CN105004089A - Cascaded unit used for both medium-high temperature cold storage house and low temperature cold storage house - Google Patents
Cascaded unit used for both medium-high temperature cold storage house and low temperature cold storage house Download PDFInfo
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- CN105004089A CN105004089A CN201510462417.4A CN201510462417A CN105004089A CN 105004089 A CN105004089 A CN 105004089A CN 201510462417 A CN201510462417 A CN 201510462417A CN 105004089 A CN105004089 A CN 105004089A
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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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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- Air Conditioning Control Device (AREA)
Abstract
The invention relates to a cascaded unit used for both a medium-high temperature cold storage house and a low temperature cold storage house. The cascaded unit comprises a high-temperature system, a low-temperature system and a control system. The high-temperature system is connected with the low-temperature system through an intermediate heat exchanger. The high-temperature system is composed of a high-temperature compressor, a high-temperature condenser and a high-temperature evaporator which are sequentially connected to form a loop. The intermediate heat exchanger is connected with the two ends of the high-temperature evaporator in parallel. The low-temperature system is composed of a low-temperature compressor, a low-temperature evaporator and the intermediate heat exchanger which are sequentially connected to form a loop. Throttling devices are installed at the liquid inlet end of the high-temperature evaporator and the high-temperature liquid inlet end of the intermediate heat exchanger respectively. The control system controls a liquid refrigerant in the high-temperature system to flow through the intermediate heat exchanger or the high-temperature evaporator by controlling switching-on or switching-off of the throttling devices. The cascaded unit can be applied to the medium-high temperature cold storage house and the low temperature cold storage house at the same time and is efficient, capable of saving energy, environmentally friendly and easy to operate.
Description
Technical field
The present invention relates to freezer refrigeration system technical field, particularly relate to a kind of middle High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store.
Background technology
Modern industry is advanced by leaps and bounds, different production divisions requires also to be not quite similar to temperature of ice house, if make the temperature that freezer reaches higher, then need the freezing unit of single-stage to cool the air in freezer, and then make middle High Temperature Refrigeratory or low-temperature cold store reach the temperature of expection.
The Chinese invention patent application being 201110053270.5 " a kind of freezers " by name as application number discloses a kind of freezer, this invention refrigeration system comprises cooler, evaporimeter and moisture trap, the cooled media outlet of cooler communicates with the cooled medium inlet of evaporimeter, the cooled media outlet of evaporimeter communicates with the import of moisture trap, the gas vent of moisture trap communicates with the refrigerant inlet of cooler, the refrigerant exit of cooler is the cold-air vent of refrigeration system, the cooler medium inlet that is cooled is the air intake of refrigeration system, it is external that the air intake of refrigeration system is positioned at cold storage chamber, cold storage chamber body is provided with hot-blast outlet and cold air inlet, the cold-air vent of refrigeration system communicates with the cold air inlet on cold storage chamber body, evaporimeter is connected with refrigerant feed system.Controlled unit by control system, cold-producing medium, by the process of " gas-liquid-gaseous state ", absorbs and is blown into heat in the air of unit by freezer, to reduce air themperature, finally make freezer be down to uniform temperature.But this refrigeration system has a definite limitation in range of operation, do not make the temperature of freezer drop to the state of low temperature or ultralow temperature by self-operating, the needs of special producing technique to low temperature or ultra low temperature cool house can not be met.
Be exclusively used in the needs providing the overlapping unit of low temperature and superfreeze water can meet some special producing techniques.The Chinese utility model patent being 201220550614.3 " a kind of with the thermoregulator efficient double base overlapping deep cooling unit of pre-cold-peace " by name as application number application discloses that a kind of with the thermoregulator efficient double base overlapping deep cooling unit of pre-cold-peace, comprise two cooling cycle systems, be respectively high-temperature level system and low-temperature level system, high-temperature level system comprises high-temperature level compressor, oil eliminator, oil cooler, condenser, economizer and condenser/evaporator; Low-temperature level system comprises low-temperature level compressor, expansion drum, low-temperature level oil eliminator, low-temperature level oil cooler, regenerator, forecooler, condenser/evaporator and low-temperature level evaporimeter, and all devices forms a whole unit.This kind of ultra low temperature overlapping unit carries out overlapping heat exchange by two groups of Vapor Compression Refrigeration Cycle systems to cold-producing medium, makes the temperature that liquid refrigerant can reach lower, thus with air heat-exchange in freezer, make freezer be down to the state of low temperature or ultralow temperature.But two cover systems in this overlapping unit must operate simultaneously, same set of unit can not control according to different situations the state that freezer reaches middle temperature or low temperature.
Therefore, in actual production, for meeting the requirement of various processes, need the freezing unit being equipped with separately different temperatures scope, to be applied to the freezer of different temperatures scope.So not only complex operation, and unit floor space is large, energy consumption is large, and lness ratio of plant is high, can not meet that modern industry is efficient, the production requirement of energy-saving and environmental protection.
Summary of the invention
The present invention is directed to the deficiency of existing freezer air-conditioner set, provide a kind of operate simple and easy, serviceability temperature wide ranges, can the High Temperature Refrigeratory of the different freezer environmental requirement of simultaneous adaptation and the dual-purpose overlapping unit of low-temperature cold store.
