a valve device (also a first valve device in the present invention) and a third extension on the upper part of the additional refrigerant amount adjustment tank 116 A third service port (service valve) 121 that communicates via a solenoid valve 119 as a valve device (also a third valve device in the present invention), and a second additional valve at the lower part of the additional refrigerant amount adjustment tank 116 A second service port (service) that communicates with an electromagnetic valve 122 as a device (also a second valve device in the present invention) and a capillary tube 123 as a pressure reducing means Comprising a lube) 124, these service port 118,121,124 is exposed to the outside from the extension refrigerant amount adjusting device 111.

  On the other hand, a high-pressure service port (service valve) 112 is connected in communication with the high-pressure side, which is the supercritical pressure of the refrigerant circuit 1, in the present embodiment, on the downstream side of the intermediate heat exchanger 80 of the refrigerator unit 3. An intermediate pressure service port (service valve) 113 is preliminarily attached to the third communication circuit 103 communicated with the intermediate pressure suction pipe 40 serving as an intermediate pressure region. In addition, a low-pressure service port (service valve) 114 is connected in advance to the refrigerant pipe 9 on the low-pressure side of the refrigerant circuit 1, and these service ports 112 to 114 are also exposed to the outside from the refrigerator unit 3. ing.

  When the additional refrigerant amount adjusting device 111 is connected to the refrigerant circuit 1, the first additional communication pipe 126 constituting the first additional communication circuit (also the first communication circuit in the present invention) is used for the first expansion communication pipe 126. The first service port 118 is detachably connected to the high-pressure service port 112 so as to communicate therewith, and the third additional communication pipe 127 constituting the third additional communication circuit (also the third communication circuit in the present invention) The third service port 121 is detachably connected to and communicated with the medium-pressure service port 113, and is connected by a second additional communication pipe 128 constituting a second additional communication circuit (also the second communication circuit in the present invention). The second service port 124 is detachably connected to and communicated with the low-pressure service port 114.

  As a result, the upper part of the additional refrigerant amount adjustment tank 116 is communicated with the high pressure side of the refrigerant circuit 1 via the first additional communication pipe 126, and the electric expansion valve 117 is provided in the first additional communication circuit. The upper part of the additional refrigerant amount adjusting tank 116 is also communicated with the intermediate pressure region of the refrigerant circuit 1 via the third additional communication pipe 127, and the electromagnetic valve 119 is provided in the third additional communication circuit. . Further, the lower part of the additional refrigerant amount adjustment tank 116 is communicated with the low pressure side of the refrigerant circuit 1 via the second additional communication pipe 128, and the electromagnetic valve 122 is provided in the second additional communication circuit. Further, an additional high pressure sensor (unit outlet side pressure detecting means) 120 is attached between the electric expansion valve 117 and the first service port 118, and the first service port 118 is connected to the high pressure service port 112. Thus, the high pressure side pressure similar to that of the unit outlet side pressure sensor 58 is detected.

  On the other hand, as shown in FIG. 2, the control device C includes a unit outlet side pressure sensor (unit outlet side pressure detecting means) 58, an additional high pressure sensor (unit outlet side pressure detecting means) 120, an outside air temperature sensor on the input side. 56, the high pressure sensor 48 and the like are connected. The unit outlet side pressure sensor 58 is connected to the first communication circuit 101 of the refrigerant quantity adjustment tank 100 and detects the pressure of the refrigerant in the refrigerant pipe 7 toward the showcase unit 5. On the output side of the control device C, an electric expansion valve (first valve device) 102, a solenoid valve (third valve device) 104, a solenoid valve (second valve device) 106, and the motor of the compressor 11 are provided. The element 11M, the fan motor 47M of the blower 47 for the gas cooler 46, and the main throttle means 62 are connected.

  Further, on the output side of the control device C, an electric expansion valve (first extension valve device) 117 of an additional refrigerant amount adjusting device 111 connected to the refrigerant circuit 1, an electromagnetic valve (third extension valve device) 119, A solenoid valve (second extension valve device) 122 is connected. Further, the control device C controls the rotational speed of the fan motor 47M of the gas cooler blower 47 based on the temperature detected by the outside air temperature sensor 56 and the evaporation temperature of the refrigerant in the evaporator 63. As described above, the control device C will be described below as a concept including a control device (not shown) on the additional refrigerant amount adjusting device 111 side. However, the additional refrigerant amount adjusting device 111 is actually added to the refrigerator unit 3. In this state, the control device on the side of the additional refrigerant amount adjusting device 111 receives the detected temperature of the outside air temperature sensor 56 and the detected pressure of the low pressure sensor 32 from the control device C of the refrigerator unit 3. Then, based on the received data and the detected pressure of the additional high pressure sensor 120, the control device on the additional refrigerant amount adjusting device 111 side controls the electric expansion valve 117 and the electromagnetic valves 119 and 122, so that a refrigerant amount adjusting tank, which will be described later. The same refrigerant recovery and discharge as 100 is executed. As a result, the refrigerant is collected in the additional refrigerant amount adjustment tank 116, and the refrigerant is discharged from the additional refrigerant amount adjustment tank 116, thereby adjusting the refrigerant amount circulating in the refrigeration apparatus R.

(A-1) Target high pressure THP
Next, as will be described later, the control device C adds the above-described refrigerant amount adjustment tank 100 and expansion based on the high-pressure side pressure HP detected by the high-pressure sensor 48 and the target value (target high-pressure: THP) of the high-pressure side pressure. The recovery of the refrigerant to the refrigerant quantity adjustment tank 116 and the release from them are controlled. In this case, the control device C determines the target high pressure THP from the outside air temperature TA and the refrigerant evaporation temperature TE in the evaporator 63.

  In the refrigeration apparatus R in which the high pressure side of the refrigerant circuit 1 is equal to or higher than the supercritical pressure as in this embodiment, when the outside air temperature TA is a certain temperature, for example, + 30 ° C. or less, a saturation cycle is performed, and at a temperature higher than + 30 ° C. A supercritical cycle is performed. Since the refrigerant is not liquefied when the supercritical cycle is performed, the temperature and pressure are not uniquely determined by the amount of refrigerant in the refrigerant circuit 1 at that time. Therefore, the target high pressure THP differs depending on the outside air temperature TA.

  In the present embodiment, as an example, when the outside air temperature TA detected by the outside air temperature sensor 56 is equal to or lower than a lower limit temperature (for example, 0 ° C.), the target high pressure THP is constant at a predetermined lower limit value THPL. The target high pressure THP is constant at a predetermined upper limit value THPH when the outside air temperature TA is higher than a predetermined temperature (upper limit temperature) higher than 30 ° C. When the outside air temperature TA is higher than the lower limit temperature and lower than the upper limit temperature, the target high pressure THP is obtained as follows.

  As the outside air temperature TA is lower than a predetermined reference temperature, for example, + 30 ° C., the target high pressure THP is determined to decrease, and as the outside air temperature TA increases, the target high pressure THP is determined to increase. Further, as described above, the higher the refrigerant evaporation temperature TE in the evaporator 63 obtained by conversion, the higher the target high pressure THP of the high-pressure side pressure becomes, due to the pressure detected by the low-pressure sensor 32. The lower the target pressure, the lower the target high pressure THP. FIG. 3 is a diagram showing a tendency of the target high pressure THP determined from the outside air temperature TA and the evaporation temperature TE.

