JP6206787B2 - Refrigeration equipment - Google Patents

Description

  The present invention relates to a refrigeration apparatus in which a refrigerant circuit is configured by a compressor, a gas cooler, an expansion valve, and an evaporator, and a high pressure side is at a supercritical pressure.

  Conventionally, this kind of refrigeration apparatus has a refrigerant circuit composed of a compressor, a gas cooler, an expansion valve, an evaporator, etc., radiates the refrigerant compressed by the compressor with the gas cooler, depressurizes with the expansion valve, and then the evaporator The ambient air is cooled by evaporation of the refrigerant at this time. In recent years, chlorofluorocarbon refrigerants cannot be used in this type of refrigeration system due to natural environmental problems. For this reason, the thing using the carbon dioxide which is a natural refrigerant | coolant is developed as a substitute of a fluorocarbon refrigerant | coolant. The carbon dioxide refrigerant is a refrigerant having a high and low pressure difference, and has a low critical pressure. It is known that the high pressure side of the refrigerant cycle is brought into a supercritical state by compression (see, for example, Patent Document 1).

  Further, in Patent Document 1, since it is a refrigeration apparatus that supplies refrigerant from a refrigerator to a plurality of showcases (load equipment) installed in a store such as a supermarket, the operation control of the compressor installed in the refrigerator is It was controlled based on the low pressure side pressure of the refrigerant circuit. Moreover, the superheat degree of the evaporator was controlled to an appropriate value by controlling the valve opening degree of the expansion valve.

JP 2011-133204 A

  Here, the increase in the high-pressure side pressure of the refrigerant circuit when the compressor of this type of refrigeration apparatus is started is greatly influenced by the inflow resistance of the refrigerant (gas refrigerant) to the evaporator of the showcase that is the load device. This inflow resistance is determined by the valve opening of the expansion valve.

  However, this expansion valve (electric expansion valve) does not operate at a speed that can follow the change in the high-pressure side pressure. Therefore, conventionally, the standard valve opening of the expansion valve is specified in advance, and when the compressor is started, the expansion valve is used as the standard valve opening to control the inflow resistance to the evaporator. The equilibrium pressure in the refrigerant circuit after the machine stops changes depending on the season.

  For this reason, the standard valve opening is too small in the summer, and refrigerant inflow to the evaporator at the start is blocked, leading to an increase in the high-pressure side pressure. On the contrary, the standard valve opening is too large in the winter. There is a problem that a so-called short cycle occurs in which an excessive amount of refrigerant flows in, the pressure on the low-pressure side decreases due to an excessive cooling capacity, and the compressor immediately stops.

  The present invention has been made to solve the conventional technical problems, and a refrigeration apparatus capable of reducing the starting load by appropriately controlling the valve opening of the expansion valve at the time of starting the compressor. The purpose is to provide.

The refrigeration apparatus of the present invention is
In a refrigerating apparatus in which a refrigerant circuit is configured by a compressor, a gas cooler, an expansion valve, and an evaporator, and the high pressure side is at a supercritical pressure, the refrigerator having the compressor and the gas cooler, the evaporator, and the expansion valve And a control means for controlling the compressor and the expansion valve, the control means being provided in the refrigerator and a refrigerator-side control means for controlling the compressor, and the load A load device side control means for controlling the expansion valve provided in the equipment , and the standard valve opening of the expansion valve held by the load equipment side control means is corrected based on the outside air temperature Thus, the valve opening of the expansion valve is changed, and the control means changes the valve opening of the expansion valve at the time of starting the compressor before starting the compressor based on the outside air temperature, Device side control means It has a standard valve opening of the expansion valve at the time of starting the compressor and a standard valve opening of the expansion valve after the start of the compressor, and each standard valve opening is corrected. .

  According to a second aspect of the present invention, in the above invention, the control means increases the valve opening degree of the expansion valve when the outside air temperature is high, and reduces the valve opening degree of the expansion valve when the outside air temperature is low. Features.

According to a third aspect of the present invention, there is provided the refrigeration apparatus according to the first aspect, wherein the control means transmits / receives data to / from the refrigerator side control means, the load equipment side control means, and the refrigerator side control means and the load equipment side control means. The main control means receives the data related to the standard valve opening of the expansion valve from the load equipment side control means, and receives the data related to the outside air temperature from the refrigerator side control means to receive the standard valve opening degree. And the data related to the corrected opening degree of the expansion valve is transmitted to the load device side control means. The load equipment side control means transmits the data related to the valve opening degree of the expansion valve transmitted from the main control means. Based on the above, the expansion valve is controlled.

