CN105004088A - Cascaded water chilling unit for dual purposes of intermediate temperature and low temperature - Google Patents
Cascaded water chilling unit for dual purposes of intermediate temperature and low temperature Download PDFInfo
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- CN105004088A CN105004088A CN201510461862.9A CN201510461862A CN105004088A CN 105004088 A CN105004088 A CN 105004088A CN 201510461862 A CN201510461862 A CN 201510461862A CN 105004088 A CN105004088 A CN 105004088A
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 60
- 230000009977 dual effect Effects 0.000 title abstract 2
- 239000007788 liquid Substances 0.000 claims abstract description 94
- 239000003507 refrigerant Substances 0.000 claims abstract description 36
- 239000003921 oil Substances 0.000 claims description 57
- 238000010438 heat treatment Methods 0.000 claims description 18
- 239000010687 lubricating oil Substances 0.000 claims description 18
- 239000007921 spray Substances 0.000 claims description 9
- 230000001502 supplementing effect Effects 0.000 claims description 7
- 238000001816 cooling Methods 0.000 description 10
- 238000005057 refrigeration Methods 0.000 description 8
- 239000003795 chemical substances by application Substances 0.000 description 5
- 230000008020 evaporation Effects 0.000 description 5
- 238000001704 evaporation Methods 0.000 description 5
- 239000000498 cooling water Substances 0.000 description 4
- 238000007710 freezing Methods 0.000 description 4
- 230000008014 freezing Effects 0.000 description 4
- 230000001050 lubricating effect Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 3
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 239000000243 solution Substances 0.000 description 3
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 230000003434 inspiratory effect Effects 0.000 description 2
- UXVMQQNJUSDDNG-UHFFFAOYSA-L Calcium chloride Chemical compound [Cl-].[Cl-].[Ca+2] UXVMQQNJUSDDNG-UHFFFAOYSA-L 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000010729 system oil Substances 0.000 description 1
Classifications
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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
- 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
- F25B2400/07—Details of compressors or related parts
- F25B2400/075—Details of compressors or related parts with parallel compressors
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/21—Reduction of parts
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention relates to a cascaded water chilling unit for dual purposes of intermediate temperature and low temperature. The cascaded water chilling 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 condenser, the intermediate heat exchanger and a low-temperature evaporator 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 water chilling unit can be used for producing high-temperature chilled water or low-temperature chilled water according to different conditions, energy is saved, environment friendliness is achieved, and operation is easy.
Description
Technical field
The present invention relates to superposition type cooling-water machine technical field, particularly relate to the superposition type handpiece Water Chilling Units that a kind of middle temperature, low temperature are dual-purpose.
Background technology
Modern industry is advanced by leaps and bounds, and the temperature requirement of different production technologies to chilled water is also not quite similar, and if desired provides the chilled water that temperature is higher, then need the handpiece Water Chilling Units of single-stage to carry out freezing to refrigerant, and then makes chilled water reach the temperature of expection.
The Chinese invention patent application being 201210240428.4 " handpiece Water Chilling Units " by name as application number discloses a kind of handpiece Water Chilling Units, compressor is furnished with in the side of heat exchanger, inspiratory limb pipeline, exhaust section pipeline, liquid pipeline section pipeline, Liquid injection cooling section pipeline, liquid level meter, and economizer, compressor is connected with evaporimeter by inspiratory limb pipeline, the high temperature and high pressure gas mouth of compressor connects exhaust section pipeline, exhaust section pipeline is connected to condenser, condenser connecting fluid pipeline section pipeline, first loop of liquid pipeline section pipeline connects economizer heat exchange mouth, economizer connects evaporimeter by electric expansion valve again, evaporimeter is connected with compressor, the second servo loop of liquid pipeline section pipeline connects the overheated mouth of economizer by electric expansion valve, economizer connects compressor again, liquid trap installed by condenser, liquid trap is connected to compressor by Liquid injection cooling section pipeline, liquid level meter is connected with liquid trap, in the same side of unit, regulator cubicle and switch board are also installed.By control system, unit is controlled, cold-producing medium is by the process of " gas-liquid-gaseous state ", absorb heat in refrigerant, to provide chilled water, but, this handpiece Water Chilling Units has a definite limitation in range of operation, does not provide low temperature and superfreeze water by self-operating, can not meet the needs of special producing technique to chilled water.
