KR20110074712A - Freezing device - Google Patents

Abstract

PURPOSE: A freezing apparatus is provided to perform a hot water supply operation using discharged heat. CONSTITUTION: A freezing apparatus includes a refrigerant circuit composed of a compressor, a gas cooler, an auxiliary fastener, an intermediate heat exchanger(70), a main fastener, and an evaporator, and a controller. The refrigerant coming out from the gas cooler is classified into two flows. The first refrigerant flow passes through the auxiliary fastener and flows to a first flow path of the intermediate heat exchanger. The second refrigerant flow flows to a second flow path of the intermediate heat exchanger, and then to the evaporator through the main fastener. The first refrigerant flow and the second refrigerant flow exchange heat in the intermediate heat exchanger. The refrigerant coming out from evaporator is sucked into the low pressure region of the compression means. The first refrigerant flow coming out from the intermediate heat exchanger is sucked into the medium pressure region of the compression means. The exhaust heat recovery heat exchanger includes an exhaust heat recovery media flow path and a refrigerant flow path. The second refrigerant flow before entering to the intermediate heat exchanger is flowed to the refrigerant flow path of the exhaust heat recovery heat exchanger.

Description

Freezer {FREEZING DEVICE}

The present invention relates to a refrigerating device in which a refrigerant circuit is composed of a compression means, a gas cooler, a tightening means and an evaporator, and the high pressure side is a supercritical pressure.

Conventionally, in this type of refrigeration apparatus, a refrigeration cycle is composed of a compression means, a gas cooler, a tightening means, and the like, and the refrigerant compressed by the compression means is radiated by the gas cooler, and the pressure is reduced by the tightening means, followed by an evaporator. The refrigerant was evaporated to cool the surrounding air by evaporation of the refrigerant at this time. Recently, these types of refrigeration systems have been unable to use the freon refrigerant due to natural environment problems and the like. For this reason, using carbon dioxide which is a natural refrigerant as a substitute for a freon refrigerant has been developed. It is known that the carbon dioxide refrigerant is a refrigerant having a high high pressure difference, a critical pressure is low, and the high pressure side of the refrigerant cycle becomes a supercritical state by compression (see Patent Document 1, for example).

[Patent Document 1] Japanese Patent Application Laid-Open No. 7-18602

In the refrigerating device, waste heat is generated when the coolant is evaporated by the evaporator to cool the cooling article. Therefore, a system has been developed to provide a hot water supply device using the waste heat and to conserve energy. At this time, the refrigerant before entering the evaporator is introduced into the heat recovery heat exchanger, and heat exchanged with the refrigerant of the heat pump unit that generates hot water circulating in the heat recovery medium flow path provided in the heat recovery heat exchanger. Hot water is generated.

Here, when the heat recovery heat exchanger is provided outside the refrigeration unit as the rear end of the gas cooler, the liquefied refrigerant can be sent to the evaporator, so that the efficiency of the refrigeration cycle can be improved, but the hot water supply efficiency using the heat recovery heat exchanger. In this case, it is necessary to provide a circuit for bypassing the gas cooler. On the other hand, when the heat recovery heat exchanger is provided at the front end of the gas cooler, there is no need to provide a circuit for bypassing such a gas cooler, and since the influence of the outside air temperature is small, the refrigerant and the feeding with high temperature are highly efficient. It is possible to heat exchange the water in the furnace.

On the other hand, in the supercritical refrigerant cycle, the inlet of the evaporator under the condition that the refrigerant temperature at the gas cooler outlet becomes high due to the high heat source temperature (for example, the outside air temperature which is heat exchanged with the gas cooler) on the gas cooler side. Since the ratio of enthalpy increases, the freezing effect is remarkably lowered. In this case, in order to secure the freezing capacity, it is necessary to increase the high pressure pressure, which causes a problem that the compression power increases and the performance coefficient also decreases.

For this reason, the refrigerant cooled by the gas cooler is classified into two refrigerant streams, and one of the classified refrigerant streams (first refrigerant streams) is tightened by the auxiliary fastening means, and then into one passage (first flow path) of the intermediate heat exchanger. The main fastening means after flowing the other refrigerant flow (second refrigerant flow) to the other flow passage (second flow passage) provided alternately with the first flow passage of the intermediate heat exchanger. A refrigeration apparatus of a so-called split cycle (two stage compression single stage expansion intermediate refrigeration cycle) for evaporating through an evaporator has been proposed.

In the above-described split cycle apparatus, the refrigerant after the heat dissipation with the gas cooler is classified, and the second refrigerant stream can be cooled by the first refrigerant flow expanded under reduced pressure, so that the specific enthalpy of the evaporator inlet 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. However, the cooling effect by the first refrigerant stream for cooling before depressurizing the second refrigerant stream is It depends on the amount of the first refrigerant flow and the second refrigerant flow through the intermediate heat exchanger.

In other words, when the amount of the first refrigerant is too large, the amount of the second refrigerant that finally evaporates in the evaporator is insufficient. On the contrary, when the amount of the first refrigerant is too small, the cooling effect by the first refrigerant (ie, , The effect of the split cycle) is minimal.

However, as described above, when the heat recovery heat exchanger is provided at the front end side of the gas cooler, there is a problem that the control of the valve device on the split cycle side is complicated in consideration of the control on the hot water heater side.

SUMMARY OF THE INVENTION The present invention has been made in order to solve the conventional technical problem, and has a so-called split circuit and has a high-critical pressure at a supercritical pressure, whereby hot water can be heated using an array, and a refrigeration cycle can be performed at high efficiency. The purpose is to drive.

In order to solve the above problems, the present invention comprises a refrigerant circuit comprising a compression means, a gas cooler, an auxiliary fastening means, an intermediate heat exchanger, a casting impregnation means, and an evaporator, and flows the refrigerant from the gas cooler in two flows. The first refrigerant flows through the auxiliary fastening means to the first flow path of the intermediate heat exchanger, the second refrigerant flows to the second flow path of the intermediate heat exchanger, and then flows through the casting impregnation means to the evaporator, Heat exchange the first refrigerant and the second refrigerant with the intermediate heat exchanger, suck the refrigerant from the evaporator into the low pressure portion of the compression means, suck the first refrigerant flow from the intermediate heat exchanger into the intermediate pressure portion of the compression means, A refrigeration apparatus in which the high pressure side becomes a supercritical pressure, comprising a heat recovery heat exchanger having a heat recovery medium flow path and a refrigerant flow path, before exiting the gas cooler and entering an intermediate heat exchanger. It characterized by passing the second coolant flow to the refrigerant passage of the heat recovery heat exchanger.

In the second aspect of the invention, in the above, carbon dioxide is used as the refrigerant.

According to the present invention, a refrigerant circuit is composed of a compression means, a gas cooler, an auxiliary tightening means, an intermediate heat exchanger, a casting impregnation means, and an evaporator, and the refrigerant from the gas cooler is classified into two streams. The refrigerant flows through the auxiliary fastening means into the first flow path of the intermediate heat exchanger, the second refrigerant flows into the second flow path of the intermediate heat exchanger, and then flows through the casting impregnation means into the evaporator, whereby the first refrigerant flows into the intermediate heat exchanger. The heat exchanger and the second refrigerant flow, the refrigerant from the evaporator sucks into the low pressure portion of the compression means, the first refrigerant flow from the intermediate heat exchanger sucks into the intermediate pressure portion of the compression means, and the high pressure side A refrigeration apparatus comprising: an array recovery heat exchanger having an array recovery medium flow path and a refrigerant flow path, wherein the second refrigerant stream before exiting the gas cooler and entering the intermediate heat exchanger is array recovery By flowing into the refrigerant flow path of the exchanger, the influence of the outside temperature is small, and the heat recovery unit heats the refrigerant of the heat pump unit which efficiently recovers the arrangement of the refrigerant flowing through the refrigerant flow path through the heat recovery heat exchanger and generates hot water flowing through the heat recovery medium flow path. It is possible to generate.

Also, since the second refrigerant flows out of the gas cooler and enters the intermediate heat exchanger, the refrigerant flows into the heat recovery heat exchanger. Therefore, when the hot water generation side is frequently used, the refrigerant temperature of the second refrigerant flows through the intermediate heat exchanger is reduced. Therefore, the amount of refrigerant of the first refrigerant stream flowing to the intermediate heat exchanger can be reduced. As a result, the amount of refrigerant flowing through the second refrigerant stream can be increased, so that the amount of evaporation of the refrigerant in the evaporator can be increased to improve the efficiency of the refrigeration cycle.

When carbon dioxide is used as the refrigerant as in the invention of claim 2, the refrigerating capacity can be effectively improved, and the performance can be improved.

1 is a refrigerant circuit diagram of a refrigerating device in this embodiment.
2 is a block diagram of a control device.
3 is a diagram showing a trend of the target high pressure HPT determined from the outside air temperature and the evaporation temperature.
4 is a partial longitudinal side view of the refrigerant regulator.
5 is a partial cross-sectional plan view of a refrigerant regulator.

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the drawings. 1 is a refrigerant circuit diagram of a refrigerating device R according to an embodiment of the present invention. The refrigerating device R in this embodiment includes a refrigerator unit 3 and a plurality of showcase units 5A and 5B, and these refrigerator units 3 and each showcase unit 5A and 5B are refrigerants. It is connected by the pipes 7 and 9 to constitute a predetermined refrigeration cycle.

