JP4169667B2 - Refrigeration system - Google Patents

Description

  The present invention relates to a refrigeration system for cooling a cooling storage facility in a store or the like, for example.

Conventionally, the inside (indoor) of a store such as a convenience store is air-conditioned and air-conditioned by an air conditioner. In addition, there are refrigerated or refrigerated open showcases and showcases with doors (cooling storage facilities) that display and sell products, and these are cooled by the refrigerator (patents). Reference 1).
JP 2002-174470 A

  By the way, the evaporator for cooling the interior of the showcase or the like as described above constitutes a refrigerant circuit together with a compressor, a condenser (these are installed in the refrigerator), and an expansion valve (a pressure reducing device). Further, the capacity of the compressor can be controlled by controlling the operating frequency, and the expansion valve is constituted by an electric expansion valve whose valve opening can be adjusted so that the degree of superheat of the refrigerant in the evaporator becomes constant. Controlled.

  On the other hand, for example, when the refrigerant circuit falls into a high load state, the high-pressure side pressure abnormally rises, so this type of system is provided with a high-pressure shut-off device. This high-pressure shut-off device protects the system by forcibly stopping the compressor when the high-pressure side pressure of the refrigerant circuit reaches a predetermined high-pressure shut-off set value. Cooling inside the cabinet will also stop.

  Therefore, conventionally, as a workaround, measures have been taken to reduce the capacity of the compressor (for example, lower the operating frequency) before the high pressure side pressure reaches the high pressure cutoff set value. However, the capacity reduction of the compressor still causes a lack of cooling capacity.

  The present invention has been made to solve the conventional technical problem, and provides a refrigeration system that can maintain the cooling capacity and the operation efficiency without any trouble while avoiding the high-load operation of the system.

According to a first aspect of the present invention, there is provided a refrigeration system having a refrigerant circuit including a compressor capable of capacity control, a condenser, an expansion valve, and an evaporator, and control means for controlling the compressor and the expansion valve. The control means adjusts the valve opening degree of the expansion valve so that the degree of superheat of the refrigerant in the evaporator is constant, and the high pressure side pressure reaches a predetermined protection set value based on the high pressure side pressure of the refrigerant circuit. When the pressure rises, the valve opening of the expansion valve is throttled until the high pressure side pressure drops below a predetermined reference value, and when the high pressure side pressure drops while the high pressure side pressure drops below the reference value, the valve In the process of expanding the opening degree and expanding the valve opening degree of the expansion valve, when the increase degree of the high-pressure side pressure becomes a predetermined specified value or less, the valve opening degree of the expansion valve is maintained, If the high-pressure side pressure drops in that state, the valve opening of the expansion valve After expansion, it is to return to the superheat constant control.

The refrigeration system of the invention of claim 2 is characterized in that, in the above invention, the control means has a high-pressure shut-off means for stopping the operation of the compressor when the high-pressure side pressure reaches a predetermined high-pressure cut-off set value, and the protection set value is It is a value lower than the high pressure cutoff set value.

In the present invention, in a refrigeration system including a compressor capable of capacity control, a condenser, an expansion valve, and an evaporator, and having a refrigerant circuit, the control means for controlling the compressor and the expansion valve is provided. The control means adjusts the valve opening of the expansion valve so that the degree of superheat of the refrigerant in the evaporator becomes constant, and when the high pressure side pressure rises to a predetermined protection set value based on the high pressure side pressure of the refrigerant circuit , Runode down the valve opening of the expansion valve, during high load operation, when the high-pressure side pressure of the refrigerant circuit is increased to protection level, throttle valve opening of the expansion valve, the evaporation temperature of the refrigerant in the evaporator The load can be reduced by lowering.

Thus, for example, when the control means has a high-pressure shut-off means for stopping the operation of the compressor when the high-pressure side pressure reaches a predetermined high-pressure cut-off set value as in claim 2 , the protection set value is set to the high-pressure cut-off set value. By setting the value to a lower value, it is possible to avoid a situation where the compressor is forcibly stopped by the high pressure shut-off means.

  In addition, although the refrigeration capacity of the refrigerator is reduced by reducing the opening degree of the expansion valve, the temperature difference between the evaporation temperature of the refrigerant in the evaporator and the temperature of the space to be cooled by the evaporator increases. As the cooling capacity of the engine increases, the actual decrease in cooling capacity can be minimized and high-load operation can be avoided. In particular, since the COP of the refrigeration system also decreases during high-load operation, a decrease in operating efficiency can be suppressed by reducing the load.

In this case, in the first aspect of the present invention, the control means throttles the valve opening degree of the expansion valve until the high pressure side pressure drops below a predetermined reference value, and the high pressure side pressure drops below the reference value. When the pressure decreases, the valve opening is expanded, and if the increase in the high-pressure side pressure becomes less than a specified value during the process of expanding the valve opening of the expansion valve, When the valve opening is maintained and the high-pressure side pressure drops in that state, after expanding the valve opening of the expansion valve, control is performed to return to constant superheat control so that high-load operation is further improved. It is possible to avoid with high accuracy.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a diagram illustrating a system configuration including a refrigerant circuit of a refrigeration system 1 according to an embodiment to which the present invention is applied. The refrigeration system 1 according to the embodiment includes, for example, air conditioning in a room 2 (in a store) of a convenience store, and the inside (cooled space) of a plurality of refrigeration cases 3 and 3 as cooling storage facilities installed therein. Cooling of the inside of the case 4 (the space to be cooled) is realized.

  In the embodiment, the first to sixth refrigeration cases 3 are installed in the refrigeration case 3, but only two of the first and second refrigeration cases 3 and 3 are shown in the drawing. The refrigeration cases 3 and 3 and the refrigeration case 4 are open showcases whose front and upper surfaces are open, as well as showcases whose openings are freely closed by transparent glass doors. The inside of the refrigerator is cooled to a refrigeration temperature (+ 3 ° C. to + 10 ° C.), chilled foods such as beverages and sandwiches are displayed, and the inside of the freezer case 4 is cooled to a freezing temperature (−10 ° C. to −20 ° C.). Frozen foods and frozen desserts such as ice cream are displayed.