The refrigeration apparatus of the invention of claim 4 is characterized in that carbon dioxide is used as a refrigerant in each of the above inventions.

  According to the present invention, in the refrigerating apparatus in which the refrigerant circuit is configured by the compressor, the gas cooler, the expansion valve, and the evaporator, and the high pressure side is at the supercritical pressure, the control means for controlling the compressor and the expansion valve is provided. Since the control means changes the valve opening degree of the expansion valve at the time of starting the compressor based on the outside air temperature, the outside air temperature is high and the equilibrium pressure of the refrigerant circuit is high as in the invention of claim 2. In situations where the expansion valve opening is increased to prevent an abnormal increase in the high-pressure side pressure, the starting load of the compressor can be reduced, while the outside air temperature is low and the equilibrium pressure is low. It is possible to prevent the occurrence of a short cycle due to excessive cooling performance by reducing the opening degree of the expansion valve.

  Further, as in the invention of claim 3 and claim 4, the control means is constructed from the refrigerator side control means, the load equipment side control means, and the main control means for transmitting and receiving data to and from the load equipment side control means. If data on the standard valve opening of the expansion valve is held and the main control means corrects the standard valve opening based on the data on the outside air temperature received from the refrigerator-side control means, the main control means and the load Even when a communication abnormality occurs with the device-side control means, the load device-side control means can set the expansion valve to the standard valve opening without any trouble.

  Furthermore, as in the invention of claim 5, the load device side control means has a standard valve opening degree of the expansion valve when starting the compressor and a standard valve opening degree of the expansion valve after starting the compressor. If the opening is corrected, the expansion valve can be controlled without any trouble from the start of the compressor to after the start. The above is particularly effective in a refrigeration apparatus using carbon dioxide as a refrigerant.

It is a refrigerant circuit figure of the refrigerating device of one example to which the present invention is applied. It is a block diagram of the control apparatus of the freezing apparatus of FIG. It is a figure explaining the operating frequency control of the compressor by the control apparatus of FIG. It is a figure explaining the valve opening degree control of the expansion valve at the time of the compressor start by the control apparatus of FIG.

  Hereinafter, embodiments of the present invention will be described in detail. FIG. 1 is a refrigerant circuit diagram of a refrigeration apparatus R according to an embodiment to which the present invention is applied. The refrigeration apparatus R in this embodiment is installed in a store such as a supermarket, and includes a refrigerator 3 and one or a plurality of showcases 4 (loading devices) in the store, and these refrigerators 3 and showcases. 4 are connected to each other by refrigerant pipes 8 and 9 via a unit outlet 6 and a unit inlet 7 to constitute a predetermined refrigerant circuit 1.

  The refrigerant circuit 1 uses, as a refrigerant, carbon dioxide whose refrigerant pressure (high pressure) on the high pressure side is equal to or higher than the critical pressure (supercritical). This carbon dioxide refrigerant is a natural refrigerant that is friendly to the global environment and takes into consideration flammability and toxicity. As the lubricating oil, existing oils such as mineral oil (mineral oil), alkylbenzene oil, ether oil, ester oil, and PAG (polyalkyl glycol) are used.

  The refrigerator 3 includes a compressor 11. In the present embodiment, the compressor 11 is a multistage compression rotary compressor, and a cylindrical sealed container 12 made of a steel plate and an electric element as a drive element disposed and housed in the upper part of the internal space of the sealed container 12. 13 and a first (low-stage side) rotary compression element (first compression element) 14 and a second (high-stage side) rotary compression which are arranged below the electric element 13 and driven by the rotating shaft thereof The rotary compression mechanism is composed of an element (second compression element) 16.

  The first rotary compression element 14 of the compressor 11 compresses the low-pressure refrigerant sucked into the compressor 11 from the low-pressure side of the refrigerant circuit 1 through the refrigerant pipe 9 and raises it to an intermediate pressure for discharge. The rotary compression element 16 further sucks in the intermediate pressure refrigerant compressed and discharged by the first rotary compression element 14, compresses it to a high pressure, and discharges it to the high pressure side of the refrigerant circuit 1. The compressor 11 is a variable frequency compressor, and the rotational frequency of the first rotary compression element 14 and the second rotary compression element 16 can be controlled by changing the operating frequency of the electric element 13.