This refrigeration cycle uses carbon dioxide whose refrigerant pressure (high pressure pressure) on the high pressure side is equal to or higher than the critical pressure (supercritical) as the refrigerant. This carbon dioxide refrigerant is excellent in the global environment and is a natural refrigerant in consideration of flammability and toxicity. Moreover, as oil as lubricating oil, existing oils, such as mineral oil (mineral oil), alkyl benzene oil, ether oil, ester oil, PAG (polyalkyl glycol), are used, for example.

The refrigerator unit 3 is equipped with two compressors 11 and 11 arranged in parallel. In the present embodiment, the compressor 11 is an internal intermediate pressure multistage compression rotary compressor, and is disposed and housed in a cylindrical sealed container 12 made of a copper plate and disposed above the inner space of the sealed container 12. A first (low stage) rotary compression arranged as a drive element 14 and a lower side of the drive element 14 and driven by a rotation shaft 16 of the drive element 14. It consists of the rotation compression mechanism part which consists of the element (1st compression element) 18 and the 2nd (high end side) rotation compression element (2nd compression element) 20. As shown in FIG.

The first rotary compression element 18 compresses and discharges the low pressure refrigerant sucked into the compressor 11 from the low pressure side of the refrigerant circuit 1 through the refrigerant pipe 9 to a medium pressure, and discharges the second rotary compression element. 20 further sucks the medium pressure refrigerant compressed and discharged into the first rotary compression element 18, compresses the pressure to high pressure, and discharges the refrigerant to the high pressure side of the refrigerant circuit 1. Compressor 11 is a variable frequency compressor, by changing the operating frequency of the transmission element 14, it is possible to control the rotational speed of the first rotary compression element 18 and the second rotary compression element 20.

The lower end side suction port 22 and the lower end side discharge port 24 communicating with the first rotary compression element 18 and the second rotary compression element 20 are connected to the side surface of the sealed container 12 of the compressor 11. The high stage side suction port 26 and the high stage side discharge port 28 are formed. Refrigerant introduction pipes 30 are connected to the lower end suction ports 22 and 22 of the compressors 11 and 11, respectively, and are joined to the refrigerant pipes 9 by joining on the upstream side.

Refrigerant gas of low pressure (LP: about 4 MPa in a normal operation state) sucked into the low pressure portion of the first rotary compression element 18 by the low stage side suction port 22 is intermediate pressure by the first rotary compression element 18. It is boosted to (MP: about 8 MPa in normal operation state) and discharged into the sealed container 12. Thereby, the inside of the airtight container 12 becomes medium pressure MP.

Then, the intermediate pressure discharge pipes 36 and 36 are connected to the lower end discharge ports 24 and 24 of the compressors 11 and 11 through which the medium pressure refrigerant gas in the sealed container 12 is discharged. It joins from the side and is connected to the one end of the intercooler 38. As shown in FIG. The intercooler 38 air-cools the medium pressure refrigerant discharged from the first rotary compression element 18, and an intermediate pressure suction pipe 40 is connected to the other end of the intercooler 38, and the intermediate pressure suction pipe 40 ) Is connected to the high stage side suction ports 26 and 26 of the compressors 11 and 11 after branching into two.

The medium pressure MP refrigerant gas sucked into the middle pressure part of the second rotary compression element 20 by the high stage side suction port 26 is compressed in the second stage by the second rotary compression element 20. This results in a refrigerant gas having a high temperature and high pressure (HP: supercritical pressure of about 12 MPa in a normal operation state).

High pressure discharge pipes 42 and 42 are connected to the high stage discharge ports 28 and 28 provided on the high pressure chamber side of the second rotary compression element 20 of each of the compressors 11 and 11, respectively. And a refrigerant circuit (7) through the oil separator (44), the gas cooler (46), the heat recovery heat exchanger (70) described below, and the intermediate heat exchanger (80) constituting a split cycle. ) Is connected.

The gas cooler 46 cools the high-pressure discharge refrigerant discharged from the compressor 11, and a gas cooler 47 for air cooling the gas cooler 46 is disposed near the gas cooler 46. . In this embodiment, the gas cooler 46 is provided in parallel with the above-described intercooler 38 and the oil cooler 74 which will be described later in detail, and these are arranged in the same air path 45. The air passage 45 is provided with an outside air temperature sensor (outdoor air temperature detecting means) 56 for detecting the outside air temperature at which the refrigerator unit 3 is disposed.

In addition, the high stage discharge ports 28 and 28 detect high pressure pressure sensors (high pressure pressure detecting means) 48 for detecting the discharge pressure of the refrigerant discharged from the second rotary compression elements 20 and 20, and the discharge refrigerant temperature. A check valve 90 having the discharge temperature sensor (discharge temperature detecting means) 50 and the high pressure side discharge port 28 of the compressor 11 toward the gas cooler 46 (oil separator 44) in the forward direction. There is provided a coolant regulator (91) having a. In addition, the detailed description of the said refrigerant | coolant regulator 91 is mentioned later.

On the other hand, showcase units 5A and 5B are respectively installed in stores and the like and are connected in parallel to refrigerant pipes 7 and 9, respectively. Each showcase unit 5A, 5B has a case side refrigerant pipe 60A, 60B connecting the refrigerant pipe 7 and the refrigerant pipe 9, and each of the case side refrigerant pipes 60A, 60B has a strainer. The strainers 61A and 61B, the casting means 62A and 62B, and the evaporators 63A and 63B are sequentially connected. Each of the evaporators 63A and 63B is adjacent to an unillustrated cold air blower which is blown by the evaporator. The refrigerant pipe 9 is connected to the low stage side suction port 22 communicating with the first rotary compression element 18 of each compressor 11 and 11 through the refrigerant introduction pipe 30 as described above. . Thereby, the refrigerant circuit 1 of the refrigerating device R in this embodiment is constituted.

The refrigeration apparatus R is provided with the control apparatus (control means) C comprised with the general-purpose microcomputer. As shown in Fig. 2, the control device C is connected to various sensors on the input side, and on the output side, various valve devices, compressors 11 and 11, fan motors of the gas cooler 47 47M) and the like. In addition, the detailed description of the said control apparatus C is mentioned later according to each control.

(A) Refrigerant amount adjustment control

Next, the refrigerant amount adjustment control of the refrigerant circuit 1 of the refrigerating device R in the present embodiment will be described. On the high pressure side that becomes the supercritical pressure of the refrigerant circuit 1, in this embodiment, the refrigerant amount adjusting tank 100 is provided on the downstream side of the intermediate heat exchanger 80 of the refrigerator unit 3 through the first communication circuit 101. Connected. The refrigerant amount adjusting tank 100 has a predetermined volume, and the first communication circuit 101 is connected to the tank 100. The first communication circuit 101 is provided with an electric expansion valve 102 as a first opening and closing means having a tightening function. In addition, the opening-closing means which has a tightening function is not limited to this, For example, it is a capillary tube and a solenoid valve (opening / closing valve) as a fastening means to the 1st communication circuit 101, for example. You may comprise.

The refrigerant amount adjusting tank 100 is connected with a second communication circuit 103 which communicates with the upper portion of the tank 100 and the intermediate pressure region of the refrigerant circuit 1. In the present embodiment, the other end of the second communication circuit 103 communicates with the 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 second communication circuit 103 is provided with a solenoid valve 104 as second opening and closing means.

The coolant amount adjusting tank 100 is connected to a third communication circuit 105 which communicates with the lower portion of the tank 100 and the intermediate pressure region of the coolant circuit 1. In the present embodiment, the other end of the third communication circuit 105 is an example of the intermediate pressure region, and similarly to the second communication circuit 103, the intermediate pressure suction pipe 40 on the outlet side of the intercooler 38 of the refrigerant circuit 1. ). The third communication circuit 105 is provided with a solenoid valve 106 as a third opening and closing means.

2, the unit outlet side pressure sensor (unit outlet side pressure detection means) 58 and the outside temperature sensor 56 are connected to the input side as shown in FIG. The unit outlet side pressure sensor 58 is a downstream side of the refrigerant amount adjusting tank 100, and detects the pressure of the refrigerant directed to the showcase units 5A and 5B. On its output side, an electric expansion valve (first opening and closing means) 102, a solenoid valve (second opening and closing means) 104, a solenoid valve (third opening and closing means) 106, and a blower for the gas cooler 46 The fan motor 47M of 47 is connected. The controller C is a fan of the gas cooler blower 47 based on the detection temperature of the outside air temperature sensor 56 and the evaporation temperature of the refrigerant in the evaporators 63A and 63B, as will be described later. The rotation speed control of the motor 47M is performed.

(A-1) Refrigerant recovery operation

Hereinafter, the refrigerant recovery operation of the refrigerant circuit 1 will be described. The control device C determines whether the detection pressure of the unit outlet side pressure sensor 58 has exceeded the predetermined recovery threshold value, or the detection pressure of the unit outlet side pressure sensor 58 is lower than the previous recovery threshold value. It exceeds the predetermined collection | recovery protection value, and determines whether the rotation speed of the said gas cooler blower 47 is the maximum value.