  In the present embodiment, the control device C calculates the target high pressure THP from the outside air temperature TA and the evaporation temperature TE using an arithmetic expression. However, the present invention is not limited to this. The target high pressure THP may be acquired based on the data table acquired from the evaporation temperature TE.

(A-2) Refrigerant recovery / refrigerant release control Hereinafter, the recovery of the refrigerant from the refrigerant circuit 1 to the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 by the control device C and the release of the refrigerant to the refrigerant circuit 1 are performed. Control will be described. The control device C performs a high pressure shut-off operation for stopping the operation of the compressor 11 when the high pressure side pressure HP detected by the unit outlet side pressure sensor 58 exceeds a predetermined high pressure protection value (for example, 12 MPa). And Based on this premise, the following control regarding refrigerant recovery and release will be described.

  The control device C is electrically driven based on the target high pressure THP described above and the high pressure side pressure HP of the refrigerant circuit 1 detected by the unit outlet side pressure sensor 58 (as described above, the additional high pressure sensor 120 for the additional refrigerant amount recovery device 111). Expansion valve (first valve device) 102 and electric expansion valve (first expansion valve device) 117, electromagnetic valve (second valve device) 106, electromagnetic valve (second expansion valve device) 122, electromagnetic valve ( By controlling the third valve device) 104 and the solenoid valve (third extension valve device) 119, the refrigerant is discharged from the refrigerant amount adjusting tank 100 and the additional refrigerant amount adjusting tank 116 while collecting the refrigerant. At the same time, the amount of circulating refrigerant in the refrigerant circuit 1 is controlled by adjusting the degree of refrigerant recovery and refrigerant release.

  Next, specific refrigerant recovery and refrigerant discharge control by the control device C will be described with reference to FIG. In the following description, only the refrigerant recovery and discharge control (control of the electric expansion valve 102 and the electromagnetic valves 106 and 104) of the refrigerant amount adjustment tank 100 will be described, but the electric expansion valve 102 is also applied to the additional refrigerant amount adjustment tank 116. The explanation will be omitted on the assumption that the electric expansion valve 117 and the electromagnetic valves 122 and 119 respectively corresponding to the electromagnetic valves 106 and 104 are controlled similarly to the case of the refrigerant amount adjusting tank 100. However, the additional refrigerant amount adjustment tank 116 is connected to the low pressure side of the refrigerant circuit 1 by the electromagnetic valve 122 and is different from the refrigerant amount adjustment tank 100 in that the refrigerant is discharged.

  FIG. 4 shows changes in the control of the opening degree of the electric expansion valve 102 and the opening / closing control of the electromagnetic valves 106 and 104 in accordance with the change in the high-pressure side pressure HP. Assuming that the high pressure side pressure HP of the refrigerant circuit 1 detected by the unit outlet side pressure sensor 58 is in the state of UP2 in FIG. 4 in the vicinity of the target high pressure THP determined as described above, the controller C performs the electric expansion. The valve opening of the valve 102 (electric expansion valve 117 in the case of the additional refrigerant amount adjustment tank 116; hereinafter the same) is fully closed, and the electromagnetic valve 106 (electromagnetic valve 119 in the case of the additional refrigerant amount adjustment tank 116). The same) is opened, and the electromagnetic valve 104 (the electromagnetic valve 122 in the case of the additional refrigerant amount adjusting tank 116, hereinafter the same) is closed. In this state, the refrigerant amount adjustment tank 100 (and the additional refrigerant amount adjustment tank 116; the same applies hereinafter) is not communicated with the high pressure side, the upper part is not communicated with the intermediate pressure region, and only the lower part is in the intermediate pressure region (additional refrigerant amount). In the case of the adjustment tank 116, it communicates with the low pressure side). Accordingly, all the refrigerant in the refrigerant amount adjustment tank 100 is discharged to the intermediate pressure region of the refrigerant circuit 1 (low pressure side in the case of the additional refrigerant amount adjustment tank 116; the same applies hereinafter), and the refrigerant amount adjustment tank 100 becomes empty. Therefore, so-called liquid sealing is prevented.

  The control device C detects the high pressure side pressure HP detected by the unit outlet pressure sensor 58 (the extended high pressure sensor 120 in the case of the extended refrigerant amount adjustment tank 116; the same applies hereinafter) at every predetermined sampling timing T1 (for example, 200 ms). Compared with the target high pressure THP, the transition of the solid arrow in FIG. 4 is determined. That is, when the high-pressure side pressure HP increases from the state of UP2 in FIG. 4 and becomes higher than, for example, the target high-pressure THP + 1.0 (MPa) (target high-pressure THP + 1.0 <high-pressure side pressure HP), the control device C Transition to the state. In the state of UP3, the control device C closes the electromagnetic valve 106 and changes the valve opening degree of the electric expansion valve 102 from the fully closed state (zero step) to the predetermined step S (for example, 100 steps). Further, the electromagnetic valve 104 is opened.

  As a result, the high-temperature and high-pressure refrigerant discharged from the high-stage discharge port 28 of the compressor 11 passes through the oil separator 44 and is cooled by the gas cooler 46 and the intermediate heat exchanger 80, and then a part thereof is opened. Flows into the refrigerant amount adjustment tank 100 via the first communication circuit 101 (the first additional communication pipe 126 in the case of the additional refrigerant amount adjustment tank 116; the same applies hereinafter). .

  Further, when the high-pressure side pressure HP further increases from the state of UP3 in FIG. 4 and becomes higher than the target high-pressure THP + 1.3 (MPa) (target high-pressure THP + 1.3 <high-pressure side pressure HP), the control device C is shown in FIG. Transition to the UP4 state. In this UP4 state, the control device C closes the electromagnetic valve 106, and the valve opening degree of the electric expansion valve 102 is further opened by a predetermined step S from step S (100 step) of UP3. ) Expand the valve opening to the open state. Further, the electromagnetic valve 104 remains open. As a result, the recovery rate of the refrigerant flowing from the first communication circuit 101 into the refrigerant amount adjustment tank 100 via the electric expansion valve 102 is increased.

  Further, when the high-pressure side pressure HP further increases from the state of UP4 in FIG. 4 and becomes higher than the target high-pressure THP + 1.6 (MPa) (target high-pressure THP + 1.6 <high-pressure side pressure HP), the control device C is shown in FIG. Transition to the UP5 state. In this UP5 state, the control device C closes the electromagnetic valve 106, and the valve opening degree of the electric expansion valve 102 is further opened by a predetermined step S from step 2S (200 steps) of UP4, and from the fully closed state, step 3S (300 steps) is performed. ) Expand the valve opening to the open state. Further, the electromagnetic valve 104 remains open. As a result, the recovery rate of the refrigerant flowing into the refrigerant amount adjustment tank 100 from the first communication circuit 101 via the electric expansion valve 102 further increases.

  During the period from UP2 to UP5, the solenoid valve 104 is opened, so that the third communication circuit 103 (the additional refrigerant amount adjustment tank) that connects the upper part of the refrigerant amount adjustment tank 100 and the intermediate pressure region of the refrigerant circuit 1 is provided. In the case of 116, the pressure in the refrigerant quantity adjustment tank 100 can be released to the outside of the tank via the third additional communication pipe 127 (hereinafter the same). Therefore, even when the supercritical cycle operation in which the refrigerant in the refrigerant circuit 1 is not liquefied, such as when the outside air temperature becomes high, the pressure in the refrigerant amount adjustment tank 100 decreases and the refrigerant amount adjustment tank The refrigerant flowing into 100 is liquefied and accumulated in the refrigerant quantity adjustment tank 100. That is, when the pressure in the refrigerant quantity adjustment tank 100 drops below the supercritical pressure, the refrigerant changes from the gas region to the saturation region, and the liquid level can be secured.

