WO2017194035A1 - 一种提高制冷或热泵系统效率的方法及运行方法 - Google Patents

一种提高制冷或热泵系统效率的方法及运行方法 Download PDF

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Publication number
WO2017194035A1
WO2017194035A1 PCT/CN2017/092349 CN2017092349W WO2017194035A1 WO 2017194035 A1 WO2017194035 A1 WO 2017194035A1 CN 2017092349 W CN2017092349 W CN 2017092349W WO 2017194035 A1 WO2017194035 A1 WO 2017194035A1
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Prior art keywords
cycle
cold storage
heat
heat pump
refrigeration
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PCT/CN2017/092349
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English (en)
French (fr)
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赵向辉
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赵向辉
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Publication of WO2017194035A1 publication Critical patent/WO2017194035A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat

Definitions

  • the present invention relates to the field of refrigeration or heat pump, and more particularly to a method and method for increasing the efficiency of a refrigeration or heat pump system.
  • the refrigeration system can be divided into high temperature type, medium temperature type and low temperature type.
  • the high temperature type evaporation temperature is generally -5 °C ⁇ 25 °C
  • the medium temperature type evaporation temperature is generally -23 °C ⁇ 10 °C
  • the low temperature type evaporation temperature is generally -46 ° C ⁇ -10 ° C.
  • Refrigeration systems in the field of cold chain generally require refrigeration and freezing conditions, and the evaporation temperature is below 10 ° C (usually below 0 ° C), and the efficiency is low.
  • the present invention provides a method for improving the efficiency of a refrigeration or heat pump system, the refrigeration or heat pump system based thereon comprising a refrigeration circuit, the refrigeration circuit being at least connected by a compressor, a condenser and a throttle device in series And an evaporator composition, the refrigeration circuit can realize a refrigeration cycle: a user refrigeration cycle, the method is:
  • the first heat exchanger enables the first regenerator medium to provide a cooling amount to the first heat exchanger, thereby making the refrigeration circuit
  • a new user refrigeration cycle can be implemented: the first overcooled user refrigeration cycle.
  • a second cold storage circuit is composed of at least a compressor, a condenser, a supercooling heat exchanger, a throttle device and an evaporator which are sequentially connected in series, and the first cold storage medium may be
  • the subcooling heat exchanger provides cooling capacity
  • the second regenerative cooling circuit can realize a refrigeration cycle: a second regenerative cycle;
  • the second heat exchanger enables the second regenerator medium to provide a cooling capacity for the second heat exchanger, thereby
  • the refrigeration circuit enables a new user refrigeration cycle.
  • a common compressor that can participate in the first cold storage cycle or participate in the first supercooled user refrigeration cycle, and is arranged in series on the communication line between the evaporator of the refrigeration circuit and the common compressor a valve member; when the first cold storage cycle is in operation, the valve member can prevent refrigerant in the first cold storage cycle from entering the refrigeration circuit along a communication line between the evaporator of the refrigeration circuit and the common compressor The evaporator, or the valve member, maintains the first subcooled user refrigeration cycle operating simultaneously below the evaporation pressure of the first cold storage cycle.
  • the solid-liquid phase temperature of the first cold storage medium is less than 29 degrees Celsius under atmospheric pressure.
  • the present invention provides an operation method based on the above-described condition of the presence of a common compressor, wherein the operation method is: during the operation of the first supercooled user refrigeration cycle, when the first cold storage medium is cooled At the end of consumption, at least one of the common compressors is preferentially involved in the first cold storage cycle.
  • the present invention provides a method for improving the efficiency of a heat pump system, the heat pump system based thereon comprising a heat pump circuit, the heat pump circuit being composed of at least a compressor, a condenser, a throttling device and an evaporator which are sequentially connected in series
  • the heat pump circuit can implement a heat pump cycle: a user heat pump cycle, the method is:
  • a second heat pump circuit the second heat pump circuit is composed of at least a compressor, a condenser, a supercooling heat exchanger, a throttling device and an evaporator which are sequentially connected in series, and the subcooling heat exchanger can be Providing heat to the first heat storage medium, and the second heat pump circuit can realize heat pump cycle: the second heat pump cycle;
  • a heat exchanger in the heat pump circuit, a heat exchanger is arranged in series between the first heat exchanger and the throttling device: the second heat exchanger enables the second heat exchanger to supply heat to the second heat storage medium, thereby The heat pump circuit enables a new user heat pump cycle.
  • a common compressor that can participate in the first heat pump cycle or participate in the first heat storage user heat pump cycle, it is arranged in series on the communication line between the evaporator of the heat pump circuit and the common compressor.
  • a valve member prevents the refrigerant in the first heat pump cycle from entering the heat pump circuit along a communication line between the evaporator of the heat pump circuit and the common compressor. The evaporator, or the valve member, maintains the first heat storage user heat pump cycle operating simultaneously below the evaporation pressure of the first heat pump cycle.
  • the solid solution temperature of the first heat storage medium is lower than 29 degrees Celsius under atmospheric pressure.
  • the present invention provides an operation method based on the above-described condition in which a common compressor is present, which is: during the first heat storage user heat pump cycle operation, when the first heat storage medium is full In the case of heat, at least one of the common compressors is preferentially involved in the first heat pump cycle.
  • the present invention can improve the efficiency of a refrigeration or heat pump system.
  • FIG. 1 is a schematic diagram showing the composition principle of a first embodiment of a prior art refrigeration system.
  • FIG. 2 is a schematic view showing the composition principle of the first embodiment of the refrigeration system of the present invention.
  • FIG. 3 is a schematic view showing the composition principle of a second embodiment of the refrigeration system of the present invention.
  • FIG. 4 is a schematic diagram showing the composition principle of a second embodiment of a prior art refrigeration system.
  • Figure 5 is a schematic view showing the composition principle of the third embodiment of the refrigeration system of the present invention.
  • Figure 6 is a schematic view showing the composition principle of the fourth embodiment of the refrigeration system of the present invention.
  • FIG. 7 is a schematic diagram showing the composition principle of a third embodiment of a prior art refrigeration system.
  • Figure 8 is a schematic view showing the composition principle of the fifth embodiment of the refrigeration system of the present invention.
  • Figure 9 is a schematic view showing the composition principle of the sixth embodiment of the refrigeration system of the present invention.
  • Figure 10 is a schematic view showing the composition principle of the seventh embodiment of the refrigeration system of the present invention.
  • Figure 11 is a schematic view showing the composition principle of the eighth embodiment of the refrigeration system of the present invention.
  • Figure 12 is a schematic view showing the composition principle of the first embodiment of the prior art heat pump system.
  • Figure 13 is a schematic view showing the composition principle of the first embodiment of the heat pump system of the present invention.
  • FIG. 1 it is a schematic diagram of the composition principle of the first embodiment of the prior art refrigeration system.
  • the compressor 11, the condenser 21, the capillary 61, and the evaporator 71 are connected in series through a pipeline to form a refrigeration circuit, and a refrigeration cycle can be realized.
  • a refrigeration cycle it is referred to herein as a user refrigeration cycle.
  • This is a refrigeration system that can be applied to a low temperature freezer. It is assumed that the low temperature freezer is set at -18 ° C and the hysteresis is 2 ° C. That is to say, when the temperature in the freezer is greater than or equal to -16 ° C, the compressor 11 is required to operate. Therefore, the refrigeration cycle of the user is provided with the cooling capacity of the refrigerator, and when the temperature in the refrigerator is less than or equal to -18 ° C, the compressor 11 is required to be stopped.
  • the evaporating temperature of the user's refrigeration cycle is generally -25 ° C ⁇ -35 ° C
  • the stable operation here refers to the temperature of the refrigerator in the interval of -18 ° C to -16 ° C
  • the user refrigeration cycle runs for a period of time (generally The state after 1 to 3 minutes) cannot also include a state in which the user's refrigeration cycle is stopped for a certain period of time (generally less than 3 minutes) in a special case, such as an evacuation cycle.
  • the compressor when applying the inverter compressor, the compressor is not controlled by setting the hysteresis to control the temperature in the freezer.
  • the temperature fluctuation in the refrigerator is smaller. Therefore, it is considered that the stable operation refers to the inside of the refrigerator.
  • the user's refrigeration cycle When the temperature is within the set temperature ⁇ 1 °C, the user's refrigeration cycle is running for a period of time (usually 3 to 10 minutes), and it cannot include the period of time before the user's refrigeration cycle stops operating under special circumstances (generally less than 3 minutes).
  • the state such as an evacuation cycle.
  • FIG. 2 is a schematic diagram showing the composition principle of the first embodiment of the refrigeration system of the present invention. It should be noted that this embodiment is an improvement of the first embodiment of the prior art refrigeration system described above.
  • the compressor 11, the condenser 21, and the exchange The heat coil 51, the two-way solenoid valve 82, the capillary 61, the evaporator 71, and the check valve 81 are sequentially connected in series through a pipeline to form a refrigeration circuit, and a new user refrigeration cycle can be realized, which is referred to herein as the first supercooling. User refrigeration cycle.
  • a pipeline is bypassed on the connecting line of the condenser 21 and the heat exchange coil 51, and the two-way electromagnetic valve 84, the capillary 41 and the heat exchange coil 52 are connected in series in series, and then the suction port of the compressor 11 is connected. Therefore, the compressor 11, the condenser 21, the two-way solenoid valve 84, the capillary 41, and the heat exchange coil 52 are sequentially connected to form a circuit, which is referred to herein as a first cold storage circuit, and the first cold storage circuit can realize another refrigeration cycle. This is referred to herein as the first cold storage cycle.
  • a container in which a cold storage tank 00 with a heat insulating layer is used, and the heat exchange coil 51 and the heat exchange coil 52 are placed in the cold storage tank 00, and the cold storage medium 00 is also placed in the cold storage tank 00, and the cold storage medium is stored.
  • 04 uses ice water, that is to say, it uses ice storage (phase change cold storage), so the cold storage temperature is 0 °C.
  • the first cold storage cycle is realized by closing the two-way electromagnetic valve 82 and opening the two-way electromagnetic valve 84.
  • the first supercooled user is realized.
  • Refrigeration cycle Obviously, in the first cold storage cycle, the heat exchange coil 52 is an evaporator and can provide cooling capacity for the ice water 04.
  • the heat exchange coil 51 is a subcooler, and the ice water 04 is Provide cooling capacity.
  • the evaporation temperature of the first cold storage cycle is generally not lower than -10 ° C.
  • the stable operation here refers to ice.
  • the first cold storage cycle is operated for a period of time (generally 1 to 3 minutes), and it cannot include a period of time before the first cold storage cycle is stopped in a special case (generally less than 3 minutes).
  • the state such as an evacuation cycle.
  • the first cold storage cycle obviously has a higher cooling efficiency, and the cold amount obtained by the first cold storage cycle is accumulated in the ice water 04, and the cold water accumulated in the ice water 04 during the first supercooled user refrigeration cycle operation.
  • the refrigerant before the throttling in the first subcooling user refrigeration cycle is transmitted through the heat exchange coil 51 to generate a large degree of subcooling, and finally converted into a part of the cold amount obtained by the first subcooling user refrigeration cycle. Therefore, the whole system has higher cooling efficiency, and its effect is similar to jet boosting technology or two-stage compression energy saving technology.
  • the two cycles can only be selected one by one, and therefore, during the first supercooled user refrigeration cycle operation, the cold storage amount of the first cold storage medium When consumed, the first cold storage cycle should be run first.
  • FIG. 3 is a schematic diagram showing the composition principle of the second embodiment of the refrigeration system of the present invention. It should be noted that the present embodiment is also an improvement of the first embodiment of the prior art refrigeration system described above. At the same time, the present embodiment has the following improvements on the basis of the previous embodiment:
  • the heat exchange coil 56 is connected in series between the heat exchange coil 51 and the two-way solenoid valve 82;
  • a pipe is bypassed on the connecting pipe between the heat exchange coil 51 and the heat exchange coil 56, and the two-way solenoid valve 86, the capillary tube 42, the heat exchange coil 57, and the check valve 87 are connected in series. Accessing the suction port of the compressor 11;
  • the cold storage medium 09 is also placed in the cold storage tank 05, and the cold storage medium 09 is made of ethylene glycol, and the phase change cold storage is selected. Therefore, the cold storage temperature of the ethylene glycol is about -12 °C.
  • the first cold storage cycle which is the same as that of the previous embodiment can be realized by sequentially connecting the compressor 11, the condenser 21, the two-way electromagnetic valve 84, the capillary 41, and the heat exchange coil 52; by the compressor 11, the condenser 21
  • the heat exchange coil 51, the two-way solenoid valve 86, the capillary tube 42, the heat exchange coil 57, and the check valve 87 are sequentially connected to form another circuit, which is referred to herein as a second cold storage circuit, and the second cold storage circuit can realize another The refrigeration cycle, referred to herein as the second cold storage cycle; by the compressor 11, the condenser 21, the heat exchange coil 51, the heat exchange coil 56, the two-way solenoid valve 82, the capillary 61, the evaporator 71, the check valve 81
  • a loop formed by serially connecting in series can implement a new user refrigeration cycle, referred to herein as a second subcooled user refrigeration cycle.
  • the first cold storage cycle is realized by closing the two-way solenoid valves 82 and 86 and opening the two-way solenoid valve 84.
  • the second subcooling user refrigeration cycle is achieved by closing the two-way solenoid valves 84 and 86 and opening the two-way solenoid valve 82.
  • the heat exchange coil 52 is an evaporator and can provide cooling capacity for the ice water 04; in the second cold storage cycle, the heat exchange coil 51 is a subcooler, and the ice water 04 provides cooling capacity thereof.
  • the heat exchange coil 57 is an evaporator and provides a cooling amount for the ethylene glycol 09; in the second supercooled user refrigeration cycle, the heat exchange coil 51 is a first-stage subcooler, and the ice water 04 provides a cooling amount thereof.
  • the heat exchange coil 56 is a second stage subcooler to which ethylene glycol 09 provides refrigeration.
  • the phase change cold storage temperature of ethylene glycol 09 is about -12 ° C.