In the present embodiment, since the intermediate pressure MP of the refrigerant circuit 1 is about 8 MPa as an appropriate value as an example, the value is set as the recovery protection value, and the recovery threshold is higher than the recovery protection value. , For example, 9 MPa. In addition, the maximum value of the rotation speed of the gas cooler blower 47 in a present Example shall be 800 rpm as an example. Moreover, you may be made on condition that predetermined time may pass after the rotation speed of the gas cooler blower 47 becomes a maximum value.

As a result, the control unit C exceeds the recovery protection value of 8 MPa even when the detection pressure of the unit outlet-side pressure sensor 58 exceeds 9 MPa, which is a recovery threshold, or when the detection pressure is less than or equal to the recovery threshold. Moreover, when the rotation speed of the said gas cooler blower 47 is set to 800 rpm which is the maximum value, it is judged that the high pressure side pressure rose abnormally by the excess gas refrigerant in the refrigerant circuit 1, The refrigerant recovery operation is performed.

In this refrigerant recovery operation, the control unit C is the electric expansion valve (first opening and closing means) 102 and the solenoid valve (second opening and closing means) 104 in a state where the solenoid valve (third opening and closing means) 106 is closed. Open). Thus, the high temperature and high pressure refrigerant discharged from the high stage side discharge port 28 of the compressors 11 and 11 passes through the oil separator 44, the gas cooler 46, the heat recovery heat exchanger 70, and the intermediate heat exchanger ( After cooling to 80, the refrigerant flows into the refrigerant amount adjusting tank 100 through the first communication circuit 101 through which the electric expansion valve 102 is opened.

At this time, since the solenoid valve 104 is opened, the refrigerant amount adjusting tank 100 is connected to the upper portion of the refrigerant amount adjusting tank 100 and the second communication circuit 103 communicating with the intermediate pressure region of the refrigerant circuit 1. Pressure within the tank may be released out of the tank. Therefore, even when the refrigerant in the refrigerant circuit 1 is operating in a gas cycle in which the refrigerant in the refrigerant circuit 1 does not liquefy, such as when the outside air temperature is high, the pressure in the tank 100 decreases and the refrigerant flowing into the tank is liquefied and the tank ( Within 100). That is, the pressure in the refrigerant amount adjusting tank 100 drops below the supercritical pressure, whereby the refrigerant becomes a saturation region from the gas region, thereby ensuring a liquid level.

As a result, the refrigerant in the refrigerant circuit 1 can be recovered to the refrigerant amount adjusting tank 100 quickly and efficiently. Therefore, the problem that abnormal high pressure is caused by the excess high refrigerant in the refrigerant circuit 1 can be solved, and it is possible to prevent overload operation of the compressors 11 and 11 due to the abnormal high pressure.

In particular, the upper portion of the refrigerant amount adjusting tank 100 and the intermediate pressure region of the refrigerant circuit 1 communicate with each other through the second communication circuit 103, so as to communicate with the low pressure side region of the refrigerant circuit 1, the low pressure It becomes possible to avoid the fall of the cooling efficiency by raising the side pressure.

In addition, in the present embodiment, even if the pressure on the high pressure side detected by the unit outlet side pressure sensor 58 is below the recovery threshold value, the blower 47 which exceeds the predetermined recovery protection value and air-cools the gas cooler 46. In the case where the rotation speed of the fan is the highest value, the coolant recovery operation is performed. Therefore, in consideration of the operating state of the blower 47, the efficiency decrease due to the abnormally high state of the high-pressure side of the coolant circuit 1 continues. It becomes possible to prevent.

(A-2) Refrigerant holding operation

On the other hand, the controller C judges whether or not the pressure on the high pressure side detected by the unit outlet side pressure sensor 58 is a recovery protection value, or 8 MPa or less in this embodiment, and when the recovery protection value is lower than the recovery protection value. Then, the refrigerant recovery operation ends and the refrigerant holding operation is performed. In this refrigerant holding operation, the control unit C maintains the state in which the solenoid valve (third opening and closing means) 106 is closed, closes the solenoid valve (second opening and closing means) 104, and the electric expansion valve (first). The opening degree of the opening / closing means 102 is maintained in the opening degree in the refrigerant recovery operation described above.

The opening degree of the electric expansion valve 102 may be smaller than the opening degree in the refrigerant recovery operation. As a result, the solenoid valve 104 is closed, so that the liquid level in the refrigerant amount adjusting tank 100 can be maintained at the pressure by the high pressure side region of the refrigerant circuit 1 through the open electric expansion valve 102. do. For this reason, the liquid rod in a refrigerant amount adjustment tank 100 can be avoided, and safety can be ensured. This makes it possible to appropriately maintain the amount of circulating refrigerant in the refrigerant circuit 1.

In addition, the controller C makes the opening degree of the electric expansion valve 102 in the refrigerant holding operation smaller than the opening degree in the refrigerant recovery operation, thereby allowing the inside of the refrigerant circuit 1 in the refrigerant amount adjusting tank 100 in the refrigerant holding operation. By excessively recovering the coolant, it is possible to effectively solve the problem of shortage of coolant in the coolant circuit 1.

(A-3) Refrigerant discharge operation

Then, the control device C has a detection pressure of the unit outlet side pressure sensor 58 that is lower than the predetermined discharge threshold (about 7 MPa in this embodiment) lower than the recovery protection value (about 8 MPa in this case). In this case, or the detection pressure of the pressure sensor 58 on the outlet side of the unit is equal to or less than the previous recovery protection value, and the rotation speed of the gas cooler blower 47 is equal to or less than a predetermined prescribed value lower than the maximum value. Determine if it is or not. In addition, in the present embodiment, the predetermined prescribed value is, for example, about 3/8 of the maximum value, that is, about 300 rpm when the maximum value is 800 rpm. Moreover, you may be made on the condition that predetermined time passes after the rotation speed of the gas cooler 47 for a gas cooler becomes below a predetermined value.

Thereby, the control apparatus C becomes the case where the detection pressure of the unit outlet side pressure sensor 58 is less than 7 Mpa which is a discharge threshold value, or the detection pressure becomes 8 Mpa or less which is a recovery protection value, When the rotation speed of the gas cooler blower 47 is at a predetermined prescribed value, in this case, 300 rpm or less, it is determined that the refrigerant in the refrigerant circuit 1 is insufficient, and the refrigerant discharge operation is executed.

In this refrigerant discharge operation, the control device C closes the electric expansion valve (first opening and closing means) 102 and the solenoid valve (second opening and closing means) 104 to close the solenoid valve (third opening and closing means) 106. Open. As a result, the liquid refrigerant accumulated in the refrigerant amount adjusting tank 100 is discharged to the refrigerant circuit 1 through the third communication circuit 105 in which the solenoid valve 106 connected to the lower portion of the tank 100 is opened. do. Therefore, unlike the case where the gas refrigerant is discharged from the upper portion of the refrigerant amount adjusting tank 100 into the refrigerant circuit 1 in a state in which gas refrigerant is mixed, the refrigerant in the refrigerant amount adjusting tank 100 can be quickly discharged to the refrigerant circuit 1. Can be. This makes it possible to operate the refrigeration apparatus at high efficiency.

(A-4) Refrigerant holding operation

Thereafter, the controller C judges whether or not the pressure on the high pressure side detected by the unit outlet-side pressure sensor 58 is a recovery protection value, in this embodiment, 8 MPa or more, and exceeds the recovery protection value. Then, the refrigerant discharge operation is terminated, and the flow shifts to the refrigerant holding operation as described above. Subsequently, the refrigerant recovery operation, the refrigerant holding operation, the refrigerant discharge operation, and the refrigerant holding operation are repeatedly executed based on the high pressure side pressure of the refrigerant circuit 1 to control the refrigerant recovery and discharge based on the high pressure side pressure. It can accurately prevent high pressure protection and overload operation. As a result, the cooling capacity of the refrigerating device can be ensured, and the COP can be optimized.

In particular, in the present embodiment, it is possible to control the refrigerant recovery and discharge operation in consideration of not only the high pressure side pressure but also the rotation speed of the blower 47 for cooling the gas cooler 46. It becomes possible to prevent the efficiency fall by continuing abnormally high state.

In the present embodiment, both the second communication circuit 103 and the third communication circuit 105 communicate with the outlet side of the intercooler 38 of the refrigerant circuit 1. As a result, the pressure loss in the intercooler 38 can be prevented, and the coolant can be smoothly discharged from the coolant amount adjustment tank 100 to the coolant circuit 1.

In addition, when the compressors 11 and 11 stop operation | movement, the control apparatus C shall perform a refrigerant | coolant discharge operation | movement. As a result, the problem that the amount of refrigerant in the refrigerant circuit 1 is insufficient when the compressors 11 and 11 are started can be solved, and an appropriate high pressure side pressure can be realized according to the pressure on the high pressure side of the compressor 11 to be operated. Can be.

In this case, the compressor 11 (compression means) employs a two-stage compression type rotary compressor in which the first and second compression elements 18 and 20 and the transmission element 14 are assembled into the sealed container 12. However, in addition to this, two types of rotary compressors, or other types of compressors, may be of a type in which refrigerant can be taken out from the intermediate pressure portion and introduced therein.