Object of the present invention is achieved by the following technical programs:
A kind of middle High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store, described overlapping unit comprises high-temperature level system, low-temperature level system and control system, described high-temperature level system is connected by Intermediate Heat Exchanger with low-temperature level system, described high-temperature level system is by high-temperature level compressor, condenser and high-temperature level evaporimeter are in turn connected to form loop, described high-temperature level evaporimeter two ends are parallel with Intermediate Heat Exchanger, described low-temperature level system to be connected with low-temperature level evaporimeter by low-temperature level compressor and to form loop with Intermediate Heat Exchanger, wherein, the liquid feeding end of described high-temperature level evaporimeter and the high-temperature level liquid feeding end of Intermediate Heat Exchanger are respectively equipped with throttling arrangement, described control system is by controlling unlatching or the closedown of throttling arrangement, control liquid refrigerant in high-temperature level system and flow through Intermediate Heat Exchanger or high-temperature level evaporimeter.
By the control of overlapping unit control system, under middle high temperature mode, high-temperature level compressor operating, low-temperature level compressor is out of service, the throttling arrangement be connected with high-temperature level evaporimeter is opened, and the throttling arrangement be connected with Intermediate Heat Exchanger cuts out, and the cold-producing medium of excessively cold high-temperature level system only flows through high-temperature level evaporimeter, and carry out heat exchange with the wind that the external world is blown into, be reduced to 15 DEG C ~-25 DEG C to make the temperature of freezer; Under low temperature mode, high-temperature level compressor and low-temperature level compressor run simultaneously, the throttling arrangement be connected with high-temperature level evaporimeter cuts out, the throttling arrangement be connected with Intermediate Heat Exchanger is opened, the cold-producing medium crossing cold high-temperature level system only flows through Intermediate Heat Exchanger, and carries out heat exchange with low-temperature level system, finally makes the temperature of low-temperature level system refrigerant reduce, the liquid refrigerant of the lower low-temperature level system of temperature carries out heat exchange with the extraneous wind be blown into, and is reduced to-25 DEG C ~-60 DEG C to make the temperature of freezer.
Wherein, described high-temperature level system also comprises high-temperature level oil eliminator, high-temperature level reservoir, high-temperature level economizer, high-temperature level absorb blower fan and high-temperature level gas-liquid separator, and outlet side and the high-temperature level condenser of described high-temperature level oil eliminator top and high-temperature level compressor are connected respectively.
Described high-temperature level reservoir liquid feeding end is connected with high-temperature level condenser, outlet end is divided into two branch roads, a branch road is provided with throttling arrangement and is connected successively by the gas supplementing opening of this throttling arrangement with high-temperature level economizer liquid feeding end, high-temperature level compressor, and another branch road is connected with high-temperature level evaporimeter by high-temperature level economizer.In high temperature economizer, the liquid refrigerant coming from high-temperature level reservoir divides two-way to enter high-temperature level economizer, and two-way cold-producing medium flows in opposite directions, one road liquid refrigerant make another road liquid refrigerant cross cold after become gaseous state, and flow back in suction muffler by pipeline through the gas supplementing opening of high-temperature level compressor; Cross cold liquid refrigerant and enter high-temperature level evaporimeter or Intermediate Heat Exchanger through pipeline.
Described high-temperature level absorbs one side that high-temperature level evaporimeter is located at by blower fan, described high-temperature level gas-liquid separator is located between high-temperature level evaporimeter and high-temperature level compressor, the suction end of high-temperature level gas-liquid separator is connected with high-temperature level evaporimeter outlet side, and outlet side is connected with high-temperature level compressor.
Further, described high-temperature level system also comprises high-temperature level lubricating oil system, and described high-temperature level lubricating oil system is that bottom high-temperature level oil eliminator, oil outlet end is connected with high-temperature level compressor by the high-temperature level oil pressure difference switch be provided with.Controlling lubricating oil by high-temperature level oil pressure difference switch to flow between oil eliminator and high-temperature level compressor, ensureing the even running when lubricating good of high-temperature level compressor.
Described high-temperature level liquid spray system is that high-temperature level reservoir outlet end is also provided with another branch road and is connected with high-temperature level compressor air suction chamber by throttling arrangement, and described throttling arrangement is also connected with the temperature sensor of the outlet side being located at high-temperature level compressor.When temperature sensor detects that the gas temperature of high-temperature level compressor outlet side is too high, the throttling arrangement that control system controls on the branch road in high-temperature level reservoir and high-temperature level compressor air suction chamber is opened, liquid refrigerant in high-temperature level reservoir flows to the suction muffler of high-temperature level compressor by this branch road, quick cooling down high-temperature stage compressor, make high-temperature level compressor recover the normal temperature run, avoid high-temperature level compressor internal part to damage.
Wherein, described low-temperature level system also comprises low-temperature level oil eliminator, low-temperature level reservoir, low-temperature level economizer, low-temperature level absorption blower fan, low-temperature level gas-liquid separator and expansion drum.Described low-temperature level oil eliminator top is connected respectively with the outlet side of low-temperature level compressor and the low-temperature level inlet end of Intermediate Heat Exchanger.Described low-temperature level reservoir liquid feeding end is connected with the low-temperature level outlet side of Intermediate Heat Exchanger, outlet end is divided into two branch roads, a branch road is provided with throttling arrangement and is connected successively by the gas supplementing opening of this throttling arrangement with low-temperature level economizer liquid feeding end, low-temperature level compressor, and another branch road is connected with low-temperature level evaporimeter by low-temperature level economizer.Described low-temperature level absorbs one side that low-temperature level evaporimeter is located at by blower fan, described low-temperature level gas-liquid separator is located between low-temperature level evaporimeter and low-temperature level compressor, the suction end of low-temperature level gas-liquid separator is connected with low-temperature level evaporimeter outlet side, and outlet side is connected with low-temperature level compressor.