  • the evaporation temperature of the second cold storage cycle is generally not lower than -20 ° C. Operation refers to the state after the temperature of ethylene glycol 09 is its freezing point (about -12 ° C), the second cold storage cycle is running for a period of time (generally 1 to 3 minutes), and it cannot include the second cold storage cycle under special circumstances. A state that is stopped for a period of time (usually less than 3 minutes), such as an evacuation cycle.
  • the evaporating temperature of the first-stage supercooled user refrigeration cycle is stable from -25 ° C to -35 ° C, and in this embodiment, the evaporating temperature of the second cold storage cycle is not lower than -20 ° C.
  • the efficiency of the second cold storage cycle is higher than that of the first-stage supercooled user refrigeration cycle, and the cold quantity obtained by the second cold storage cycle is accumulated in the ethylene glycol 09, which is accumulated in the ethylene glycol 09 during the second supercooled user refrigeration cycle operation.
  • the cold amount is transferred to the refrigerant before the throttling in the second subcooling user refrigeration cycle through the heat exchange coil 56, so that it has a greater degree of subcooling than the first user supercooling cycle, and finally converts to the second pass.
  • FIG. 4 it is a schematic diagram of the composition principle of the second embodiment of the prior art refrigeration system.
  • the compressor 11, the condenser 21, the accumulator 31, the two-way solenoid valve 82, the thermal expansion valve 61, and the evaporator 71 are sequentially connected in series through a pipeline to form a refrigeration circuit, and a refrigeration cycle can be realized. It is referred to herein as the user refrigeration cycle.
  • This is a refrigeration system that can be used on small cryogenic refrigerators.
  • the temperature of the cold storage is set to -20 ° C
  • the hysteresis is 2 ° C. That is, when the temperature in the cold storage is greater than or equal to -18 ° C, compression is required.
  • the machine 11 is operated so that the user refrigeration cycle provides cooling for the cold storage, and when the temperature in the cold storage is less than or equal to -20 ° C, the compressor 11 is required to be shut down.
  • the evaporating temperature of the user's refrigeration cycle is generally -27 ° C ⁇ -35 ° C
  • the stable operation here refers to the temperature of the cold storage in the interval of -20 ° C to -18 ° C
  • the user refrigeration cycle runs for a period of time (generally The state after 1 to 3 minutes) cannot also include a state in which the user's refrigeration cycle is stopped for a certain period of time (generally less than 3 minutes) in a special case, such as an evacuation cycle.
  • the compressor when applying the inverter compressor, the compressor is not controlled by setting the hysteresis to control the temperature in the cold storage.
  • the temperature fluctuation in the cold storage is smaller. Therefore, it is considered that the stable operation refers to the cold storage.
  • the temperature is within the set temperature ⁇ 1 °C, the user's refrigeration cycle is running for a period of time (usually 3 to 10 minutes), and it cannot include the period of time before the user's refrigeration cycle stops operating under special circumstances (generally less than 3 minutes).
  • the state such as an evacuation cycle.
  • FIG. 5 is a schematic diagram showing the composition principle of the third embodiment of the refrigeration system of the present invention. It should be noted that this embodiment is an improvement of the second embodiment of the above prior art refrigeration system.
  • the compressor 11, the condenser 21, the accumulator 31, the two-way solenoid valve 85, the heat exchange coil 51, the thermal expansion valve 61, the evaporator 71, and the check valve 81 are connected in series through a pipeline.
  • a refrigeration circuit is formed and a new user refrigeration cycle can be implemented, referred to herein as the first subcooled user refrigeration cycle.
  • a thermal expansion valve 41 is disposed on the connecting line between the accumulator 31 and the heat exchange coil 51, and the thermal expansion valve 41 is connected in parallel with the two-way solenoid valve 85, in the heat exchange coil 51 and the thermal expansion valve 61.
  • a connecting line is connected to the inlet pipe to connect the suction port of the compressor 11, and a two-way solenoid valve 83 is connected in series to the bypass line.
  • the compressor 11, the condenser 21, the accumulator 31, the thermal expansion valve 41, the heat exchange coil 51, and the two-way solenoid valve 83 are sequentially connected to form a circuit, which is referred to herein as a first cold storage circuit, and the first cold storage circuit
  • a first cold storage circuit which is referred to herein as a first cold storage circuit
  • the first cold storage circuit Another refrigeration cycle can be implemented, referred to herein as the first cold storage cycle.
  • a container in which a cold storage tank 00 with a heat insulating layer is used, the heat exchange coil 51 is placed in the cold storage tank 00, and the cold storage medium 04 is also placed in the cold storage tank 00, and the cold storage medium 04 is ice water, that is, It is said that ice storage (phase change cold storage) is used, so the cold storage temperature is 0 °C.
  • the first cold storage cycle is realized by closing the two-way electromagnetic valve 85 and opening the two-way electromagnetic valve 83.
  • the heat exchange coil 51 is an evaporator and can provide cooling capacity for the ice water 04.
  • the heat exchange coil 51 is a subcooler, and the ice water 04 is Provide cooling capacity. Since the cold storage temperature of ice water 04 is 0 ° C, reasonable After the thermal expansion valve 41 and the heat exchange coil 51 are matched, the evaporation temperature of the first cold storage cycle is generally not lower than -10 ° C.
  • the stable operation means that the temperature of the ice water 04 is 0 ° C.
  • the state after a cold storage cycle has been running for a period of time does not include a state (for example, less than 3 minutes) before the first cold storage cycle is stopped in a special case, such as an evacuation cycle.
  • a special case such as an evacuation cycle.
  • the evaporation temperature of the first cold storage cycle will decrease as the freezing rate of ice water 04 rises, the evaporation temperature of the first cold storage cycle is generally not under the premise of controlling the freezing rate (for example, not more than 50%). Will be below -10 ° C.
  • the method of controlling the icing rate preferentially adopts a pressure control method: the suction pressure (gauge pressure) of the first cold storage cycle is lower than 3.3 Bar (the refrigerant R404A is used here, and the evaporation temperature corresponding to the gauge pressure of 3.3 Bar is - At 10 ° C), the first cold storage cycle is stopped.
  • the evaporation temperature during steady operation of the user refrigeration cycle is -27 ° C to -35 ° C, and the evaporation temperature of the first cold storage cycle is not lower than -10 here.
  • the first cold storage cycle obviously has a higher cooling efficiency, and the cold quantity obtained by the first cold storage cycle is accumulated in the ice water 04, and the cold accumulated in the ice water 04 passes during the first supercooled user refrigeration cycle operation.
  • the heat exchange coil 51 is transferred to the refrigerant before the throttling in the first subcooling user refrigeration cycle to generate a large degree of subcooling, and finally converted into a part of the cold amount obtained by the first subcooling user refrigeration cycle. Therefore, the whole system has higher cooling efficiency, and its effect is similar to jet boosting technology or two-stage compression energy saving technology.
  • the first subcooling user refrigeration cycle When the first subcooling user refrigeration cycle is performed, if there is no subcooling before the refrigerant is throttled, the cooling efficiency and the cooling capacity are significantly lower than the first regenerative cycle. On the other hand, in order to reduce the cost, the installation is convenient, and the smaller the volume of the cold storage tank 00, the better. Then, when the cold storage has been required for a long period of time, if the ice content or temperature of the ice water 04 is not controlled, the first subcooled user refrigeration cycle performed by the refrigeration system will soon have no subcooling.
  • first Cool storage cycle the first supercooled user refrigeration cycle---the first cold storage cycle---the first supercooled user refrigeration cycle
  • the cold quantity obtained by the first cold storage cycle is stored in the ice water 04, and then passed Increasing the degree of subcooling of the first supercooled user refrigeration cycle is converted into the amount of cold supplied to the cold storage, so that the cooling capacity provided to the cold storage per unit time is increased, and the cooling efficiency is also improved.
  • the first condition is that the temperature of the ice water 04 is greater than 5 ° C. At this time, it is required to start to supply the cold storage medium 04 with a cooling amount
  • the second condition is that the first cold storage cycle has a low suction pressure.
  • the refrigerant R404A is used here, the evaporation temperature corresponding to the gauge pressure of 3.3Bar is -10 °C, and the icing rate is generally not less than 50%).
  • the cold storage temperature is greater than or equal to -18 ° C. At this time, it is required to start to supply cold capacity to the cold storage.
  • the fourth condition is that the cold storage temperature is less than or equal to -20 ° C. At this time, it is required to stop providing cold capacity to the cold storage.
  • the specific control method can be:
  • the first supercooled user refrigeration cycle When the first supercooled user refrigeration cycle is running, if the above condition is satisfied, the first cold storage cycle is preferentially operated until the upper The condition 2 is satisfied, and then the first supercooled user refrigeration cycle is operated;
  • the first cold storage cycle is preferentially operated until the above condition 2 is satisfied, and then the first supercooled user refrigeration cycle is operated;
  • the first cold storage cycle is immediately executed until the above condition 2 is satisfied.
  • the above control method is suitable for the case where the cold storage tank 00 is particularly compact. Further, if the cold storage tank 00 can be larger, a condition 5 can be added: after the first cold storage cycle is operated, the temperature from the ice water 04 is less than or equal to At 5 ° C, the cold storage refrigeration cycle lasts for more than 5 minutes. At this time, due to the large volume of the cold storage tank 00, the stored ice water 04 is more, and the freezing rate of the ice water 04 is far less than 50%, but the accumulated cooling capacity at this time is generally sufficient for the first supercooled user to cool. Cycle for 20 minutes.
  • the specific control method at this time is: when the above condition 1 and the above condition 3 are satisfied, the first cold storage cycle is preferentially operated until the above condition 2 or the above condition 5 is satisfied, and then the first supercooled user refrigeration cycle is operated; the first supercooling is performed; When the user refrigeration cycle is running, if the above condition is satisfied, the first cold storage cycle is preferentially operated until the above condition 2 or the above condition 5 is satisfied, and then the first supercooled user refrigeration cycle is operated.
  • the first cold storage cycle is immediately executed until the condition 2 or the condition 5 is satisfied. If the condition 5 is satisfied at this time, and the condition 2 and the condition 3 are not satisfied, the operation continues. A cold storage cycle until the above condition two or the above condition three is satisfied.
  • condition six the time is between 10:00 and 6:00 in the evening, because the electricity rate is low or the ambient temperature is low during this time, then the control method of the previous paragraph can be adjusted to When the above condition 4 is satisfied, the first cold storage cycle is executed until the above condition 2 or the above condition 5 is satisfied; if the above condition 5 is satisfied and the above condition 2 is not satisfied, and the above condition 3 and the above condition 6 are not satisfied, then If the above condition 5 is satisfied and the above condition 2 is not satisfied, and the above condition 3 is not satisfied and the above condition 6 is satisfied, the first cold storage cycle is continued until the above condition 2 is satisfied or the above condition 3 is satisfied or the above condition 6 is satisfied. Not satisfied.
  • FIG. 6 is a schematic diagram showing the composition principle of the fourth embodiment of the refrigeration system of the present invention. It should be noted that this embodiment is also an improvement of the second embodiment of the above-mentioned prior art refrigeration system. At the same time, the present embodiment has the following improvements on the basis of the previous embodiment:
  • the thermal expansion is sequentially connected in series.
  • the valve 42 and the heat exchange coil 56 are also provided with a two-way solenoid valve 88 in parallel at both ends of the thermal expansion valve 42, and a tube is bypassed on the connecting line between the heat exchange coil 56 and the thermal expansion valve 61.
  • the road is connected to the suction port of the compressor 11, and a two-way solenoid valve 87 is arranged in series on the bypass line;
  • the cold storage medium 09 is also provided with the cold storage medium 09, and the cold storage medium 09 is made of ethylene glycol, and the phase change cold storage is selected. Therefore, the cold storage temperature of the ethylene glycol is about -12 °C.
  • the compressor 11, the condenser 21, the accumulator 31, the thermal expansion valve 41, the heat exchange coil 51, and the two-way solenoid valve 83 are sequentially connected to realize the same first cold storage cycle as in the previous embodiment;
  • the machine 11, the condenser 21, the accumulator 31, the two-way solenoid valve 85, the heat exchange coil 51, the thermal expansion valve 42, the heat exchange coil 56, and the two-way solenoid valve 87 are sequentially connected to form another circuit, which is referred to herein as
  • the second regenerative circuit can realize another refrigeration cycle, which is referred to herein as a second regenerative cycle; by the compressor 11, the condenser 21, the accumulator 31, the two-way solenoid valve 85, and the heat exchange coil 51.
  • the two-way solenoid valve 88, the heat exchange coil 56, the thermal expansion valve 61, the evaporator 71, and the check valve 81 are sequentially connected in series to form a new user refrigeration cycle, which is referred to herein as the second supercooled user. Refrigeration cycle.
  • the first cold storage cycle is realized by closing the two-way solenoid valves 85, 87, 88 and opening the two-way solenoid valve 83, by closing the two-way solenoid valves 83, 88, and opening the two-way solenoid valve 85 At 87, a second cold storage cycle is realized. By closing the two-way solenoid valves 83, 87 and opening the two-way solenoid valves 85, 88, the second subcooling user refrigeration cycle is realized.
  • the heat exchange coil 51 is an evaporator and can provide cooling capacity for the ice water 04; in the second cold storage cycle, the heat exchange coil 51 is a subcooler, and the ice water 04 provides cooling capacity thereof.
  • the heat exchange coil 56 is an evaporator and provides a cooling amount for the ethylene glycol 09; in the second supercooled user refrigeration cycle, the heat exchange coil 51 is a first-stage subcooler, and the ice water 04 provides a cooling amount thereof.
  • the heat exchange coil 56 is a second stage subcooler to which ethylene glycol 09 provides refrigeration.
  • the phase change cold storage temperature of ethylene glycol 09 is about -12 ° C.
  • the evaporation temperature during the stable operation of the second cold storage cycle is generally not lower than -20 ° C.
  • the stable operation refers to the state after the temperature of the ethylene glycol 09 is its freezing point (about -12 ° C), and the second cold storage cycle is operated for a period of time (generally 1 to 3 minutes), and cannot include the special case.