(B) split cycle

Next, the split cycle of the refrigerating apparatus R in this embodiment is demonstrated. In the present embodiment, the refrigerating device R includes a first rotary compression element (low end side) 18, an intercooler 38, and a combiner as a confluence device for joining the flows of two fluids of the compressors 11 and 11. (81), second rotary compression element (high end side) 20 of each compressor (11, 11), oil separator (44), gas cooler (46), classifier (82), auxiliary tightening means (auxiliary expansion valve) (83), the intermediate heat exchanger (80), the casting means (main expansion valve) 62A, 62B, and the evaporator 63A, 63B constitute a refrigeration cycle.

The classifier 82 is a classifier that branches the refrigerant from the gas cooler 46 into two streams. That is, the classifier 82 of the present embodiment classifies the refrigerant from the gas cooler 46 into the first and second refrigerants, flows the first refrigerants into the auxiliary circuit, and passes the second refrigerants into the main circuit. It is configured to shed.

In the main circuit in FIG. 1, the first rotary compression element 18, the intercooler 38, the combiner 81, the second rotary compression element 20, the gas cooler 46, the classifier 82, and the intermediate heat exchange It is an annular refrigerant circuit composed of the second flow path 80B of the machine 80, the casting impregnation means 62A, 62B, and the evaporators 63A, 63A, and the auxiliary circuit is an auxiliary tightening means 83 from the classifier 82. And a circuit leading to the combiner 81 sequentially through the first flow path 80A of the intermediate heat exchanger 80.

The auxiliary fastening means 83 is classified in the classifier 82 to depressurize the first refrigerant flow flowing in the auxiliary circuit. The intermediate heat exchanger 80 is a heat exchanger that performs heat exchange between the first refrigerants of the auxiliary circuit decompressed by the auxiliary fastening means 83 and the second refrigerants classified by the classifier 82. The intermediate heat exchanger 80 is provided in such a manner that heat exchange is possible between the second flow path 80B through which the second refrigerant flows and the first flow path 80A through which the first refrigerant flows. By passing through the 2nd flow path 80B, since a 2nd refrigerant | coolant is cooled by the 1st refrigerant flow which flows through the 1st flow path 80A, specific enthalpy in the evaporators 63A and 63B can be made small.

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

The discharge temperature sensor 50 is provided in the high stage side discharge port 28 of the compressors 11 and 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 a downstream side of the coolant amount adjustment tank 100, and detects the pressure of the coolant toward the showcase units 5A and 5B. The low pressure pressure sensor 32 is connected to the low pressure side of the refrigerant circuit 1 and, in this embodiment, the downstream side of each of the evaporators 63A and 63B, and is connected to the lower end side suction ports 22 and 22 of the compressors 11 and 11. It is provided in the refrigerant pipe (9) and detects the suction pressure of the refrigerant directed to the refrigerant introduction pipe (30). The intermediate pressure pressure sensor 49 is an intermediate pressure region of the refrigerant circuit 1, and in this embodiment, an auxiliary circuit of a split cycle, which is used for the first refrigerant flow after passing through the first flow path 80A of the intermediate heat exchanger 80. Detect the pressure.

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 exiting 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 end side suction port 22 of the compressor 11 and detects the suction temperature of the refrigerant directed to the refrigerant introduction pipe 30. On the output side, an auxiliary tightening means 83 constituting the split cycle is connected. The opening tightening means 83 is controlled by the step motor.

Hereinafter, the opening degree control of the auxiliary tightening means 83 will be described in detail. The auxiliary tightening means 83 is a predetermined initial valve opening degree at the start of operation of the compressor 11. Then, the control apparatus C determines the operation amount which increases the valve opening degree of the auxiliary tightening means 83 based on the following 1st control amount, 2nd control amount, and 3rd control amount.

(B-1) Increase of valve opening of auxiliary tightening means

The first control amount DT cont can be obtained based on the discharge refrigerant temperature DT of the compressor 11. The controller C judges whether or not the temperature DT detected by the discharge temperature sensor 50 is higher than a predetermined value DT0, and when the discharge refrigerant temperature DT is higher than a predetermined value DT0, the opening degree of the auxiliary tightening means 83 is increased. Let it be a control amount acting in the direction of increasing. The predetermined value DT0 is set to an allowable low temperature (+ 95 ° C as an example) which is less than a limit temperature (such as + 100 ° C) that enables proper operation of the compressor 11, and when the temperature rises, By increasing the opening degree of the tightening means 83, 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 MP cont is a control amount that adjusts the amount of refrigerant flowing into the auxiliary circuit of the split cycle to optimize the intermediate pressure MP. In this embodiment, calculation is made 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 pressure sensor 32. It is judged whether or not the pressure MP of the intermediate pressure region of the refrigerant circuit 1 detected by the intermediate pressure pressure sensor 49 is higher than the (measured) appropriate intermediate pressure value, and the pressure MP of the intermediate pressure region is appropriate. When it is lower than the pressure value, it acts in the direction which increases the opening degree of the auxiliary fastening means 83. FIG.

In addition, the appropriate intermediate pressure value may be calculated from a rising average of the detected high pressure side pressure HP and the low pressure side pressure LP, and in addition, an appropriate intermediate pressure value is previously determined from the high pressure side pressure HP and the low pressure side pressure LP. May be obtained experimentally and determined from the data table constructed based on this.

In this embodiment, the second control amount MP cont 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. For example, the following may be adopted. That is, overcompression 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 pressure sensor 32 is performed. A determination value MPO is obtained, and it is judged whether or not the overcompression 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 the overcompression determination value MPO is a high pressure. When it is lower than the side pressure HP, it acts in the direction which increases the opening degree of the auxiliary fastening means 83. FIG. By reflecting the second control amount in the opening degree control of the auxiliary tightening means 83, the pressure difference between the high pressure side pressure HP, the medium pressure region MP, and the low pressure side pressure LP can be maintained appropriately, thereby stabilizing the operation of the refrigeration cycle. Can be planned.

The third control amount SP cont is a control amount that aims to optimize the refrigerant temperature LT coming from the second flow path of the intermediate heat exchanger 80. In the present embodiment, the control device C is the temperature GCT of the refrigerant passing through the gas cooler 46 detected by the gas cooler outlet temperature sensor 52 and the intermediate heat exchanger detected by the unit outlet temperature sensor 54. It is judged whether or not the difference (GCT-LT) with the temperature LT of the second refrigerant stream passing through 80 is smaller than the predetermined value SP, and when small, it acts in the direction of increasing the opening degree of the auxiliary tightening means 83.

Here, the predetermined value SP is different in the case where the high pressure side pressure HP is the supercritical region of the refrigerant and the saturation region. 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, when the outside air temperature is high, for example, at + 31 ° C. or higher. If it is determined that it is a critical area, and the outside air temperature is low, for example, it is determined that it is a saturated area below + 31 ° C. If it is determined that the supercritical region is a predetermined value SP, the predetermined value SP is set up. If it is determined that it is a saturated region, the predetermined value SP is set down. In this embodiment, the predetermined value SP is 35 ° C in the supercritical region and 20 ° C in the saturated region.

The control device C adds three control amounts obtained as described above, that is, the first control amount DT cont, the second control amount MP cont, and the third control amount SP cont, and adds the auxiliary tightening means ( The operation amount of the valve opening degree of 83) is determined, and the valve opening degree is increased based on this.

(B-2) Valve opening degree reduction control of auxiliary tightening means

In addition, the controller C differs from the temperature LT of the second refrigerant stream passing through the intermediate heat exchanger 80 or the discharge refrigerant temperature DT from the compressor 11 and the temperature GCT of the refrigerant passing through the gas cooler 46. The amount of operation to reduce the opening degree of the valve of the auxiliary tightening means 83 is determined.

That is, the control unit C determines whether or not the temperature LT of the second refrigerant stream passing 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 deg. As a result, when the unit outlet temperature is 0 ° C. or less, the second refrigerant stream cooled in the intermediate heat exchanger 80 is excessively cooled by operating in a direction of reducing the opening degree of the auxiliary fastening means 83. can do.

In addition, the controller C differs between the temperature DT detected by the discharge temperature sensor 50 and the temperature GCT of the refrigerant passing through the gas cooler 46 detected by the gas cooler outlet temperature sensor 52 (DT-GCT). Is determined to be lower than the predetermined value TDT, and if it is low, it acts in the direction of reducing the opening degree of the auxiliary fastening means 83.

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

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

In the refrigerating device R according to the present embodiment having the split cycle as described above, the refrigerant after the heat dissipation with the gas cooler 46 is sorted, and the refrigerant is expanded under reduced pressure by the auxiliary fastening means 83. The second refrigerant stream can be cooled, so that the specific enthalpy of the inlet of each evaporator 63A, 63B can be reduced. As a result, the freezing effect can be increased, and the performance can be effectively improved as compared with the conventional apparatus. In addition, the sorted first refrigerant flow is returned from the high stage side suction port 26 of the compressor 11 to the second rotary compression element 20 (intermediate pressure section), and therefore, from the low stage side suction port 22 of the compressor 11. The amount of the second refrigerant flow sucked into the first rotary compression element 18 (low pressure portion) is reduced, and the amount of compression work at the first rotary compression element 18 (low end) for compressing from low pressure to medium pressure is reduced. Decreases. As a result, the compression power in the compressor 11 is lowered and the coefficient of performance is improved.