  In this figure, 6 is an air conditioner (air conditioning system) provided with an air conditioning refrigerant circuit 7, and 8 is a refrigerant circuit 9 for cooling storage equipment for cooling the inside of the refrigerator cases 3, 3 and the freezing case 4. Is a cooling device (cooling storage equipment system). The air conditioner 6 includes indoor units 11 and 11 installed on the ceiling of the room 2 and an outdoor unit 12 installed outside the store, and an air-conditioning refrigerant circuit 7 is arranged between them. Has been.

  The air conditioning refrigerant circuit 7 includes two compressors (rotary compressors) 13A (frequency control operation by an inverter) and 13B (constant speed operation) installed in an exterior case of the outdoor unit 12, a check valve 5A, 5B, oil separator 10, four-way valve 14, heat source side heat exchanger 16, expansion valve (pressure reducing means comprising an electric expansion valve with adjustable valve opening) 17, 18, 19, and cascade heat exchanger 21, a check valve 22, an accumulator 23, and the like, and use side heat exchangers 27 and 27 installed on the indoor unit 11 side (air conditioning system).

  Reference numeral 26 denotes an outdoor unit controller (a controller that constitutes an air-conditioning system control means, which is constituted by a general-purpose microcomputer) for controlling equipment on the outdoor unit 12 side of the air conditioner 6 based on temperature and pressure. Yes, provided in the outdoor unit 12. Reference numeral 24 denotes a blower for ventilating the outside air to the heat source side heat exchanger 16 and is provided at a position corresponding to the heat source side heat exchanger 16 in the outdoor unit 12. This outdoor unit controller 26 forcibly stops the compressors 13A and 13B when the high-pressure side pressure of the air conditioning refrigerant circuit 7 rises to a predetermined high-pressure cutoff set value, and when it drops to a predetermined return set value. It has a high-pressure cutoff function (high-pressure cutoff means) that allows operation. This high-pressure shut-off function may be configured by a high-pressure shut-off device separate from the outdoor unit controller 26. Reference numeral 28 denotes an indoor unit controller (a controller that constitutes an air-conditioning system control means, which is constituted by a general-purpose microcomputer) for controlling equipment on the indoor unit 11 side of the air conditioner 6 based on temperature and pressure. Are provided in the indoor unit 11 (one is not shown). Reference numerals 15 and 15 denote blowers for ventilating the indoor 2 (in-store) air to the use side heat exchangers 27 and 27, provided at positions corresponding to the use side heat exchangers 27 and 27 in the indoor unit 11, respectively. It has been.

  The compressors 13A and 13B are connected in parallel to each other, and the discharge sides of the compressors 13A and 13B are joined via check valves 5A and 5B, respectively, and connected to one inlet of the four-way valve 14 ( Each check valve 5A, 5B has a four-way valve 14 direction as a forward direction). One outlet of the four-way valve 14 is connected to the inlet of the heat source side heat exchanger 16. The heat source side heat exchanger 16 includes an inlet side 16A having a relatively small flow resistance composed of a large number of parallel pipes and an outlet side 16B in which these are aggregated into a small number of parallel pipes or a single pipe. The outlet on the outlet side 16B of the heat source side heat exchanger 16 is connected to the inlet of the expansion valve 18 via the expansion valve 17, and the outlet of the expansion valve 18 is diverted across the indoor unit 11, so that each use side heat It is connected to the inlets of the exchangers 27 and 27.

  After the outlets of the use side heat exchangers 27 and 27 are joined, they cross the outdoor unit 12 and are connected to the other inlet of the four-way valve 14. The other outlet of the four-way valve 14 is connected to the accumulator 23 via the check valve 22. It is connected to the. And the exit of this accumulator 23 is connected to the suction side of compressor 13A, 13B. The check valve 22 has a forward direction on the accumulator 23 side.

  The piping between the expansion valves 17 and 18 is connected to the inlet of the expansion valve 19, and the outlet of the expansion valve 19 is connected to the inlet of the air conditioning side passage 21 </ b> A of the cascade heat exchanger 21. The outlet of the air conditioning side passage 21A of the cascade heat exchanger 21 is connected to the suction side of the compressors 13A and 13B via an accumulator 23.

  On the other hand, the cooling device 8 is provided with a refrigerant circuit 9 for cooling storage equipment between the outdoor unit 12 and the refrigeration cases 3 and 3 and the refrigeration case 4 installed in the room 2 (inside the store). The refrigerant circuit 9 for the cooling storage facility includes a first compressor (scroll compressor) 37, a condenser (heat exchanger) 38, and two four-way valves 39, 41 installed in the outer case of the outdoor unit 12. (The flow control means is constituted by these two four-way valves), the check valve 42, the oil separator 31, the receiver tank 36, etc., the refrigeration cases 3, 3 and the refrigeration cases 3, 3 Refrigerating evaporators 43 and 43 for cooling the inside of the refrigerator, expansion valves (electric expansion valves with adjustable valve opening) 44 and 44, electromagnetic valves 46, 46 and 47, check valves 48 (for the cooling storage system) A refrigeration system constituting a part), a freezing evaporator 49 that is installed in the freezing case 4 and cools the inside of the freezing case 4, an expansion valve (an electric expansion valve whose valve opening degree can be adjusted) 51, a solenoid valve 52, 53, second compressor (rotary Presser) 54, check valve 30, and, and a refrigeration system) or the like constituting a part of the oil separator 45 (cooled storage facilities system.