  On the side surface of the sealed container 12 of the compressor 11, a low-stage suction port 17 communicating with the first rotary compression element 14, a low-stage discharge port 18 communicating with the inside of the sealed container 12, and a second rotational compression A high-stage suction port 19 and a high-stage discharge port 21 communicating with the element 16 are formed. A refrigerant introduction pipe 22 is connected to the lower stage side suction port 17 of the compressor 11 and is connected to the refrigerant pipe 9.

  The low-pressure refrigerant gas (LP: about 2.6 MPa in the normal operation state) sucked into the low-pressure portion of the first rotary compression element 14 from the low-stage suction port 17 is intermediate pressure by the first rotary compression element 14. The pressure is increased to (MP: about 5.5 MPa in a normal operation state) and discharged into the sealed container 12. Thereby, the inside of the airtight container 12 becomes an intermediate pressure (MP).

  An intermediate pressure discharge pipe 23 is connected to the low-stage discharge port 18 of the compressor 11 through which the intermediate pressure refrigerant gas in the sealed container 12 is discharged, and is connected to one end of the intercooler 24. The intercooler 24 air-cools the intermediate pressure refrigerant discharged from the first rotary compression element 14, and an intermediate pressure suction pipe 26 is connected to the other end of the intercooler 24. The suction pipe 26 is connected to the higher stage suction port 19 of the compressor 11.

  The medium-pressure (MP) refrigerant gas sucked into the second rotary compression element 16 by the high-stage side suction port 19 is compressed by the second stage by the second rotary compression element 16, and the high-temperature high-pressure (HP : Supercritical pressure of about 9 MPa in a normal operation state).

  One end of a high-pressure discharge pipe 27 is connected to the high-stage discharge port 21 provided on the high-pressure chamber side of the second rotary compression element 16 of the compressor 11, and the other end is a gas cooler (heat radiator) 28. Connected to the entrance. An oil separator 20 is provided in the high-pressure discharge pipe 27. The oil separator 20 separates the oil in the refrigerant discharged from the compressor 11 and returns it to the sealed container 12 of the compressor 11 via the oil passage 25A of the oil cooler 25 and the electric valve 25B. Reference numeral 55 denotes a float switch for detecting the oil level in the compressor 11.

  The gas cooler 28 cools the high-pressure discharged refrigerant discharged from the compressor 11, and a gas cooler blower 31 for air-cooling the gas cooler 28 is disposed in the vicinity of the gas cooler 28. In the present embodiment, the gas cooler 28 is juxtaposed with the intercooler 24 described above, and these are disposed in the same air passage. And the exit of the gas cooler 28 is connected to the refrigerant | coolant piping 8 via the split heat exchanger (intermediate heat exchanger) 29 etc. which comprise a split cycle.

  On the other hand, the showcase 4 is installed in a store such as a supermarket or a convenience store, and is connected to the refrigerant pipes 8 and 9. The showcase 4 is provided with an expansion valve (electric expansion valve) 32 and an evaporator 33, and sequentially connected between the refrigerant pipe 8 and the refrigerant pipe 9 (the expansion valve 32 is on the refrigerant pipe 8 side, The evaporator 33 is the refrigerant pipe 9 side). Adjacent to the evaporator 33 is a cooler circulation blower 53 (FIG. 2) for blowing air to the evaporator 33. The refrigerant pipe 9 is connected to the low-stage suction port 17 that communicates with the first rotary compression element 14 of the compressor 11 via the refrigerant introduction pipe 22 as described above. Thereby, the refrigerant circuit 1 of the refrigeration apparatus R in the present embodiment is configured. In the figure, reference numeral 37 denotes a check valve having a forward direction on the oil separator 20 side, and is interposed in the high pressure discharge pipe 27.

  In addition, the refrigerant circuit 1 of the refrigeration apparatus R of the embodiment is a split cycle, and serves as a merging device that merges the first rotary compression element (low stage side) 14 of the compressor 11, the intercooler 24, and the two fluid flows. , A second rotary compression element (high stage side) 16 of the compressor 11, a gas cooler 28, a split heat exchanger 29, a flow divider 42, an auxiliary expansion valve (auxiliary electric expansion valve) 43, an expansion valve 32, And an evaporator 33.