Here, the effect of the so-called split cycle depends on the amount of the first refrigerant flow and the second refrigerant flow through the intermediate heat exchanger 80. That is, when the amount of the first refrigerant is too large, the amount of the second refrigerant that finally evaporates in the evaporators 63A and 63B is insufficient. On the contrary, when the amount of the first refrigerant is too small, the effect of the split cycle is insignificant. Done. On the other hand, the pressure of the first refrigerant flow which has been depressurized by the auxiliary fastening means 83 is the intermediate pressure of the refrigerant circuit 1, and the controlling of the intermediate pressure is controlling the amount of the first refrigerant flow.

In this embodiment, as described above, when the temperature DT (discharge temperature sensor 50) of the discharged refrigerant from the compressor 11 is higher than the predetermined value DT0, the direction of increasing the opening degree of the auxiliary tightening means 83 is increased. Auxiliary tightening means when the pressure MP in the intermediate pressure region of the refrigerant circuit 1 is lower than the first control amount which acts as a function and an appropriate intermediate pressure value obtained from the high pressure side pressure HP and the low pressure side pressure LP of the refrigerant circuit 1. The difference between the temperature GCT 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 (GCT-LT) Is smaller than the predetermined value SP, the third control amount acting in the direction of increasing the opening degree of the auxiliary tightening means 83 is calculated, and the first to third control amounts are summed, so that the valve of the auxiliary tightening means 83 is increased. The operation amount for increasing the opening degree is determined. In addition, when the temperature LT is lower than the predetermined value, or when the temperature DT-GCT is lower than the predetermined value TDT, the operation amount is determined in the direction of reducing the valve opening degree of the auxiliary tightening means 83.

Thereby, the temperature DT of the discharged refrigerant can be kept below the predetermined value DT0 by the first control amount, and the intermediate pressure MP of the refrigerant circuit 1 can be optimized by the second control amount, whereby the low pressure side The pressure difference between the pressure LP, the intermediate pressure MP, and the high pressure side pressure HP can be properly maintained. Moreover, the temperature LT of the 2nd refrigerant | coolant which passed through the intermediate heat exchanger 80 can be made low by a 3rd control amount, and a refrigeration effect can be maintained. As a result, it is possible to achieve high efficiency and stabilization of the refrigerating apparatus.

In addition, when the high pressure side pressure HP is in the supercritical region, the controller C raises the predetermined value SP, lowers the predetermined value TDT, and decreases the predetermined value SP when the high pressure side pressure HP is in the saturation region. By raising the predetermined value TDT, it is possible to change and control the third control amount and the predetermined values SP and TDT of the first control amount by dividing the high pressure side pressure HP into the supercritical region and the saturation region.

As a result, 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 securely ensured, and the problem that liquid backflow occurs in the compressor 11 can be avoided. In the case where the high pressure side pressure HP is in the supercritical region, such liquid backflow does not occur, so that the efficiency can be set as a priority.

Further, the second control amount in the above embodiment is supplementary tightening when the overcompression determination value MPO obtained from the pressure MP and the low pressure side pressure LP of the intermediate pressure region of the refrigerant circuit 1 is lower than the high pressure side pressure HP of the refrigerant circuit. As the second control amount acting in the direction of increasing the opening degree of the means, the first and third control amounts are summed to determine the operation amount of the valve opening degree of the auxiliary tightening means. The pressure difference between the low pressure side pressure LP, the intermediate pressure MP, and the high pressure side pressure HP can be appropriately maintained.

Moreover, the 1st refrigerant | coolant stream which came out from the intermediate heat exchanger 80 in this Example can be returned to the exit side of the said intercooler 38 by the combiner 81 provided in the exit side of the intercooler 38, and the intercooler ( By preventing the pressure loss at 38, it is possible to smoothly join the refrigerant flows from the intermediate heat exchanger 80 to the intermediate pressure side of the refrigerant circuit 1.

(C) heat recovery heat exchanger

Next, the heat recovery heat exchanger 70 employed in the refrigerating device R according to the present embodiment will be described. The heat recovery heat exchanger (70) in the present embodiment includes the second refrigerants sorted by the fractionator (82) via the gas cooler (46), and the carbon dioxide refrigerant (heat recovery recovery) of the heat pump unit constituting the hot water supply device (not shown). Heat exchanger for heat exchange with a medium). In the present embodiment, the hot water supply device includes a refrigerant circuit (not shown), a water heat exchanger, a pressure reducing device, and an evaporator connected in a tubular shape in a refrigerant pipe and a water heat exchanger. And a heat pump unit having a water circuit which is returned to the low temperature tank after heating, and the evaporator of the heat pump unit is arranged by the heat recovery medium flow path 70B of the heat recovery heat exchanger 70. Configure. As a result, the heat recovery heat exchanger 70 is provided in a heat exchangeable relationship between the refrigerant flow path 70A through which the second refrigerant flows in the split cycle as described above and the heat recovery medium flow path 70B. When the refrigerant of the heat pump unit flowing through the heat recovery medium flow path 70B of the heat recovery heat exchanger 70 passes, the second refrigerant flow passing through the gas cooler 46 in the refrigerant flow path 70A is cooled.

Here, in the present embodiment, the second coolant flows out from the gas cooler 46 and enters the intermediate heat exchanger 80 constituting the split cycle through the coolant flow path 70A of the heat recovery heat exchanger 70. As a result, the coolant flows through the heat recovery medium flow path 70B constituting the hot water supply device by efficiently recovering the heat flow of the refrigerant flowing through the refrigerant flow path 70A by the heat recovery heat exchanger 70. It can be used for heating, and efficient hot water generation can be made possible.

In addition, since the second refrigerant flows out of the gas cooler 46 and enters the intermediate heat exchanger 80, the configuration is such that the heat recovery heat exchanger 70 flows the second refrigerant stream. In this case, since the refrigerant temperature of the second refrigerant stream flowing through the intermediate heat exchanger 80 can be lowered, the amount of refrigerant of the first refrigerant stream flowing through the intermediate heat exchanger 80 can be reduced. As a result, the amount of refrigerant flowing through the second refrigerant stream can be increased, so that the amount of evaporation of the refrigerant in the evaporators 63A and 63B can be increased to improve the efficiency of the refrigeration cycle.

In particular, when carbon dioxide is used as the refrigerant as in the present embodiment, the refrigerating capacity can be effectively improved, and the performance can be improved.

In addition, in the refrigerating device R of this embodiment, the gas cooler bypass circuit 71 which bypasses the gas cooler 46 may be provided. In this case, a solenoid valve 72 is interposed in the gas cooler bypass circuit 71, and the solenoid valve (valve device) 72 is opened and closed controlled by the control device C as described above.

As a result, when the amount of usage in the hot water supply device is large and the refrigerant flowing through the heat recovery medium flow path 70B (evaporator) of the heat pump unit cannot be sufficiently evaporated, the controller C opens the solenoid valve 72. In addition, a portion of the high temperature refrigerant flowing into the gas cooler 46 may be introduced into the gas cooler bypass circuit 71 to pass the refrigerant flow path 70A of the heat recovery heat exchanger 70 as it is. This makes it possible to effectively use the arrangement and to perform temperature compensation on the hot water supply side.

(D) Control of blowers for gas coolers

Next, the control of the gas cooler blower 47 which cools the gas cooler 46 as mentioned above is demonstrated. As shown in Fig. 2, the control device C according to the present embodiment has a high pressure sensor (high pressure pressure detecting means) 48, 48, a low pressure pressure sensor 32, and an outside temperature sensor 56 on the input side. ) Is connected. Here, since the pressure detected by the low pressure pressure sensor 32 and the evaporation temperature TE in the evaporators 63A and 63B have a constant relationship, the controller C is connected to the pressure detected by the low pressure pressure sensor 32. Thus, the evaporation temperature TE of the refrigerant in the evaporators 63A and 63B is converted into and obtained. Moreover, the gas cooler blower 47 which air-cools the gas cooler 46 is connected to the output side of the control apparatus C. As shown in FIG.

The controller C controls the rotation speed of the blower 47 for gas cooler so that the high pressure side pressure HP detected by the high pressure sensor 48 becomes a predetermined target value (target high pressure: THP). The target high pressure THP is determined from the outside temperature TA and the evaporation temperature TE of the refrigerant in the evaporators 63A and 63B.

In the refrigerating device R in which the high pressure side of the refrigerant circuit 1 is equal to or greater than the supercritical pressure as in the present embodiment, when the outside temperature TA is at a certain temperature, for example, + 30 ° C. or less, a saturation cycle is performed, and +30 At a temperature higher than < RTI ID = 0.0 > Since the refrigerant does not liquefy when the gas cycle is performed, the temperature and the pressure in the amount of the refrigerant in the refrigerant circuit 1 at that time are not uniquely determined. For this reason, the target high pressure THP differs depending on the outside temperature TA.