Described expansion drum is parallel between low-temperature level oil eliminator outlet side branch road and low-temperature level gas-liquid separator outlet side branch road by system pipeline, between described expansion drum and low-temperature level oil eliminator, pipeline is also provided with throttling arrangement.
Further, described low-temperature level system also comprises low-temperature level lubricating oil system, and described low-temperature level lubricating oil system is that bottom low-temperature level oil eliminator, oil outlet end is connected with low-temperature level compressor by the low-temperature level oil pressure difference switch be provided with.Controlling lubricating oil by low-temperature level oil pressure difference switch to flow between oil eliminator and low-temperature level compressor, ensureing the even running when lubricating good of low-temperature level compressor.
Described low-temperature level liquid spray system is that low-temperature level reservoir outlet end is also provided with another branch road and is connected with low-temperature level compressor air suction chamber by throttling arrangement, and described throttling arrangement is also connected with the temperature sensor of the outlet side being located at low-temperature level compressor.When temperature sensor detects that the gas temperature of low-temperature level compressor outlet side is too high, the throttling arrangement that control system controls on the branch road in low-temperature level reservoir and low-temperature level compressor air suction chamber is opened, liquid refrigerant in low-temperature level reservoir flows to the suction muffler of low-temperature level compressor by this branch road, quick cooling low-temperature level compressor, make low-temperature level compressor recover the normal temperature run, avoid low-temperature level compressor internal part to damage.
In this, High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store carry out work in such a way:
Design temperature on the panel of described control system, control system, according to design temperature, judges that design temperature is in middle high temperature mode temperature range or low temperature mode temperature range, wherein, middle high temperature mode temperature range is 15 DEG C ~-25 DEG C, and low temperature mode temperature range is-25 DEG C ~-60 DEG C.If judge, design temperature is in middle high temperature mode temperature range, then control overlapping unit and enter middle high temperature mode, if design temperature is in low temperature mode temperature range, then controls overlapping unit and enters low temperature mode.
Under middle high temperature mode, described control system controls high-temperature level compressor and opens, and the throttling arrangement of connection high-temperature level economizer, high-temperature level evaporimeter is in opening; Low-temperature level compressor shutdown, connects the throttling arrangement closedown of low-temperature level economizer, low-temperature level evaporimeter, expansion drum, Intermediate Heat Exchanger.
Gaseous refrigerant flows into high-temperature level oil eliminator by high-temperature level compressor outlet side through system pipeline, and cold-producing medium enters high-temperature level condenser from the outlet side of high-temperature level oil eliminator.Cold-producing medium becomes liquid state from gaseous state in high-temperature level condenser, and liquid refrigerant enters into high-temperature level reservoir by high-temperature level condenser, enters high-temperature level economizer make cold-producing medium excessively cold from high-temperature level reservoir cold-producing medium out through throttling arrangement throttling.Cross cold cold-producing medium and enter high-temperature level evaporimeter through throttling arrangement, cold-producing medium evaporates and absorbs the heat being absorbed the external wind that blower fan is blown into by high-temperature level, cold-producing medium enters high-temperature level gas-liquid separator after high-temperature level evaporimeter, finally gets back to high-temperature level compressor inlet end.
Under low temperature mode, described control system controls compressor in high-temperature level system and opens, and the throttling arrangement connecting high-temperature level economizer is opened, and the throttling arrangement connecting high-temperature level evaporimeter cuts out; Low-temperature level system compressors and connect low-temperature level economizer, low-temperature level evaporimeter, expansion drum, Intermediate Heat Exchanger throttling arrangement open.
Gaseous refrigerant flows into high-temperature level oil eliminator by high-temperature level compressor outlet side through system pipeline, and cold-producing medium enters high-temperature level condenser from the outlet side of high-temperature level oil eliminator.Cold-producing medium becomes liquid state from gaseous state in high-temperature level condenser, and liquid refrigerant enters into high-temperature level reservoir by high-temperature level condenser, enters high-temperature level economizer make cold-producing medium excessively cold from high-temperature level reservoir cold-producing medium out through throttling arrangement throttling.Cross cold cold-producing medium and enter Intermediate Heat Exchanger through throttling arrangement, in Intermediate Heat Exchanger, cold-producing medium evaporation absorbs the heat of low-temperature level system refrigerant, cold-producing medium enters high-temperature level gas-liquid separator after Intermediate Heat Exchanger, finally gets back to the inlet end of high-temperature level compressor.In low-temperature level system, gaseous refrigerant flows into low-temperature level oil eliminator by low-temperature level compressor outlet side through system pipeline.Cold-producing medium enters Intermediate Heat Exchanger from the outlet side of low-temperature level oil eliminator, in Intermediate Heat Exchanger, condensation of refrigerant heat release becomes liquid state from gaseous state, liquid refrigerant enters into low-temperature level reservoir by Intermediate Heat Exchanger, makes cold-producing medium excessively cold from low-temperature level reservoir cold-producing medium out through low-temperature level economizer.Cross cold cold-producing medium and enter low-temperature level evaporimeter through throttling arrangement, in low-temperature level evaporimeter, cold-producing medium evaporation absorbs by the heat absorbing the external wind that blower fan is blown into.Last cold-producing medium enters low-temperature level gas-liquid separator through low-temperature level evaporimeter, finally gets back to the inlet end of low-temperature level compressor.
Preferably, described high-temperature level compressor is screw compressor; Low-temperature level compressor is screw machine compressor or piston compressor.