  The flow divider 42 is a flow dividing device that branches the refrigerant from the split heat exchanger 29 into two flows. That is, the flow divider 42 of the present embodiment diverts the refrigerant from the split heat exchanger 29 into the first refrigerant flow and the second refrigerant flow, and flows the first refrigerant flow to the auxiliary circuit. The refrigerant flow is configured to flow through the main circuit.

  The main circuit in FIG. 1 includes the first rotary compression element 14, the intercooler 24, the merger 41, the second rotary compression element 16, the check valve 37, the oil separator 20, the gas cooler 28, and the split heat exchanger 29. This is an annular refrigerant circuit composed of the second flow path 29B, the flow divider 42, the expansion valve 32, and the evaporator 33. The auxiliary circuit is the first of the auxiliary expansion valve 43 and the split heat exchanger 29 from the flow divider 42. It is a circuit that reaches the merger 41 sequentially through the flow path 29A.

  The refrigerant discharged from the first rotary compression element 14 of the compressor 11 is air-cooled by the intercooler 24 and then sucked into the second rotary compression element 16 of the compressor 11 through the merger 41 and compressed. Then, it is discharged from the second rotary compression element 16 and passes through the check valve 37, the oil separator 20, the gas cooler 28, the second flow path 29B (second refrigerant flow) of the split heat exchanger 29, and the flow divider 42. It reaches the expansion valve 32. Therefore, the refrigerant is decompressed and then flows into the evaporator 33 and evaporates. The cooling ability is exhibited by the endothermic action at this time. The expansion valve 32 controls the superheat degree of the evaporator 33 to an appropriate value.

  The auxiliary expansion valve 43 diverts the first refrigerant flow that is diverted by the flow divider 42 and flows through the auxiliary circuit. The split heat exchanger 29 is a heat exchanger that performs heat exchange between the first refrigerant flow in the auxiliary circuit decompressed by the auxiliary expansion valve 43 and the second refrigerant flow that has exited from the gas cooler 28. In the split heat exchanger 29, a second flow path 29B through which the second refrigerant flow flows and a first flow path 29A through which the first refrigerant flow flows are provided in a heat exchangeable relationship. Since the second refrigerant flow is cooled by the first refrigerant flow flowing through the first flow path 29A by passing through the second flow path 29B of the split heat exchanger 29, the ratio in the evaporator 33 is reduced. It is comprised so that enthalpy can be made small.

  The expansion valve 32 is provided by a showcase-side controller 36 as load device-side control means constituting a control device C as control means described later, and the auxiliary expansion valve 43 is also used as a refrigerator-side control means constituting the control device C. The chiller side controller 34 controls the valve opening to an appropriate value, thereby realizing efficient operation.

  The refrigerant amount is adjusted via the first communication circuit 51 on the high pressure side, which is the supercritical pressure of the refrigerant circuit 1, in the present embodiment, on the downstream side of the split heat exchanger 29 and the flow divider 42 of the refrigerator 3. A tank 52 is connected. The first communication circuit 51 is provided with an expansion valve (electric expansion valve) 56 having an opening adjustment function in order to adjust the refrigerant recovery amount.

  In addition, a second communication circuit 58 that connects the inside of the refrigerant quantity adjustment tank 52 and the intermediate pressure region of the refrigerant circuit 1 is connected to the upper part of the refrigerant quantity adjustment tank 52. In the present embodiment, the other end of the second communication circuit 58 is communicated with the intermediate pressure suction pipe 26 on the outlet side of the intercooler 24 of the refrigerant circuit 1 as an example of the intermediate pressure region. An electromagnetic valve 59 is interposed in the second communication circuit 58.

  Further, a third communication circuit 62 is connected to the lower part of the refrigerant quantity adjustment tank 52 to communicate the lower part in the refrigerant quantity adjustment tank 52 and the intermediate pressure region of the refrigerant circuit 1. In the present embodiment, the other end of the third communication circuit 62 is connected to the downstream side of the auxiliary expansion valve 43 as an example of the intermediate pressure region, and finally the intermediate pressure on the outlet side of the intercooler 24 of the refrigerant circuit 1. The suction pipe 26 is communicated. In the third communication circuit 62, an electromagnetic valve 63 and a capillary tube (throttle means) 64 are interposed.