  • the evaporation temperature of the second cold storage cycle decreases with the increase of the freezing rate of ethylene glycol 09
  • the evaporation temperature of the second cold storage cycle is generally controlled under the condition of controlling the freezing rate (for example, not more than 50%). Will not be lower than -20 ° C.
  • the method of controlling the icing rate may preferentially adopt a pressure control method: the suction pressure (gauge pressure) of the second cold storage cycle is lower than 2.0 Bar (here, the refrigerant R404A is used, and the evaporation temperature corresponding to the gauge pressure of 2.0 Bar is At -20 ° C), the second cold storage cycle is stopped.
  • the evaporating temperature of the first supercooled user refrigeration cycle is -27 ° C to -35 ° C
  • the evaporating temperature of the second cold storage cycle is not lower than -20 ° C in the embodiment.
  • the efficiency of the second cold storage cycle is higher than that of the first supercooled user refrigeration cycle, and the cold quantity obtained by the second cold storage cycle is accumulated in the ethylene glycol 09, which is accumulated in the ethylene glycol 09 during the second supercooled user refrigeration cycle operation.
  • the cold amount is transferred to the refrigerant before the throttling in the second subcooling user refrigeration cycle through the heat exchange coil 56, so that it has a greater degree of subcooling than the first user supercooling cycle, and finally converts to the second pass.
  • Cold user refrigeration cycle A part of the cold quantity is obtained, so that the whole system has higher cooling efficiency, and the effect is similar to the three-stage compression energy-saving technology.
  • FIG. 7 it is a schematic diagram of the composition principle of the third embodiment of the prior art refrigeration system.
  • the compressors 11, 12, 13, 14 are connected in parallel as a compressor group, the exhaust ports of the four compressors are in communication, the suction ports are also connected, the two-way solenoid valve 91, the thermal expansion valve 61, and the evaporator 71
  • the first refrigerating device is formed in series after being connected in series, and the two-way electromagnetic valve 92, the thermal expansion valve 62, and the evaporator 72 are sequentially connected in series to form a second refrigerating device, a two-way electromagnetic valve 93, a thermal expansion valve 63, and an evaporator 73.
  • a third refrigerating device is formed in series after being connected in series, and the two-way solenoid valve 94, the thermal expansion valve 64, and the evaporator 74 are sequentially connected in series to form a fourth refrigerating device, and the four refrigerating devices are connected in parallel as a refrigerating device group, and the above-mentioned compression
  • the unit, the condenser 21, the accumulator 31, and the above-described refrigerating unit are sequentially connected in series to form a refrigerating circuit, and a refrigeration cycle can be realized, which is referred to herein as a user refrigeration cycle.
  • the utility model relates to a refrigeration system which can be applied to a plurality of small cold storages.
  • the first refrigeration device, the second refrigeration device, the third refrigeration device and the fourth refrigeration device are respectively used for the first cold storage, the second cold storage, the third cold storage,
  • the fourth cold storage provides cooling capacity, and the four cold storages can be set to different temperatures.
  • the first cold storage requires a cold amount
  • the two-way solenoid valve 91 is opened, and when the cold amount is not required, the two-way solenoid valve 91 is closed, and the other cold stores are similarly pushed.
  • the above compressor group controls the number of power-on by low-pressure suction pressure. When the low-pressure pressure is high, the number of compressors is large. When the low-pressure pressure is low, the number of compressors is small, when the low-pressure pressure is lower than the minimum setting. At the time of the value, the compressor is completely shut down.
  • FIG. 8 is a schematic diagram showing the composition principle of the fifth embodiment of the refrigeration system of the present invention. It should be noted that this embodiment is an improvement of the third embodiment of the above prior art refrigeration system.
  • the third embodiment of the above prior art refrigeration system is applied to four medium temperature cold storages, the first cold storage set temperature is 8 ° C, the second cold storage set temperature is 6 ° C, and the third cold storage set temperature At 5 ° C, the fourth cold storage set temperature is 2 ° C, and the temperature difference is 2 ° C.
  • the evaporating temperature set during system operation is -6 ° C (the evaporating temperature here is converted by measuring the suction pressure of the compressor), and that each time the evaporating temperature is increased by 1 ° C, one more compressor is required, and the evaporating temperature is lowered.
  • 1 °C requires less opening of a compressor, that is to say, when the evaporation temperature is higher than -4 °C, it is required that all four compressors are fully opened, and when the evaporation temperature is reduced to less than or equal to -5 °C, only three compressors are required.
  • the evaporation temperature When the evaporation temperature is reduced to -6 ° C or less, it is required to open only 2 compressors, and when the evaporation temperature is reduced to -7 ° C or less, it is required to open only one compressor, and the evaporation temperature is reduced to -8 ° C or less. It is required that all four compressors are closed, and when the evaporation temperature rises to -7 °C or higher, one compressor is required to be opened. When the evaporation temperature rises to -6 °C or higher, two compressors are required to be opened, and the evaporation temperature rises. When the temperature is greater than or equal to -5 °C, it is required to open three compressors. When the evaporation temperature rises to -4 °C or higher, four compressors are required. Then, it can be considered that the evaporation temperature of the user's refrigeration cycle is -8 ° C ⁇ -4 ° C.
  • This embodiment is based on the third embodiment of the prior art refrigeration system described above, and the following improvements are made:
  • the refrigerant side of the plate heat exchanger 51 is connected in series, thereby the compressor group, the condenser 21, the accumulator 31, and the plate heat exchanger 51.
  • the above refrigeration device group is in turn Connected to form a new refrigeration circuit, and can achieve a new user refrigeration cycle, referred to herein as the first supercooled user refrigeration cycle;
  • the refrigerant side of the compressor 15, the condenser 25, the electronic expansion valve 65, and the plate heat exchanger 75 are sequentially connected in series through a pipeline to form a circuit, and a refrigeration cycle can be realized, which is referred to herein as a first cold storage cycle. ;
  • the water pump side, the water flow side of the plate heat exchanger 51, and the heat preservation water tank 00 are connected in series through the pipeline, thereby forming a loop, which can realize water circulation by turning on the water pump 01, which is referred to herein as water circulation one;
  • the water flow side of the water pump 02, the plate heat exchanger 75, and the heat preservation water tank 00 are connected in series through the pipeline, thereby forming another loop, which can also realize water circulation by opening the water pump 02, which is referred to herein as water circulation 2.
  • the first cold storage cycle is realized.
  • the first subcooled user refrigeration cycle is achieved when the compressor train consisting of compressors 11, 12, 13 and 14 is operating.
  • the plate heat exchanger 75 is an evaporator and supplies cold water to the cold water 04 through the water circulation two.
  • the plate heat exchanger 51 is a subcooler, and the cold water 04 passes through the water circulation.
  • a cooling capacity is provided for the plate heat exchanger 51.
  • the temperature of the cold water 04 is set to 12 ° C, and the difference is 3 ° C, that is, the temperature of the cold water 04 is greater than or equal to 15 ° C, the first cold storage cycle is required, and the temperature of the cold water 04 is less than or equal to 12 ° C.
  • the cold storage cycle stops. Therefore, the evaporating temperature of the first cold storage cycle is generally not lower than 7 ° C.
  • the stable operation here refers to the first cold storage cycle running for a period of time (generally 1 to 3) when the cold water temperature is in the range of 12 ° C to 15 ° C.
  • the state after the minute cannot also include a state in which the first cold storage cycle is stopped for a certain period of time (generally less than 3 minutes) in a special case, such as an evacuation cycle. Further, it is considered here that the cold storage temperature of the cold water 04 is 12 ° C to 15 ° C.
  • the evaporating temperature of the user's refrigeration cycle is -8 ° C to -4 ° C
  • the stable operating evaporating temperature of the first regenerative cycle is not lower than 7 ° C, the first cold storage cycle.
  • the cooling capacity is high, and the cold quantity obtained by the first cold storage cycle is accumulated in the cold water 04 through the water circulation 2.
  • the first supercooled user refrigeration cycle is running, the cold accumulated in the cold water 04 is exchanged by the water cycle and the plate type.
  • the heater 51 is transferred to the refrigerant before the throttling in the first subcooling user refrigeration cycle to generate a large degree of subcooling, and finally converted into a part of the cold amount obtained by the first subcooling user refrigeration cycle, thereby
  • the entire system has high cooling efficiency, and its effect is similar to jet boosting technology or two-stage compression energy saving technology.
  • FIG. 9 is a schematic diagram showing the composition principle of the sixth embodiment of the refrigeration system of the present invention. It should be noted that this embodiment is also an improvement of the third embodiment of the above prior art refrigeration system.
  • the third embodiment of the above prior art refrigeration system is applied to four low temperature cold storages, the first cold storage set temperature is -18 ° C, the second cold storage set temperature is -20 ° C, and the third cold storage is set.
  • the fixed temperature is -23 ° C, the fourth cold storage set temperature is -25 ° C, and the temperature difference is 2 ° C.
  • the evaporation temperature set during operation is -31 ° C (the evaporation temperature here is converted by measuring the suction pressure of the compressor), and a dead zone interval of 2 ° C is set, that is, the evaporation temperature is higher than or equal to At -30 °C, 4 compressors are required to be fully open. When the evaporation temperature is lower than or equal to -32 °C, all 4 compressors are required to be closed. In addition, one compressor can only be turned on (or off) at one time, and the compressor is turned on and off. The compressor has a minimum start-up interval (for example, 2 minutes), and the compressors that are closed before and after have the minimum required interval (for example, 1 minute).
  • the compressor When the evaporation temperature is -32 ° C to -30 ° C, the compressor The number of power on and off is maintained. Then, it can be considered that the evaporation temperature of the user's refrigeration cycle is stable from -32 ° C to -30 ° C.
  • This embodiment is based on the third embodiment of the prior art refrigeration system described above, and the following improvements are made:
  • the heat exchange coil 51 is connected in series on the connecting line between the accumulator 31 and the above-mentioned refrigerating unit, so that the compressor unit (composed of the compressors 11, 12 and 13 in parallel), the condenser 21, and the liquid storage
  • the heat exchanger coil 51 and the refrigeration device group are sequentially connected to form a refrigeration circuit, and a new user refrigeration cycle can be realized, which is referred to herein as a first supercooled user refrigeration cycle;
  • a container is provided.
  • a cold storage tank 00 with a heat insulating layer is used, in which a cold storage medium 04 is also disposed, and the cold storage medium 04 is ice water, that is, ice storage cold storage (phase change cold storage), so the cold storage temperature is 0 °C.
  • the two-way solenoid valve 84 is opened, and the compressor 14 is operated to realize the first cold storage cycle, and any one or more of the two-way solenoid valves 91, 92, 93, and 94 are opened, and the compressors 11, 12, and 13 are operated. Any one or more of them can realize the first supercooled user refrigeration cycle.
  • the heat exchange coil 52 is an evaporator and can provide cooling capacity for the ice water 04.
  • the heat exchange coil 51 is a subcooler, and the ice water 04 is Provide cooling capacity. Since the cold storage temperature of the ice water 04 is 0 ° C, after the thermal expansion valve 41 and the heat exchange coil 52 are properly matched, the evaporation temperature of the first cold storage cycle is generally not lower than -10 ° C.
  • the evaporating temperature of the user's refrigeration cycle is stable from -32 ° C to -30 ° C, and the evaporating temperature of the first cold storage cycle is not lower than -10 ° C, the first cold storage.
  • the cycle obviously has a high cooling efficiency, and the cold amount obtained by the first cold storage cycle is accumulated in the ice water 04.
  • the cold amount accumulated in the ice water 04 passes through the heat exchange coil 51.
  • FIG. 10 is a schematic diagram showing the composition principle of the seventh embodiment of the refrigeration system of the present invention. It should be noted that this embodiment is also an improvement of the third embodiment of the above-mentioned prior art refrigeration system. At the same time, the present embodiment is based on the previous embodiment:
  • a heat exchange coil 56 is connected in series; then, on the connecting line between the heat exchange coil 51 and the heat exchange coil 56 a bypass line is connected, and the two-way electromagnetic valve 86, the thermal expansion valve 42, the heat exchange coil 57, and the one-way valve 87 are connected in series to the suction port of the compressor 14;
  • the cold storage medium 09 is also provided with the cold storage medium 09, and the cold storage medium 09 is made of ethylene glycol, and the phase change cold storage is selected. Therefore, the cold storage temperature of the ethylene glycol is about -12 °C.
  • the first cold storage cycle which is the same as that of the previous embodiment can be realized by sequentially connecting the compressor 14, the condenser 21, the accumulator 31, the two-way electromagnetic valve 84, the thermal expansion valve 41, and the heat exchange coil 52;
  • the compressor 14, the condenser 21, the accumulator 31, the heat exchange coil 51, the two-way solenoid valve 86, the thermal expansion valve 42, the heat exchange coil 57, and the check valve 87 are sequentially connected to form another circuit, thereby realizing Another refrigeration cycle, referred to herein as the second cold storage cycle; by the compressor group (consisting of the compressors 11, 12, and 13 in parallel), the condenser 21, the accumulator 31, the heat exchange coil 51, and the heat exchange coil 56.
  • the above-mentioned refrigeration device group is connected in series in series to realize a new user refrigeration cycle, which is referred to herein as a second supercooled user refrigeration cycle.
  • the first cold storage cycle is realized by closing the two-way electromagnetic valve 86 and opening the two-way electromagnetic valve 84
  • the second cold storage cycle is realized by closing the two-way electromagnetic valve 84 and opening the two-way electromagnetic valve 86; Any one or more of the two-way solenoid valves of the above-described refrigerating device group are opened, and any one or more of the compressors 11, 12, and 13 are operated to realize a second supercooled user refrigeration cycle.
  • the heat exchange coil 52 is an evaporator and can provide cooling capacity for the ice water 04; in the second cold storage cycle, the heat exchange coil 51 is a subcooler, and the ice water 04 provides cooling capacity thereof.
  • the heat exchange coil 57 is an evaporator and can provide a cooling amount for the ethylene glycol 09.