Preferably, the throttling arrangement in described overlapping unit is electric expansion valve, or is the throttling arrangements such as heating power expansion valve, orifice plate, capillary.
In addition, described high-temperature level lubricating oil system uses cooling water or Air flow, or utilizes the refrigerant cools of self.
The cold-producing medium of described high-temperature level system is R22, R404a or R134a type cold-producing medium; The cold-producing medium of described low-temperature level system is R23 or R507 type cold-producing medium.
Compared with prior art, technical solution of the present invention has following beneficial effect:
(1) the middle High Temperature Refrigeratory that relates to of technical solution of the present invention and the dual-purpose overlapping unit operation wide ranges of low-temperature cold store, simple to operate, stable and reliable operation, strong adaptability, can provide and select different operational modes according to different situations, for freezer provides different colds, under middle high temperature mode, freezer can be made to stablize and to be down to 15 DEG C ~-25 DEG C.Under low temperature mode, freezer can be made to stablize and to be down to-25 DEG C ~-60 DEG C, not need the freezing unit being equipped with different model in response to different situations, the object of a tractor serves several purposes can be reached.This unit is energy-efficient, and minimizing equipment takes up an area, reduces the vacancy rate of equipment, adapts to the requirement to the freezing unit of freezer in modern industry.
(2) in this, High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store arrange spray system and lubricating oil system in high-temperature level system and low-temperature level system simultaneously, compressor can be made to keep preferably running temperature, with lubricating oil unobstructed flowing within the compressor, improve the service life of compressor, thus improve the stability of this handpiece Water Chilling Units refrigerating operaton.
Accompanying drawing explanation
Fig. 1 is the structural representation of the embodiment of the present invention 1;
Wherein, 1-high-temperature level compressor, 2-high-temperature level oil eliminator, 3-high-temperature level condenser, 4-high-temperature level reservoir, 5-high-temperature level economizer, 6-heating power expansion valve, 7-high-temperature level oil pressure difference switch, 8-electric expansion valve, 9-high-temperature level evaporimeter, 10-high-temperature level absorbs blower fan, 11-high-temperature level gas-liquid separator, 12-electric expansion valve, 13-Intermediate Heat Exchanger, 14-low-temperature level compressor, 15-low-temperature level oil eliminator, 16-expansion drum, 17-low-temperature level reservoir, 18-heating power expansion valve, 19-low-temperature level economizer, 20-electric expansion valve, 21-low-temperature level evaporimeter, 22-low-temperature level absorbs blower fan, 23-low-temperature level gas-liquid separator, 24-expansion valve, 25-expansion valve, 26-low-temperature level oil pressure difference switch, 27-temperature sensor, 28-temperature sensor.
Detailed description of the invention
Be described principle of the present invention and feature below in conjunction with accompanying drawing, examples cited are only for explaining technical scheme of the present invention, and protection scope of the present invention is not limited only to this.
If Fig. 1 is the dual-purpose overlapping unit of a kind of middle High Temperature Refrigeratory and low-temperature cold store, described overlapping unit comprises high-temperature level system, low-temperature level system and control system, described high-temperature level system is connected by Intermediate Heat Exchanger 13 with low-temperature level system, described high-temperature level system is by high-temperature level compressor 1, high-temperature level condenser 3 and high-temperature level evaporimeter 9 are in turn connected to form loop, described high-temperature level evaporimeter 9 two ends are parallel with Intermediate Heat Exchanger 13, described low-temperature level system to be connected with low-temperature level evaporimeter 21 by low-temperature level compressor 14 and to form loop with Intermediate Heat Exchanger 13, wherein, the liquid feeding end of described high-temperature level evaporimeter 9 is provided with electric expansion valve 8, the high-temperature level liquid feeding end of described Intermediate Heat Exchanger is provided with electric expansion valve 12, described control system is by controlling unlatching or the closedown of electric expansion valve 8 and electric expansion valve 12, control liquid refrigerant in high-temperature level system and flow through Intermediate Heat Exchanger 13 or high-temperature level evaporimeter 9.
By the control of overlapping unit control system, under middle high temperature mode, high-temperature level compressor 1 runs, low-temperature level compressor 14 is out of service, the throttling arrangement be connected with high-temperature level evaporimeter 9 is opened, and the throttling arrangement be connected with Intermediate Heat Exchanger 13 cuts out, and excessively cold high-temperature level refrigeration agent only flows through high-temperature level evaporimeter 9, and carry out heat exchange with the wind that the external world is blown into, be reduced to 15 DEG C ~-25 DEG C to make the temperature of freezer; Under low temperature mode, high-temperature level compressor 1 and low-temperature level compressor 14 run simultaneously, the throttling arrangement be connected with high-temperature level evaporimeter 9 cuts out, the throttling arrangement be connected with Intermediate Heat Exchanger 13 is opened, cross cold high-temperature level refrigeration agent and only flow through Intermediate Heat Exchanger 9, and carry out heat exchange with low-temperature level system, finally make the temperature of low-temperature level cold-producing medium reduce, the liquid low temperature level cold-producing medium that temperature is lower carries out heat exchange with the extraneous wind be blown into, and is reduced to-25 DEG C ~-60 DEG C to make the temperature of freezer.