  Thereby, the refrigerant | coolant in the refrigerant circuit 1 can be collect | recovered to the refrigerant | coolant amount adjustment tank 100 (and expansion refrigerant | coolant amount adjustment tank 116) rapidly and efficiently. Accordingly, it is possible to eliminate the disadvantage that the refrigerant circuit 1 has an excessively high pressure on the high pressure side, resulting in an abnormally high pressure, and it is possible to prevent the compressor 11 from being overloaded due to the high pressure abnormality.

  Thus, the control device C increases the opening degree of the electric expansion valve 102 as the high-pressure side pressure HP increases, and increases the refrigerant recovery rate to the refrigerant amount adjustment tank 100.

  Next, by collecting the refrigerant in the refrigerant amount adjustment tank 100 in this way, the high pressure side pressure HP detected by the unit outlet pressure sensor 58 from the state of UP5 is reduced, and the high pressure side pressure HP is, for example, the target high pressure THP + 0. When the pressure drops below 6 (MPa), the control device C transitions to the state of DN4 in FIG. The control device C takes in the high pressure side pressure HP detected by the unit outlet pressure sensor 58 at every predetermined sampling timing T2 (for example, 3 s) longer than the sampling timing T1, and compares it with the target high pressure THP in FIG. The transition of the dashed arrow is determined.

  In the state of DN4, the control device C reduces the valve opening of the electric expansion valve 102 to step S / 2 (a state in which 50 steps are opened from the fully closed state. The refrigerant recovery speed is the lowest) and the solenoid valve. 104 closes. Further, the electromagnetic valve 106 is opened after a predetermined time t1 (for example, 10 s) and then closed. Thus, a predetermined amount of refrigerant is released from the refrigerant amount adjustment tank 100 to the intermediate pressure region of the refrigerant circuit 1 via the electromagnetic valve 104 while collecting the refrigerant in the refrigerant amount adjustment tank 100 via the electric expansion valve 102. Is done.

  When the high-pressure side pressure HP continues to decrease due to the release of the refrigerant, for example, when the pressure falls below the target high-pressure THP + 1.2 (MPa) (high-pressure side pressure HP ≦ target high-pressure + 1.2), the control device C selects DN3 in FIG. Transition to the state. In the state of DN3, the control device C similarly reduces the opening degree of the electric expansion valve 102 to step S / 2, and keeps the electromagnetic valve 104 closed. Further, the electromagnetic valve 106 is opened again for a predetermined time t1, and then closed. As a result, while the refrigerant is collected in the refrigerant quantity adjustment tank 100 via the electric expansion valve 102, a predetermined amount of refrigerant further enters the intermediate pressure region of the refrigerant circuit 1 from the refrigerant quantity adjustment tank 100 via the electromagnetic valve 104. Released.

  Also, when the refrigerant is discharged, the high pressure side pressure HP continues to decrease, for example, when the pressure decreases to a target high pressure THP + 0.9 (MPa) or less (high pressure side pressure HP ≦ target high pressure + 0.9), the control device C uses FIG. Transition to the state of DN2. Even in the state of DN2, the control device C similarly reduces the opening degree of the electric expansion valve 102 to step S / 2 and keeps the electromagnetic valve 104 closed. Further, the electromagnetic valve 106 is opened again for a predetermined time t1, and then closed. As a result, while the refrigerant is collected in the refrigerant quantity adjustment tank 100 via the electric expansion valve 102, a predetermined amount of refrigerant further enters the intermediate pressure region of the refrigerant circuit 1 from the refrigerant quantity adjustment tank 100 via the electromagnetic valve 104. Released.

  Then, even when the refrigerant is discharged, the high pressure side pressure HP continues to decrease. For example, when the pressure falls below the target high pressure THP (high pressure side pressure ≦ target high pressure), the control device C transitions to the state of DN1 in FIG. In the state of DN1, the control device C fully closes the electric expansion valve 102 and keeps the electromagnetic valve 104 closed. Further, when the electromagnetic valve 106 is opened, it returns to the same state as the state of UP2 described above.

  As described above, the control device C gradually releases the refrigerant from the refrigerant amount adjustment tank 100 as the high-pressure side pressure HP decreases, that is, by gradually opening the electromagnetic valve 106 for a predetermined time t1 at every sampling timing T2. Release to the low pressure side.

  When the high pressure side pressure HP starts to increase from the state of DN1 in FIG. 4 and becomes higher than the target high pressure THP (high pressure side pressure HP> target high pressure THP), the control device C transitions to the state of UP2 in FIG. However, the state of each valve is the same. Further, when the high pressure side pressure HP is increased by the discharge of the refrigerant from the state of DN2 in FIG. 4 and becomes higher than the target high pressure THP + 1.0 (MPa), for example (high pressure side pressure HP> target high pressure THP + 1.0), control is performed. Device C transitions to the state of UP3 in FIG. That is, in the state of UP3, the control device C closes the electromagnetic valve 106, changes the valve opening degree of the electric expansion valve 102 from the fully closed state (zero step) to the step S (100 step), and opens the electromagnetic valve 104. . As a result, the refrigerant recovery rate increases.

  Further, when the high pressure side pressure HP is increased by the discharge of the refrigerant from the state of DN3 in FIG. 4 and becomes higher than the target high pressure THP + 1.3 (MPa), for example (high pressure side pressure HP> target high pressure THP + 1.3), control is performed. Device C transitions to the state of UP4 in FIG. That is, in the state of UP4, the control device C closes the electromagnetic valve 106, changes the valve opening degree of the electric expansion valve 102 from the fully closed state (zero step) to the step 2S (200 step), and opens the electromagnetic valve 104. . Thereby, the refrigerant recovery rate further increases.

  Further, when the high pressure side pressure HP is increased by the discharge of the refrigerant from the state of DN3 in FIG. 4 and becomes higher than, for example, the target high pressure THP + 1.6 (MPa) (high pressure side pressure HP> target high pressure THP + 1.6), control is performed. Device C transitions to the state of UP5 in FIG. That is, in the state of UP5, the control device C closes the solenoid valve 106, changes the valve opening degree of the electric expansion valve 102 from the fully closed state (zero step) to the step 3S (300 step), and opens the solenoid valve 104. . Thereby, the refrigerant recovery rate further increases.

  On the other hand, when the refrigerant is recovered from the state of UP4 in FIG. 4 and the high pressure side pressure HP is lowered, for example, the target high pressure THP + 0.3 (MPa) or less (high pressure side pressure HP ≦ target high pressure THP + 0.3), The control device C transitions to the state of DN3 in FIG. That is, in the state of DN3, the control device C reduces the opening degree of the electric expansion valve 102 to step S / 2, closes the electromagnetic valve 104, opens the electromagnetic valve 106 for a predetermined time t1, and then closes it. Thus, a predetermined amount of refrigerant is released from the refrigerant amount adjustment tank 100 to the intermediate pressure region of the refrigerant circuit 1 via the electromagnetic valve 104 while collecting the refrigerant in the refrigerant amount adjustment tank 100 via the electric expansion valve 102. Is done.