  The expansion valve 56 and the electromagnetic valves 59 and 63 of the refrigerant amount adjustment tank 52 are controlled by the above-described refrigerator-side controller 34, and the expansion valve 56 is opened based on the increase in the high-pressure side pressure HP of the refrigerant circuit 1. The solenoid valve 59 is opened, the solenoid valve 63 is closed, the refrigerant is collected in the refrigerant quantity adjustment tank 52, and the solenoid valve 59 is closed based on the decrease in the high pressure side pressure HP. Open to release refrigerant. Thereby, the amount of circulating refrigerant in the refrigerant circuit 1 is controlled to an appropriate value, and the high pressure side pressure HP is prevented from rising due to an excessive amount of circulating refrigerant.

  Further, the intermediate pressure region of the refrigerant circuit 1 on the outlet side of the intercooler 24 of the refrigeration apparatus R, in the present embodiment, the second communication circuit 58 connected to the outlet side of the intercooler 24, and the refrigerant circuit 1 In the present embodiment, a bypass circuit 71 that communicates with the refrigerant introduction pipe 22 is provided on the low pressure side. The bypass circuit 71 is provided with an electromagnetic valve 72 that is opened when the compressor 11 is started to improve startability.

  In FIG. 1, PS1 is connected to the high-pressure discharge pipe 27 and detects a high-pressure side pressure HP of the refrigerant circuit 1 that is the discharge pressure of the compressor 11, and PS2 is connected to the refrigerant introduction pipe 22 and connected to the compressor 11. PS3 is an intermediate pressure sensor that is connected to the intermediate pressure suction pipe 26 and detects the intermediate pressure MP of the refrigerant circuit 1.

  In FIG. 1, TS1 is connected to the high pressure discharge pipe 27 to detect the discharge refrigerant temperature of the compressor 11 and TS2 is connected to the outlet of the gas cooler 28 to detect the refrigerant temperature coming out of the gas cooler 28. TS3 is a split outlet temperature sensor connected to the outlet of the first flow path 29A of the split heat exchanger 29, TS4 is an outlet temperature sensor of the refrigerator 3, TS5 is an inlet temperature sensor of the refrigerator 3, and TS6 is It is an outside temperature sensor that detects outside temperature.

  Next, FIG. 2 is a block diagram of a control device C as control means of the refrigeration apparatus R. In this figure, 35 is a main controller as main control means installed in a management room of the store, 34 is a refrigerator controller as the above-mentioned refrigerator side control means provided in the refrigerator 3, and 36 is each This is the above-described showcase-side controller as showcase-side control means provided in each showcase 4. Each controller is constituted by a general-purpose microcomputer, and the main controller 35 is connected to the refrigerator-side controller 34 and the showcase-side controller 36 (one or a plurality) by a communication line so that data can be transmitted and received. Has been.

  Each sensor (represented by S in FIG. 2) such as the above-described outside temperature sensor TS6 is connected to the input of the refrigerator-side controller 34, and further, the compressor 11 is connected to the output of the refrigerator-side controller 34. (Electric element 13), auxiliary expansion valve 43, gas cooler blower 31, expansion valve 56, electromagnetic valves 59 and 63, electric valve 25B, and the like are connected. An input of the showcase-side controller 36 is connected to an internal temperature sensor 60 for detecting the internal temperature of the showcase 4, and an output of the showcase-side controller 36 is connected to the expansion valve 32, the aforementioned cool air circulation blower 53, etc. Is connected.

  The showcase-side controller 36 controls the expansion valve 32 and the cool air circulation blower 60 based on various setting data such as the setting temperature transmitted from the main controller 35 and the internal temperature detected by the internal temperature sensor 53. In addition, data related to the information, operation state, and alarm set for itself is transmitted to the main controller 35. The refrigerator-side controller 34 is also connected to the output based on various setting data (including a target range and stop value of the low-pressure side pressure LP described later) transmitted from the main controller 35 and the temperature and pressure detected by each sensor S. The compressor 11, the expansion valves 43 and 56, the electromagnetic valves 59 and 63, and the like are controlled, and the above-described split cycle control and refrigerant recovery / release control using the refrigerant amount adjustment tank 52 are executed.