  32 is a refrigerator controller (a controller constituting a cooling storage facility system control means, comprising a general-purpose microcomputer) that controls equipment on the outdoor unit 12 side of the cooling device 8 based on temperature and pressure, The outdoor unit 12 is provided. The refrigerator controller 32 forcibly stops the compressors 37 and 54 when the high-pressure side pressure HP of the refrigerant circuit 9 for the cooling storage facility rises to a predetermined high-pressure cut-off set value HP1, and reaches a predetermined return set value. It has a high-pressure shut-off function (high-pressure shut-off means) that allows operation when it descends. The high-pressure shut-off function may be configured by a high-pressure shut-off device that is separate from the refrigerator controller 32. Reference numeral 35 denotes a blower for passing outside air through the condenser 38, and is provided at a position corresponding to the condenser 38 of the outdoor unit 12. In addition, 50 is a refrigeration case controller (a controller that constitutes a cooling storage facility system control means, configured by a general-purpose microcomputer) that controls equipment on the refrigeration case 3, 3 side based on temperature and pressure, Refrigerating cases 3 and 3 are respectively provided (one is not shown). Further, 55 is a refrigeration case controller (a controller constituting a cooling storage facility system control means, which is constituted by a general-purpose microcomputer) that controls equipment on the refrigeration case 4 side based on temperature and pressure. 4 is provided. The refrigeration case controller 50, the refrigeration case controller 55, and the refrigerator controller 32 constitute control means in the present invention.

  Reference numerals 20 and 20 denote blowers for ventilating the cold air in the refrigerator cases 3 and 3 to the evaporators 43 and 43, respectively. The refrigerators 43 and 43 in the refrigerator cases 3 and 3, respectively. It is provided at the corresponding position. Reference numeral 25 denotes a blower for passing cold air in the refrigerator case 4 through the freezer evaporator 49, and is provided at a position corresponding to the freezer evaporator 49 in the freezer case 4.

  The discharge side of the compressor 37 is connected to one inlet of the four-way valve 39 via the oil separator 31, and one outlet of the four-way valve 39 is connected to the inlet of the condenser 38. The condenser 38 includes an inlet side 38A having a relatively small flow resistance composed of a large number of parallel pipes, and an outlet side 38B in which these are aggregated into a small number of parallel pipes or a single pipe. The outlet on the outlet side 38B of the condenser 38 is connected to the inlet of the receiver tank 36, and the outlet of the receiver tank 36 is connected to one inlet of the four-way valve 41.

  One outlet of the four-way valve 41 is connected to the inlet of the case side passage 21 </ b> B of the cascade heat exchanger 21. The cascade heat exchanger 21 exchanges heat between the refrigerant that passes through the air conditioning side passage 21A and the case side passage 21B that are formed inside, thereby cooling the low pressure side of the air conditioning refrigerant circuit 7 and cooling it. The high-pressure side of the storage facility refrigerant circuit 9 is thermally coupled.

  The outlet of the case side passage 21 </ b> B of the cascade heat exchanger 21 is connected to the other inlet of the four-way valve 39, and the other outlet of the four-way valve 39 is connected to the other inlet of the four-way valve 41. The other outlet of the four-way valve 41 exits from the outdoor unit 12 and branches into the room 2 (inside the store). One of the branched pipes is further branched, and one of the branched pipes is connected to the inlet of the expansion valve 44 via the solenoid valves 47 and 46 in order, and the outlet of the expansion valve 44 is the evaporator for refrigeration of the first refrigeration case 3. 43 is connected to the entrance. The other is connected to the inlet of the expansion valve 44 via the electromagnetic valve 46, and the outlet of the expansion valve 44 is connected to the inlet of the refrigeration evaporator 43 of the second refrigeration case 3.

  The other pipe branched into the room 2 (inside the store) is connected to the inlet of the expansion valve 51 via the electromagnetic valve 52, and the outlet of the expansion valve 51 is connected to the inlet of the refrigeration evaporator 49. The solenoid valve 53 is connected in parallel to the series circuit of the solenoid valve 52 and the expansion valve 51.

  The outlet of the refrigeration evaporator 49 is connected to the suction side of the compressor 54 via the check valve 30 (the check valve 30 is in the forward direction on the compressor 54 side). The compressor 54 is a compressor having a smaller output than the compressor 37, and its discharge side is connected to the suction side of the compressor 37 via an oil separator 45. That is, the compressor 37 and the compressor 54 are connected in series on the refrigerant circuit. The outlets of the refrigeration evaporators 43 and 43 are connected to the outlet side of the oil separator 45 on the discharge side of the compressor 54 after joining. The check valve 48 is connected between the check valve 30 before the compressor 54 and the solenoid valves 46 and 47, and the directions of the solenoid valves 46 and 47 are the forward directions. Further, the check valve 42 is connected between the suction side of the compressor 37 and the pipe that exits the oil separator 31, and the oil separator 31 direction is the forward direction. A predetermined amount of refrigerant such as R-410A and R-404A is sealed in the refrigerant circuits 7 and 9, for example.

  The operation of the refrigeration system 1 of the present invention will be described with the above configuration. The compressors 37 and 13A are controlled in operating frequency by an inverter (capacity control), and the compressor 13B and the compressor 54 are operated at a constant speed. The operation of the entire refrigeration system 1 is controlled by a main controller (main control means) 56 composed of a general-purpose microcomputer.

  Here, the main controller 56 is connected to the outdoor unit controller 26, the indoor unit controller 28, the refrigerator controller 32, the refrigeration case controller 50, and the refrigeration case controller 55 so as to be able to perform data communication. Receive and collect status data. Then, based on the received data, an optimum operation pattern at that time, which will be described later, is determined, and the data relating to this optimum operation pattern and the operation data of each device are stored in the outdoor unit controller 26, the indoor unit controller 28, the refrigerator controller 32, and the refrigerator. The data is transmitted to the case controller 50 and the refrigeration case controller 55. The outdoor unit controller 26, the indoor unit controller 28, the refrigerator controller 32, the refrigeration case controller 50, and the refrigeration case controller 55 are described later on the basis of the data regarding the optimum operation pattern received from the main controller 56 and the operation data of each device. Perform the action.