  Further, when the high pressure side pressure HP is lowered by the recovery of the refrigerant from the state of UP3 in FIG. 4 and becomes lower than the target high pressure THP, for example (high pressure side pressure HP ≦ target high pressure THP), the control device C selects DN2 in FIG. Transition to the state. That is, in the state of DN2, the control device C makes the valve opening degree of the electric expansion valve 102 reduced to step S / 2, closes the electromagnetic valve 104, opens the electromagnetic valve 106 for a predetermined time t1, and then closes it. Thus, a predetermined amount of refrigerant is released from the refrigerant amount adjustment tank 100 to the intermediate pressure region of the refrigerant circuit 1 via the electromagnetic valve 104 while collecting the refrigerant in the refrigerant amount adjustment tank 100 via the electric expansion valve 102. Is done.

  For example, when the high pressure side pressure HP is higher than the target high pressure THP + 1.2 (MPa) and stabilized below the target high pressure THP + 1.6 (MPa) in the state of DN4 in FIG. 4, the control device C is in the state of DN4. To maintain. That is, the high pressure side pressure HP is maintained higher than the target high pressure THP, so that the cooling performance of the refrigeration apparatus R is ensured.

  Since the refrigerant amount adjustment tank 100 and the additional refrigeration apparatus 116 are connected to the refrigerant circuit 1 in this way, the refrigerant that has become excessive in the refrigerant circuit 1 is supplied from the high pressure side to the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank. 116, and the refrigerant is discharged from the refrigerant amount adjustment tank 100 to the intermediate pressure region of the refrigerant circuit 1 and from the additional refrigerant amount adjustment tank 116 to the low pressure side, so that the circulating refrigerant amount in the refrigerant circuit 1 is appropriately maintained. It becomes possible to do. Thereby, the disadvantage that the high pressure side in the refrigerant circuit 1 becomes abnormally high can be solved, and the overload operation of the compressor 11 due to the high pressure abnormality can be prevented.

  In particular, the control device C controls the circulating refrigerant amount by discharging the refrigerant to the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 while collecting the refrigerant, and adjusting the degree of collection and release based on the target high pressure THP. Thus, it is possible to prevent sudden fluctuations in the circulating refrigerant amount accompanying the recovery of the refrigerant into the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 and the release of the refrigerant therefrom.

  Further, as the high pressure side pressure HP of the refrigerant circuit 1 increases, the control device C changes the refrigerant recovery rate to the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116, and the high pressure side pressure HP increases. Accordingly, the refrigerant recovery rate is increased, so that excessive refrigerant recovery can be prevented in advance, and the amount of circulating refrigerant suddenly increases with the recovery of refrigerant to the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116. It is possible to effectively prevent such fluctuations.

  Further, while collecting the refrigerant in the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116, the refrigerant is discharged from the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 based on the high pressure side pressure HP of the refrigerant circuit 1. Then, as the high pressure side pressure HP of the refrigerant circuit 1 decreases, the refrigerant is gradually released from the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116, and thus from the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116. This makes it possible to effectively prevent a sudden change in the amount of circulating refrigerant accompanying the release of the refrigerant.

  Accordingly, it is possible to appropriately maintain and manage the circulating refrigerant amount in the refrigerant circuit 1 of the refrigeration apparatus R in which the high pressure side becomes the critical pressure, and to realize stable cooling performance.

  Further, the control device C changes the refrigerant recovery rate to the refrigerant quantity adjustment tank 100 and the additional refrigerant quantity adjustment tank 116 by the opening degree of the electric expansion valves 102 and 117, and adjusts the refrigerant quantity by the opening time of the electromagnetic valves 106 and 122. Since the refrigerant is gradually released from the tank 100 and the additional refrigerant quantity adjustment tank 116, the degree of refrigerant recovery to the refrigerant quantity adjustment tank 100 and the additional refrigerant quantity adjustment tank 116 and the release of the refrigerant from them is electrically expanded. It becomes possible to accurately control the opening of the valves 102 and 117 and the opening time of the electromagnetic valves 106 and 122.

  Further, when the control device C collects the refrigerant in the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116, it opens the electromagnetic valves 104 and 119, so that the pressure in the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 is increased. The refrigerant in the refrigerant circuit 1 can be smoothly collected in the refrigerant quantity adjustment tank 100 and the additional refrigerant quantity adjustment tank 116. At this time, since the upper part of the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 and the intermediate pressure region of the refrigerant circuit 1 are communicated with each other, the low pressure side pressure increases unlike the case where the refrigerant circuit 1 communicates with the low pressure side region. It is possible to avoid a decrease in cooling efficiency due to being performed.

  Further, the control device C controls the recovery of the refrigerant to the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 and the discharge of the refrigerant from them with reference to the target high pressure THP of the refrigerant circuit 1, so that the high pressure side pressure HP is set. Based on this, the degree of refrigerant recovery and release can be controlled, and high pressure protection and overload operation can be accurately prevented. As a result, the cooling performance of the refrigeration apparatus R can be ensured, and the COP can be optimized.

  In this case, as described above, since the control device C determines the target high pressure THP based on the outside air temperature and the evaporation temperature of the refrigerant in the evaporator 63, the state of the refrigerant changing into the saturation cycle and the supercritical cycle depending on the outside air temperature is taken into consideration. In addition, a suitable high-pressure side pressure can be realized based on the evaporation temperature, and high-efficiency operation is possible.

  In this case, the compressor 11 (compression means) employs a two-stage compression rotary compressor in which the first and second compression elements 18 and 20 and the electric element are incorporated in the sealed container 12. In addition to this, it may be of a type in which the refrigerant can be taken out and introduced from the intermediate pressure section with two single-stage rotary compressors or other types of compressors.

(B) Split cycle Next, the split cycle of the refrigeration apparatus R of the embodiment will be described. The refrigeration apparatus R in the embodiment includes the first rotary compression element (low stage side 18) of each compressor 11, the intercooler 38, a merger 81 as a merger that merges two fluid flows, and each compressor. 11, the second rotary compression element (high stage side) 20, oil separator 44, gas cooler 46, flow divider 82, auxiliary throttle means (auxiliary expansion valve) 83, intermediate heat exchanger 80, main throttle means (main expansion valve) ) 62 and the evaporator 63 constitute a refrigeration cycle.

  The flow divider 82 is a flow dividing device that divides the refrigerant from the gas cooler 46 into two flows. That is, the flow divider 82 of the present embodiment diverts the refrigerant that has exited the gas cooler 46 into the first refrigerant flow and the second refrigerant flow, the first refrigerant flow through the auxiliary circuit, and the second refrigerant flow. In the main circuit.

  The main circuit in FIG. 1 is the first rotary compression element 18 of the compressor 11, the intercooler 38, the merger 81, the second rotary compression element 20, the gas cooler 46, the flow divider 82, and the intermediate heat exchanger 80. 2 is an annular refrigerant circuit composed of the second flow path 80B, the main throttle means 62, and the evaporator 63, and the auxiliary circuit is connected from the flow divider 82 to the auxiliary throttle means 83 and the first flow path 80A of the intermediate heat exchanger 80. A circuit that sequentially reaches the merger 81 is shown. The second communication circuit 105 on the downstream side of the solenoid valve 106 and the capillary tube 107 joins the inlet of the first flow path 80 </ b> A on the downstream side of the auxiliary throttle means 83.