(A) Control of operation frequency of compressor Next, control of the operation frequency of the compressor 11 (electric element 13) by the refrigerator side controller 34 is demonstrated using FIG. The refrigerator side controller 34 of the refrigerator 3 controls the operating frequency of the compressor 11 (electric element 13) based on the low pressure LP of the refrigerant circuit 1 detected by the low pressure sensor PS2.

  In this embodiment, the refrigerator-side controller 34 performs zone control as shown in FIG. That is, when the low pressure side pressure LP detected by the low pressure sensor PS2 is in the zone 1 higher than the upper limit value of the predetermined target range, the operating frequency of the compressor 11 is increased by 1 Hz every predetermined time t1 (for example, 10 seconds). The increase in the operating frequency reaches a peak at a predetermined control limit upper limit. Further, when the low pressure side pressure LP is in the zone 3 lower than the lower limit value of the target range, the operating frequency of the compressor 11 is decreased by 1 Hz every predetermined time t2 (for example, 1 second) shorter than the predetermined time t1. That is, the decreasing speed for decreasing the operating frequency of the compressor 11 is faster than the increasing speed for increasing the operating frequency. This is to prevent the low-pressure side pressure LP from reaching the stop value described later as much as possible. This decrease in operating frequency also bottoms out at a predetermined control limit lower limit.

  Further, when the low pressure side pressure LP is in the zone 2 which is not less than the lower limit value and not more than the upper limit value, that is, when the low pressure side pressure LP is within the target range, the operating frequency of the compressor 11 is not changed. As a result, the operating frequency of the compressor 11 is increased / decreased so that the low pressure LP of the refrigerant circuit 1 is within the target range during normal operation.

  Note that, for example, when the expansion valves 32 of all the connected showcases 4 are closed, the low-pressure side pressure is further reduced from the lower limit value by the control of the operating frequency of the compressor 11, and is lower than the lower limit value. When the temperature drops to below the stop value and becomes the zone 4, the refrigerator-side controller 34 stops the compressor 11.

  When the compressor 11 is stopped, the refrigerator-side controller 34 prohibits the start of the compressor 11 for a predetermined time (restart prohibition time). Meanwhile, the pressure on the high pressure side and the low pressure side in the refrigerant circuit 1 becomes the equilibrium pressure. After that, when the temperature inside the showcase 4 rises or the like, the expansion valve 32 opens, and when the low-pressure pressure LP rises higher than a predetermined restart value (for example, the above-described upper limit value), the restart prohibition time has elapsed. Under the condition, the refrigerator controller 34 starts the compressor 11.

(B) Stabilization control when the compressor is started Next, stabilization control when the compressor 11 is started will be described. As described above, the refrigerator controller 34 performs control to increase / decrease the operating frequency of the compressor 11 and stop the compressor 11 so that the low pressure LP is within the target range. The equilibrium pressure in the refrigerant circuit 1 after stopping varies depending on the outside air temperature. The equilibrium pressure is high in summer when the outside air temperature is high, and the equilibrium pressure is low in winter when the outside air temperature is low.

  When the compressor 11 is started in a state where the equilibrium pressure is high, since the low pressure side pressure LP is in the zone 1, the operating frequency of the compressor 11 immediately rises to a high value. On the other hand, since the evaporator 33 of the showcase 4 is cold, the low-pressure side pressure LP rapidly decreases, reaches a stop value, and the compressor 11 is stopped. Therefore, the compressor 11 repeats frequent start / stop (so-called short cycle), and the so-called overshoot of the operating frequency increases and the high-pressure side pressure HP abnormally increases.

  Conversely, when the compressor 11 is started in a state where the equilibrium pressure is low, the load (cooling load) on the showcase 4 side is small and the evaporator 33 is also cold, so the low pressure side pressure LP rapidly decreases. Again, the stop value is reached, and the compressor 11 is repeatedly put into a state where it is repeatedly started and stopped.

  Therefore, the refrigerator-side controller 34 in the present invention monitors the change in the low-pressure side pressure LP of the refrigerant circuit 1 detected by the low-pressure sensor PS2 after the compressor 11 is started, and the lowering speed of the low-pressure side pressure LP is predetermined. When it is determined that the value is equal to or greater than the specified value (steep), even if the low pressure side pressure LP is in the tongue lowering zone 1, the increase in the operating frequency of the compressor 11 is prohibited.