(1) Optimal operation pattern 1: Air conditioner cooling operation (Fig. 1)
First, when the main controller 56 determines that the cooling operation of the air conditioner 6 is optimal in summer or the like, the data related to the optimal operation pattern 1 is the outdoor unit controller 26, the indoor unit controller 28, the refrigerator controller 32, the refrigeration case controller. 50 and the refrigeration case controller 55.

  Based on the received data, the outdoor unit controller 26 communicates the one inlet of the four-way valve 14 with one outlet and the other inlet with the other outlet. Further, the expansion valve 17 is fully opened. Then, the compressors 13A and 13B are operated. The outdoor unit controller 26 controls the capacity by adjusting the operating frequency of the compressor 13A.

  When the compressors 13A and 13B are operated, the high-temperature and high-pressure gas refrigerant discharged from the discharge sides of the compressors 13A and 13B enters the inlet side 16A of the heat source side heat exchanger 16 via the four-way valve 14. Outside air is ventilated by the air blower 24 to the heat source side heat exchanger 16, and the refrigerant dissipates heat here to be condensed and liquefied. That is, in this case, the heat source side heat exchanger 16 functions as a condenser. The liquid refrigerant exits from the outlet side 16B from the inlet side 16A of the heat source side heat exchanger 16 via the outlet side 16B. And after passing the expansion valve 17, it branches. One of the branches reaches the expansion valve 18, where it is throttled to a low pressure (decompression), and then branches into each use side heat exchanger 27, 27 and evaporates there.

  The air in the room 2 (inside the store) is ventilated by the blowers 15 and 15 through the use side heat exchangers 27 and 27, and the air in the room 2 is cooled by an endothermic action due to evaporation of the refrigerant. Thereby, the room 2 (inside the store) is cooled. The low-temperature gas refrigerant that has exited from the use side heat exchangers 27 and 27 merges, and then passes from the other inlet of the four-way valve 14 to the other outlet, and sequentially passes through the check valve 22 and the accumulator 23, and then enters the compressor 13A. The circulation sucked into the suction side of 13B is repeated. The indoor unit controller 28 blows air to the use side heat exchangers 27 and 27 so that the temperature of the room 2 (inside the store) becomes the set temperature based on the temperature of the use side heat exchangers 27 and 27 and the air temperature sucked into the use side heat exchangers 27 and 27. 15 and 15 are controlled. Information from the indoor unit controller 28 is transmitted to the main controller 56, and the outdoor unit controller 26 controls the operation of the compressors 13A and 13B based on this information.

  The other refrigerant branched after passing through the expansion valve 17 reaches the expansion valve 19 where it is throttled to a low pressure (decompression), and then flows into the air conditioning side passage 21A of the cascade heat exchanger 21 where it evaporates. The cascade heat exchanger 21 is cooled by the endothermic action due to the evaporation of the refrigerant in the air-conditioning refrigerant circuit 7 and becomes a low temperature. The low-temperature gas refrigerant exiting the cascade heat exchanger 21 repeats circulation through the accumulator 23 and sucked into the suction sides of the compressors 13A and 13B.

  The outdoor unit controller 26 is configured such that the refrigerant temperature at the entrance / exit of the use side heat exchangers 27, 27, the temperature of the use side heat exchangers 27, 27, the refrigerant temperature at the entrance / exit of the cascade heat exchanger 21, or the cascade heat exchanger. The valve openings of the expansion valves 18 and 19 are adjusted so as to achieve an appropriate degree of superheat based on the temperature of 21.

  On the other hand, the refrigerator controller 32 causes the one inlet of the four-way valve 39 of the refrigerant circuit 9 for the cooling storage facility of the cooling device 8 to communicate with one outlet and the other inlet to communicate with the other outlet. Further, the one inlet of the four-way valve 41 is communicated with one outlet, and the other inlet is communicated with the other outlet. Then, the compressor 37 and the compressor 54 are operated. The high-temperature and high-pressure gas refrigerant discharged from the compressor 37 is separated by the oil separator 31 and then enters the inlet side 38 </ b> A of the condenser 38 through the four-way valve 39. Outside air is also passed through the condenser 38 by the blower 35, and the refrigerant flowing into the condenser 38 dissipates heat and condenses there.

  The refrigerant that has passed through the inlet side 38A of the condenser 38 reaches the outlet side 38B and exits there. The refrigerant from the condenser 38 enters the receiver tank 36 from the inlet side of the receiver tank 36, and is temporarily stored therein to separate the gas / liquid. The separated liquid refrigerant exits from the outlet of the receiver tank 36, passes through the four-way valve 41, and then enters the case side passage 21 </ b> B of the cascade heat exchanger 21. The refrigerant in the refrigerant circuit 9 for the cooling storage facility that has entered the case-side passage 21B is cooled by the cascade heat exchanger 21 that is at a low temperature due to the evaporation of the refrigerant in the air-conditioning refrigerant circuit 7 as described above, and is further in a supercooled state. Increase.

  The refrigerant supercooled in the cascade heat exchanger 21 is branched after sequentially passing through the four-way valve 39 and the four-way valve 41, one is further branched, and the other is sequentially passed through the electromagnetic valves 47 and 46 and then the expansion valve 44. After being squeezed there (reduced pressure), it flows into the refrigeration evaporator 43 of the first refrigeration case 3 and evaporates there. The other branched part passes through the electromagnetic valve 46 and reaches the expansion valve 44. After being throttled (decompression), it flows into the refrigerating evaporator 43 of the second refrigerating case 3 and evaporates there. The refrigeration evaporators 43, 43 are respectively ventilated and circulated by the blowers 20, 20, and the air in the refrigeration cases 3, 3 is circulated, and the internal air is cooled by the endothermic action due to the evaporation of the refrigerant. Thereby, the refrigerator cooling of the refrigeration cases 3 and 3 is performed. The low-temperature gas refrigerant exiting the refrigeration evaporators 43, 43 joins and then reaches the outlet side of the oil separator 45 of the compressor 54.