  The auxiliary throttle means 83 diverts the first refrigerant flow that is diverted by the flow divider 82 and flows through the auxiliary circuit. The intermediate heat exchanger 80 includes a first refrigerant flow in the auxiliary circuit decompressed by the auxiliary throttle means 83 and a refrigerant discharged from the lower part of the refrigerant amount adjustment tank 100 through the second communication circuit 105 (hereinafter referred to as “the refrigerant”). This heat exchanger generally performs heat exchange between the first refrigerant flow) and the second refrigerant flow diverted by the flow divider 82. In the intermediate heat exchanger 80, a second flow path 80B through which the second refrigerant flow flows and a first flow path 80A through which the first refrigerant flow flows are provided in a heat exchangeable relationship. Since the second refrigerant flow is cooled by the first refrigerant flow flowing through the first flow path 80A by passing through the second flow path 80B of the intermediate heat exchanger 80, the ratio in the evaporator 63 Enthalpy can be reduced.

  As shown in FIG. 2, the control device C includes a discharge temperature sensor (discharge temperature detection means) 50, a unit outlet side pressure sensor (unit outlet side pressure detection means) 58, an intermediate pressure sensor (intermediate pressure pressure) on the input side. 49), low pressure sensor (suction pressure detection means) 32, gas cooler outlet temperature sensor (gas cooler outlet temperature detection means) 52, unit outlet temperature sensor (unit outlet temperature detection means) 54, unit inlet temperature sensor (inlet temperature detection) Means) 34 is connected.

  The discharge temperature sensor 50 is provided at the high-stage discharge port 28 of each compressor 11 and detects the discharge temperature of the refrigerant discharged from the second rotary compression element 20. The unit outlet side pressure sensor 58 is as described above. The low pressure sensor 32 is provided in the refrigerant pipe 9 connected to the low pressure side suction port 22 of the compressor 11 on the low pressure side of the refrigerant circuit 1, in the present embodiment, on the downstream side of each evaporator 63. The suction pressure of the refrigerant toward the refrigerant introduction pipe 30 is detected. The intermediate pressure sensor 49 detects the pressure of the third communication circuit 103 on the downstream side of the solenoid valve 104 in the intermediate pressure region of the refrigerant circuit 1, in this embodiment.

  The gas cooler outlet temperature sensor 52 is provided on the outlet side of the gas cooler 46 and detects the temperature (GCT) of the refrigerant that has exited the gas cooler 46. The unit outlet temperature sensor 54 is provided on the outlet side of the intermediate heat exchanger 80 connected to the refrigerant pipe 7 and detects the unit outlet temperature (LT). The unit inlet temperature sensor 34 is provided in the refrigerant pipe 9 connected to the lower stage suction port 22 of the compressor 11 and detects the refrigerant suction temperature toward the refrigerant introduction pipe 30. Further, auxiliary throttle means 83 constituting a split cycle is connected to the output side of the control device C. The auxiliary throttle means 83 is also an electric expansion valve whose opening degree is controlled by a step motor.

  Hereinafter, the opening degree control of the auxiliary throttle means 83 will be described in detail. The auxiliary throttle means 83 has a predetermined initial valve opening when the compressor 11 starts operating. Thereafter, the control device C determines an operation amount for increasing the valve opening degree of the auxiliary throttle means 83 based on the following first control amount, second control amount, and third control amount.

(B-1) Valve Opening Increase Control of Auxiliary Throttle Means The first control amount (DTcont) is obtained based on the discharge refrigerant temperature DT of the compressor 11. The control device C determines whether or not the temperature DT detected by the discharge temperature sensor 50 is higher than a predetermined value DT0. If the discharge refrigerant temperature DT is higher than the predetermined value DT0, the control device C The control amount acts in the direction of increasing the opening. The predetermined value DT0 is set to a temperature (for example, + 95 ° C.) that is slightly lower than a limit temperature (for example, + 100 ° C.) that enables proper operation of the compressor 11. When the temperature rises, the auxiliary throttle means 83 is opened. By increasing the degree, the temperature rise of the compressor 11 is suppressed, and control is performed so that the compressor 11 does not reach the limit temperature.

  The second control amount (MPcont) is a control amount for adjusting the amount of refrigerant flowing through the auxiliary circuit of the split cycle to optimize the intermediate pressure (MP). In this embodiment, it is calculated (obtained) from the high pressure side pressure HP of the refrigerant circuit 1 detected by the unit outlet side pressure sensor 58 and the low pressure side pressure LP of the refrigerant circuit 1 detected by the low pressure sensor 32. It is determined whether or not the pressure MP in the intermediate pressure region of the refrigerant circuit 1 detected by the intermediate pressure sensor 49 is higher than the appropriate intermediate pressure value, and the pressure MP in the intermediate pressure region is lower than the appropriate intermediate pressure value. In this case, the auxiliary throttle means 83 is acted in the direction of increasing the opening degree.

  The appropriate intermediate pressure value may be calculated from the geometric mean of the detected high-pressure side pressure HP and the low-pressure side pressure LP. In addition, an appropriate intermediate pressure value may be calculated from the high-pressure side pressure HP and the low-pressure side pressure LP in advance. The intermediate pressure value may be obtained experimentally and determined from a data table constructed based on this.

  In the present embodiment, the second control amount (MPcont) is determined by comparing the appropriate intermediate pressure value obtained from the high pressure side pressure HP and the low pressure side pressure LP with the pressure MP in the intermediate pressure region. However, the present invention is not limited to this. For example, the following may be adopted. That is, the over-compression determination value MPO is obtained from the pressure MP in the intermediate pressure region of the refrigerant circuit 1 detected by the intermediate pressure sensor 49 and the low-pressure side pressure LP of the refrigerant circuit 1 detected by the low-pressure sensor 32. It is determined whether the compression determination value MPO is lower than the high pressure side pressure HP of the refrigerant circuit 1 detected by the unit outlet side pressure sensor 58, and when the over compression determination value MPO is lower than the high pressure side pressure HP, The auxiliary throttle means 83 is operated in the direction of increasing the opening degree. By reflecting the second control amount in the opening degree control of the auxiliary throttle means 83, the pressure difference among the high pressure side pressure HP, the intermediate pressure region pressure MP, and the low pressure side pressure LP can be appropriately maintained, and the refrigeration cycle The operation can be stabilized.

  The third control amount (SPcont) is a control amount for optimizing the refrigerant temperature LT that has come out of the second flow path of the intermediate heat exchanger 80. In the present embodiment, the control device C includes the refrigerant temperature GCT that has passed through the gas cooler 46 detected by the gas cooler outlet temperature sensor 52 and the second refrigerant flow that has passed through the intermediate heat exchanger 80 detected by the unit outlet temperature sensor 54. It is determined whether or not the difference (GCT−LT) from the temperature LT is smaller than the predetermined value SP. If the difference is smaller, the opening degree of the auxiliary throttle means 83 is increased.

  Here, the predetermined value SP is different depending on whether the high-pressure side pressure HP is in the supercritical region or the saturation region of the refrigerant. In the present embodiment, whether the high-pressure side pressure HP is a supercritical region or a saturated region is based on the outside air temperature detected by the outside air temperature sensor 56, and when the outside air temperature is high, for example, at + 31 ° C. or higher, If it is determined that the temperature is in the supercritical region and the outside air temperature is low, for example, if it is less than + 31 ° C., it is determined that the region is a saturated region. If it is determined that the region is a supercritical region, the predetermined value SP is set to be increased, and if it is determined to be a saturated region, the predetermined value SP is decreased. In this embodiment, the predetermined value SP is 35 ° C. in the supercritical region and 20 ° C. in the saturation region.