  As a result, after starting the compressor 11 in a state where the refrigerant circuit 1 is at an equilibrium pressure, an increase in the operating frequency of the compressor 11 is prohibited in a situation where the low-pressure side pressure LP suddenly decreases. The inconvenience that the low-pressure side pressure LP reaches the stop value and is immediately stopped as the low-pressure side pressure LP after the compressor 11 is started can be avoided. Therefore, it is possible to solve the problem that the refrigeration apparatus R repeats frequent starting and stopping of the compressor 11 at the start, and to stabilize the operating state at an early stage.

(C) Valve opening degree control of expansion valve when starting compressor Next, control of the expansion valve 32 when starting the compressor 11 will be described. As described above, the increase in the high-pressure side pressure HP of the refrigerant circuit 1 when the compressor 11 is started is greatly influenced by the inflow resistance of the refrigerant (gas refrigerant) to the evaporator 33 of the showcase 4. Is determined by the valve opening of the expansion valve 32. However, the expansion valve (electric expansion valve) 32 does not operate at a speed that can follow the change in the high-pressure side pressure HP.

  Therefore, conventionally, the standard valve opening degree of the expansion valve 32 is defined in advance, and when the compressor 11 is started, the inflow resistance to the evaporator 33 is controlled using the valve opening degree of the expansion valve 32 as the standard valve opening degree. However, as described above, the equilibrium pressure in the refrigerant circuit 1 after the compressor 11 is stopped changes depending on the season, so that the standard valve opening is too small in the summer, leading to an increase in the high-pressure side pressure HP. On the other hand, the standard valve opening is too large and excessive refrigerant flows into the evaporator 33, the low-pressure side pressure LP decreases due to excessive cooling capacity, and the compressor 11 immediately stops as described above ( Short cycle).

  Therefore, the main controller 35 corrects the standard valve opening based on the outside air temperature, and changes the valve opening of the expansion valve 32 when the compressor 11 is started. FIG. 4 shows the state of the valve opening control. First, the standard valve opening degree of the expansion valve 32 in this embodiment is shown at the center on the right side of FIG. 4, and correction values (variations) are shown above and below it. The left side of FIG. 4 shows the transition of the outside air temperature.

  In the case of the embodiment, the standard valve opening of the expansion valve 32 is classified into a valve opening at the start of the compressor 11 (that is, a valve opening at the start) and a valve opening after the start, In the case of the showcase 4, the standard valve opening degree at the time of starting is 150 pulses, the standard valve opening degree after starting is 120 pulses, and the showcase side controller 36 holds in advance. The number of pulses indicates the valve opening of the expansion valve 32, which is an electric expansion valve, and is zero (0) in the fully closed state. The larger the number of pulses, the larger the valve opening.

  When the showcase 4 is connected to the refrigerant pipes 8 and 9 and the showcase-side controller 36 is connected to the main controller 35, the main controller 35 receives data on the standard valve opening degree from the showcase-side controller 36. read. Further, data related to the outside temperature detected by the outside temperature sensor TS6 is received from the refrigerator-side controller 34 and read.

  When the outside air temperature is high, the main controller 35 corrects the standard valve opening degree read from the showcase side controller 36 in the direction of expanding, and the outside air temperature is low. The standard valve opening is corrected and changed in the direction of reduction. In the case of the embodiment, when the outside air temperature rises to 30 ° C. or more, 150 pulses are added to the standard valve opening degree at the time of starting and the standard valve opening degree after starting (change amount), and the outside air temperature falls. When the temperature becomes 10 ° C. or lower, 50 pulses are subtracted from the standard valve opening at the start and the standard valve opening after the start (change amount).

  That is, when the outside air temperature is 30 ° C. or higher (equilibrium pressure high), the standard valve opening at the time of starting is expanded to 300 pulses, and the standard valve opening after the starting is expanded to 280 pulses. On the other hand, when the outside air temperature is 10 ° C. or lower (equilibrium pressure is low), the standard valve opening at the time of starting is reduced to 100 pulses, and the standard valve opening after the starting is reduced to 70 pulses.

  Moreover, from the state in which the outside air temperature rises to 15 ° C. or higher and further rises to 30 ° C., and from the state in which the outside air temperature falls to 25 ° C. or less, the air temperature further falls to 10 ° C. Until that time, the main controller 35 does not perform such correction. The fact that the arrows do not overlap on the left side of FIG. 4 means hysteresis.