  The other refrigerant branched out of the cascade heat exchanger 21 passes through the electromagnetic valve 52 and reaches the expansion valve 51. After being throttled (decompression), it flows into the refrigeration evaporator 49 where it evaporates. The internal air of the refrigeration case 4 is also ventilated and circulated by the blower 25 to the freezing evaporator 49, and the internal air is cooled by the endothermic action due to the evaporation of the refrigerant. Thereby, the inside cooling of the freezing case 4 is performed.

  The low-temperature gas refrigerant exiting the freezing evaporator 49 passes through the check valve 30 and reaches the compressor 54 where it is compressed and pressure on the outlet side of the refrigerating evaporators 43 and 43 (low pressure side pressure of the refrigerating system). After the pressure has been increased to about 50 ° C., the oil is discharged from the compressor 54, and the oil is separated by the oil separator 45, and then merges with the refrigerant from the refrigeration evaporators 43 and 43. The merged refrigerant repeats circulation that is sucked into the suction side of the compressor 37.

  Thus, since the high pressure side refrigerant of the refrigerant circuit 9 for the cooling storage facility can be supercooled by the low pressure side refrigerant of the air conditioning refrigerant circuit 7 flowing through the air conditioning side passage 21A of the cascade heat exchanger 21, the refrigeration case 3, 3 and the cooling capacity in the evaporators 43, 43, 49 of the refrigeration case 4 and the operation efficiency of the refrigerant circuit 9 for the cooling storage facility are improved. In this case, since the refrigerant on the high pressure side of the refrigerant circuit 9 for the cooling storage facility flows into the case side passage 21B of the cascade heat exchanger 21 via the condenser 38, the degree of superheat of the air conditioning refrigerant circuit 7 is also in an appropriate range. Can be maintained.

  Further, the pressure of the refrigerant discharged from the refrigeration evaporator 49 of the refrigerant circuit 9 for the cooling storage facility is lower than the refrigerant discharged from the refrigeration evaporators 43 and 43 because its evaporation temperature is lowered, but the refrigeration evaporation. Before being merged with the refrigerant discharged from the coolers 43, 43, the compressor 54 compresses and pressurizes the interior of the refrigeration cases 3, 3 and the freezing case 4 smoothly by the respective evaporators 43, 43, 49. While cooling, the pressure of the refrigerant sucked into the compressor 37 of the refrigerant circuit 9 for the cooling storage facility can be adjusted so that the operation can be performed without any trouble.

  Here, the refrigeration case controller 50 is the temperature inside the refrigeration cases 3 and 3 (actual temperature of the space to be cooled), the discharge cold air temperature through the refrigeration evaporators 43 and 43, or the suction to the refrigeration evaporators 43 and 43. Based on the cold air temperature, the refrigerant temperature on the outlet side of the refrigeration evaporator 43, or the temperature of the refrigeration evaporator 43, the valve openings of the expansion valves 44 and 44 are adjusted. Thereby, the superheat degree of the refrigerant in each of the refrigeration evaporators 43 and 43 is set to an appropriate value (constant superheat degree) while keeping the inside of the refrigerators of the refrigeration cases 3 and 3 at the above-described refrigeration temperature.

  That is, when the internal temperature of the refrigeration case 3 is high and cooling is necessary, the refrigeration case controller 50 increases the valve opening degree of the expansion valve 44 corresponding to the refrigeration evaporator 43 of the refrigeration case 3 to refrigerate. More refrigerant flows through the evaporator 43. When the internal temperature of the refrigeration case 3 is low and cooling is not required much, the valve opening of the expansion valve 44 is reduced to reduce the amount of refrigerant flowing into the refrigeration evaporator 43. Thereby, while controlling the internal temperature of each refrigeration case 3 and 3 to each setting temperature, the superheat degree of the refrigerant | coolant in the evaporator 43 for refrigeration is kept constant, and when cooling is unnecessary (for example, lower than setting temperature) The expansion valve 44 is finally closed when the internal temperature falls below a predetermined lower limit temperature).

  The refrigeration case controller 55 is configured such that the inside temperature of the refrigeration case 4, the temperature of the discharged cold air passing through the refrigeration evaporator 49, the temperature of the suction cold air into the refrigeration evaporator 49, the refrigerant temperature on the outlet side of the refrigeration evaporator 49, Alternatively, the valve opening of the expansion valve 51 is adjusted based on the temperature of the freezing evaporator 49. As a result, while maintaining the inside of the freezing case 4 to be cooled to the above-described freezing temperature, an appropriate degree of superheat (constant superheat) is obtained. The control of the expansion valve 51 is the same as that of the expansion valve 43 described above.

  The refrigerator controller 32 controls the operating frequency (capacity) of the compressor 37 based on the low pressure LP of the refrigerant circuit 9 for the cooling storage facility. In this case, a set value for the low pressure side pressure defined in advance is defined in the refrigerator controller 32. An upper limit value and a lower limit value are set above and below the set value with a certain differential, and compression is performed when the low-pressure side pressure LP of the refrigerant circuit 9 for the cooling storage facility decreases to the lower limit value. The operating frequency of the machine 37 is lowered to a low frequency.

  In this way, when the low pressure side pressure LP of the refrigerant circuit 9 for the cooling storage facility is reduced to the lower limit value, the refrigerant inflow amount to the refrigeration evaporator 43 of the refrigeration case 3 is reduced by lowering the operating frequency of the compressor 37. Therefore, the cooling capacity is also reduced. As a result, the refrigeration case controller 50 controls the expansion valve 44 so as to expand the valve opening, so that a decrease in the low-pressure side pressure of the refrigerant circuit 9 for the cooling storage facility is prevented. Therefore, the COP of the compressor 37 is prevented from decreasing due to the decrease in the low-pressure side pressure.