  The control device C adds the three control amounts obtained as described above, that is, the first control amount (DTcont), the second control amount (MPcont), and the third control amount (SPcont). Thus, the operation amount of the valve opening of the auxiliary throttle means 83 is determined, and the valve opening is increased based on this.

(B-2) Valve Opening Reduction Control of Auxiliary Throttle Means Further, the control device C is configured such that the temperature LT of the second refrigerant flow that has passed through the intermediate heat exchanger 80 or the refrigerant temperature DT discharged from the compressor 11 and the gas cooler. The operation amount for reducing the valve opening degree of the auxiliary throttle means 83 is determined from the difference from the refrigerant temperature GCT after 46.

  That is, the control device C determines whether or not the temperature LT of the second refrigerant flow that has passed through the intermediate heat exchanger 80 detected by the unit outlet temperature sensor 54 is lower than a predetermined value. In this embodiment, the predetermined value is 0 ° C. as an example. Thereby, when the unit outlet temperature is 0 ° C. or lower, the second refrigerant flow cooled in the intermediate heat exchanger 80 is excessively cooled by operating in the direction of reducing the opening degree of the auxiliary throttle means 83. Can eliminate the inconvenience.

  Further, in the control device C, the difference (DT−GCT) between the temperature DT detected by the discharge temperature sensor 50 and the temperature GCT of the refrigerant passed through the gas cooler 46 detected by the gas cooler outlet temperature sensor 52 is based on the predetermined value TDT. It is determined whether or not it is low. If it is low, the opening of the auxiliary throttle means 83 is acted in a direction to reduce it.

  Here, the predetermined value TDT differs depending on whether the high-pressure side pressure HP is in the supercritical region or the saturation region of the refrigerant. In the present embodiment, as in the case of obtaining the third control amount, whether the high-pressure side pressure HP is in the supercritical region or the saturated region is determined based on the outside air temperature. When it is determined that the region is a supercritical region, the predetermined value TDT is set to be lowered. When it is determined that the region is a saturated region, the predetermined value TDT is increased. In this embodiment, the predetermined value TDT is 10 ° C. in the supercritical region and 35 ° C. in the saturation region.

  When the temperature LT of the second refrigerant flow that has passed through the intermediate heat exchanger 80 is equal to or lower than a predetermined value (0 ° C.), the control device C or the discharge refrigerant temperature DT from the compressor 11 and the refrigerant that has passed through the gas cooler 46 When the difference from the temperature GCT is lower than the predetermined value TDT, the operation amount of the valve opening of the auxiliary throttle means 83 is determined, and the valve opening is reduced based on this, regardless of the valve opening increase control.

  In the refrigeration apparatus R in the present embodiment having the split cycle as described above, the second refrigerant is separated by the first refrigerant flow that is diverted and decompressed by the auxiliary throttle means 83 after the refrigerant that has radiated heat by the gas cooler 46 is divided. The flow can be cooled, and the specific enthalpy at the inlet of the evaporator 63 can be reduced. As a result, the refrigeration effect can be increased and the performance can be effectively improved as compared with the conventional apparatus. Further, since the divided first refrigerant flow is returned to the second rotary compression element 20 (intermediate pressure portion) from the high-stage suction port 26 of the compressor 11, the first refrigerant flow from the low-stage suction port 22 of the compressor 11 is returned. The amount of the second refrigerant flow sucked into the first rotary compression element 18 (low pressure part) decreases, and the compression work in the first rotary compression element 18 (low stage part) for compression from low pressure to intermediate pressure Decrease. As a result, the compression power in the compressor 11 is reduced and the coefficient of performance is improved.

  Here, the effect of the so-called split cycle depends on the amounts of the first refrigerant flow and the second refrigerant flow flowing through the intermediate heat exchanger 80. That is, if the amount of the first refrigerant flow is too large, the amount of the second refrigerant flow that finally evaporates in the evaporator 63 is insufficient, and conversely if the amount of the first refrigerant flow is too small, the split cycle. The effect will fade. On the other hand, the pressure of the first refrigerant flow depressurized by the auxiliary throttle means 83 is the intermediate pressure of the refrigerant circuit 1, and controlling the intermediate pressure controls the amount of the first refrigerant flow.

  Here, in this embodiment, as described above, when the temperature DT (discharge temperature sensor 50) of the refrigerant discharged from the compressor 11 is higher than the predetermined value DT0, the opening of the auxiliary throttle means 83 is increased. When the pressure MP in the intermediate pressure region of the refrigerant circuit 1 is lower than the appropriate intermediate pressure value obtained from the first control amount, the high pressure side pressure HP and the low pressure side pressure LP of the refrigerant circuit 1, the auxiliary throttle means 83 The difference (GCT−LT) between the second control amount acting in the direction of increasing the opening degree and the temperature LT of the refrigerant passing through the gas cooler 46 and the temperature LT of the second refrigerant flow passing through the intermediate heat exchanger 80 is predetermined. If the value of the auxiliary throttle means 83 is smaller than the value SP, a third control amount acting in the direction of increasing the opening degree of the auxiliary throttle means 83 is calculated, and the first to third control quantities are added together to calculate the valve of the auxiliary throttle means 83. The operation amount to increase the opening A constant. Further, when the temperature LT is lower than a predetermined value, or when the temperature DT-GCT is lower than the predetermined value TDT, the operation amount is determined in a direction to reduce the valve opening degree of the auxiliary throttle means 83.

  As a result, the temperature DT of the discharged refrigerant can be kept at a predetermined value DT0 or less by the first control amount, and the intermediate pressure MP of the refrigerant circuit 1 can be optimized by the second control amount. The pressure difference among LP, intermediate pressure MP, and high-pressure side pressure HP can be kept appropriate. In addition, the temperature LT of the second refrigerant flow that has passed through the intermediate heat exchanger 80 can be lowered by the third control amount, and the refrigeration effect can be maintained. As a result, it is possible to achieve high efficiency and stabilization of the refrigeration apparatus as a whole.

  Further, the control device C increases the predetermined value SP and decreases the predetermined value TDT when the high pressure side pressure HP is in the supercritical region, and decreases the predetermined value SP when the high pressure side pressure HP is in the saturation region. By increasing the value TDT, control is performed by changing the third control amount and the predetermined values SP and TDT of the first control amount separately for the case where the high pressure side pressure HP is in the supercritical region and the case where it is in the saturation region. It becomes possible to do.

  Thereby, even when the high-pressure side pressure HP is in the saturation region, the degree of superheat in the intermediate heat exchanger 80 can be reliably ensured, and the inconvenience of causing a liquid back in the compressor 11 can be avoided. Further, when the high-pressure side pressure HP is in the supercritical region, such a liquid back does not occur, and therefore, the efficiency can be set as a priority.

  Note that the second control amount in the above embodiment is supplemented when the overcompression determination value MPO obtained from the pressure MP and the low pressure LP in the intermediate pressure region of the refrigerant circuit 1 is lower than the high pressure HP of the refrigerant circuit. As the second control amount acting in the direction of increasing the opening of the throttle means, the operation amount of the valve opening of the auxiliary throttle means can be determined by adding the first to third control amounts. Similarly to the above, the intermediate pressure MP of the refrigerant circuit can be optimized, whereby the pressure difference among the low pressure side pressure LP, the intermediate pressure MP, and the high pressure side pressure HP can be kept appropriate.