In this embodiment, as an example, when the outside temperature TA detected by the outside temperature sensor 56 is below the lower limit temperature (for example, 0 ° C), the target high pressure THP is made constant at a predetermined lower limit THPL. Further, the target high pressure THP is made constant at a predetermined upper limit value THPH at or above the predetermined temperature (upper limit temperature) in which the outside temperature TA is higher than 30 ° C. When the outside 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 temperature TA is lower than a predetermined reference temperature, for example, + 30 ° C., the air temperature TA is determined in the direction of lowering the target value THP of the high pressure side pressure, and the higher the air temperature TA is determined in the direction of increasing the target value THP. Further, as described above, the higher the evaporation temperature TE of the refrigerant in the evaporators 63A, 63B obtained in terms of the pressure detected by the low pressure pressure sensor 32 than the predetermined reference temperature, the higher the target of the high pressure side pressure. The value THP is determined in the direction of increasing, and the lower value is determined in the direction of lowering the target value THP. 3 is a graph showing a tendency of the target high pressure THP determined from the outside temperature TA and the evaporation temperature TE.

In addition, in this embodiment, although the control apparatus C calculates the target high pressure THP from an external temperature TA and the evaporation temperature TE using a calculation formula, it is not limited to this, The external temperature TA and the evaporation temperature TE are previously mentioned. The target high pressure THP may be obtained based on the data table obtained from the data table.

And the control apparatus C is based on the high pressure side pressure HP detected by the high pressure pressure sensor (high pressure pressure detection means) 48, the target high pressure THP, the deviation e of these HP and THP, and P based on the said deviation e. (Proportional. Proportional differential calculation is performed from D (control in the direction of reducing the variation in deviation e) in proportion to the magnitude of the deviation e) and D (differential. The rotation speed of the blower 47 for gas coolers used is determined. The higher the target high pressure THP is, the higher the rotational speed of the blower 47 is, and the lower the target high pressure THP is, the lower the rotational speed of the blower 47 can be.

Thereby, the control apparatus C of the gas cooler blower 47 is based on the outside air temperature TA and the evaporation temperature of the refrigerant in the evaporator (acquired in terms of the low pressure pressure detected by the low pressure pressure sensor 32) TE. By controlling the rotation speed, the rotation speed of the gas cooler blower 47 can be controlled so that an appropriate high pressure pressure may be made even in the refrigerating device R in which the high pressure side becomes a supercritical pressure. Thereby, high efficiency operation can be realized while reducing the noise by the operation of the gas cooler blower 47.

In the present embodiment, the control unit C uses the target value THP of the high pressure side pressure of the refrigerant circuit 1 based on the outside temperature TA and the evaporation temperature TE, for example, the lower the outside temperature TA, the target value THP. To lower the evaporation temperature TE, determine the target value THP in the direction of increasing the target value THP, and control the gas cooler 47 so that the high pressure side pressure becomes the target value THP, By taking into account the refrigerant state changing between the saturation cycle and the gas cycle, it is possible to realize the desired high pressure side pressure based on the evaporation temperature TE, thereby realizing high efficiency operation. As such, the present invention is particularly effective in a supercritical refrigerant circuit (supercritical refrigeration cycle) using carbon dioxide as the refrigerant.

(E) Oil Separator

On the other hand, the oil separator 44 is interposed in the high pressure discharge pipe 42 which connects the high stage side discharge port 28 of the compressor 11 and the gas cooler 46 as mentioned above. The oil separator 44 separates and captures oil contained in the high-pressure discharge refrigerant discharged from the compressor 11 from the refrigerant, and the oil separator 44 returns oil captured by the compressor 11 to the compressor 11. The return circuit 73 is connected. The oil return circuit 73 is provided with an oil cooler 74 for cooling the captured oil. On the downstream side of the oil cooler 74, the oil return circuit 73 is branched into two systems and each strainer ( 75) and the flow regulating valve (electric valve) 76 are connected to the sealed container 12 of the compressor 11. Since the inside of the hermetic container 12 of the compressor 11 is maintained at an intermediate pressure as described above, the trapped oil is held by the pressure difference between the high pressure in the oil separator 44 and the intermediate pressure in the hermetic container 12. (12) It is returned to me. In the sealed container 12 of the compressor 11, an oil level sensor 77 for detecting the level of oil held in the sealed container 12 is provided.

The oil return circuit 73 is provided with an oil bypass circuit 78 for bypassing the oil cooler 74, and the oil bypass circuit 78 is provided with a solenoid valve (valve device) 79. It is. The solenoid valve 79 is controlled to open and close by the control apparatus C as mentioned above. As described above, the oil cooler 74 is provided in the same air path 45 as the gas cooler 46, and air cooled by the gas cooler 47.

By the above structure, the control apparatus C judges whether the temperature detected by the outdoor air temperature sensor 56 provided in the air path 45 became below predetermined oil low temperature (predetermined value), and oil low temperature degree. When it exceeds, the solenoid valve 79 of the oil bypass circuit 78 is closed.

Thereby, the high temperature high pressure refrigerant discharged from the high stage side discharge port 28 of each compressor 11 and 11 joins in the downstream of the 2nd rotary compression elements 20 and 20, and the oil separator 44 and the gas cooler Through the 46, etc., to the refrigerator units 3 and 3; The oil contained in the high temperature high pressure refrigerant introduced into the oil separator 44 is captured separately from the refrigerant. Since the inside of the hermetic container 12 of the compressor 11 is maintained at an intermediate pressure, the trapped oil is separated from the oil return circuit (by the pressure difference between the high pressure in the oil separator 44 and the middle pressure of the hermetic container 12). 28 is returned to the compressor (11).

The oil flowing into the oil return circuit 28 is air cooled by the operation of the blower 47 to the oil cooler 74 disposed in the same air path 45 as the gas cooler 46. After passing through the oil cooler 74, it is separated into two systems and returned to the compressor 11 via the strainer 75 and the flow regulating valve 76. As a result, the oil, which has become high with the high temperature refrigerant, is cooled by the oil cooler 74 and returned to the compressor 11, so that the temperature rise of the compressor 11 can be suppressed.

On the other hand, when the temperature detected by the outside air temperature sensor 56 falls below a predetermined oil lower limit temperature (predetermined value), the control device C opens the solenoid valve 79 of the oil bypass circuit 78. do. As a result, the oil separated from the refrigerant in the oil separator 44 returns to the compressors 11 and 11 through the oil bypass circuit 78 of the oil return circuit 28 without passing through the oil cooler 74. In addition, when the temperature detected by the ambient temperature sensor 56 reaches the oil upper limit temperature which is higher than the oil lower limit temperature by a predetermined temperature, the control unit C closes the solenoid valve 79.

Thus, even when the oil temperature is lowered due to the decrease in the outside air temperature and the viscosity of the oil is increased, the solenoid valve 79 is opened to open the oil bypass circuit without passing through the oil cooler 74. Through 78, the oil in the oil separator 44 can be returned to the compressor 11. Thereby, oil return to the compressor 11 can be made smooth.

In particular, in this embodiment, the oil cooler 74 is provided in the same air path 45 as the gas cooler 46, and the blower 47 is blower irrespective of the temperature of the oil cooler 74 as described above. Since the control of 47 is performed, the concentration of the oil cooler 74 is lowered more than necessary by the operation of the blower 47, and it is easy to inject refrigerant into the oil, but the controller C By opening the solenoid valve 79 of the oil bypass circuit 78, the oil in the oil separator 44 is pumped through the oil bypass circuit 78 without passing through the oil cooler 74 smoothly. Can be reversed. This makes it possible to simplify the control and make it effective especially when the air cooling amount cannot be adjusted.

When the outside air temperature is lower than the predetermined oil lower limit temperature (predetermined value), the controller C opens the flow path of the oil bypass circuit 78 by the solenoid valve 79, so that the coolant is introduced into the oil. It is possible to prevent the viscosity from rising and return the oil in the oil separator 44 to the compressor 11 through the oil bypass circuit 78 which bypasses the oil cooler 74 correctly.

In the present embodiment, the solenoid valve 79 is opened and closed based on the temperature detected by the outside air temperature sensor 56 provided in the air path 45. However, the present invention is not limited thereto. Means for detecting the temperature of the oil separator 44 are provided, and the solenoid valve 79 opens the flow path of the oil bypass circuit 78 when the temperature detected by the temperature detecting means is lower than a predetermined value. You may use it. In this case as well, the refrigerant is prevented from injecting into the oil and the viscosity is increased, thereby returning the oil in the oil separator 44 to the compressor 11 through the oil bypass circuit 78 bypassing the oil cooler 74. It becomes possible.

In addition, when carbon dioxide is used as the refrigerant as in the present embodiment, by controlling as described above, the oil can be smoothly returned to the compressor 11, and the refrigerating capacity can be effectively improved, thereby improving performance. Can be planned.

(F) Compressor startability improvement (bypass circuit)

Next, startability improvement control of the compressor 11 is demonstrated. As shown in FIG. 2, the intermediate pressure region of the refrigerant circuit 1 on the outlet side of the intercooler 38 of the refrigerating device R described above, in the present embodiment, is connected to the outlet side of the intercooler 38. Alternatively, a bypass circuit 84 passing through the third communication circuits 104 and 105 and the low pressure side of the refrigerant circuit 1 and in this embodiment the refrigerant outlet side of the evaporators 63A and 63B is provided. The bypass circuit 84 is provided with a solenoid valve (valve device) 85. And the control apparatus C is connected with the compressor 11, 11 and the solenoid valve 85 as shown in FIG. The controller C makes it possible to detect (acquire) the operating frequency of the compressor 11.