  • the heat exchange coil 51 is a first-stage subcooler, and the ice water 04 provides cold.
  • the amount of heat exchange coil 56 is a second stage subcooler to which ethylene glycol 09 provides refrigeration.
  • phase change cold storage temperature of ethylene glycol 09 is about -12 ° C. Therefore, after the thermal expansion valve 42 and the heat exchange coil 57 are properly matched, the evaporation temperature of the second cold storage cycle is generally not lower than -20 ° C.
  • the evaporation temperature of the first supercooled user refrigeration cycle is stable from -32 ° C to -30 ° C, and the evaporating temperature of the second cold storage cycle is not lower than -20 ° C. Therefore, the second cold storage
  • the efficiency of the cycle is higher than that of the first supercooled user refrigeration cycle, and the cold amount obtained by the second cold storage cycle is accumulated in the ethylene glycol 09, and the accumulated cold amount in the ethylene glycol 09 during the second supercooled user refrigeration cycle operation
  • the refrigerant before the throttling in the second subcooling user refrigeration cycle is transmitted through the heat exchange coil 56 to have a greater degree of subcooling than the first user supercooling cycle, and finally converted into a second subcooling user.
  • Refrigeration cycle system A part of the cooling capacity is taken, so that the whole system has higher cooling efficiency, and the effect is similar to the three-stage compression energy-saving technology.
  • FIG. 11 is a schematic diagram showing the composition principle of the eighth embodiment of the refrigeration system of the present invention. It should be noted that the present embodiment is also an improvement of the third embodiment of the above-mentioned prior art refrigeration system. At the same time, the present embodiment is based on the sixth embodiment of the refrigeration system of the present invention described above:
  • a two-way solenoid valve 89 is connected in series to the suction port of the compressor 13 and the other compressor suction pipe, and a bypass pipe is connected between the compressor 13 and the two-way solenoid valve 89.
  • a pipeline the bypass pipeline is connected in series with the heat exchange coil 53, the thermal expansion valve 46 and the two-way solenoid valve 90, and is connected with the connecting pipeline between the accumulator 31 and the heat exchange coil 51;
  • the heat exchange coil 53 is placed in the cold storage tank 00.
  • the compressor 13, the condenser 21, the accumulator 31, the two-way solenoid valve 90, the thermal expansion valve 46, and the heat exchange coil 53 are sequentially connected in series to form another cold storage circuit, and the circuit can also realize the cold storage cycle. It is the same as the original first cold storage cycle, so it is called the added first cold storage cycle. Meanwhile, due to the arrangement of the two-way solenoid valves 81 and 89, the compressor 13 and the compressor 14 may also perform the first supercooling user refrigeration cycle together with the compressors 11 and 12.
  • the two-way solenoid valve 89 When the compressor 13 is in operation, the two-way solenoid valve 89 is closed and the two-way solenoid valve 90 is opened to realize the added first cold storage cycle, the two-way solenoid valve 90 is closed and the two-way solenoid valve 89 is opened, and the compressor 13 participates in the first pass. Cold user refrigeration cycle.
  • the two-way solenoid valve 81 When the compressor 14 is in operation, the two-way solenoid valve 81 is closed and the two-way solenoid valve 84 is opened to realize the first cold storage cycle, the two-way solenoid valve 84 is closed and the two-way solenoid valve 81 is opened, and the compressor 14 participates in the first supercooling user. Refrigeration cycle.
  • this embodiment can configure the compressor more flexibly as needed.
  • at least one of the compressors 13 and 14 preferentially participates in the first cold storage cycle (including the first cold storage cycle described above and the added first cold storage cycle).
  • FIG. 12 it is a schematic diagram of the composition principle of the first embodiment of the prior art heat pump system.
  • the compressor 11 is a jet-enhanced compressor, and has an exhaust port, a gas supply port, and an intake port, an exhaust port of the compressor 11, a condenser 21, an electronic expansion valve 60, and a primary side of the plate heat exchanger 70.
  • the gas supply ports of the compressor 11 are sequentially connected through a pipeline to form a circuit, which is referred to herein as a first circuit; an exhaust port of the compressor 11, a condenser 21, a secondary side of the plate heat exchanger 70, and an electronic expansion valve 61.
  • the suction ports of the evaporator 71 and the compressor 11 are sequentially connected through the pipeline to form another circuit, which is referred to as a second circuit; the first circuit and the second circuit together form a heat pump circuit, and when the compressor 11 is in operation, The opening of the electronic expansion valves 60 and 61 is adjusted, and the heat pump circuit realizes the heat pump cycle, which is referred to herein as the user heat pump cycle.
  • the state before the operation is stopped (generally less than 3 minutes), such as the evacuation cycle; in addition, the evaporation temperature refers to the evaporation temperature of the evaporator 71 in the second circuit, and cannot be the evaporation temperature of the plate heat exchanger 70 in the first circuit. .
  • FIG. 13 is a schematic diagram showing the composition principle of the first embodiment of the heat pump system of the present invention. It should be noted that the present embodiment is an improvement of the first embodiment of the above prior art heat pump system, and the improvement is as follows:
  • a line is connected in series to connect the electronic expansion valve 41 and the heat exchange coil 52 in series, and then Into the suction port of the compressor 11;
  • a container is provided, here a heat storage tank 00 with a thermal insulation layer, the heat exchange coils 51 and 52 are placed in the heat storage tank 00;
  • the heat storage medium 00 is further disposed in the heat storage tank 00, and the heat storage medium 04 is made of ethylene glycol, and the phase change heat storage is selected. Therefore, the heat storage temperature of the ethylene glycol is about -12 °C.
  • the exhaust port of the compressor 11, the condenser 21, the electronic expansion valve 60, the primary side of the plate heat exchanger 70, and the air supply port of the compressor 11 are sequentially connected to each other, forming the same first as in the previous embodiment.
  • a circuit; the exhaust port of the compressor 11, the condenser 21, the secondary side of the plate heat exchanger 70, the electronic expansion valve 41, the heat exchange coil 52, and the suction port of the compressor 11 are sequentially connected to form another circuit.
  • This circuit, together with the first circuit, is referred to herein as the first heat pump circuit; the exhaust port of the compressor 11, the condenser 21, the secondary side of the plate heat exchanger 70, the heat exchange coil 51, and the electronic expansion valve 61.
  • the evaporator 71, the check valve 81, and the suction port of the compressor 11 are sequentially connected to form a circuit, and a new user heat pump cycle can be realized together with the first circuit, which is referred to herein as a first heat storage user heat pump cycle.
  • the heat pump cycle is realized by the first heat pump circuit by closing the electronic expansion valve 61 and adjusting the opening degrees of the electronic expansion valves 60 and 41, which is referred to herein as the first heat pump cycle; when the compressor 11 is running, The first heat storage user heat pump cycle is achieved by closing the electronic expansion valve 41 and adjusting the opening degrees of the electronic expansion valves 60 and 61.
  • the heat exchange coil 52 is an evaporator, the ethylene glycol 04 provides heat thereto, and the condenser 21 provides heat to the indoor user;
  • the plate heat exchanger 70 is The first stage subcooler, the heat exchange coil 51 is a second stage subcooler, the heat exchange coil 51 supplies heat to the ethylene glycol 04, and the condenser 21 provides heat to the indoor user.
  • the phase transition temperature of ethylene glycol 04 is about -12 ° C. Because of the phase change heat storage, the heat storage temperature is about -12 ° C. After the electronic expansion valve 41 is properly adjusted and the heat exchange coil 52 is properly matched, the first The evaporation temperature of the heat pump cycle is generally not stable. It will be lower than -18 °C.
  • the stable operation mentioned here means that the temperature of ethylene glycol 04 is its freezing point (about -12 °C) and the temperature of the room is in the range of 20 ⁇ 1 °C, the first heat pump is cycled for a period of time (The state after 1 to 3 minutes is generally not included in a state in which the first heat pump cycle is stopped for a certain period of time (generally less than 3 minutes) in a special case, such as an evacuation cycle.
  • the evaporating temperature of the user heat pump cycle stable operation is generally -30 ° C, and the evaporating temperature of the first heat pump cycle stable operation is not lower than -18 ° C,
  • the efficiency of the first heat pump cycle is higher than the user heat pump cycle.
  • the heat accumulated in the ethylene glycol 04 is supplied to the first heat pump cycle through the heat exchange coil 52, and the efficiency of the first heat pump cycle is higher, so that the entire system has higher heating efficiency, and the effect thereof is obtained. Similar to three-stage compression energy-saving technology.
  • the container according to the present invention for storing a cold storage medium which may be a common container or an uncommon container, for example, a heat exchange capable of storing a cold storage medium (or a heat storage medium).
  • a cold storage medium or a heat storage medium
  • a heat storage medium such as an ice coil
  • FIG. 1 can be interpreted as a schematic diagram of the composition principle of the second embodiment of the prior art heat pump technology, in which the compressor 11, the condenser 21, the capillary 61, and the evaporator 71 are sequentially connected in series to form a heat pump circuit, which is referred to herein as a user.
  • Heat pump cycle when the user heat pump cycle is running, the evaporator 71 draws heat from the outdoor air, the condenser 21 provides heat to the indoor user, and when the outdoor ambient temperature is -18 degrees, the evaporating temperature of the user heat pump cycle is about -25 °C. .
  • the second embodiment of the heat pump system of the present invention is an improvement of the second embodiment of the prior art heat pump technology, wherein the compressor 11, the condenser 21, the heat exchange coil 51, the two-way solenoid valve 82, the capillary 61, the evaporator 71,
  • the one-way valve 81 is connected in series through a pipeline to form a heat pump circuit, and a new user heat pump cycle can be realized, which is referred to herein as a first heat storage user heat pump cycle.
  • a pipeline is bypassed on the connecting line of the condenser 21 and the heat exchange coil 51, and the two-way electromagnetic valve 84, the capillary 41 and the heat exchange coil 52 are connected in series in series, and then the suction port of the compressor 11 is connected. Therefore, the compressor 11, the condenser 21, the two-way solenoid valve 84, the capillary 41, and the heat exchange coil 52 are sequentially connected to each other to form a circuit, which is referred to herein as a first heat pump circuit, and the circuit can be Another heat pump cycle is implemented, referred to herein as the first heat pump cycle.
  • a container in which a cold storage tank 00 with a heat insulating layer is used, and the heat exchange coil 51 and the heat exchange coil 52 are placed in the cold storage tank 00, and the cold storage medium 00 is also placed in the cold storage tank 00, and the cold storage medium is stored.
  • 04 uses ice water, that is to say, it uses ice storage (phase change cold storage), so the cold storage temperature is 0 °C.
  • the first heat pump cycle is realized by closing the two-way solenoid valve 82 and opening the two-way solenoid valve 84.
  • the first heat storage user heat pump is realized. cycle.
  • the heat exchange coil 52 is an evaporator, and the ice water 04 provides heat thereto.
  • the heat exchange coil 51 is a subcooler, which can provide ice water 04. Heat. Since the regenerative temperature of the ice water 04 is 0 ° C, after the capillary 41 and the heat exchange coil 52 are properly matched, the evaporation temperature of the first heat pump cycle is generally not lower than -10 ° C.
  • the evaporating temperature of the user heat pump cycle stable operation is -25 ° C
  • the first heat pump cycle stable operation evaporating temperature is not lower than -10 ° C
  • the first A heat pump cycle obviously has higher efficiency.
  • the heat exchange coil 51 supplies heat to the ice water 04, and does not affect the condenser 21 to provide heat to the user, but in the first heat pump cycle.
  • the heat accumulated in the ice water 04 is supplied to the first heat pump cycle through the heat exchange coil 52, and the efficiency of the first heat pump cycle is higher, so that the entire system has higher heating efficiency, and the effect is similar to that of the jet boosting technology. Or two-stage compression energy-saving technology.
  • FIG. 3 it can be explained as a schematic diagram of the composition principle of the third embodiment of the heat pump system of the present invention. I will not explain too much here.