Be exclusively used in the needs providing the overlapping handpiece Water Chilling Units of low temperature and superfreeze water can meet some special producing techniques.The Chinese invention patent application being 200920089793.3 " ultra low temperature overlapping units " by name as application number discloses a kind of Water cooling low temperature unit directly utilizing more than 30 DEG C cooling water outputs-40 DEG C ~-75 DEG C of low-temperature receivers.It is in separate unit Water cooling low temperature unit, adopt two groups of independently Vapor Compression Refrigeration Cycle systems, and wherein the condenser heat of a group is used as another evaporation endothermic organized.And two groups of heat transmission independently between Vapor Compression Refrigeration Cycle system adopt efficient composite heat exchanger, improve set heat exchange efficiency, and heat trnasfer of cutting down the number of intermediate links loses, and realizes the long-lived operation of stability and high efficiency.This kind of ultra low temperature overlapping unit carries out overlapping heat exchange by two groups of Vapor Compression Refrigeration Cycle systems to chiller refrigeration agent, makes the temperature that liquid refrigerant can reach lower, thus with refrigerant heat exchange, produce cryogenic freezing water.But two cover systems in this overlapping unit must operate simultaneously, this unit is warm in can not producing according to different situations, the chilled water of low temperature.
Therefore, in actual production, for meeting the requirement of various processes, need the cooling-water machine being equipped with separately different temperatures scope, so not only complex operation, and 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 overlapping handpiece Water Chilling Units in prior art, provide a kind of cost low, save space, simple to operate, range of operation is wide, the superposition type cooling-water machine that can simultaneously provide middle temperature, the middle temperature of cryogenic freezing water, low temperature dual-purpose.
Object of the present invention is achieved by the following technical programs:
Temperature in one, the superposition type handpiece Water Chilling Units that low temperature is dual-purpose, described superposition type handpiece Water Chilling Units comprises high-temperature level system and 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 is by low-temperature level compressor, low-temperature level condenser, Intermediate Heat Exchanger and low-temperature level evaporimeter are in turn connected to form loop, 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 water chilling unit control system, under middle temperature pattern, 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 excessively cold high-temperature level refrigeration agent only flows through high-temperature level evaporimeter, and carry out heat exchange with extraneous refrigerating medium, to provide between the higher chilled water of 15 ~-25 DEG C of temperature.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, cross cold high-temperature level refrigeration agent and only flow through Intermediate Heat Exchanger, and carry out heat exchange with low-temperature level system, finally make the temperature of low-temperature level cold-producing medium reduce, and with extraneous refrigerating medium heat exchange, to provide between the lower chilled water of-25 DEG C ~-60 DEG C temperature.
Wherein, described high-temperature level system also comprises high-temperature level oil eliminator, high-temperature level reservoir, high-temperature level economizer 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 gas-liquid separator is located between high-temperature level evaporimeter and high-temperature level compressor, and 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 condenser, low-temperature level reservoir, low-temperature level economizer, low-temperature level gas-liquid separator and expansion drum.Described low-temperature level oil eliminator top is connected with the outlet side of low-temperature level compressor and the inlet end of low-temperature level condenser.
Described low-temperature level reservoir liquid feeding end is connected with Intermediate Heat Exchanger low-temperature level outlet end, the outlet end of low-temperature level reservoir 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 gas-liquid separator is located between low-temperature level evaporimeter and low-temperature level compressor, and 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.
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 of 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.