  In addition, the first refrigerant flow output from the intermediate heat exchanger 80 in this embodiment can be returned to the outlet side of the intercooler 38 by the merger 81 provided on the outlet side of the intercooler 38. Thus, it is possible to prevent the pressure loss at 38 and smoothly join the refrigerant flow coming out of the intermediate heat exchanger 80 to the intermediate pressure side of the refrigerant circuit 1.

  Furthermore, in the embodiment, since the refrigerant released from the refrigerant quantity adjustment tank 100 is also flowing through the first flow path 80A of the intermediate heat exchanger 80, the released refrigerant also flows through the second flow path 80B. There is an effect that can be used for cooling of.

(D) Control of Gas Cooler Blower Next, control of the gas cooler blower 47 that air-cools the gas cooler 46 as described above will be described. As shown in FIG. 2, the control device C in the present embodiment is connected to a high pressure sensor (high pressure detector) 48, a low pressure sensor 32, and an outside air temperature sensor 56 on the input side. Here, since the pressure detected by the low pressure sensor 32 and the evaporation temperature TE in the evaporator 63 have a certain relationship, the controller C evaporates by the pressure detected by the low pressure sensor 32. The refrigerant evaporation temperature TE in the vessel 63 is converted and acquired. Further, a fan motor 47M of a gas cooler blower 47 that air-cools the gas cooler 46 is connected to the output side of the control device C.

  The control device C controls the rotational speed of the gas cooler blower 47 so that the high pressure side pressure HP detected by the high pressure sensor 48 becomes the target high pressure: THP. That is, the control device C uses the high pressure side pressure HP detected by the high pressure sensor 48 (high pressure detection means), the target high pressure THP, the deviation e between these HP and THP, and P (proportional deviation based on the deviation e). Proportional differential operation is performed from D (differentiation, control in the direction to reduce the change of the deviation e), and derived as an operation amount in proportion to the magnitude of e. The rotational speed of the gas cooler blower 47 (the fan motor 47M) is determined. The rotational speed of the blower 47 is increased as the target high pressure THP is higher, and the rotational speed of the blower 47 is decreased as the target high pressure THP is lower.

  Thereby, the control apparatus C controls the rotation speed of the gas cooler blower 47 based on the outside air temperature TA and the evaporation temperature of refrigerant in the evaporator (converted from the low pressure detected by the low pressure sensor 32) TE. By doing so, even if the refrigeration apparatus R has a supercritical pressure on the high pressure side, the rotational speed of the gas cooler blower 47 can be controlled so as to have an appropriate high pressure. Thereby, high efficiency operation can be realized while reducing noise due to operation of the gas cooler blower 47.

  In the present embodiment, the control device C reduces the target value THP of the high-pressure side pressure of the refrigerant circuit 1 based on the outside air temperature TA and the evaporation temperature TE, for example, the lower the outside air temperature TA, the lower the target value THP. As the temperature TE is higher, the target value THP is determined in the direction of increasing the target value THP, and the gas cooler blower 47 is controlled so that the high-pressure side pressure becomes the target value THP. In consideration of the state of the refrigerant changing to the supercritical cycle, a suitable high-pressure side pressure can be realized based on the evaporation temperature TE, thereby realizing a highly efficient operation.

(E) Oil Separator On the other hand, an oil separator 44 is interposed in the high-pressure discharge pipe 42 that connects the high-stage discharge port 28 of the compressor 11 and the gas cooler 46 as described above. The oil separator 44 separates and captures the oil contained in the high-pressure discharged refrigerant discharged from the compressor 11 from the refrigerant. The oil separator 44 returns the captured oil to the compressor 11. An oil return circuit 73 is connected. The oil return circuit 73 is provided with an oil tank 79 and an oil cooler 74 for cooling the captured oil. The oil return circuit 73 is branched into two systems on the downstream side of the oil cooler 74, and the flow rate is adjusted respectively. It is connected to the hermetic container 12 of the compressor 11 via a valve (electric valve) 76. Since the inside of the sealed container 12 of the compressor 11 is maintained at an intermediate pressure as described above, the trapped oil is caused by the differential pressure between the high pressure in the oil separator 44 and the intermediate pressure in the sealed container 12. 12 is returned. The hermetic container 12 of the compressor 11 is provided with an oil level float switch 77 that detects the level of oil held in the hermetic container 12.

  Further, as described above, the oil cooler 74 is installed in the same air passage 45 as the gas cooler 46 and is air-cooled by the gas cooler blower 47. The high-temperature and high-pressure refrigerant discharged from the high-stage discharge port 28 of each compressor 11 merges on the downstream side of the second rotary compression element 20, and is connected to the showcase unit 5 via the oil separator 44, the gas cooler 46, and the like. The The oil contained in the high-temperature and high-pressure refrigerant that has flowed into the oil separator 44 is separated from the refrigerant and captured. Since the inside of the sealed container 12 of the compressor 11 is maintained at an intermediate pressure, the trapped oil is supplied to the oil return circuit 28 by the differential pressure between the high pressure in the oil separator 44 and the intermediate pressure in the sealed container 12. To the compressor 11.

  The oil flowing into the oil return circuit 28 is air-cooled by the operation of the blower 47 in the oil cooler 74 disposed in the same air passage 45 as the gas cooler 46. After passing through the oil cooler 74, it is separated into two systems, and returns to the compressor 11 through the flow rate adjusting valve 76. As a result, the oil heated to a high temperature together with the high-temperature refrigerant is cooled by the oil cooler 74 and returned to the compressor 11, so that an increase in the temperature of the compressor 11 can be suppressed.

(F) Refrigerant Enclosed Amount Adjusting Mechanism Next, the refrigerant enclosed amount adjusting mechanism 131 provided in the refrigeration apparatus R will be described. The refrigerant charging amount adjusting mechanism 131 is provided in the refrigerator unit 3. A discharge pipe 132 is connected in communication with the refrigerant pipe 9 of the refrigerant circuit 1 in the refrigerator unit 3, and a discharge valve 133 including an electric valve is attached to the discharge pipe 132. In the embodiment, the discharge pipe 132 and the discharge valve 133 are attached to the refrigerant pipe 9. However, the present invention is not limited thereto, and the intermediate pressure discharge pipe 36 on the inlet side of the intercooler 38 and the outlet of the intercooler 38 are not limited thereto. It may be attached to the intermediate pressure region of the refrigerant circuit 1 such as the intermediate pressure suction pipe 40 on the side.

  The discharge pipe 132, the discharge valve 133, and the control device C constitute a refrigerant charging amount adjusting mechanism 131, and the discharge valve 133 is connected to the output side of the control device C. In the control device C, for example, a predetermined discharge regulation value (for example, 11.1 MPa) that is higher than a recovery threshold value (10.5 MPa) as one of the conditions for starting the refrigerant recovery operation described above and lower than the high-pressure protection value (12 MPa). The discharge valve 133 is opened and closed based on the specified discharge value (11.5 MPa) and, for example, the recovery threshold value (10.5 MPa) described above.