Wherein, described high-temperature level system also comprises high-temperature level oil eliminator 2, high-temperature level reservoir 4, high-temperature level economizer 5, high-temperature level absorb blower fan 10 and high-temperature level gas-liquid separator 11, and outlet side and the high-temperature level condenser 3 of described high-temperature level oil eliminator 2 top and high-temperature level compressor 1 are connected respectively.Described high-temperature level reservoir 4 liquid feeding end is connected with high-temperature level condenser 3, outlet end is divided into two branch roads, a branch road is provided with heating power expansion valve 6 and is connected successively by the gas supplementing opening of this heating power expansion valve 6 with high-temperature level economizer 5 liquid feeding end, high-temperature level compressor 1, and another branch road is connected with high-temperature level evaporimeter 9 by high-temperature level economizer 5.In high temperature economizer 5, the liquid refrigerant coming from high-temperature level reservoir 4 divides two-way to enter high-temperature level economizer 5, and flowed in opposite directions by cold-producing medium, one road liquid refrigerant make another road liquid refrigerant cross cold after become gaseous state, and to be flowed back in suction muffler by the gas supplementing opening of pipeline through high-temperature level compressor 1.Cross cold liquid refrigerant and enter high-temperature level evaporimeter 9 or Intermediate Heat Exchanger 13 through pipeline.
Described high-temperature level absorbs one side that high-temperature level evaporimeter 9 is located at by blower fan 10, described high-temperature level gas-liquid separator 11 is located between high-temperature level evaporimeter 9 and high-temperature level compressor 1, the suction end of high-temperature level gas-liquid separator 11 is connected with high-temperature level evaporimeter 9 outlet side, and outlet side is connected with high-temperature level compressor 1.
Described high-temperature level system also comprises high-temperature level lubricating oil system, and described high-temperature level lubricating oil system is that bottom high-temperature level oil eliminator 2, oil outlet end is connected with high-temperature level compressor 1 by the high-temperature level oil pressure difference switch 7 be provided with.Controlling lubricating oil by high-temperature level oil pressure difference switch 7 to flow between oil eliminator 2 and high-temperature level compressor 1, ensureing high-temperature level compressor 1 even running when lubricating good.
Described high-temperature level liquid spray system is that high-temperature level reservoir 4 outlet end is also provided with another branch road and is connected with high-temperature level compressor 1 suction muffler by expansion valve 24, and described expansion valve 24 is also connected with the temperature sensor 27 of the outlet side being located at high-temperature level compressor 1.When temperature sensor 27 detects that the gas temperature of high-temperature level compressor 1 outlet side is too high, control system controls high-temperature level reservoir 4 and opens with the expansion valve 24 on the branch road of high-temperature level compressor 1 suction muffler, liquid refrigerant in high-temperature level reservoir 4 flows to the suction muffler of high-temperature level compressor 1 by this branch road, quick cooling down high-temperature stage compressor 1, makes high-temperature level compressor 1 recover the normal temperature run.
Wherein, described low-temperature level system also comprises low-temperature level oil eliminator 15, low-temperature level reservoir 17, low-temperature level economizer 19, low-temperature level absorption blower fan 22, low-temperature level gas-liquid separator 23 and expansion drum 16; Described low-temperature level oil eliminator 15 top is connected respectively with the outlet side of low-temperature level compressor 14 and the low-temperature level inlet end of Intermediate Heat Exchanger 13.Described low-temperature level reservoir 17 liquid feeding end is connected with the low-temperature level outlet side of Intermediate Heat Exchanger 13, outlet end is divided into two branch roads, a branch road is provided with heating power expansion valve 18 and is connected successively by the gas supplementing opening of this heating power expansion valve 18 with low-temperature level economizer 19 liquid feeding end, low-temperature level compressor 14, and another branch road is connected with low-temperature level evaporimeter 21 by low-temperature level economizer 19.Described low-temperature level absorbs one side that low-temperature level evaporimeter 21 is located at by blower fan 22, described low-temperature level gas-liquid separator 23 is located between low-temperature level evaporimeter 19 and low-temperature level compressor 14, the suction end of low-temperature level gas-liquid separator 23 is connected with low-temperature level evaporimeter 21 outlet side, and outlet side is connected with high-temperature level compressor 14.
Described expansion drum 16 is parallel between low-temperature level oil eliminator 15 outlet side branch road and low-temperature level gas-liquid separator 23 outlet side branch road by system pipeline, between described expansion drum 16 and low-temperature level oil eliminator 15, pipeline is also provided with throttling arrangement.
Described low-temperature level system also comprises low-temperature level lubricating oil system, and described low-temperature level lubricating oil system is that bottom low-temperature level oil eliminator 15, oil outlet end is connected with low-temperature level compressor 14 by the low-temperature level oil pressure difference switch 26 be provided with.Controlling lubricating oil by low-temperature level oil pressure difference switch 26 to flow between oil eliminator 15 and low-temperature level compressor 14, ensureing low-temperature level compressor 14 even running when lubricating good.
Described low-temperature level liquid spray system is that low-temperature level reservoir 17 outlet end is also provided with another branch road and is connected with low-temperature level compressor 14 suction muffler by expansion valve 25, and described expansion valve 25 is also connected with the temperature sensor 28 of the outlet side being located at low-temperature level compressor 14.When temperature sensor detects that the gas temperature of low-temperature level compressor 14 outlet side is too high, control system controls low-temperature level reservoir 17 and opens with the expansion valve 25 on the branch road of low-temperature level compressor 14 suction muffler, liquid refrigerant in low-temperature level reservoir 17 flows to the suction muffler of low-temperature level compressor 14 by this branch road, quick cooling low-temperature level compressor 14, makes low-temperature level compressor 14 recover the normal temperature run.