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Abstract

一种提高制冷或热泵系统效率的方法，制冷或热泵系统包含制冷回路，制冷回路可实现用户制冷循环，方法为：A）设置一个回路：第一蓄冷回路，第一蓄冷回路可实现制冷循环：第一蓄冷循环；B）选取一种蓄冷介质：第一蓄冷介质；C）使第一蓄冷循环为第一蓄冷介质提供冷量，并控制第一蓄冷介质的温度，使第一蓄冷循环稳定运行的蒸发温度高于用户制冷循环稳定运行的蒸发温度；D）使第一蓄冷介质为用户制冷循环中节流前的制冷剂提供冷量。

Description

一种提高制冷或热泵系统效率的方法及运行方法 技术领域
本发明涉及制冷或热泵领域，特别是涉及一种提高制冷或热泵系统效率的方法及运行方法。
背景技术
根据制冷系统运行时的蒸发温度，可把制冷系统分为高温型、中温型和低温型，高温型的蒸发温度一般在-5℃～25℃，中温型的蒸发温度一般在-23℃～10℃，低温型的蒸发温度一般在-46℃～-10℃。
通常，蒸发温度越高，制冷系统的效率越高，蒸发温度越低，制冷系统的效率越低。
冷链领域的制冷系统，一般要求的是冷藏冷冻工况，蒸发温度在10℃以下(通常低于0℃)，效率较低。
目前，我国冷链整体能耗水平较高，明显高于欧美发达国家。虽然冷链领域的节能可以从多方面着手，但是制冷系统始终是节能的重点。目前，在中小型冷藏冷冻制冷系统中，压缩机多采用单级压缩，压缩比大，而且采用毛细管或膨胀阀节流，节流损失大，导致相应的制冷系统效率较低。虽然喷气增焓技术，多级压缩节能技术，复叠式制冷技术均可提高制冷系统的效率，但是，或者因为相应的压缩机种类少(甚至没有小规格的)，或者因为系统成本太高等各方面原因，导致无法在中小型冷藏冷冻制冷系统中应用。
另外，在我国北方，冬季使用空调供暖效率较低，虽然喷气增焓技术在热泵领域应用广泛，但是，受限于室外环境温度，效率仍然不高。
发明内容
本发明的目的是提供一种方法及相关的运行方法，用来提高制冷或热泵系统的效率。
为实现上述目的，本发明提供了一种提高制冷或热泵系统效率的方法，所基于的制冷或热泵系统包含制冷回路，所述制冷回路至少由依次串联连通的压缩机、冷凝器、节流装置、蒸发器组成，所述制冷回路可实现制冷循环：用户制冷循环，所述方法是：
A)设置一个回路：第一蓄冷回路，第一蓄冷回路至少由依次串联连通的压缩机、冷凝器、节流装置、蒸发器组成，第一蓄冷回路可实现制冷循环：第一蓄冷循环；
B)选取一种蓄冷介质：第一蓄冷介质，设置一个容器：第一容器，在第一容器中存放第一蓄冷介质；
C)使第一蓄冷循环为第一蓄冷介质提供冷量，并控制第一蓄冷介质的温度：第一蓄冷温度，使第一蓄冷循环稳定运行的蒸发温度高于用户制冷循环稳定运行的蒸发温度；
D)在所述制冷回路的冷凝器和节流装置之间串联设置换热器：第一换热器，使第一蓄冷介质可为第一换热器提供冷量，从而使所述制冷回路可实现新的用户制冷循环：第一过冷用户制冷循环。
为进一步提高效率，在上述方法基础上进一步的方法是：
E)再设置一个回路：第二蓄冷回路，第二蓄冷回路至少由依次串联连通的压缩机、冷凝器、过冷换热器、节流装置、蒸发器组成，第一蓄冷介质可为所述过冷换热器提供冷量，第二蓄冷回路可实现制冷循环：第二蓄冷循环；
F)再选取一种蓄冷介质：第二蓄冷介质，再设置一个容器：第二容器，在第二容器中存放第二蓄冷介质；
G)使第二蓄冷循环为第二蓄冷介质提供冷量，并控制第二蓄冷介质的温度，使其低于第一蓄冷温度，使第二蓄冷循环稳定运行的蒸发温度高于第一过冷用户制冷循环稳定运行的蒸发温度；
H)在所述制冷回路的第一换热器和节流装置之间串联设置换热器：第二换热器，使第二蓄冷介质可为第二换热器提供冷量，从而使所述制冷回路可实现新的用户制冷循环。
优先的，存在既可以参与第一蓄冷循环，也可以参与第一过冷用户制冷循环的公共压缩机时，在所述制冷回路的蒸发器与所述公共压缩机之间的连通管路上串联设置阀件；第一蓄冷循环运行时，所述阀件可阻止第一蓄冷循环中的制冷剂沿所述制冷回路的蒸发器与所述公共压缩机之间的连通管路进入所述制冷回路的蒸发器，或者所述阀件可使同时运行的第一过冷用户制冷循环维持低于第一蓄冷循环的蒸发压力。
优先的，大气压力下，第一蓄冷介质的固液相变温度低于29摄氏度。
为实现上述目的，本发明提供了一种运行方法，基于上述的存在公共压缩机的状况，所述运行方法是：在第一过冷用户制冷循环运行过程中，当第一蓄冷介质的蓄冷量消耗完时，使至少一台所述公共压缩机优先参与第一蓄冷循环。
为实现上述目的，本发明提供了一种提高热泵系统效率的方法，所基于的热泵系统包含热泵回路，所述热泵回路至少由依次串联连通的压缩机、冷凝器、节流装置、蒸发器组成，所述热泵回路可实现热泵循环：用户热泵循环，所述方法是：
A)设置一个回路：第一热泵回路，第一热泵回路至少由依次串联连通的压缩机、冷凝器、节流装置、蒸发器组成，第一热泵回路可实现热泵循环：第一热泵循环；
B)选取一种蓄热介质：第一蓄热介质，设置一个容器：第一容器，在第一容器中存放 第一蓄热介质；
C)使第一蓄热介质为第一热泵循环提供热量，并控制第一蓄热介质的温度：第一蓄热温度，使第一热泵循环稳定运行的蒸发温度高于用户热泵循环稳定运行的蒸发温度；
D)在所述热泵回路的冷凝器和节流装置之间串联设置换热器：第一换热器，使第一换热器可为第一蓄热介质提供热量，从而使所述热泵回路可实现新的用户热泵循环：第一蓄热用户热泵循环。
为进一步提高效率，在上述方法基础上进一步的方法如下：
E)再设置一个回路：第二热泵回路，第二热泵回路至少由依次串联连通的压缩机、冷凝器、过冷换热器、节流装置、蒸发器组成，所述过冷换热器可为第一蓄热介质提供热量，第二热泵回路可实现热泵循环：第二热泵循环；
F)再选取一种蓄热介质：第二蓄热介质，再设置一个容器：第二容器，在第二容器中存放第二蓄热介质；
G)使第二蓄热介质为第二热泵循环提供热量，并控制第二蓄热介质的温度，使其低于第一蓄热温度，使第二热泵循环稳定运行的蒸发温度高于第一蓄热用户热泵循环稳定运行的蒸发温度；
H)在所述热泵回路中第一换热器和节流装置之间串联设置换热器：第二换热器，使第二换热器可为第二蓄热介质提供热量，从而使所述热泵回路可实现新的用户热泵循环。
优先的，存在既可以参与第一热泵循环，也可以参与第一蓄热用户热泵循环的公共压缩机时，在所述热泵回路的蒸发器与所述公共压缩机之间的连通管路上串联设置阀件；第一热泵循环运行时，所述阀件可阻止第一热泵循环中的制冷剂沿所述热泵回路的蒸发器与所述公共压缩机之间的连通管路进入所述热泵回路的蒸发器，或者所述阀件可使同时运行的第一蓄热用户热泵循环维持低于第一热泵循环的蒸发压力。
优先的，大气压力下，第一蓄热介质的固液相变温度低于29摄氏度。
为实现上述目的，本发明提供了一种运行方法，基于上述的存在公共压缩机的状况，所述运行方法是：在第一蓄热用户热泵循环运行过程中，当第一蓄热介质蓄满热量时，使至少一台所述公共压缩机优先参与第一热泵循环。
基于上述技术方案，本发明能够提高制冷或热泵系统的效率。
附图说明
图1为现有技术制冷系统第一实施例的组成原理示意图。
图2为本发明制冷系统第一实施例的组成原理示意图。
图3为本发明制冷系统第二实施例的组成原理示意图。
图4为现有技术制冷系统第二实施例的组成原理示意图。
图5为本发明制冷系统第三实施例的组成原理示意图。
图6为本发明制冷系统第四实施例的组成原理示意图。
图7为现有技术制冷系统第三实施例的组成原理示意图。
图8为本发明制冷系统第五实施例的组成原理示意图。
图9为本发明制冷系统第六实施例的组成原理示意图。
图10为本发明制冷系统第七实施例的组成原理示意图。
图11为本发明制冷系统第八实施例的组成原理示意图。
图12为现有技术热泵系统第一实施例的组成原理示意图。
图13为本发明热泵系统第一实施例的组成原理示意图。
具体实施方式
以下结合附图和实施例，对本发明的技术方案做进一步的详细描述。
如图1所示，为现有技术制冷系统第一实施例的组成原理示意图。其中，压缩机11、冷凝器21、毛细管61、蒸发器71通过管路依次串联连接，形成制冷回路，并可以实现制冷循环，为了方便说明，这里称其为用户制冷循环。这是一个可以应用在低温冷柜上的制冷系统，这里假定低温冷柜设置温度为-18℃，回差为2℃，也就是说，冷柜内温度大于或等于-16℃时，要求压缩机11运行，从而使用户制冷循环为冷柜提供冷量，冷柜内温度小于或等于-18℃时，要求压缩机11停机。
用户制冷循环稳定运行的蒸发温度一般为-25℃～-35℃，这里所说的稳定运行是指冷柜内温度在-18℃至-16℃这个区间时，用户制冷循环运行一段时间(一般为1～3分钟)后的状态，同时也不能包括特殊情况下用户制冷循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。
当然，应用变频压缩机时，不是通过设定回差来控制压缩机开停从而控制冷柜内的温度，应用变频压缩机时冷柜内的温度波动更小，因此这里认为稳定运行是指冷柜内的温度在设定温度±1℃区间时，用户制冷循环运行一段时间(一般为3～10分钟)后的状态，同时也不能包括特殊情况下用户制冷循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。
如图2所示，为本发明制冷系统第一实施例的组成原理示意图。需要说明的是，本实施例是对上述现有技术制冷系统第一实施例的改进。本实施例中，压缩机11、冷凝器21、换 热盘管51、二通电磁阀82、毛细管61、蒸发器71、单向阀81通过管路依次串联连接，形成制冷回路，并可以实现新的用户制冷循环，这里称其为第一过冷用户制冷循环。此外，在冷凝器21与换热盘管51的连接管路上旁通一条管路，依次串联连接二通电磁阀84、毛细管41和换热盘管52后，连接压缩机11的吸气口，从而使压缩机11、冷凝器21、二通电磁阀84、毛细管41、换热盘管52依次连通形成一个回路，这里称其为第一蓄冷回路，第一蓄冷回路可实现另一个制冷循环，这里称其为第一蓄冷循环。另外，设置一个容器，这里采用一个带有保温层的蓄冷槽00，换热盘管51和换热盘管52都置于蓄冷槽00中，蓄冷槽00中还放有蓄冷介质04，蓄冷介质04采用冰水，也就是说采用冰蓄冷(相变蓄冷)，因此蓄冷温度为0℃。
压缩机11运行时，通过关闭二通电磁阀82并打开二通电磁阀84，实现了第一蓄冷循环，通过关闭二通电磁阀84并打开二通电磁阀82，实现了第一过冷用户制冷循环。显然，第一蓄冷循环中，换热盘管52是蒸发器并可以为冰水04提供冷量，第一过冷用户制冷循环中，换热盘管51是过冷器，冰水04为其提供冷量。由于冰水04的蓄冷温度是0℃，合理匹配毛细管41和换热盘管52后，第一蓄冷循环稳定运行的蒸发温度一般不会低于-10℃，这里所说的稳定运行是指冰水04的温度为0℃时，第一蓄冷循环运行一段时间(一般为1～3分钟)后的状态，同时也不能包括特殊情况下第一蓄冷循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。
在上述现有技术制冷系统第一实施例的说明中，已说明用户制冷循环稳定运行时的蒸发温度为-25℃～-35℃，而这里第一蓄冷循环稳定运行的蒸发温度不低于-10℃，第一蓄冷循环明显具有较高的制冷效率，第一蓄冷循环制取的冷量蓄积在冰水04中，在第一过冷用户制冷循环运行时，冰水04中蓄积的冷量通过换热盘管51传递给第一过冷用户制冷循环中节流前的制冷剂，使其产生较大的过冷度，并最终转化为第一过冷用户制冷循环制取的一部分冷量，从而使整个系统具有较高的制冷效率，其效果类似喷气增焓技术或者两级压缩节能技术。
由于第一蓄冷循环和第一过冷用户制冷循环共用压缩机11，导致两个循环只能择一进行，因此，在第一过冷用户制冷循环运行过程中，当第一蓄冷介质的蓄冷量消耗完时，应该优先运行第一蓄冷循环。
如图3所示，为本发明制冷系统第二实施例的组成原理示意图。需要说明的是，本实施例也是对上述现有技术制冷系统第一实施例的改进，同时，本实施例在上一实施例的基础上做了如下改进：
1、在换热盘管51和二通电磁阀82之间的管路上串联连接了换热盘管56；
2、在换热盘管51和换热盘管56之间的连接管路上旁通一条管路，并依次串联连接二通电磁阀86、毛细管42、换热盘管57、单向阀87后，接入压缩机11的吸气口；
3、再设置一个容器，这里采用带有保温层的蓄冷槽05，换热盘管56和换热盘管57都置于蓄冷槽05中；
4、蓄冷槽05中还放有蓄冷介质09，蓄冷介质09采用乙二醇，并选择相变蓄冷，因此乙二醇的蓄冷温度约为-12℃。
由此，由压缩机11、冷凝器21、二通电磁阀84、毛细管41、换热盘管52依次连通可实现与上一实施例相同的第一蓄冷循环；由压缩机11、冷凝器21、换热盘管51、二通电磁阀86、毛细管42、换热盘管57、单向阀87依次连通形成另一个回路，这里称其为第二蓄冷回路，第二蓄冷回路可实现另一个制冷循环，这里称其为第二蓄冷循环；由压缩机11、冷凝器21、换热盘管51、换热盘管56、二通电磁阀82、毛细管61、蒸发器71、单向阀81依次串联连通形成的回路可实现新的用户制冷循环，这里称其为第二过冷用户制冷循环。