Warm in this, that low temperature is dual-purpose superposition type handpiece Water Chilling Units carries 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 temperature model temperature scope or low temperature mode temperature range, wherein, middle temperature model temperature scope 15 DEG C ~-25 DEG C, low temperature mode temperature range-25 DEG C ~-60 DEG C.If judge, design temperature is in middle temperature model temperature scope, then control overlapping unit and enter middle temperature pattern, if design temperature is in low temperature mode temperature range, then controls overlapping unit and enters low temperature mode.
Under middle temperature pattern, 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 of extraneous refrigerating medium, and 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 high-temperature level 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 enters low-temperature level condenser by low-temperature level compressor outlet side after system pipeline inflow low-temperature level oil eliminator; In low-temperature level condenser, condensation of refrigerant heat release becomes liquid state from gaseous state, liquid refrigerant enters Intermediate Heat Exchanger by low-temperature level condenser and cools, after cooling, the lower liquid refrigerant of temperature 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 the heat of extraneous refrigerating medium.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 superposition type handpiece Water Chilling Units is electric expansion valve, or is heating power expansion valve, orifice plate, capillary.
In addition, the refrigerating medium of described handpiece Water Chilling Units is anti-icing fluid, comprises the ethylene glycol solution of mass fraction 32.4% ~ 63%, the calcium chloride solution of mass fraction 18% ~ 30%, the glacial epoch refrigerant of LM-1 ~ LM-8 model.
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 comprises R23 or R507 type cold-producing medium.
Compared with prior art, technical solution of the present invention has following beneficial effect:
(1) the handpiece Water Chilling Units range of operation that relates to of technical solution of the present invention is wide, simple to operate, stable and reliable operation, strong adaptability, can provide and select different operational modes according to different situations, to provide the chilled water of different temperatures, under middle temperature pattern, the chilled water of 15 ~-25 DEG C can be produced, under low temperature mode, the chilled water of-25 DEG C ~-60 DEG C can be produced, do not need the handpiece Water Chilling Units being equipped with different model in response to different situations, reach the object of a tractor serves several purposes.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) this handpiece Water Chilling Units arranges 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-expansion valve, 6-high-temperature level economizer, 7-heating power expansion valve, 8-high-temperature level evaporimeter, 9-high-temperature level gas-liquid separator, 10-expansion valve, 11-low-temperature level compressor, 12-low-temperature level oil eliminator, 13-low-temperature level condenser, 14-Intermediate Heat Exchanger, 15-magnetic valve, 16-low-temperature level reservoir, 17-low-temperature level economizer, 18-expansion valve, 19-low-temperature level evaporimeter, 20-low-temperature level gas-liquid separator, 21-expansion drum, 22-expansion valve, 23-expansion valve, 24-magnetic valve, 25-magnetic valve, 26-high-temperature level oil pressure difference switch, 27-temperature sensor, 28-low-temperature level oil pressure difference switch, 29-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 the present invention, and protection scope of the present invention is not limited only to this.
embodiment 1
If Fig. 1 is the dual-purpose superposition type handpiece Water Chilling Units of a kind of middle temperature, low temperature, described superposition type handpiece Water Chilling Units comprises high-temperature level system and low-temperature level system, and control system.Described high-temperature level system is connected by Intermediate Heat Exchanger 14 with low-temperature level system, and described high-temperature level system is in turn connected to form loop by high-temperature level compressor 1, high-temperature level condenser 3 and high-temperature level evaporimeter 8.Described high-temperature level evaporimeter 8 two ends are parallel with Intermediate Heat Exchanger 14, and described low-temperature level system forms loop successively by low-temperature level compressor 11, low-temperature level condenser 13, Intermediate Heat Exchanger 14 and low-temperature level evaporimeter 19.Wherein, the liquid feeding end of described high-temperature level evaporimeter 8 is provided with heating power expansion valve 7 and magnetic valve 24, the high-temperature level liquid feeding end of described Intermediate Heat Exchanger 14 is provided with heating power expansion valve 15 and magnetic valve 25, described control system, by controlling unlatching or the closedown of heating power expansion valve 7, magnetic valve 24, heating power expansion valve 15 and magnetic valve 25, controls liquid refrigerant in high-temperature level system and flows through Intermediate Heat Exchanger 14 or high-temperature level evaporimeter 8.