With the above configuration, the startability improvement control operation of the compressor 11 will be described. As described above, the low pressure refrigerant gas sucked into the low pressure portion of the first rotary compression element 18 by the low stage side suction port 22 while the compressor 11 is operating is supplied to the first rotary compression element 18. The pressure is increased to an intermediate pressure and discharged into the sealed container 12. The medium pressure refrigerant gas in the sealed container 12 is discharged from the lower end side discharge port 24 of the compressor 11 to the intermediate pressure discharge pipe 36, and through the intermediate pressure suction pipe 40 to which the intercooler 38 is connected. It is sucked into the high stage side suction port 26. The area until discharged from the first rotary compression element 18 and sucked into the second rotary compression element 20 through the high stage side suction port 26 becomes an intermediate pressure region.

The medium pressure refrigerant gas sucked into the middle pressure portion of the second rotary compression element 20 by the high stage side suction port 26 is compressed in the second stage by the second rotary compression element 20 to become a high temperature and high pressure refrigerant gas. And discharged from the high stage discharge port 28 to the high pressure discharge pipe 42, the oil separator 44, the gas cooler 46, the heat recovery heat exchanger 70, the intermediate heat exchanger 80, and the refrigerant pipe 7. And the regions up to the casting means 62A, 62B of the showcase units 5A, 5B become the high pressure side.

Then, by expanding under reduced pressure by the casting means 62A, 62B, the refrigerant circuit 1 extends from the lower evaporator 63A, 63B to the lower end side suction port 22 communicating with the first rotary compression element 18. It becomes the low pressure side of.

When the compressor 11 is restarted after the operation of the compressor 11 is stopped, the control device C opens the solenoid valve 85 until the compressor 11 rises to a predetermined operating frequency. Thus, the flow path of the bypass circuit 84 is opened. The predetermined operating frequency is an operating frequency at which the compressor 11 enables effective torque control, and is set to 35 Hz as an example in this embodiment.

Thereby, the solenoid valve 85 is opened until it starts up from the stop state of the compressor 11, and it raises to the said predetermined | prescribed operation frequency, and it pressurizes to the intermediate pressure by the 1st rotary compression element 18, The refrigerant in the intermediate pressure region discharged from the low stage side discharge port 24 to the intermediate pressure discharge pipe 36 is passed through the bypass circuit 84 to the low pressure side region of the refrigerant circuit 1 after passing through the intercooler 38. Inflow. As a result, the pressure between the intermediate pressure region and the low pressure side region of the refrigerant circuit 1 is equalized.

As a result, the predetermined torque cannot be secured at the time of starting from the start of the compressor 11 to the predetermined operating frequency, but during this time, the middle pressure region and the low pressure side region are equalized, so that the outside air temperature is increased. Because of the high pressure, even if the medium pressure tends to be high, the problem that the medium pressure approaches the high pressure can be solved.

For this reason, while the torque shortage at the time of starting of the compressor 11 arises, the starting failure by the approach of the pressure of an intermediate | middle pressure area | region and the pressure of a high pressure area | region can be avoided beforehand, and it is stable, High efficiency operation can be realized. In addition, the controller C closes the solenoid valve 85 and closes the flow path of the bypass circuit 84 after the detected operating frequency of the compressor 11 rises to a predetermined operating frequency. The same normal refrigeration cycle is performed.

(G) Improvement of startability of compressor (check valve)

The refrigerant regulator 91 is provided in the high pressure discharge pipe 42 of each compressor 11 in this embodiment. Here, the refrigerant regulator 91 will be described with reference to a partial longitudinal side view of the refrigerant regulator 91 of FIG. 4 and a partial cross-sectional plan view of FIG. The refrigerant regulator 91 is constituted by an airtight container 92 having a predetermined capacity, and the refrigerant discharged from the high stage discharge port 28 of the compressor 11 flows into the side surface of the container 92. The inflow part 96 is formed in communication, and the high pressure discharge pipe 42 (high end side discharge port 28 side) is connected. In addition, the upper end surface of the container 92 is formed with the refrigerant discharge part 97 which flows out the refrigerant | coolant in the container 92, and the high pressure discharge piping 42 (gas cooler 46 side) is connected.

The container 92 is partitioned up and down by partition walls 93, and the lower side is a coolant inlet chamber 94, and the upper side is a coolant outlet chamber 95. The coolant inlet chamber 94 is formed in communication with the coolant inlet unit 96, and the coolant outlet chamber 95 is formed in communication with the coolant outlet unit 97. A suction port 98 is provided on the refrigerant inlet chamber 94 side of the partition wall 93, and the suction port 98 is formed in communication with the suction passage 99 formed in the partition wall 93.

On the refrigerant outlet chamber 95 side of the suction passage 99, a check valve 90, which is located above the inside of the container 92, is composed of a reed valve. The check valve 90 moves from the coolant inlet chamber 94 side toward the coolant outlet chamber 95 in the forward direction (from the high end discharge port 28 of the compressor 11 to the gas cooler 46 (oil separator 44). ) Is the forward direction. In the vicinity of the check valve 90, a support 90A is fixed to the check valve 90 at a predetermined interval.

And the oil return pipe 86 connected with the compressor 11 mentioned above is provided in the container lower end part of this container 92. The oil return pipe 86 is connected to the oil return circuit 73, whereby the oil return pipe 86 communicates with the inside of the container 92.

With the above configuration, the refrigerant discharged from the high stage discharge port 28 of the compressor 11 flows into the refrigerant inlet chamber 94 from the refrigerant inlet 96 of the refrigerant regulator 91 through the high temperature discharge pipe 42. do. Since the refrigerant inlet chamber 94 has a predetermined volume, the pulsation can be absorbed by the muffler effect and leveled.

The refrigerant in the refrigerant inlet chamber (94) passes through the suction passage (99) through the suction port (98), and the check valve (90) forwards from the refrigerant inlet chamber (94) toward the refrigerant outlet chamber (95). It is discharged into the refrigerant discharge chamber 95 through the. Since the check valve 90 is constituted by a reed valve as described above, noise can be eliminated.

The coolant in the coolant discharge chamber 95 is discharged to the hot discharge pipe 42 toward the gas cooler 46 through the coolant discharge unit 97.

Here, in the container 92 of the coolant regulator 91, the check valve 90 which makes the direction toward the gas cooler 46 (oil separator 44) from the high end discharge port 28 of the compressor 11 in the forward direction. Is provided, the high pressure refrigerant at the gas cooler 46 side is prevented by the check valve 90 of the refrigerant regulator 91 interposed in the high pressure discharge pipe 42 even when the compressor 11 is stopped. ) Do not communicate with the side. Therefore, even when the operation of the compressor 11 is stopped and the high pressure side and the intermediate pressure are equalized in the sealed container 12, the casting is provided near the evaporators 63A and 63B from the check valve 90. The pressure on the high pressure side of the refrigerant circuit 1 to the means 62A, 62B can be maintained.

In other words, when the check valve 90 is not provided, the high pressure side and the medium pressure side are equalized in the stationary compressor 11. On the other hand, in the closed container 12, the low pressure side and the medium pressure side are difficult to equalize easily because only the low pressure side is immersed in oil. However, when starting the compressor 11, since the pressure difference in the refrigerant circuit 1 is large, a predetermined time until the whole of the refrigerant circuit 1 is equalized is required, and the startability is poor.

However, in this embodiment, since the pressure on the high pressure side of the refrigerant circuit 1 is maintained by the check valve 90 after the compressor 11 is stopped, the startability of such a compressor 11 can be improved. have. In addition, since the whole inside of the refrigerant circuit 1 is not equalized, the refrigeration cycle apparatus can be made more efficient.

In addition, as in the present embodiment, when the plurality of compressors 11 and 11 are provided in the refrigerating device R, in this case, connected in parallel with each other, the refrigerant regulator 91 having the check valve 90 is provided. ) Is provided corresponding to each compressor 11 at a position before the high pressure discharge pipes 42 and 42 of the compressors 11 and 11 join. This makes it possible to further operate the compressor having a multi-configuration, thereby improving capacity controllability.

As described above, since the container 92 of the refrigerant regulator 91 provided with the check valve 90 has a predetermined capacity, the oil separator for separating oil from the refrigerant can also be exhibited. The oil accumulated in the lower part of the said container 92 can be returned to the corresponding compressor 11 and 11 smoothly through the oil return pipe 86 provided in the said lower end part.

(H) Defrost control of the evaporator

As described above, each showcase unit 5A, 5B is connected in parallel to the refrigerant pipes 7 and 9, respectively. Each of the showcase units 5A and 5B and the case side refrigerant pipes 60A and 60B connecting the refrigerant pipe 7 and the refrigerant pipe 9 are strainers 61A and 61B and casting means 62A, respectively. 62B) and evaporator 63A, 63B are connected one by one.