In this, High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store carry out work in such a way:
Design temperature on the panel of described control system, control system, according to design temperature, judges that design temperature is in middle high temperature mode temperature range or low temperature mode temperature range, wherein, middle high temperature mode temperature range is 15 DEG C ~-25 DEG C, and low temperature mode temperature range is-25 DEG C ~-60 DEG C.If judge, design temperature is in middle high temperature mode temperature range, then control overlapping unit and enter middle high temperature mode, if design temperature is in low temperature mode temperature range, then controls overlapping unit and enters low temperature mode.
Under middle high temperature mode, when temperature of ice house needs to reduce, described control system controls high-temperature level compressor 1 and opens, connection high-temperature level economizer 5, the heating power expansion valve 6 of high-temperature level evaporimeter 9, electric expansion valve 8 are in opening, and the electric expansion valve 12 connecting Intermediate Heat Exchanger is in closed condition; Low-temperature level system compressors 1 is shut down, and its heating power expansion valve 18, electric expansion valve 20 are in closed condition.
Gaseous refrigerant flows into high-temperature level oil eliminator 2 by high-temperature level compressor 1 outlet side through system pipeline, and cold-producing medium enters high-temperature level condenser 3 from the outlet side of high-temperature level oil eliminator 2; Cold-producing medium becomes liquid state from gaseous state in high-temperature level condenser 3, liquid refrigerant enters into high-temperature level reservoir 4 by high-temperature level condenser 3, enters high-temperature level economizer 5 make cold-producing medium excessively cold from high-temperature level reservoir 4 cold-producing medium out through heating power expansion valve 6 throttling; Cross cold cold-producing medium and enter high-temperature level evaporimeter 9 through electric expansion valve 8, cold-producing medium evaporates and absorbs the heat being absorbed the external wind that blower fan 10 is blown into by high-temperature level, cold-producing medium enters high-temperature level gas-liquid separator 11 after high-temperature level evaporimeter 9, finally gets back to high-temperature level compressor 1 inlet end;
Under low temperature mode, described control system controls high-temperature level compressor 1 in high-temperature level system and opens, and the heating power expansion valve 6 connecting high-temperature level economizer 5 is opened, and the electric expansion valve 8 connecting high-temperature level evaporimeter 9 is closed; Low-temperature level system compressors 14, and connect the heating power expansion valve 18 of low-temperature level economizer 19, the electric expansion valve 20 connecting low-temperature level evaporimeter, the throttling arrangement connecting expansion drum 16, the electric expansion valve 12 that connects Intermediate Heat Exchanger 13 open.
Gaseous refrigerant flows into high-temperature level oil eliminator 2 by high-temperature level compressor 1 outlet side through system pipeline, and cold-producing medium enters high-temperature level condenser 3 from the outlet side of high-temperature level oil eliminator 2; Cold-producing medium becomes liquid state from gaseous state in high-temperature level condenser 3, liquid refrigerant enters into high-temperature level reservoir 4 by high-temperature level condenser 3, enters high-temperature level economizer 5 make cold-producing medium excessively cold from high-temperature level reservoir 4 cold-producing medium out through heating power expansion valve 6 throttling; Cross cold cold-producing medium and enter Intermediate Heat Exchanger 13 through electric expansion valve 12, in Intermediate Heat Exchanger 13, cold-producing medium evaporation absorbs the heat of low-temperature level system refrigerant, cold-producing medium enters high-temperature level gas-liquid separator 11 after Intermediate Heat Exchanger 13, finally gets back to the inlet end of high-temperature level compressor 1.In low-temperature level system, gaseous refrigerant flows into low-temperature level oil eliminator 15 by low-temperature level compressor 14 outlet side through system pipeline; Cold-producing medium enters Intermediate Heat Exchanger 13 from the outlet side of low-temperature level oil eliminator 15, in Intermediate Heat Exchanger 13, condensation of refrigerant heat release becomes liquid state from gaseous state, liquid refrigerant enters into low-temperature level reservoir 17 by Intermediate Heat Exchanger 13, makes cold-producing medium excessively cold from low-temperature level reservoir 17 cold-producing medium out through low-temperature level economizer 19; Cross cold cold-producing medium and enter low-temperature level evaporimeter 21 through electric expansion valve 20, in low-temperature level evaporimeter 21, cold-producing medium evaporation absorbs the heat being absorbed the external wind that blower fan 22 is blown into by low-temperature level.Last cold-producing medium enters low-temperature level gas-liquid separator 23 through low-temperature level evaporimeter 21, finally gets back to the inlet end of low-temperature level compressor 14.
Claims (10)
1. High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store in one kind, described overlapping unit comprises high-temperature level system, low-temperature level system and control system, described high-temperature level system is connected by Intermediate Heat Exchanger with low-temperature level system, described high-temperature level system is by high-temperature level compressor, high-temperature level condenser and high-temperature level evaporimeter are in turn connected to form loop, described high-temperature level evaporimeter two ends are parallel with Intermediate Heat Exchanger, described low-temperature level system to be connected with low-temperature level evaporimeter by low-temperature level compressor and to form loop with Intermediate Heat Exchanger, it is characterized in that, the liquid feeding end of described high-temperature level evaporimeter and the high-temperature level liquid feeding end of Intermediate Heat Exchanger are respectively equipped with throttling arrangement, described control system is by controlling unlatching or the closedown of throttling arrangement, control liquid refrigerant in high-temperature level system and flow through Intermediate Heat Exchanger or high-temperature level evaporimeter.