By the control of overlapping water chilling unit control system, under middle temperature pattern, high-temperature level compressor 1 runs, low-temperature level compressor 11 is out of service, the heating power expansion valve 7 be connected with high-temperature level evaporimeter 8 and magnetic valve 24 are opened, and the heating power expansion valve 15 be connected with Intermediate Heat Exchanger 14 and magnetic valve 25 are closed.Cross cold high-temperature level refrigeration agent and only flow through high-temperature level evaporimeter 8, and carry out heat exchange with extraneous refrigerating medium, to provide between the higher chilled water of 15 ~-25 DEG C of temperature.Under low temperature mode, high-temperature level compressor 1 and low-temperature level compressor 11 run simultaneously, and the heating power expansion valve 7 be connected with high-temperature level evaporimeter 8 and magnetic valve 24 are closed, and the heating power expansion valve 15 be connected with Intermediate Heat Exchanger 14 and magnetic valve 25 are opened.Cross cold high-temperature level refrigeration agent and only flow through Intermediate Heat Exchanger 8, and carry out heat exchange with low-temperature level system, finally make the temperature of low-temperature level cold-producing medium reduce, and with extraneous refrigerating medium heat exchange, to provide between the lower chilled water of-25 DEG C ~-60 DEG C temperature.
Wherein, described high-temperature level system also comprises high-temperature level oil eliminator 2, high-temperature level reservoir 4, high-temperature level economizer 6 and high-temperature level gas-liquid separator 9, 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 expansion valve 5 and is connected successively by the gas supplementing opening of this expansion valve 5 with high-temperature level economizer 6 liquid feeding end, high-temperature level compressor 1, and another branch road is connected with high-temperature level evaporimeter 8 by high-temperature level economizer 6.Described high-temperature level gas-liquid separator 9 is located between high-temperature level evaporimeter 8 and high-temperature level compressor 1, and the suction end of high-temperature level gas-liquid separator 9 is connected with high-temperature level evaporimeter 8 outlet side, and outlet side is connected with high-temperature level compressor 1.
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 2, oil outlet end is connected with high-temperature level compressor 1 by the high-temperature level oil pressure difference switch 26 be provided with.Controlling lubricating oil by high-temperature level oil pressure difference switch 26 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 10, and described expansion valve 10 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 10 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, make high-temperature level compressor 1 recover the normal temperature run, avoid high-temperature level compressor 1 internal part to damage.
Wherein, described low-temperature level system also comprises low-temperature level oil eliminator 12, low-temperature level reservoir 16, low-temperature level economizer 17, low-temperature level gas-liquid separator 20 and expansion drum 21.Described low-temperature level oil eliminator 12 top is connected with the outlet side of low-temperature level compressor 11 and the inlet end of low-temperature level condenser 13.
Described low-temperature level reservoir 16 liquid feeding end is connected with Intermediate Heat Exchanger 14 low-temperature level outlet end, the outlet end of low-temperature level reservoir 16 is divided into two branch roads, a branch road is provided with expansion valve 22 and is connected successively by the gas supplementing opening of this expansion valve 22 with low-temperature level economizer 17 liquid feeding end, low-temperature level compressor 11, and another branch road is connected with low-temperature level evaporimeter 19 by low-temperature level economizer 17.
Described low-temperature level gas-liquid separator 20 is located between low-temperature level evaporimeter 19 and low-temperature level compressor 11, and the suction end of low-temperature level gas-liquid separator 20 is connected with low-temperature level evaporimeter 19 outlet side, and outlet side is connected with low-temperature level compressor 11.
Described expansion drum 21 is parallel between low-temperature level oil eliminator 12 outlet side branch road and low-temperature level gas-liquid separator 20 outlet side branch road by system pipeline, and described expansion drum 21 two ends 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 11 by the low-temperature level oil pressure difference switch 28 be provided with.Controlling lubricating oil by low-temperature level oil pressure difference switch 28 to flow between oil eliminator 12 and low-temperature level compressor 11, ensureing low-temperature level compressor 11 even running when lubricating good.