压缩机11运行时，通过关闭二通电磁阀82和86并打开二通电磁阀84，实现了第一蓄冷循环，通过关闭二通电磁阀82和84并打开二通电磁阀86，实现了第二蓄冷循环，通过关闭二通电磁阀84和86并打开二通电磁阀82，实现了第二过冷用户制冷循环。
显然，第一蓄冷循环中，换热盘管52是蒸发器并可为冰水04提供冷量；第二蓄冷循环中，换热盘管51是过冷器，冰水04为其提供冷量，换热盘管57是蒸发器并为乙二醇09提供冷量；第二过冷用户制冷循环中，换热盘管51是第一级过冷器，冰水04为其提供冷量，换热盘管56是第二级过冷器，乙二醇09为其提供冷量。
乙二醇09的相变蓄冷温度约为-12℃，合理匹配毛细管42和换热盘管57后，第二蓄冷循环稳定运行的蒸发温度一般不会低于-20℃，这里所说的稳定运行是指乙二醇09的温度为其冰点(约-12℃)时，第二蓄冷循环运行一段时间(一般为1～3分钟)后的状态，同时也不能包括特殊情况下第二蓄冷循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。
上一个实施例中，一级过冷用户制冷循环稳定运行的蒸发温度仍为-25℃～-35℃，而本实施例中第二蓄冷循环稳定运行的蒸发温度不低于-20℃，第二蓄冷循环的效率高于一级过冷用户制冷循环，第二蓄冷循环制取的冷量蓄积在乙二醇09中，在第二过冷用户制冷循环运行时，乙二醇09中蓄积的冷量通过换热盘管56传递给第二过冷用户制冷循环中节流前的制冷剂，使其相比第一用户过冷循环拥有更大的过冷度，并最终转化为第二过冷用户制冷循环制取的一部分冷量，从而使整个系统具有较高的制冷效率，其效果类似三级压缩节能技术。
如图4所示，为现有技术制冷系统第二实施例的组成原理示意图。其中，压缩机11、冷凝器21、储液器31、二通电磁阀82、热力膨胀阀61、蒸发器71通过管路依次串联连接，形成制冷回路，并可以实现制冷循环，为了方便说明，这里称其为用户制冷循环。这是一个可以应用在小型低温冷库上的制冷系统，在这里，低温冷库温度设定为-20℃，回差为2℃，也就是说，冷库内温度大于或等于-18℃时，要求压缩机11运行，从而使用户制冷循环为冷库提供冷量，冷库内温度小于或等于-20℃时，要求压缩机11停机。
用户制冷循环稳定运行的蒸发温度一般为-27℃～-35℃，这里所说的稳定运行是指冷库内温度在-20℃至-18℃这个区间时，用户制冷循环运行一段时间(一般为1～3分钟)后的状态，同时也不能包括特殊情况下用户制冷循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。
当然，应用变频压缩机时，不是通过设定回差来控制压缩机开停从而控制冷库内的温度，应用变频压缩机时冷库内的温度波动更小，因此这里认为稳定运行是指冷库内的温度在设定温度±1℃区间时，用户制冷循环运行一段时间(一般为3～10分钟)后的状态，同时也不能包括特殊情况下用户制冷循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。
如图5所示，为本发明制冷系统第三实施例的组成原理示意图。需要说明的是，本实施例是对上述现有技术制冷系统第二实施例的改进。本实施例中，压缩机11、冷凝器21、储液器31、二通电磁阀85、换热盘管51、热力膨胀阀61、蒸发器71、单向阀81通过管路依次串联连接，形成制冷回路，并可以实现新的用户制冷循环，这里称其为第一过冷用户制冷循环。此外，在储液器31与换热盘管51之间的连接管路上设置有热力膨胀阀41，热力膨胀阀41与二通电磁阀85并联连接，在换热盘管51与热力膨胀阀61之间的连接管路上旁通有一条管路连接压缩机11的吸气口，并在这条旁通管路上串联连接有二通电磁阀83。由此，压缩机11、冷凝器21、储液器31、热力膨胀阀41、换热盘管51、二通电磁阀83依次连通形成回路，这里称其为第一蓄冷回路，第一蓄冷回路可实现另一个制冷循环，这里称其为第一蓄冷循环。另外，设置一个容器，这里采用一个带有保温层的蓄冷槽00，换热盘管51置于蓄冷槽00中，蓄冷槽00中还放有蓄冷介质04，蓄冷介质04采用冰水，也就是说采用冰蓄冷(相变蓄冷)，因此蓄冷温度为0℃。
压缩机11运行时，通过关闭二通电磁阀85并打开二通电磁阀83，实现了第一蓄冷循环，通过关闭二通电磁阀83并打开二通电磁阀85，实现了第一过冷用户制冷循环。显然，第一蓄冷循环中，换热盘管51是蒸发器并可以为冰水04提供冷量，第一过冷用户制冷循环中，换热盘管51是过冷器，冰水04为其提供冷量。由于冰水04的蓄冷温度是0℃，合理 匹配热力膨胀阀41和换热盘管51后，第一蓄冷循环稳定运行的蒸发温度一般不会低于-10℃，这里所说的稳定运行是指冰水04的温度为0℃时，第一蓄冷循环运行一段时间(一般为1～3分钟)后的状态，不包括特殊情况下第一蓄冷循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。虽然随着冰水04结冰率的上升，第一蓄冷循环的蒸发温度会有所下降，但在控制结冰率(比如不大于50％)的前提下，第一蓄冷循环的蒸发温度一般不会低于-10℃。在此，控制结冰率的方法优先采用压力控制的方法：第一蓄冷循环的吸气压力(表压力)低于3.3Bar(在这里采用制冷剂R404A，表压3.3Bar对应的蒸发温度为-10℃)时，停止第一蓄冷循环。
在上述对现有技术制冷系统第二实施例的说明中，已说明用户制冷循环稳定运行时的蒸发温度为-27℃～-35℃，而这里第一蓄冷循环的蒸发温度不低于-10℃，第一蓄冷循环明显具有较高的制冷效率，第一蓄冷循环制取的冷量蓄积在冰水04中，在第一过冷用户制冷循环运行时，冰水04中蓄积的冷量通过换热盘管51传递给第一过冷用户制冷循环中节流前的制冷剂，使其产生较大的过冷度，并最终转化为第一过冷用户制冷循环制取的一部分冷量，从而使整个系统具有较高的制冷效率，其效果类似喷气增焓技术或者两级压缩节能技术。
当进行第一过冷用户制冷循环时，如果制冷剂节流前没有过冷度，其制冷效率和制冷量均明显低于第一蓄冷循环。另一方面，为了降低成本，安装方便，蓄冷槽00的体积越小越好。那么，当冷库较长一段时间一直要求制冷时，如果冰水04的冰含量或温度不加控制，那么制冷系统进行的第一过冷用户制冷循环很快就没有过冷度。此时，虽然冷库要求制冷，但是，如果停止第一过冷用户制冷循环并运行第一蓄冷循环，对冰水04的冰含量和水温加以控制，那么系统可以稳定在间隔性的状态：第一蓄冷循环---第一过冷用户制冷循环---第一蓄冷循环---第一过冷用户制冷循环，而第一蓄冷循环制取的冷量储存在冰水04中后，又通过增加第一过冷用户制冷循环的过冷度转化为提供给冷库的冷量，这样，系统单位时间内给冷库提供的冷量增加了，制冷效率也提升了。
为了便于说明，在这里设定几个具体的条件，条件一为冰水04的温度大于5℃，此时要求开始给蓄冷介质04提供冷量，条件二为第一蓄冷循环的吸气压力低于3.3Bar(在这里采用制冷剂R404A，表压3.3Bar对应的蒸发温度为-10℃，此时结冰率一般不低于50％)，此时要求停止给冰水04提供冷量，条件三为冷库温度大于或等于-18℃，此时要求开始给冷库提供冷量，条件四为冷库温度小于或等于-20℃，此时要求停止给冷库提供冷量。
具体的控制方法可以为：
第一过冷用户制冷循环运行时，若上述条件一满足，则优先运行第一蓄冷循环，直到上 述条件二满足，再运行第一过冷用户制冷循环；
上述条件一和上述条件三都满足(比如初次上电)时，优先运行第一蓄冷循环，直到上述条件二满足，再运行第一过冷用户制冷循环；
上述条件四满足时，马上运行第一蓄冷循环，直到上述条件二满足。
上述控制方法针对蓄冷槽00特别紧凑的情况比较合适，进一步的，如果蓄冷槽00可以更大一点，那么，可以增设一个条件五：第一蓄冷循环运行后，从冰水04的温度小于或等于5℃时开始，蓄冷制冷循环持续运行的时间超过5分钟。此时，由于蓄冷槽00的体积较大，所储存的冰水04较多，冰水04的结冰率还远不到50％，但是此时蓄积的冷量一般足够第一过冷用户制冷循环运行20分钟。这时的具体控制方法为：上述条件一和上述条件三都满足时，优先运行第一蓄冷循环，直到上述条件二或上述条件五满足，再运行第一过冷用户制冷循环；第一过冷用户制冷循环运行时，若上述条件一满足，则优先运行第一蓄冷循环，直到上述条件二或上述条件五满足，再运行第一过冷用户制冷循环。
进一步的，上述条件四满足时，马上运行第一蓄冷循环，直到上述条件二或上述条件五满足，如果此时上述条件五满足，而上述条件二和上述条件三都不满足，则继续运行第一蓄冷循环，直到上述条件二或上述条件三满足。
进一步的，还可以设定有条件六：时间在晚上10:00至早上6:00之间，因为这段时间电费较低或者环境温度较低，这时，可以把上一段落的控制方法调整为：上述条件四满足时，运行第一蓄冷循环，直到上述条件二或上述条件五满足；如果此时上述条件五满足而上述条件二不满足，而且上述条件三和上述条件六都不满足，则停机；如果此时上述条件五满足而上述条件二不满足，而且上述条件三不满足而上述条件六满足，则继续运行第一蓄冷循环，直到上述条件二满足或者上述条件三满足或者上述条件六不满足。
如图6所示，为本发明制冷系统第四实施例的组成原理示意图。需要说明的是，本实施例也是对上述现有技术制冷系统第二实施例的改进，同时，本实施例在上一实施例的基础上做了如下改进：
1、在换热盘管51和热力膨胀阀61之间的连接管路上，从(二通电磁阀83所在旁通管路的)旁通口到热力膨胀阀61这一段，依次串联连接热力膨胀阀42和换热盘管56，还在热力膨胀阀42的两端并联设置二通电磁阀88，在换热盘管56与热力膨胀阀61之间的连接管路上，还旁通有一条管路连接压缩机11的吸气口，并在这条旁通管路上串联设置有二通电磁阀87；
2、再设置一个容器，这里采用带有保温层的蓄冷槽05，换热盘管56置于蓄冷槽05中；
3、蓄冷槽05中还放有蓄冷介质09，蓄冷介质09采用乙二醇，并选择相变蓄冷，因此乙二醇的蓄冷温度约为-12℃。
由此，压缩机11、冷凝器21、储液器31、热力膨胀阀41、换热盘管51、二通电磁阀83依次连通实现了与上一实施例相同的第一蓄冷循环；由压缩机11、冷凝器21、储液器31、二通电磁阀85、换热盘管51、热力膨胀阀42、换热盘管56、二通电磁阀87依次连通形成另一个回路，这里称其为第二蓄冷回路，第二蓄冷回路可实现又一个制冷循环，这里称其为第二蓄冷循环；由压缩机11、冷凝器21、储液器31、二通电磁阀85、换热盘管51、二通电磁阀88、换热盘管56、热力膨胀阀61、蒸发器71、单向阀81依次串联连通形成的回路实现了新的用户制冷循环，这里称其为第二过冷用户制冷循环。
压缩机11运行时，通过关闭二通电磁阀85、87、88，并打开二通电磁阀83，实现了第一蓄冷循环，通过关闭二通电磁阀83、88，并打开二通电磁阀85、87，实现了第二蓄冷循环，通过关闭二通电磁阀83、87，并打开二通电磁阀85、88，实现了第二过冷用户制冷循环。
显然，第一蓄冷循环中，换热盘管51是蒸发器并可为冰水04提供冷量；第二蓄冷循环中，换热盘管51是过冷器，冰水04为其提供冷量，换热盘管56是蒸发器并为乙二醇09提供冷量；第二过冷用户制冷循环中，换热盘管51是第一级过冷器，冰水04为其提供冷量，换热盘管56是第二级过冷器，乙二醇09为其提供冷量。
乙二醇09的相变蓄冷温度约为-12℃，合理匹配热力膨胀阀42和换热盘管56后，第二蓄冷循环稳定运行时的蒸发温度一般不会低于-20℃，这里所说的稳定运行是指乙二醇09的温度为其冰点(约-12℃)时，第二蓄冷循环运行一段时间(一般为1～3分钟)后的状态，同时也不能包括特殊情况下第二蓄冷循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。虽然随着乙二醇09结冰率的上升，第二蓄冷循环的蒸发温度会有所下降，但在控制结冰率(比如不大于50％)的前提下，第二蓄冷循环的蒸发温度一般不会低于-20℃。在此，控制结冰率的方法可优先采用压力控制的方法：第二蓄冷循环的吸气压力(表压力)低于2.0Bar(在这里采用制冷剂R404A，表压2.0Bar对应的蒸发温度为-20℃)时，停止第二蓄冷循环。
上一实施例中，第一过冷用户制冷循环稳定运行的蒸发温度仍为-27℃～-35℃，而本实施例中第二蓄冷循环稳定运行的蒸发温度不低于-20℃，第二蓄冷循环的效率高于第一过冷用户制冷循环，第二蓄冷循环制取的冷量蓄积在乙二醇09中，在第二过冷用户制冷循环运行时，乙二醇09中蓄积的冷量通过换热盘管56传递给第二过冷用户制冷循环中节流前的制冷剂，使其相比第一用户过冷循环拥有更大的过冷度，并最终转化为第二过冷用户制冷循环 制取的一部分冷量，从而使整个系统具有较高的制冷效率，其效果类似三级压缩节能技术。