2. according to claim 1 in High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store, it is characterized in that, described high-temperature level system also comprises high-temperature level oil eliminator, high-temperature level reservoir, high-temperature level economizer, high-temperature level absorption blower fan and high-temperature level gas-liquid separator; Outlet side and the high-temperature level condenser of described high-temperature level oil eliminator top and high-temperature level compressor are connected respectively; Described high-temperature level reservoir liquid feeding end is connected with high-temperature level condenser, outlet end is divided into two branch roads, a branch road is provided with throttling arrangement and is connected successively by the gas supplementing opening of this throttling arrangement with high-temperature level economizer liquid feeding end, high-temperature level compressor, and another branch road is connected with high-temperature level evaporimeter by high-temperature level economizer; Described high-temperature level absorbs one side that high-temperature level evaporimeter is located at by blower fan, described high-temperature level gas-liquid separator is located between high-temperature level evaporimeter and high-temperature level compressor, the suction end of high-temperature level gas-liquid separator is connected with high-temperature level evaporimeter outlet side, and outlet side is connected with high-temperature level compressor.
3. according to claim 2 in High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store, it is characterized in that, described high-temperature level system also comprises high-temperature level lubricating oil system, and described high-temperature level lubricating oil system is that bottom high-temperature level oil eliminator, oil outlet end is connected with high-temperature level compressor by the high-temperature level oil pressure difference switch be provided with.
4. according to claim 2 in High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store, it is characterized in that, described high-temperature level system also comprises high-temperature level liquid spray system, described high-temperature level liquid spray system is that high-temperature level reservoir outlet end is also provided with another branch road and is connected with high-temperature level compressor air suction chamber by throttling arrangement, and described throttling arrangement is also connected with the temperature sensor being located at high-temperature level compressor outlet side.
5. according to claim 1 in High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store, it is characterized in that, described low-temperature level system also comprises low-temperature level oil eliminator, low-temperature level reservoir, low-temperature level economizer, low-temperature level absorption blower fan, low-temperature level gas-liquid separator and expansion drum; Described low-temperature level oil eliminator top is connected respectively with the outlet side of low-temperature level compressor and the low-temperature level inlet end of Intermediate Heat Exchanger; Described low-temperature level reservoir liquid feeding end is connected with the low-temperature level outlet end of Intermediate Heat Exchanger, outlet end is divided into two branch roads, a branch road is provided with throttling arrangement and is connected successively by the gas supplementing opening of this throttling arrangement with low-temperature level economizer liquid feeding end, low-temperature level compressor, and another branch road is connected with low-temperature level evaporimeter by low-temperature level economizer; Described low-temperature level absorbs one side that low-temperature level evaporimeter is located at by blower fan, described low-temperature level gas-liquid separator is located between low-temperature level evaporimeter and low-temperature level compressor, the suction end of low-temperature level gas-liquid separator is connected with low-temperature level evaporimeter outlet side, and outlet side is connected with low-temperature level compressor;
Described expansion drum is parallel between low-temperature level oil eliminator outlet side branch road and low-temperature level gas-liquid separator outlet side branch road by system pipeline, and the pipeline that described expansion drum is connected with low-temperature level oil eliminator is also provided with throttling arrangement.
6. according to claim 5 in High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store, it is characterized in that, described low-temperature level system also comprises low-temperature level lubricating oil system, and described low-temperature level lubricating oil system is that bottom low-temperature level oil eliminator, oil outlet end is connected with low-temperature level compressor by the low-temperature level oil pressure difference switch be provided with.
7. according to claim 5 in High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store, it is characterized in that, described low-temperature level system also comprises high-temperature level liquid spray system, described low-temperature level liquid spray system is that low-temperature level reservoir outlet end is also provided with another branch road and is connected with low-temperature level compressor air suction chamber by throttling arrangement, and described throttling arrangement is also connected with the temperature sensor being located at low-temperature level compressor outlet side.
8. High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store according to any one of claim 1 ~ 7, it is characterized in that, described overlapping unit runs in the following manner:
Design temperature on the panel of described control system, control system is selected to control described overlapping unit according to design temperature and is entered middle high temperature mode or low temperature mode;
Under middle high temperature mode, described control system controls high-temperature level compressor and opens, and the throttling arrangement of connection high-temperature level economizer, high-temperature level evaporimeter is in opening; Low-temperature level compressor shutdown, connects the throttling arrangement closedown of low-temperature level economizer, low-temperature level evaporimeter, expansion drum, Intermediate Heat Exchanger;
Under low temperature mode, described control system controls compressor in high-temperature level system and opens, and the throttling arrangement connecting high-temperature level economizer is opened, and the throttling arrangement connecting high-temperature level evaporimeter cuts out; Low-temperature level system compressors, and the throttling arrangement unlatching connecting low-temperature level economizer, low-temperature level evaporimeter, expansion drum, Intermediate Heat Exchanger.
9. according to claim 1 in High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store, it is characterized in that, described high-temperature level compressor is screw compressor; Low-temperature level compressor is screw machine compressor or piston compressor.
10. according to claim 8 in High Temperature Refrigeratory and the dual-purpose overlapping unit of low-temperature cold store, it is characterized in that, the throttling arrangement in described overlapping unit is electric expansion valve, heating power expansion valve, orifice plate or capillary.