  When all the expansion valves 44, 44, 51 are fully closed and the low-pressure side pressure LP is lowered to an extremely low value, the compressor 37 is stopped. Thereafter, if any one of the expansion valves 44, 44, 51 is opened and the low pressure side pressure rises, the refrigerator controller 32 starts the compressor 37, and when the low pressure side pressure rises to the upper limit value, the compressor 37 The operation frequency is increased to a high frequency.

(2-1) Control 1 during high load operation of refrigerant circuit for cooling storage facility 1
On the other hand, the refrigerator controller 32 is configured so that the refrigerant circuit 9 for the cooling storage facility becomes in a high load state due to factors such as an increase in the internal load of the refrigeration case 3 or an increase in the ambient temperature. When HP rises to a predetermined high pressure cutoff set value HP1, the compressors 37 and 54 are forcibly stopped. Thereby, the refrigerant circuit 9 for cooling storage facilities is protected. When the high pressure side pressure HP is lowered to a predetermined return setting value, the operation of the compressors 37 and 54 is permitted. However, when the compressors 37 and 54 are forcibly stopped, the refrigeration case 3 or There arises an inconvenience that cooling of the inside of the freezing case 4 is stopped.

  In view of this, the refrigerator controller 32 predefines a protection set value HP2 for the high pressure side pressure HP as a value lower than the high pressure cutoff set value HP1. And when the refrigerant circuit 9 for cooling storage facilities falls into a high load state and the high-pressure side pressure HP rises to the protection set value HP2, it notifies the refrigeration case controller 50 and the refrigeration case controller 55 to that effect. When receiving the notification from the refrigerator controller 32, the refrigeration case controller 50 and the refrigeration case controller 55 reduce the opening degrees of the expansion valves 44 and 44 and the expansion valve 51, respectively. In this case, the valve opening is gradually reduced at a predetermined step rate per predetermined time.

  As the opening degree of the expansion valves 44, 44, 51 is reduced in this way, the degree of superheat of the refrigerant in the refrigeration evaporator 43 and the refrigeration evaporator 49 increases, and the evaporation temperature decreases. The load on the storage facility refrigerant circuit 9 is reduced, and the high-pressure side pressure HP decreases. The refrigeration case controller 50 and the refrigeration case controller 55 sequentially receive the data of the high pressure side pressure HP from the refrigerator controller 32, and the above described until the high pressure side pressure HP of the refrigerant circuit 9 for the cooling storage facility falls below a predetermined reference value HP3. In this manner, the valve openings of the expansion valves 44, 44, 51 are reduced, and the valve opening at that time is maintained when the expansion valve 44, 44, 51 is reduced to a reference value HP3 or less.

  Next, the refrigeration case controller 50 and the refrigeration case controller 55 have the expansion valve 44 when the high pressure side pressure HP decreases while the high pressure side pressure HP decreases to the reference value HP3 or less and the valve opening degree is maintained. , 44 and 51 are expanded. Also in this case, expansion is performed in stages at a rate of a predetermined step per predetermined time. By this expansion, the high pressure side pressure HP tends to increase again, but in the process of expanding the valve opening degree of the expansion valves 44, 44, 51, the increase degree of the high pressure side pressure HP becomes equal to or less than a predetermined specified value dHP. In that case, the valve openings of the expansion valves 44, 44, 51 are maintained at that time. When the high pressure side pressure HP decreases in this state, the valve opening degree of the expansion valves 44, 44, 51 is expanded, and then the normal superheat degree constant control described above is restored.

  Thus, it is possible to avoid the high load operation of the refrigerant circuit 9 for the cooling storage facility with high accuracy while avoiding the situation where the compressors 37 and 54 are forcibly stopped due to the high pressure cutoff function. Although the refrigerating capacity of the refrigerator is reduced by reducing the opening degree of the expansion valves 44, 44, 51, the evaporating temperature of the refrigerant in the refrigerating evaporator 43 and the refrigerating evaporator 49 and the refrigerating case cooled to it. 3 and the internal temperature of the freezing case 4 increase, so that the cooling capacity of each of the evaporators 43 and 49 increases. For this reason, a decrease in actual cooling capacity can be minimized. In particular, since the COP of the refrigerant circuit also decreases during high load operation, a decrease in operating efficiency can be suppressed by reducing the load.

(2-2) Control 2 during high load operation of refrigerant circuit for cooling storage facility 2
In addition, you may further simplify control of the valve opening degree of the expansion valve 44, 44, 51 mentioned above. Also in this case, when the refrigerant circuit 9 for the cooling storage facility falls into a high load state and the high pressure side pressure HP rises to the protection set value HP2, this is notified to the refrigeration case controller 50 and the refrigeration case controller 55. . When receiving the notification from the refrigerator controller 32, the refrigeration case controller 50 and the refrigeration case controller 55 reduce the opening degrees of the expansion valves 44 and 44 and the expansion valve 51, respectively. In this case, the valve opening is gradually reduced at a predetermined step rate per predetermined time.

  The refrigeration case controller 50 and the refrigeration case controller 55 sequentially receive the data of the high pressure side pressure HP from the refrigerator controller 32, and the above described until the high pressure side pressure HP of the refrigerant circuit 9 for the cooling storage facility falls below a predetermined reference value HP3. As described above, the valve opening degree of the expansion valves 44, 44, 51 is reduced, and control is performed so as to return to the normal superheat degree constant control described above when the reference value HP3 or less is reached. According to such a configuration, the high load operation of the refrigerant circuit 9 for the cooling storage facility can be avoided while avoiding the forced stop of the compressors 37 and 54 with relatively simple control.