如图7所示，为现有技术制冷系统第三实施例的组成原理示意图。其中，压缩机11、12、13、14并联连接为压缩机组，这四台压缩机的排气口相连通，吸气口也相连通，二通电磁阀91、热力膨胀阀61、蒸发器71依次串联连接后形成第一个制冷装置，二通电磁阀92、热力膨胀阀62、蒸发器72依次串联连接后形成第二个制冷装置，二通电磁阀93、热力膨胀阀63、蒸发器73依次串联连接后形成第三个制冷装置，二通电磁阀94、热力膨胀阀64、蒸发器74依次串联连接后形成第四个制冷装置，这四个制冷装置并联连接为制冷装置组，上述压缩机组、冷凝器21、储液器31、上述制冷装置组依次串联连通后，形成制冷回路，并可以实现制冷循环，这里称其为用户制冷循环。
这是一个可以应用在多个小冷库上的制冷系统，第一制冷装置、第二制冷装置、第三制冷装置、第四制冷装置分别用来为第一冷库、第二冷库、第三冷库、第四冷库提供冷量，这四个冷库可以设定为不同的温度。当第一冷库需要冷量时，二通电磁阀91打开，不需要冷量时，二通电磁阀91关闭，其他冷库依次类推。上述压缩机组通过低压吸气压力来控制开机的数量，当低压压力偏高时，压缩机开启的数量多，当低压压力偏低时，压缩机开启的数量少，当低压压力低于最低设定值时，压缩机全部关机。
如图8所示，为本发明制冷系统第五实施例的组成原理示意图。需要说明的是，本实施例是对上述现有技术制冷系统第三实施例的改进。在此，首先假定上述现有技术制冷系统第三实施例是应用于四个中温冷库上，第一冷库设定温度为8℃，第二冷库设定温度为6℃，第三冷库设定温度为5℃，第四冷库设定温度为2℃，温度回差均为2℃。假设系统运行时设定的蒸发温度为-6℃(这里的蒸发温度通过测定压缩机的吸气压力换算而来)，而且蒸发温度每升高1℃要求多开一个压缩机，蒸发温度每降低1℃要求少开一个压缩机，也就是说，蒸发温度高于-4℃度时，要求4台压缩机全开，蒸发温度降低至小于或等于-5℃时，要求只开3台压缩机，蒸发温度降低至小于等于-6℃时，要求只开2台压缩机，蒸发温度降低至小于等于-7℃时，要求只开1台压缩机，蒸发温度降低至小于等于-8℃时，要求4台压缩机全部关闭，蒸发温度升高至大于等于-7℃时，要求开1台压缩机，蒸发温度升高至大于等于-6℃时，要求开2台压缩机，蒸发温度升高至大于等于-5℃时，要求开3台压缩机，蒸发温度升高至大于等于-4℃时，要求开4台压缩机。那么，这里可以认为用户制冷循环稳定运行的蒸发温度为-8℃～-4℃。
本实施例在上述现有技术制冷系统第三实施例的基础上，做了如下改进：
1、在储液器31和上述制冷装置组之间的连接管路上，串联连接板式换热器51的制冷剂侧，从而由上述压缩机组、冷凝器21、储液器31、板式换热器51、上述制冷装置组依次 连通形成新的制冷回路，并可以实现新的用户制冷循环，这里称其为第一过冷用户制冷循环；
2、通过管路依次串联连接压缩机15、冷凝器25、电子膨胀阀65、板式换热器75的制冷剂侧，从而形成一个回路，并可以实现制冷循环，这里称其为第一蓄冷循环；
3、设置一个容器，这里采用一个保温水箱00，其中还置有蓄冷介质04，蓄冷介质04采用水，也就是说采用水蓄冷；
4、通过管路依次串联连接水泵01、板式换热器51的水流侧、保温水箱00，从而形成一个回路，此回路通过开启水泵01可以实现水循环，这里称其为水循环一；
5、通过管路依次串联连接水泵02、板式换热器75的水流侧、保温水箱00，从而形成又一个回路，此回路通过开启水泵02也可以实现水循环，这里称其为水循环二。
压缩机15和水泵02运行时，实现了第一蓄冷循环。由压缩机11、12、13和14组成的压缩机组运行时，实现了第一过冷用户制冷循环。显然，第一蓄冷循环中，板式换热器75是蒸发器并通过水循环二为冷水04提供冷量，第一过冷用户制冷循环中，板式换热器51是过冷器，冷水04通过水循环一为板式换热器51提供冷量。在这里，设定冷水04的温度为12℃，回差为3℃，即冷水04的温度大于或等于15℃时要求第一蓄冷循环运行，冷水04的温度小于或等于12℃时要求第一蓄冷循环停止。因此第一蓄冷循环稳定运行的蒸发温度一般不低于7℃，这里所说的稳定运行是指冷水温度在12℃至15℃这个区间时，第一蓄冷循环运行一段时间(一般为1～3分钟)后的状态，同时也不能包括特殊情况下第一蓄冷循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。另外，在此认为冷水04的蓄冷温度为12℃～15℃。
在本实施例一开始的说明中，已说明用户制冷循环稳定运行的蒸发温度为-8℃～-4℃，而这里第一蓄冷循环的稳定运行蒸发温度不低于7℃，第一蓄冷循环明显具有较高的制冷效率，第一蓄冷循环制取的冷量通过水循环二蓄积在冷水04中，在第一过冷用户制冷循环运行时，冷水04中蓄积的冷量通过水循环一和板式换热器51传递给第一过冷用户制冷循环中节流前的制冷剂，使其产生较大的过冷度，并最终转化为第一过冷用户制冷循环制取的一部分冷量，从而使整个系统具有较高的制冷效率，其效果类似喷气增焓技术或者两级压缩节能技术。
如图9所示，为本发明制冷系统第六实施例的组成原理示意图。需要说明的是，本实施例也是对上述现有技术制冷系统第三实施例的改进。在此，首先假定上述现有技术制冷系统第三实施例是应用于四个低温冷库上，第一冷库设定温度为-18℃，第二冷库设定温度为-20℃，第三冷库设定温度为-23℃，第四冷库设定温度为-25℃，温度回差均为2℃。假设系统 运行时设定的蒸发温度为-31℃(这里的蒸发温度通过测定压缩机的吸气压力换算而来)，并设定一个死区区间为2℃，也就是说，蒸发温度高于或等于-30℃时，要求4台压缩机全开，蒸发温度低于或等于-32℃时，要求4台压缩机全部关闭，另外要求一次性只能开启(或关闭)一台压缩机，前后开启的压缩机其开机时间间隔有最低要求(例如2分钟)，前后关闭的压缩机其关机时间隔也有最低要求(例如1分钟)，当蒸发温度在-32℃～-30℃时，压缩机的开机和关机数量均维持不变。那么，这里可以认为用户制冷循环稳定运行的蒸发温度为-32℃～-30℃。
本实施例在上述现有技术制冷系统第三实施例的基础上，做了如下改进：
1、在储液器31和上述制冷装置组之间的连接管路上，串联连接换热盘管51，从而由压缩机组(由压缩机11、12和13并联组成)、冷凝器21、储液器31、换热盘管51、所述制冷装置组依次连通形成制冷回路，并可以实现新的用户制冷循环，这里称其为第一过冷用户制冷循环；
2、断开压缩机14的吸气口与其他压缩机吸气口的连通，并在储液器31和换热盘管51的连接管路上旁通一条管路，该旁通管路依次串联连接二通电磁阀84、热力膨胀阀41和换热盘管52后接入压缩机14的吸气口，这样，压缩机14、冷凝器21、储液器31、二通电磁阀84、热力膨胀阀41依次连通形成一个回路，并可以实现制冷循环，这里称其为第一蓄冷循环；
3、设置一个容器，这里采用带有保温层的蓄冷槽00，其中还置有蓄冷介质04，蓄冷介质04采用冰水，也就是采用冰蓄冷(相变蓄冷)，因此蓄冷温度为0℃。
打开二通电磁阀84，并运行压缩机14，可实现第一蓄冷循环，二通电磁阀91、92、93和94中的任一个或多个打开，并运行压缩机11、12和13中的任一台或多台，可实现第一过冷用户制冷循环。显然，第一蓄冷循环中，换热盘管52是蒸发器并可为冰水04提供冷量，第一过冷用户制冷循环中，换热盘管51是过冷器，冰水04为其提供冷量。由于冰水04的蓄冷温度是0℃，因此，合理匹配热力膨胀阀41和换热盘管52后，第一蓄冷循环稳定运行的蒸发温度一般不会低于-10℃。
在本实施例一开始的说明中，已说明用户制冷循环稳定运行的蒸发温度为-32℃～-30℃，而这里第一蓄冷循环稳定运行的蒸发温度不低于-10℃，第一蓄冷循环明显具有较高的制冷效率，第一蓄冷循环制取的冷量蓄积在冰水04中，在第一过冷用户制冷循环运行时，冰水04中蓄积的冷量通过换热盘管51传递给第一过冷用户制冷循环中节流前的制冷剂，使其产生较大的过冷度，并最终转化为第一过冷用户制冷循环制取的一部分冷量，从而使整个系统具有较高的制冷效率，其效果类似喷气增焓技术或者两级压缩节能技术。
如图10所示，为本发明制冷系统第七实施例的组成原理示意图。需要说明的是，本实施例也是对上述现有技术制冷系统第三实施例的改进，同时，本实施例是在上一实施例的基础上做了如下改进：
1、在换热盘管51和与上述制冷装置组之间的连接管路上，串联连接有换热盘管56；然后，在换热盘管51和换热盘管56之间的连接管路上，旁通一条管路，并依次串联连接二通电磁阀86、热力膨胀阀42、换热盘管57、单向阀87后接入压缩机14的吸气口；
2、再设置一个容器，这里采用带有保温层的蓄冷槽05，换热盘管56和57均置于蓄冷槽05中；
3、蓄冷槽05中还放有蓄冷介质09，蓄冷介质09采用乙二醇，并选择相变蓄冷，因此乙二醇的蓄冷温度约为-12℃。
由此，由压缩机14、冷凝器21、储液器31、二通电磁阀84、热力膨胀阀41、换热盘管52依次连通可实现与上一实施例相同的第一蓄冷循环；由压缩机14、冷凝器21、储液器31、换热盘管51、二通电磁阀86、热力膨胀阀42、换热盘管57、单向阀87依次连通形成另一个回路，从而可实现又一个制冷循环，这里称其为第二蓄冷循环；由压缩机组(由压缩机11、12和13并联而成)、冷凝器21、储液器31、换热盘管51、换热盘管56、上述制冷装置组依次串联连通可实现新的用户制冷循环，这里称其为第二过冷用户制冷循环。
压缩机14运行时，通过关闭二通电磁阀86并打开二通电磁阀84，实现了第一蓄冷循环，通过关闭二通电磁阀84并打开二通电磁阀86，实现了第二蓄冷循环；上述制冷装置组中的任一个或多个二通电磁阀打开，并运行压缩机11、12和13中的任一台或多台，可实现第二过冷用户制冷循环。
显然，第一蓄冷循环中，换热盘管52是蒸发器并可为冰水04提供冷量；第二蓄冷循环中，换热盘管51是过冷器，冰水04为其提供冷量，换热盘管57是蒸发器，并可为乙二醇09提供冷量；第二过冷用户制冷循环中，换热盘管51是第一级过冷器，冰水04为其提供冷量，换热盘管56是第二级过冷器，乙二醇09为其提供冷量。
乙二醇09的相变蓄冷温度约为-12℃，因此，合理匹配热力膨胀阀42和换热盘管57后，第二蓄冷循环稳定运行的蒸发温度一般不会低于-20℃。
上一实施例中，第一过冷用户制冷循环稳定运行的蒸发温度仍为-32℃～-30℃，而第二蓄冷循环稳定运行的蒸发温度不低于-20℃，因此，第二蓄冷循环的效率高于第一过冷用户制冷循环，第二蓄冷循环制取的冷量蓄积在乙二醇09中，在第二过冷用户制冷循环运行时，乙二醇09中蓄积的冷量通过换热盘管56传递给第二过冷用户制冷循环中节流前的制冷剂，使其相比第一用户过冷循环拥有更大的过冷度，并最终转化为第二过冷用户制冷循环制 取的一部分冷量，从而使整个系统具有较高的制冷效率，其效果类似三级压缩节能技术。
如图11所示，为本发明制冷系统第八实施例的组成原理示意图。需要说明的是，本实施例也是对上述现有技术制冷系统第三实施例的改进，同时，本实施例是在上述本发明制冷系统第六实施例的基础上做了如下改进：
1、在压缩机14和换热盘管52之间的连接管路上旁通一条管路，该旁通管路串联连接二通电磁阀81后与其他压缩机的吸气管连通；
2、在压缩机13的吸气口与其他压缩机吸气管连接的管路上串接二通电磁阀89，同时，在压缩机13和二通电磁阀89之间的连接管路上旁通一条管路，该旁通管路依次串接换热盘管53、热力膨胀阀46和二通电磁阀90后，与储液器31和换热盘管51之间的连接管路连通；
3、换热盘管53置于蓄冷槽00中。
由此，由压缩机13、冷凝器21、储液器31、二通电磁阀90、热力膨胀阀46、换热盘管53依次串联连通形成了又一个蓄冷回路，此回路也可实现蓄冷循环，与原有的第一蓄冷循环作用一样，因此这里称其为增设的第一蓄冷循环。同时，由于二通电磁阀81和89的设置，压缩机13和压缩机14也可以与压缩机11和12一起进行第一过冷用户制冷循环。
压缩机13运行时，关闭二通电磁阀89并打开二通电磁阀90，实现了增设的第一蓄冷循环，关闭二通电磁阀90并打开二通电磁阀89，压缩机13参与第一过冷用户制冷循环。
压缩机14运行时，关闭二通电磁阀81并打开二通电磁阀84，实现了第一蓄冷循环，关闭二通电磁阀84并打开二通电磁阀81，压缩机14参与第一过冷用户制冷循环。
显然，本实施例可根据需要，更加灵活的配置压缩机。当然，蓄冷槽00中冰水04蓄积的冷量用光时，压缩机13和14中至少要有一台优先参与第一蓄冷循环(包括上述的第一蓄冷循环和增设的第一蓄冷循环)。
如图12所示，为现有技术热泵系统第一实施例的组成原理示意图。其中，压缩机11为喷气增焓压缩机，有排气口、补气口和吸气口，压缩机11的排气口、冷凝器21、电子膨胀阀60、板式换热器70的一次侧、压缩机11的补气口通过管路依次连接，形成一个回路，这里称其为第一回路；压缩机11的排气口、冷凝器21、板式换热器70的二次侧、电子膨胀阀61、蒸发器71、压缩机11的吸气口通过管路依次连接，形成又一个回路，这里称其为第二回路；第一回路与第二回路一起，形成热泵回路，压缩机11运行时，调节电子膨胀阀60和61的开度，热泵回路实现了热泵循环，这里称其为用户热泵循环。