And the 1st communication pipe | tube 64A which communicates with the inlet side of the casting means 62B corresponding to the other evaporator 63B is connected to the outlet side of one evaporator 63A, and the said 1st communication pipe 64A is connected. ), A solenoid valve (valve device) 65A is interposed. Moreover, the 2nd communication pipe 64B which communicates with the inlet side of 62 A of casting casting means corresponding to one evaporator 63A is connected to the exit side of the other evaporator 63B, and the said 2nd communication pipe 64B is connected. ) Is provided with a solenoid valve (valve device) 65B. In addition, in this embodiment, the casting means 62A, 62B is constituted by an electric expansion valve. In addition, the casting means 62A, 62B may be constituted by a capillary tube as a tightening means, a bypass tube bypassing it, and a solenoid valve.

Further, solenoid valves (valve devices) 66A and 66B are provided on the downstream side of the classifier with the communication tubes 64A and 64B connected to the outlet side of the evaporator 63A or 63B of the case-side refrigerant pipes 60A and 60B. Intervened. These solenoid valves 65A, 65B, 66A, 66B constitute flow path control means.

On the other hand, as mentioned above, the gas cooler bypass circuit 71 which bypasses the gas cooler 46 which comprises the refrigerant circuit 1 is provided. The gas cooler bypass circuit 71 is provided with a solenoid valve 72. The solenoid valves 65A, 65B, 66A, 66B, 72 and the casting means 62A, 62B are controlled to be opened and closed by the controller C as described above.

By the above structure, first, the defrost control of one evaporator 63A is demonstrated. When defrosting one of the evaporators 63A, the controller C flows the flow path control means through the refrigerant from the evaporator 63A to the first communication tube 64A, and delivers the refrigerant from the evaporator 63B to the compressor ( Control to return to 11) is performed. That is, 62 A of casting impingement means corresponding to the evaporator 63A is developed, and the solenoid valve 65A and the train valve 66B of the first communication pipe 64A are opened. The solenoid valve 65B and the solenoid valve 66A of the second communication pipe 64B are closed. In addition, when the casting impingement means 62A is composed of a capillary tube, a bypass tube bypassing it, and a solenoid valve, the solenoid valve of the bypass tube is opened.

As a result, the high temperature and high pressure refrigerant discharged from the compressor 11 passes through the gas cooler 46, the heat recovery heat exchanger 70, the intermediate heat exchanger 80, and the refrigerant pipe 7 to the case side refrigerant pipe 60A. The gas refrigerant flows into the one evaporator 63A as it passes through the casting impregnating means 62A. Since the solenoid valve 66A is closed and the solenoid valve 65A is open, the refrigerant liquefied by the defrost of the evaporator 63A is open, so that the first communication pipe 64A is opened. It flows in through the inlet side of the casting means 62B corresponding to the other evaporator 63B.

For this reason, the refrigerant liquefied by the defrost of one evaporator 63A is expanded under reduced pressure by the casting means 62B corresponding to the other evaporator 63B, and evaporates by the other evaporator 63B. Thereby, the problem that the refrigerant liquefied by the defrost of one evaporator 63A directly returns to the compressor 11 can be solved.

When performing the defrost of the other evaporator 63B, the control apparatus C flows the said flow path control means into the 2nd communication tube 64B, and the refrigerant | coolant from the evaporator 63A flows the refrigerant | coolant from the evaporator 63B. Control to return to (11) is performed. That is, the casting means 62B corresponding to the evaporator 63B is developed, and the solenoid valve 65B and the solenoid valve 66A of the second communication tube 64B are opened. The solenoid valve 65A and the solenoid valve 66B of the second communication pipe 64A are closed.

As a result, the high temperature and high pressure refrigerant discharged from the compressor 11 is passed through the gas cooler 46, the heat recovery heat exchanger 70, the intermediate heat exchanger 80, and the refrigerant pipe 7 to the case side refrigerant pipe 60B. The gas refrigerant flows into the other evaporator 63B as it passes through the casting impregnation means 62B. Since the solenoid valve 66B is closed and the solenoid valve 65B is opened, the refrigerant liquefied by the defrost of the evaporator 63B is open, so that the second communication tube 64B is used. Through this, it flows into the inlet side of the casting means 62A corresponding to one evaporator 63A. For this reason, the refrigerant liquefied by the defrost of the other evaporator 63B expands under reduced pressure by the casting means 62A corresponding to the one evaporator 63A, and evaporates by the one evaporator 63A.

In this way, the refrigerant liquefied by defrosting is directly evaporated to the compressor 11 by evaporating the refrigerant liquefied by mutual defrosting in the refrigerating device R having a plurality of evaporators 63A and 63B. It can solve the problem of returning. Moreover, it becomes possible to realize the defrost of these evaporators 63A and 63B with such a simple structure.

In the present embodiment, the defrosts of the evaporators 63A and 63B of the two refrigerator units 5A and 5B are described as an example. However, even when the number of evaporators is increased, the refrigerants liquefied by mutual defrosting are further evaporated. By the evaporation treatment, the effect of the present invention can be obtained.

In addition, in the present embodiment, the control unit C is a solenoid valve provided in the gas cooler bypass circuit 71 at the time of defrosting when the temperature detected by the outside temperature sensor 56 is a predetermined low temperature. Open 72). As a result, the refrigerant having a high temperature (passed through the gas cooler bypass circuit 71), which avoids the gas cooler 46 serving as a supercritical cycle, can be introduced into the evaporator in which defrosting is performed.

As a result, when the coolant temperature flowing into the evaporator for defrosting at a low outside temperature or the like is low, it is possible to supply a coolant of a higher temperature, thereby achieving efficient defrosting.

In addition, since the defrost using the arrangement can be realized, heating means such as a special heater can be made unnecessary, and energy saving can be achieved. Moreover, since the energization of the heater at the time of defrosting can be avoided, the peak power can be cut.

As in the present embodiment, when carbon dioxide is used as the refrigerant, the discharge temperature from the compressor 11 increases, so that the defrosting performance of the evaporator can be improved.

R Refrigeration Unit C Control Unit (Control Unit)
1 Refrigerant Circuit 3 Refrigerator Unit
5A, 5B Showcase Unit 7, 9 Refrigerant Piping
11 Compressor 12 Airtight Container
14 Transmission element 18 First rotary compression element
20 Second rotary compression element 22 Low end side suction port
24 Low Stage Side Outlet 26 High Stage Side Inlet
28 High stage outlet 32 Low pressure sensor (Suction pressure detection means)
34 Unit inlet temperature sensor (inlet temperature detection means)
36 Medium pressure discharge pipe 38 Intercooler
42 High Pressure Discharge Pipe 44 Oil Separator
45 furnace 46 gas cooler
47 Blower for gas cooler 48 High pressure sensor (High pressure detection means)
49 Medium pressure sensor (medium pressure detection means)
S0 discharge temperature sensor (discharge temperature detection means)
52 Gas cooler outlet temperature sensor (gas cooler outlet temperature detection means)
54 Unit outlet temperature sensor (unit outlet temperature detection means)
56 Ambient air temperature sensor
58 Unit outlet side pressure sensor (unit outlet side pressure detection means)
60A, 60B Case side refrigerant piping 62A, 62B Casting
63A, 63B Evaporator 64A, 64B Communicating Tube
65A, 65B solenoid valve (valve device. Flow control means)
66A, 66B solenoid valve (valve device. Flow control means)
70 Heat Recovery Heat Exchanger 70A Refrigerant Flow
70B Array Recovery Medium Euro 71 Gas Cooler Bypass Circuit
72 Solenoid valve (valve unit) 73 Oil return circuit
74 Oil cooler 76 Flow control valve (motor valve)
78 Oil bypass circuit 79 Solenoid valve (valve device)
80 Intermediate heat exchanger 80A 1st flow path
80B 2nd flow path 83 auxiliary expansion valve (auxiliary tightening means)
84 Bypass Circuit 85 Solenoid Valve (Valve Device)
86 oil return pipe 90 check valve
91 Refrigerant Regulator 92 Airtight Container
93 Partition Wall 100 Refrigerant Volume Adjustment Tank
101 first communication circuit
102 Electric expansion valve (first opening and closing means with tightening function)
103 Second communication circuit 104 Solenoid valve (second opening and closing means)
105 Third communication circuit 106 Solenoid valve (third open / close means)

Claims (2)

A refrigerant circuit is composed of a compression means, a gas cooler, an auxiliary fastening means, an intermediate heat exchanger, a casting impregnation means, and an evaporator. The refrigerant from the gas cooler is classified into two streams, and the first refrigerant flow is defined as the above-mentioned. Flows to the first flow path of the intermediate heat exchanger through an auxiliary fastening means, to flow the second refrigerant flow to the second flow path of the intermediate heat exchanger, and then to the evaporator through the casting impregnation means, Heat-exchanging the first refrigerant stream and the second refrigerant stream, sucking the refrigerant from the evaporator into the low pressure portion of the compression means, and sucking the first refrigerant flow from the intermediate heat exchanger into the intermediate pressure portion of the compression means; In addition, in the refrigerating device in which the high pressure side becomes a supercritical pressure,
A heat recovery heat exchanger having a heat recovery medium flow path and a refrigerant flow path,
And a second coolant flowing out of the gas cooler before entering the intermediate heat exchanger into a coolant flow path of the heat recovery heat exchanger. The method according to claim 1,
Refrigerating apparatus characterized in that the carbon dioxide is used as the refrigerant.

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