(3) Optimal operation pattern 2: Heating operation of the air conditioner (Fig. 2)
Next, the heating operation of the air conditioner 6 in winter will be described with reference to FIG. When the main controller 56 determines that the heating operation of the air conditioner 6 is optimal, the data regarding the optimal operation pattern 2 includes the outdoor unit controller 26, the indoor unit controller 28, the refrigerator controller 32, the refrigeration case controller 50, and the refrigeration case controller 50. It is transmitted to the case controller 55.

  Based on the received data, the outdoor unit controller 26 switches so that one inlet of the four-way valve 14 communicates with the other outlet and the other inlet communicates with one outlet. The expansion valve 17 is fully closed and the expansion valve 18 is fully opened. Then, the compressors 13A and 13B are operated. When the compressors 13A and 13B are operated, the high-temperature and high-pressure gas refrigerant discharged from the discharge sides of the compressors 13A and 13B enters the use-side heat exchangers 27 and 27 through the four-way valve 14 from the oil separator 10. The air in the room 2 (inside the store) is ventilated by the blowers 15 and 15 through the use side heat exchangers 27 and 27 as described above, and the refrigerant dissipates heat and heats the air in the room 2 while condensing itself. Liquefaction. Thereby, the room 2 (inside the store) is heated.

  The refrigerant liquefied in the use side heat exchangers 27, 27 exits from the use side heat exchangers 27, 27, passes through the expansion valve 18, reaches the expansion valve 19, where it is throttled to a low pressure (decompression), and then cascaded. After flowing into the air conditioning side passage 21A of the heat exchanger 21 and evaporating and absorbing heat there, the circulation is repeated through the accumulator 23 and sucked into the suction sides of the compressors 13A and 13B.

  The outdoor unit controller 26 adjusts the valve opening degree of the expansion valve 19 based on the refrigerant temperature at the inlet / outlet of the cascade heat exchanger 21 or the temperature of the cascade heat exchanger 21 so that the degree of superheat is appropriate. The indoor unit controller 28 also blows air to the use side heat exchangers 27 and 27 so that the temperature of the room 2 (inside the store) is set to the set temperature based on the temperature of the use side heat exchanger 27 and the air temperature sucked into the use side heat exchanger 27. 15 and 15 are controlled. Further, the operation of the compressors 13A and 13B is controlled by the outdoor unit controller 26 as described above.

  On the other hand, the refrigerator controller 32 switches the one-way inlet 39 of the four-way valve 39 of the refrigerant circuit 9 for the cooling storage facility of the cooling device 8 to communicate with the other outlet, and the other inlet communicates with one outlet. The one inlet 41 is switched to communicate with the other outlet, and the other inlet is communicated with one outlet. The other solenoid valves and the like are the same as in the cooling operation described above. That is, the electromagnetic valves 46, 46, 47 and 52 are opened, and the compressors 37 and 54 are operated.

  Thus, the high-temperature and high-pressure gas refrigerant discharged from the compressor 37 sequentially passes through the four-way valves 39 and 41 and first enters the case-side passage 21B of the cascade heat exchanger 21. That is, the high-temperature and high-pressure gas refrigerant discharged from the compressor 37 is directly supplied to the case side passage 21 </ b> B of the cascade heat exchanger 21 before going to the condenser 38. Since the refrigerant of the refrigerant circuit 9 for the cooling storage facility that has entered the case side passage 21B dissipates heat in the cascade heat exchanger 21, it is cooled by the refrigerant of the air conditioning refrigerant circuit 7 that evaporates in the air conditioning side passage 21A as described above. Deliver heat. As a result, the refrigerant in the air conditioning refrigerant circuit 7 pumps up the waste heat of the refrigerant in the refrigerant circuit 9 for the cooling storage facility.

  The refrigerant that has passed through the case side passage 21B of the cascade heat exchanger 21 then enters the inlet side 38A of the condenser 38 via the four-way valve 39. Outside air is also passed through the condenser 38 by the blower 35, and the refrigerant flowing into the condenser 38 dissipates heat and condenses there.

  The refrigerant that has passed through the inlet side 38A of the condenser 38 reaches the outlet side 38B and exits there. The refrigerant from the condenser 38 enters the receiver tank 36 from the inlet side of the receiver tank 36, and is temporarily stored therein to separate the gas / liquid. The separated liquid refrigerant exits from the outlet of the receiver tank 36, passes through the four-way valve 41, and then branches, and goes to the electromagnetic valves 46, 47, and 52 as described above.

  By such operation, during the heating operation of the air conditioning refrigerant circuit 7 of the air conditioner 6, the waste heat of the high-pressure side refrigerant of the refrigerant circuit 9 for the cooling storage facility is recovered by the cascade heat exchanger 21 and the air conditioning refrigerant circuit 7. It becomes possible to convey to the use side heat exchangers 27, 27. As a result, the heating capacity of the air conditioner 6 can be improved, and the efficiency of the refrigeration system 1 that cools the indoor air conditioning and the refrigeration cases 3 and 3 and the refrigeration case 4 as a whole is improved. Energy saving can be achieved.

  Particularly in this case, since the refrigerant on the high pressure side of the refrigerant circuit 9 for the cooling storage facility is passed through the cascade heat exchanger 21 before the condenser 38, the waste heat recovery from the high pressure side refrigerant of the refrigerant circuit 9 for the cooling storage facility is performed. The heating capacity in the use side heat exchangers 27 and 27 of the air conditioning refrigerant circuit 7 can be further improved.

  Here, when the air conditioner 6 is lightly loaded, such as when the store 2 is relatively warm, the outdoor unit controller 26 reduces the refrigerant flow rate by reducing the valve opening of the expansion valve 19, so that cascade heat exchange is performed. However, in the present invention, the refrigerant on the high pressure side of the refrigerant circuit 9 for the cooling storage facility is passed through the cascade heat exchanger 21 and then condensed. Therefore, when the heat radiation amount of the refrigerant in the cascade heat exchanger 21 of the cooling storage facility refrigerant circuit 9 becomes excessive during the heating operation of the air conditioning refrigerant circuit 7, the condenser 38. The excess amount of heat is released at. As a result, a stable waste heat recovery operation can be realized.