这是一个可以应用在我国北方冬季制热的热泵系统，这里假定室外环境温度为-25℃，室内设定温度为20℃，压缩机11可变频调节，用户热泵循环稳定运行时的蒸发温度一般 为-30℃，这里认为稳定运行是指室内的温度在20±1℃区间时，用户热泵循环运行一段时间(一般为3～10分钟)后的状态，同时也不能包括特殊情况下用户热泵循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环；此外，蒸发温度指的是第二回路中蒸发器71的蒸发温度，不能是第一回路中板式换热器70的蒸发温度。
如图13所示，为本发明热泵系统第一实施例的组成原理示意图。需要说明的是，本实施例是对上述现有技术热泵系统第一实施例的改进，改进如下：
1、第二回路中，在板式换热器70的二次侧和电子膨胀阀61之间的连接管路上，串联连接换热盘管51，在压缩机11的吸气口和蒸发器71之间的管路上，串联连接有单向阀81；
2、在第二回路中板式换热器70的二次侧和换热盘管51之间的连接管路上，旁通一条管路依次串联连接电子膨胀阀41和换热盘管52后，接入压缩机11的吸气口；
3、设置一个容器，这里采用带有保温层的蓄热槽00，换热盘管51和52均置于蓄热槽00中；
4、蓄热槽00中还放有蓄热介质04，蓄热介质04采用乙二醇，并选择相变蓄热，因此乙二醇的蓄热温度约为-12℃。
由此，由压缩机11的排气口、冷凝器21、电子膨胀阀60、板式换热器70的一次侧和压缩机11的补气口依次连通，形成了与上一实施例相同的第一回路；由压缩机11的排气口、冷凝器21、板式换热器70的二次侧、电子膨胀阀41、换热盘管52、压缩机11的吸气口依次连通形成另一个回路，该回路与第一回路一起，在此称其为第一热泵回路；由压缩机11的排气口、冷凝器21、板式换热器70的二次侧、换热盘管51、电子膨胀阀61、蒸发器71、单向阀81、压缩机11的吸气口依次连通形成的回路，可与第一回路一起实现新的用户热泵循环，这里称其为第一蓄热用户热泵循环。
压缩机11运行时，通过关闭电子膨胀阀61并调节电子膨胀阀60和41的开度，由第一热泵回路实现了热泵循环，在此称其为第一热泵循环；压缩机11运行时，通过关闭电子膨胀阀41并调节电子膨胀阀60和61的开度，从而实现了第一蓄热用户热泵循环。
显然，第一热泵循环中，换热盘管52是蒸发器，乙二醇04为其提供热量，冷凝器21为室内用户提供热量；第一蓄热用户热泵循环中，板式换热器70是第一级过冷器，换热盘管51是第二级过冷器，换热盘管51为乙二醇04提供热量，冷凝器21为室内用户提供热量。
乙二醇04的相变温度约为-12℃，由于采用相变蓄热，因此其蓄热温度约为-12℃，合理调节电子膨胀阀41并合理匹配换热盘管52后，第一热泵循环稳定运行的蒸发温度一般不 会低于-18℃，这里所说的稳定运行是指乙二醇04的温度为其冰点(约-12℃)且室内的温度在20±1℃区间时，第一热泵循环运行一段时间(一般为1～3分钟)后的状态，同时也不能包括特殊情况下第一热泵循环停止运行前一段时间(一般小于3分钟)的状态，例如抽空循环。
在上述对现有技术热泵系统第一实施例的说明中，已说明用户热泵循环稳定运行的蒸发温度一般为-30℃，而第一热泵循环稳定运行的蒸发温度不低于-18℃，因此，第一热泵循环的效率高于用户热泵循环，在第一蓄热用户热泵循环运行时，换热盘管51为乙二醇04提供热量，也不影响冷凝器21为用户提供热量，而在第一热泵循环运行时，乙二醇04中蓄积的热量通过换热盘管52提供给第一热泵循环，第一热泵循环的效率更高，从而使整个系统具有更高的制热效率，其效果类似三级压缩节能技术。
在此需要补充说明的是：
1、本发明所述的容器，用来存放蓄冷介质(或蓄热介质)，可以是常见的容器，也可以是不常见的容器，例如：能存放蓄冷介质(或蓄热介质)的换热器(如结冰盘管)，可以是能移动的，也可以是不能移动的，例如：建筑物中的消防水池，甚至是在地下或半地下布置的空间，可以是规则的，也可以是不规则的。
2、通过类似本发明已阐明的方法，可以进一步实现更多过冷级数的用户制冷循环，其节能效果更好。但是，考虑到要优先选择相变蓄冷，就需要更多种有理想相变温度的蓄冷介质(或蓄热介质)，比较受限。
3、本发明在实施例中对热泵所述不多，所属技术领域的普通技术人员应当理解，制冷与热泵道理完全相通。
例如，图1所示可以解释为现有热泵技术第二实施例的组成原理示意图，其中压缩机11、冷凝器21、毛细管61、蒸发器71依次串联连通形成热泵回路，在此称其为用户热泵循环，用户热泵循环运行时，蒸发器71攫取室外空气中的热量，冷凝器21为室内用户提供热量，室外环境温度为-18度时，用户热泵循环稳定运行的蒸发温度约为-25℃。
图2所示，可以解释为本发明热泵系统第二实施例的组成原理示意图。本发明热泵系统第二实施例是对现有热泵技术第二实施例的改进，其中，压缩机11、冷凝器21、换热盘管51、二通电磁阀82、毛细管61、蒸发器71、单向阀81通过管路依次串联连接，形成热泵回路，并可以实现新的用户热泵循环，这里称其为第一蓄热用户热泵循环。此外，在冷凝器21与换热盘管51的连接管路上旁通一条管路，依次串联连接二通电磁阀84、毛细管41和换热盘管52后，连接压缩机11的吸气口，从而使压缩机11、冷凝器21、二通电磁阀84、毛细管41、换热盘管52依次连通并形成一个回路，这里称其为第一热泵回路，这个回路可 实现另一个热泵循环，这里称其为第一热泵循环。另外，设置一个容器，这里采用一个带有保温层的蓄冷槽00，换热盘管51和换热盘管52都置于蓄冷槽00中，蓄冷槽00中还放有蓄冷介质04，蓄冷介质04采用冰水，也就是说采用冰蓄冷(相变蓄冷)，因此蓄冷温度为0℃。
压缩机运行时，通过关闭二通电磁阀82并打开二通电磁阀84，实现了第一热泵循环，通过关闭二通电磁阀84并打开二通电磁阀82，实现了第一蓄热用户热泵循环。显然，第一热泵循环中，换热盘管52是蒸发器，冰水04为其提供热量，第一蓄热用户热泵循环中，换热盘管51是过冷器，可为冰水04提供热量。由于冰水04的蓄热温度是0℃，合理匹配毛细管41和换热盘管52后，第一热泵循环稳定运行的蒸发温度一般不会低于-10℃。
在上述对现有技术热泵系统第二实施例的说明中，已说明用户热泵循环稳定运行的蒸发温度为-25℃，而这里第一热泵循环稳定运行的蒸发温度不低于-10℃，第一热泵循环明显具有更高的效率，在第一蓄热用户热泵循环运行时，换热盘管51为冰水04提供热量，也不影响冷凝器21为用户提供热量，而在第一热泵循环运行时，冰水04中蓄积的热量通过换热盘管52提供给第一热泵循环，第一热泵循环的效率更高，从而使整个系统具有更高的制热效率，其效果类似喷气增焓技术或者两级压缩节能技术。
依次类推，图3所示，可以解释为本发明热泵系统第三实施例的组成原理示意图。在此不再做过多说明。
最后应当说明的是：以上所述的现有技术及改进实施例仅用于说明本发明的技术方案而非对其限制，所属技术领域的普通技术人员应当理解，仍可以对上述的现有技术进行修改或者对部分技术特征进行等效替换，也可以对本发明的具体实施方式进行修改或者对部分技术特征进行等效替换。所以，只要不脱离本发明技术方案的精神，均应该涵盖在本发明请求保护的技术方案范围当中。

Claims (10)

  1. 一种提高制冷或热泵系统效率的方法，所基于的制冷或热泵系统包含制冷回路，所述制冷回路至少由依次串联连通的压缩机、冷凝器、节流装置、蒸发器组成，所述制冷回路可实现制冷循环：用户制冷循环，其特征在于：
    A)设置一个回路：第一蓄冷回路，第一蓄冷回路至少由依次串联连通的压缩机、冷凝器、节流装置、蒸发器组成，第一蓄冷回路可实现制冷循环：第一蓄冷循环；
    B)选取一种蓄冷介质：第一蓄冷介质，设置一个容器：第一容器，在第一容器中存放第一蓄冷介质；
    C)使第一蓄冷循环为第一蓄冷介质提供冷量，并控制第一蓄冷介质的温度：第一蓄冷温度，使第一蓄冷循环稳定运行的蒸发温度高于用户制冷循环稳定运行的蒸发温度；
    D)在所述制冷回路的冷凝器和节流装置之间串联设置换热器：第一换热器，使第一蓄冷介质可为第一换热器提供冷量，从而使所述制冷回路可实现新的用户制冷循环：第一过冷用户制冷循环。
  2. 根据权利要求1所述的一种提高制冷或热泵系统效率的方法，其特征在于：
    E)再设置一个回路：第二蓄冷回路，第二蓄冷回路至少由依次串联连通的压缩机、冷凝器、过冷换热器、节流装置、蒸发器组成，第一蓄冷介质可为所述过冷换热器提供冷量，第二蓄冷回路可实现制冷循环：第二蓄冷循环；
    F)再选取一种蓄冷介质：第二蓄冷介质，再设置一个容器：第二容器，在第二容器中存放第二蓄冷介质；
    G)使第二蓄冷循环为第二蓄冷介质提供冷量，并控制第二蓄冷介质的温度，使其低于第一蓄冷温度，使第二蓄冷循环稳定运行的蒸发温度高于第一过冷用户制冷循环稳定运行的蒸发温度；
    H)在所述制冷回路的第一换热器和节流装置之间串联设置换热器：第二换热器，使第二蓄冷介质可为第二换热器提供冷量，从而使所述制冷回路可实现新的用户制冷循环。
  3. 根据权利要求1所述的一种提高制冷或热泵系统效率的方法，其特征在于：
    存在既可以参与第一蓄冷循环，也可以参与第一过冷用户制冷循环的公共压缩机时，在所述制冷回路的蒸发器与所述公共压缩机之间的连通管路上串联设置阀件(81)；
    第一蓄冷循环运行时，所述阀件(81)可阻止第一蓄冷循环中的制冷剂沿所述制冷回路的蒸发器与所述公共压缩机之间的连通管路进入所述制冷回路的蒸发器，或者所述阀件(81)可使同时运行的第一过冷用户制冷循环维持低于第一蓄冷循环的蒸发压力。
  4. 根据权利要求1所述的一种提高制冷或热泵系统效率的方法，其特征在于：
    大气压力下，第一蓄冷介质的固液相变温度低于29摄氏度。
  5. 一种运行方法，基于上述权利要求3所述的存在公共压缩机的状况，其特征在于：
    在第一过冷用户制冷循环运行过程中，当第一蓄冷介质的蓄冷量消耗完时，使至少一台所述公共压缩机优先参与第一蓄冷循环。
  6. 一种提高热泵系统效率的方法，所基于的热泵系统包含热泵回路，所述热泵回路至少由依次串联连通的压缩机、冷凝器、节流装置、蒸发器组成，所述热泵回路可实现热泵循环：用户热泵循环，其特征在于：
    A)设置一个回路：第一热泵回路，第一热泵回路至少由依次串联连通的压缩机、冷凝器、节流装置、蒸发器组成，第一热泵回路可实现热泵循环：第一热泵循环；
    B)选取一种蓄热介质：第一蓄热介质，设置一个容器：第一容器，在第一容器中存放第一蓄热介质；
    C)使第一蓄热介质为第一热泵循环提供热量，并控制第一蓄热介质的温度：第一蓄热温度，使第一热泵循环稳定运行的蒸发温度高于用户热泵循环稳定运行的蒸发温度；
    D)在所述热泵回路的冷凝器和节流装置之间串联设置换热器：第一换热器，使第一换热器可为第一蓄热介质提供热量，从而使所述热泵回路可实现新的用户热泵循环：第一蓄热用户热泵循环。
  7. 根据权利要求6所述的一种提高热泵系统效率的方法，其特征在于：
    E)再设置一个回路：第二热泵回路，第二热泵回路至少由依次串联连通的压缩机、冷凝器、过冷换热器、节流装置、蒸发器组成，所述过冷换热器可为第一蓄热介质提供热量，第二热泵回路可实现热泵循环：第二热泵循环；
    F)再选取一种蓄热介质：第二蓄热介质，再设置一个容器：第二容器，在第二容器中存放第二蓄热介质；
    G)使第二蓄热介质为第二热泵循环提供热量，并控制第二蓄热介质的温度，使其低于第一蓄热温度，使第二热泵循环稳定运行的蒸发温度高于第一蓄热用户热泵循环稳定运行的蒸发温度；
    H)在所述热泵回路中第一换热器和节流装置之间串联设置换热器：第二换热器，使第二换热器可为第二蓄热介质提供热量，从而使所述热泵回路可实现新的用户热泵循环。
  8. 根据权利要求6所述的一种提高热泵系统效率的方法，其特征在于：
    存在既可以参与第一热泵循环，也可以参与第一蓄热用户热泵循环的公共压缩机时，在所述热泵回路的蒸发器与所述公共压缩机之间的连通管路上串联设置阀件(81)；
    第一热泵循环运行时，所述阀件(81)可阻止第一热泵循环中的制冷剂沿所述热泵回路的蒸发器与所述公共压缩机之间的连通管路进入所述热泵回路的蒸发器，或者所述阀件 (81)可使同时运行的第一蓄热用户热泵循环维持低于第一热泵循环的蒸发压力。
  9. 根据权利要求6所述的一种提高热泵系统效率的方法，其特征在于：
    大气压力下，第一蓄热介质的固液相变温度低于29摄氏度。
  10. 一种运行方法，基于上述权利要求8所述的存在公共压缩机的状况，其特征在于：
    在第一蓄热用户热泵循环运行过程中，当第一蓄热介质蓄满热量时，使至少一台所述公共压缩机优先参与第一热泵循环。
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