  As described above, when the detected pressure of the unit outlet side pressure sensor 58 rises and exceeds the recovery threshold (10.5 MPa), the control device C supplies the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 described above. The refrigerant recovery operation is started. When the control device C starts the refrigerant recovery operation, the electric expansion valve 102, the electromagnetic valve 104, the electric expansion valve 117, and the electromagnetic valve 119 are opened as described above, so that the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 are reached. The refrigerant recovery capacity is the maximum. However, if the amount of refrigerant enclosed in the refrigerant circuit 1 is originally excessive (overfilling), the refrigerant cannot be fully recovered even if the refrigerant recovery capacity is maximized in each tank, and the detected pressure of the unit outlet side pressure sensor 58 Will rise further without going down.

  Here, in the case of a refrigeration apparatus R such as the present invention that operates under both conditions of a saturation cycle and a supercritical cycle, an appropriate amount of sealing is determined by the temperature (outside air temperature) when the refrigerant is sealed in the refrigerant circuit 1. What is difficult to judge and sealed in winter when the outside air temperature is low becomes overfilled in the summer and the high pressure side rises abnormally.

  Therefore, when the detected pressure (high pressure side pressure) of the unit outlet side pressure sensor 58 rises to the above-mentioned predetermined discharge value (11.5 MPa), the control device C opens the discharge valve 133 and supplies the refrigerant through the discharge pipe 132. The refrigerant is discharged from the circuit 1 to the outside. Since the detected pressure of the unit outlet side pressure sensor 58 decreases due to the discharge of the refrigerant, the detected pressure of the unit outlet side pressure sensor 58 exceeds the high pressure protection value (12 MPa), and the compressor 11 is stopped. Is prevented in advance. When the detected pressure of the unit outlet side pressure sensor 58 decreases to the above-described recovery threshold (discharge stop value; 10.5 MPa), the control device C closes the discharge valve 133 and stops the discharge of the refrigerant. Thereafter, the above-described refrigerant recovery operation is entrusted. Thereby, the refrigerant | coolant for an overfill is discharged | emitted.

  In this way, the control device C opens the discharge valve 133 and overfills the refrigerant circuit 1 from the discharge pipe 132 to the outside when the high-pressure side pressure of the refrigerant circuit 1 rises abnormally and exceeds a predetermined predetermined discharge value. Therefore, even when the season changes and the refrigeration apparatus R falls into the refrigerant overfill state, the refrigerant filling amount in the refrigerant circuit 1 is automatically adjusted to an appropriate value. . Therefore, adjustment of the refrigerant filling amount of the refrigeration apparatus R operated in both the saturation cycle and the supercritical cycle is extremely easy. In particular, when the refrigerant amount adjustment tank 100 and the additional refrigerant amount adjustment tank 116 are provided as in the embodiment, and the refrigerant is overfilled so that the refrigerant cannot be recovered, the overfill state is determined by the refrigerant charging amount adjustment mechanism 131. It will be possible to resolve it reliably.

  Further, in this case, the discharge pipe 132 is attached in communication with the low pressure side (example) or the intermediate pressure region of the refrigerant circuit 1, and the discharge valve 133 discharges the refrigerant from the low pressure side, and therefore discharges from the high pressure side. Compared to the case, the refrigerant can be discharged gently, and the disadvantage of discharging the refrigerant more than necessary is prevented.

  In addition, although the Example demonstrated the refrigeration apparatus R which attached the expansion refrigerant | coolant amount adjustment apparatus 111 provided with the expansion refrigerant | coolant amount adjustment tank 116, it is not restricted to it, Only the refrigerant | coolant amount adjustment tank 100 is provided in the refrigerator unit 3. The present invention is also effective for the refrigeration apparatus R.

  Furthermore, each numerical value illustrated in the embodiment is not limited thereto, and may be appropriately set according to the refrigeration apparatus R.

R Refrigeration equipment C Control equipment (control means)
DESCRIPTION OF SYMBOLS 1 Refrigerant circuit 3 Refrigerator unit 5 Showcase unit 7, 9 Refrigerant piping 11 Compressor 36 Intermediate pressure discharge piping 38 Intercooler 44 Oil separator 46 Gas cooler 48 High pressure sensor (high pressure detection means)
49 Intermediate pressure sensor (Intermediate pressure detection means)
58 Unit outlet pressure sensor (Unit outlet pressure detector)
62 Main throttle means (throttle means)
63 Evaporator 80 Intermediate heat exchanger 80A First flow path 80B Second flow path 83 Auxiliary expansion valve (auxiliary throttle means)
DESCRIPTION OF SYMBOLS 100 Refrigerant amount adjustment tank 101 1st communication circuit 102 Electric expansion valve (1st valve apparatus which has a throttling function)
103 Third communication circuit 104 Solenoid valve (third valve device)
105 Second communication circuit 106 Solenoid valve (second valve device)
111 Additional refrigerant amount adjusting device 116 Additional refrigerant amount adjusting tank 117 Electric expansion valve (first expansion valve device having a throttling function)
119 Solenoid valve (third extension valve device)
122 Solenoid valve (second expansion valve device)
126 First extension communication pipe (configures a first extension communication circuit)
127 Third extension communication pipe (configures a third extension communication circuit)
128 Second extension communication pipe (configures a second extension communication circuit)
131 Refrigerant charge amount adjustment mechanism

Claims (4)

In the refrigerating apparatus in which the refrigerant circuit is configured by the compression means, the gas cooler, the throttling means, and the evaporator, and the high pressure side is the supercritical pressure,
A refrigerant amount adjusting tank connected to the refrigerant circuit;
A first communication circuit communicating the refrigerant amount adjustment tank and the high pressure side of the refrigerant circuit;
A second communication circuit communicating the lower part of the refrigerant amount adjustment tank and the intermediate pressure region of the refrigerant circuit, or the low pressure side;
A third communication circuit communicating the upper part of the refrigerant amount adjustment tank and the intermediate pressure region of the refrigerant circuit;
A first valve device having a throttling function provided in the first communication circuit;
A second valve device provided in the second communication circuit;
A third valve device provided in the third communication circuit;
Control means for recovering the circulating refrigerant on the high-pressure side of the refrigerant circuit in the refrigerant amount adjustment tank and releasing the refrigerant collected in the refrigerant amount adjustment tank to an intermediate pressure region or a low-pressure side of the refrigerant circuit; ,
The control means determines a target value of the high-pressure side pressure of the refrigerant circuit based on an outside air temperature and an evaporation temperature of the refrigerant in the evaporator,
When the high-pressure side pressure of the refrigerant circuit is higher than the target value of the high-pressure side pressure, the third valve device is opened and the refrigerant is recovered into the refrigerant amount adjustment tank by the valve opening of the first valve device. When the speed is changed and the high pressure side pressure of the refrigerant circuit is lower than the target value of the high pressure side pressure, the first valve device is slightly opened and the second valve device is opened according to the opening time. A refrigeration apparatus that gradually discharges refrigerant from a refrigerant quantity adjustment tank . 2. The refrigeration apparatus according to claim 1, wherein the control unit controls the valve opening degree of the first valve device to gradually open as the high-pressure side pressure of the refrigerant circuit increases . The said control means opens the said 2nd valve apparatus only for predetermined time, and discharge | releases a refrigerant | coolant gradually from a refrigerant | coolant amount adjustment tank as the high pressure side pressure of the said refrigerant circuit falls. The refrigeration apparatus according to claim 1 or claim 2. The refrigeration apparatus according to any one of claims 1 to 3, wherein carbon dioxide is used as the refrigerant.

Images