  Further, as described above, the flow paths are switched using the four-way valves 39 and 41, and the cooling air circuit 7 is connected to the condenser 38 and the outlet of the refrigerant circuit 9 for the cooling storage facility during the cooling operation and the heating operation. The flow direction of the refrigerant flowing through the receiver tank 36 is the same. As a result, the pressure loss of the refrigerant flowing in the refrigerant circuit 9 for the cooling storage facility is reduced compared to the case where the refrigerant flows in the condenser 38 and the receiver tank 36 are opposite between the cooling operation and the heating operation. It becomes possible to prevent or suppress, and efficient operation becomes possible. In particular, since the flow path is switched by the two four-way valves 39, 41, the configuration of the refrigerant circuit 9 for the cooling storage facility can be simplified.

(4) Optimal operation pattern 3: Control when almost no heat radiation is required in the cascade heat exchanger of the cooling device during heating operation of the air conditioner (FIG. 3)
Here, during the heating operation of the air conditioner 6 as described above, if the indoor (in-store) air load is further reduced and the heating capacity becomes excessive, the outdoor unit controller 26 determines the compressor 13B based on the indoor temperature information. The operating frequency is lowered and the heating capacity is lowered. On the other hand, even if such control is performed and an excessive amount of heat is released in the condenser 38 as described above, the heat radiation in the cascade heat exchanger 21 of the refrigerant circuit 9 for the cooling storage facility of the cooling device 8 is reduced. In a situation that is hardly required, the heating capacity of the air conditioner 6 becomes excessive with the circuit of FIG.

  In such a case, the refrigerator controller 32 switches the four-way valves 39 and 41 from the state shown in FIGS. That is, in this case, the refrigerator controller 32 switches the four-way valve 39 so that the one inlet communicates with one outlet and the other inlet communicates with the other outlet. The one-way inlet of the four-way valve 41 is switched to one outlet and the other inlet is switched to communicate with the other outlet.

  As a result, the high-temperature and high-pressure refrigerant discharged from the compressor 37 passes through the condenser 38 and dissipates heat in the same manner as in FIG. 1, and then flows into the cascade heat exchanger 21, so that the air-conditioning refrigerant circuit 7 can be avoided from being overheated by the cascade heat exchanger 21.

  In the embodiment, the present invention has been described with a refrigeration system that cools indoor air-conditioning and cooling storage equipment in a convenience store. However, the present invention is not limited thereto, and the present invention is also effective when only cooling storage equipment is cooled. . Further, in the embodiment, the capacity control of the compressor is realized by controlling the operation frequency by the inverter. However, the present invention is not limited to this, and various capacity controls can be applied. Furthermore, when the evaporating temperature of the refrigerant in the refrigeration evaporator 43 can be measured regardless of the inside temperature TP and the set temperature TS, the change control of the set value LPS is based on the evaporating temperature and the set temperature. You may go. Further, in the above embodiment, the compressors 37 and 13A are controlled in capacity by controlling the operation frequency by an inverter. However, the meaning of capacity control is not limited to this, and a plurality of compressors are connected in parallel (for example, a plurality of constants). This includes the case of switching the number of units operated by parallel connection of high-speed compressors, parallel connection of one constant-speed compressor and one inverter-controlled compressor, or controlling the operation frequency in addition to that.

It is a figure explaining the system configuration containing the refrigerant circuit of the refrigerating system of the example to which the present invention is applied (at the time of cooling operation of the air conditioner). It is a figure explaining the heating operation of the air conditioner of the refrigeration system of the Example to which this invention is applied. It is a figure explaining the operation | movement when hardly radiating heat in the cascade heat exchanger of the cooling device at the time of the heating operation of the air conditioner of the refrigeration system of the Example to which this invention is applied.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Refrigeration system 3 Refrigeration case 4 Refrigeration case 6 Air conditioner 7 Air-conditioning refrigerant circuit 8 Cooling device 9 Refrigerating circuit for cooling storage equipment 13A, 13B, 37, 54 Compressor 14 Four-way valve 16 Heat source side heat exchanger 21 Cascade heat exchange 28 Use side heat exchanger 32 Refrigerator controller 38 Condenser 39, 41 Four-way valve (flow path control means)
43 Refrigerating evaporator 44, 51 Expansion valve 49 Refrigerating evaporator 50 Refrigerating case controller 55 Refrigerating case controller

Claims (2)

In a refrigeration system in which a refrigerant circuit is configured by including a compressor capable of controlling capacity, a condenser, an expansion valve, and an evaporator,
  Control means for controlling the compressor and the expansion valve;
  The control means adjusts the valve opening of the expansion valve so that the degree of superheat of the refrigerant in the evaporator is constant, and the high pressure side pressure is set to a predetermined protection setting value based on the high pressure side pressure of the refrigerant circuit. When the pressure increases, the valve opening of the expansion valve is reduced until the high pressure side pressure drops below a predetermined reference value, and the high pressure side pressure drops while the high pressure side pressure drops below the reference value. In the case where the opening degree of the expansion valve is expanded and the increase degree of the high-pressure side pressure becomes a predetermined specified value or less in the process of expanding the opening degree of the expansion valve, the expansion valve When the valve opening degree is maintained and the high pressure side pressure decreases in this state, the valve opening degree of the expansion valve is expanded, and then the refrigeration system returns to the constant superheat degree control. The control means includes high pressure cutoff means for stopping the operation of the compressor when the high pressure side pressure reaches a predetermined high pressure cutoff set value, and the protection set value is lower than the high pressure cutoff set value. The refrigeration system of claim 1, wherein

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