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107631507A (en) * | 2017-11-02 | 2018-01-26 | 珠海格力电器股份有限公司 | Air-conditioning device and refrigeration storage system control method |
| CN108266915A (en) * | 2018-03-05 | 2018-07-10 | 天津商业大学 | It is a kind of to use single working medium CO2Make the cascade refrigeration system of refrigerant |
| CN109579408A (en) * | 2018-12-29 | 2019-04-05 | 南京久鼎制冷空调设备有限公司 | A kind of freezer water-cooled all-in-one machine |
| CN110375469A (en) * | 2019-06-24 | 2019-10-25 | 广东伊莱智科科技有限公司 | A kind of frequency conversion overlapping machine control method, device, equipment and storage medium |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101158530A (en) * | 2007-10-31 | 2008-04-09 | 蓬莱京鲁渔业有限公司 | Ultra low temperature cool house |
| CN101182958A (en) * | 2007-11-21 | 2008-05-21 | 山东富尔达空调设备有限公司 | Two-stage compression high-temperature water source heat pump machine group using low-temperature heat power supply |
| CN201866979U (en) * | 2010-10-15 | 2011-06-15 | 中山长虹电器有限公司 | Household air conditioner capable of realizing low-temperature heating |
| KR101335278B1 (en) * | 2012-07-19 | 2013-11-29 | 에스에이비(주) | Dual cycle heat pump system |
| CN103486754A (en) * | 2013-08-26 | 2014-01-01 | 安徽亿瑞深冷能源科技有限公司 | Energy-saving middle temperature refrigerant/middle temperature refrigerant cascade refrigeration system |
| CN203501524U (en) * | 2013-06-08 | 2014-03-26 | 北京振兴华龙制冷设备有限责任公司 | Double compressor cascade type low temperature air source heat pump unit |
| CN104236164A (en) * | 2014-09-15 | 2014-12-24 | 美意(浙江)空调设备有限公司 | Ultra-high temperature cascade water source heat pump system |
| CN204254921U (en) * | 2014-09-22 | 2015-04-08 | 广东申菱空调设备有限公司 | The low-temperature cold water unit structure of single machine two-stage |
-
2015
- 2015-07-31 CN CN201510462417.4A patent/CN105004089A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101158530A (en) * | 2007-10-31 | 2008-04-09 | 蓬莱京鲁渔业有限公司 | Ultra low temperature cool house |
| CN101182958A (en) * | 2007-11-21 | 2008-05-21 | 山东富尔达空调设备有限公司 | Two-stage compression high-temperature water source heat pump machine group using low-temperature heat power supply |
| CN201866979U (en) * | 2010-10-15 | 2011-06-15 | 中山长虹电器有限公司 | Household air conditioner capable of realizing low-temperature heating |
| KR101335278B1 (en) * | 2012-07-19 | 2013-11-29 | 에스에이비(주) | Dual cycle heat pump system |
| CN203501524U (en) * | 2013-06-08 | 2014-03-26 | 北京振兴华龙制冷设备有限责任公司 | Double compressor cascade type low temperature air source heat pump unit |
| CN103486754A (en) * | 2013-08-26 | 2014-01-01 | 安徽亿瑞深冷能源科技有限公司 | Energy-saving middle temperature refrigerant/middle temperature refrigerant cascade refrigeration system |
| CN104236164A (en) * | 2014-09-15 | 2014-12-24 | 美意(浙江)空调设备有限公司 | Ultra-high temperature cascade water source heat pump system |
| CN204254921U (en) * | 2014-09-22 | 2015-04-08 | 广东申菱空调设备有限公司 | The low-temperature cold water unit structure of single machine two-stage |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107631507A (en) * | 2017-11-02 | 2018-01-26 | 珠海格力电器股份有限公司 | Air-conditioning device and refrigeration storage system control method |
| CN107631507B (en) * | 2017-11-02 | 2023-06-20 | 珠海格力电器股份有限公司 | Air conditioner and control method of refrigeration house system |
| CN108266915A (en) * | 2018-03-05 | 2018-07-10 | 天津商业大学 | It is a kind of to use single working medium CO2Make the cascade refrigeration system of refrigerant |
| CN109579408A (en) * | 2018-12-29 | 2019-04-05 | 南京久鼎制冷空调设备有限公司 | A kind of freezer water-cooled all-in-one machine |
| CN110375469A (en) * | 2019-06-24 | 2019-10-25 | 广东伊莱智科科技有限公司 | A kind of frequency conversion overlapping machine control method, device, equipment and storage medium |
| CN110701664A (en) * | 2019-11-11 | 2020-01-17 | 江苏天舒电器有限公司 | Wide-ring-temperature multi-stage water outlet variable-frequency air energy cascade type heat engine system and working method thereof |
| CN110701664B (en) * | 2019-11-11 | 2023-05-05 | 江苏天舒电器有限公司 | Wide-ring-temperature multistage water outlet variable-frequency air energy cascade heat engine system and working method thereof |
| CN112325496A (en) * | 2020-11-04 | 2021-02-05 | 四方科技集团股份有限公司 | Cold and hot matching unit for meat processing and control method |
| CN112325496B (en) * | 2020-11-04 | 2022-04-26 | 四方科技集团股份有限公司 | Cold and hot matching unit for meat processing and control method |
| CN114111232A (en) * | 2021-12-27 | 2022-03-01 | 山东新华医疗器械股份有限公司 | Temperature control system of freeze dryer |
| CN115031421A (en) * | 2022-04-14 | 2022-09-09 | 江阴市索创工业精密制冷设备有限公司 | Low-temperature skid-mounted refrigerating unit of hydrogenation machine |
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Address after: 528313 Shunde City, Foshan province Chencun town machinery and equipment Park, No. ten, No. Road, No. 8 Applicant after: GUANGDONG SHENLING AIR-CONDITIONING EQUIPMENT CO., LTD. Address before: 528313 Shunde City, Foshan province Chencun town machinery and equipment Park, No. ten, No. Road, No. 8 Applicant before: Guangdong Shenling Air Conditioning Equipment Co., Ltd. |
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