  As described above, when the refrigerator-side controller 34 starts the compressor 11, the refrigerator-side controller 34 transmits data of a start notice (start notice) to the main controller 35. When the main controller 35 receives the start notice from the refrigerator-side controller 34, the valve opening at the time of starting the expansion valve 32 corrected as described above, or the valve opening not corrected (that is, the standard valve opening). Is sent to the showcase-side controller 36. The showcase-side controller 36 controls the expansion valve 32 to the valve opening degree at the start time of the expansion valve 32 received from the main controller 35 at the start time of the compressor 11 (actually from immediately before), and after the start, The expansion valve 32 is controlled to the received valve opening after starting.

  Thus, the valve opening degree of the expansion valve 32 at the time of starting the compressor 11 is changed based on the outside air temperature, and the valve opening degree of the expansion valve 32 is changed in a situation where the outside air temperature is high and the equilibrium pressure of the refrigerant circuit 1 is high. This expands to prevent an abnormal increase in the high-pressure side pressure HP, and the starting load of the compressor 11 can be reduced. In addition, the valve opening degree of the expansion valve 32 is low when the outside air temperature is low and the equilibrium pressure is low. It is possible to prevent the occurrence of short cycles due to excessive cooling performance.

  In addition, when the data about the valve opening corrected from the main controller 35 cannot be received, the showcase-side controller 36 controls the expansion valve 32 with the standard valve opening held by itself. That is, in the case of the embodiment, the standard valve opening degree of the expansion valve 32 is held by the showcase side controller 36 of the showcase 4, so that a communication abnormality has occurred between the main controller 35 and the showcase side controller 36. Even in the case, the showcase-side controller 36 can set the expansion valve 32 to the standard valve opening degree without any trouble from the start time of the compressor 11 to after the start.

  In the embodiment, the low pressure side pressure LP is controlled within the target range by the zone control. However, the present invention is not limited to this, and the present invention is effective even if it is controlled to the target value by so-called PID control or the like. Moreover, each numerical value shown in the Example is not limited to them, and should be appropriately changed according to the scale and application of the refrigeration apparatus.

C Control device (control means)
R Refrigeration apparatus 1 Refrigerant circuit 3 Refrigerator 4 Showcase 8, 9 Refrigerant piping 11 Compressor 24 Intercooler 28 Gas cooler 32 Expansion valve 33 Evaporator 34 Refrigerator side controller (refrigerator side control means)
35 Main controller (main control means)
36 Showcase side controller (showcase side control means)

Claims (4)

In a refrigeration system in which a refrigerant circuit is configured by a compressor, a gas cooler, an expansion valve, and an evaporator, and the high pressure side is a supercritical pressure.
A refrigerator having the compressor and the gas cooler, and a load device having the evaporator and an expansion valve,
Control means for controlling the compressor and the expansion valve;
The control unit is provided with the refrigerator, and includes a refrigerator side control unit that controls the compressor, and a load device side control unit that is provided in the load device and controls the expansion valve .
Standard valve opening of the expansion valve in which the load device control unit held by, by being corrected based on the outside air temperature, the valve opening degree of the expansion valve is changed,
The control means, based on the outside air temperature, changes the valve opening of the expansion valve at the time of starting the compressor before starting the compressor,
The load device side control means has a standard valve opening of the expansion valve at the time of starting the compressor and a standard valve opening of the expansion valve after the start of the compressor, and each standard valve opening is A refrigeration apparatus characterized in that each is corrected.   The refrigeration according to claim 1, wherein the control means expands the valve opening of the expansion valve when the outside air temperature is high, and reduces the valve opening of the expansion valve when the outside air temperature is low. apparatus. The control means is constructed from the refrigerator side control means, the load equipment side control means, and the main control means for transmitting and receiving data to and from the refrigerator side control means and the load equipment side control means,
The main control means receives data relating to the standard valve opening degree of the expansion valve from the load device side control means, receives data relating to the outside air temperature from the refrigerator side control means, and corrects the standard valve opening degree. In addition to sending the corrected data about the valve opening of the expansion valve to the load device side control means,
The refrigeration apparatus according to claim 2, wherein the load device side control means controls the expansion valve based on data relating to a valve opening degree of the expansion valve transmitted from the main control means. The refrigeration apparatus according to any one of claims 1 to 3, wherein carbon dioxide is used as a refrigerant.

Images