Described low-temperature level liquid spray system is that low-temperature level reservoir 16 outlet end is also provided with another branch road and is connected with low-temperature level compressor 11 suction muffler by expansion valve 23, and described expansion valve 23 is also connected with the temperature sensor 29 of the outlet side of low-temperature level compressor 11.When temperature sensor 29 detects that the gas temperature of low-temperature level compressor outlet side is too high, control system controls low-temperature level reservoir 14 and opens with the expansion valve 23 on the branch road of low-temperature level compressor 11 suction muffler, liquid refrigerant in low-temperature level reservoir 16 flows to the suction muffler of low-temperature level compressor 11 by this branch road, quick cooling low-temperature level compressor 11, make low-temperature level compressor 11 recover the normal temperature run, avoid low-temperature level compressor 11 internal part to damage.
Warm in this, that low temperature is dual-purpose superposition type handpiece Water Chilling Units carries 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 temperature model temperature scope or low temperature mode temperature range, wherein, middle temperature model temperature scope 15 DEG C ~-25 DEG C, low temperature mode temperature range-25 DEG C ~-60 DEG C.If judge, design temperature is in middle temperature model temperature scope, then control overlapping unit and enter middle temperature pattern, if design temperature is in low temperature mode temperature range, then controls overlapping unit and enters low temperature mode.
Under middle temperature pattern, described control system controls high-temperature level compressor 1 in high-temperature level system and opens, the expansion valve 5 of connection high-temperature level economizer 6, the heating power expansion valve 7 connecting high-temperature level evaporimeter, magnetic valve 24 are in opening, and the heating power expansion valve 15, the magnetic valve 25 that connect Intermediate Heat Exchanger are in closed condition; Low-temperature level system compressors 11 is shut down, and heating power expansion valve 15, magnetic valve 25, expansion valve 22, expansion valve 18, connects the throttling arrangement of expansion drum and be 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, and liquid refrigerant enters into high-temperature level reservoir 4 by high-temperature level condenser 3, enters high-temperature level economizer 6 make cold-producing medium excessively cold from high-temperature level reservoir 4 cold-producing medium out through expansion valve 5 throttling.Cross cold cold-producing medium and enter high-temperature level evaporimeter 8 through heating power expansion valve 7, magnetic valve 24, cold-producing medium evaporates and absorbs the heat of extraneous refrigerating medium, cold-producing medium enters high-temperature level gas-liquid separator 9 after high-temperature level evaporimeter 8, 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 expansion valve 5 connecting high-temperature level economizer 6 is opened, and the heating power expansion valve 7, the magnetic valve 24 that connect high-temperature level evaporimeter 8 are closed.Low-temperature level system compressors 11 and heating power expansion valve 15, magnetic valve 25, expansion valve 22, expansion valve 18, the throttling arrangement that connects expansion drum are in opening
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, and liquid refrigerant enters into high-temperature level reservoir 4 by high-temperature level condenser 3, enters high-temperature level economizer 6 make cold-producing medium excessively cold from high-temperature level reservoir 4 cold-producing medium out through expansion valve 5 throttling.Cross cold cold-producing medium and enter Intermediate Heat Exchanger 14 through magnetic valve 25, heating power expansion valve 15, in Intermediate Heat Exchanger 14, cold-producing medium evaporation absorbs the heat of low-temperature level system refrigerant, cold-producing medium enters high-temperature level gas-liquid separator 9 after Intermediate Heat Exchanger 14, 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 12 by low-temperature level compressor 11 outlet side through system pipeline; In low-temperature level system, gaseous refrigerant enters low-temperature level condenser 13 by low-temperature level compressor 11 outlet side after system pipeline inflow low-temperature level oil eliminator 12; In low-temperature level condenser 13, condensation of refrigerant heat release becomes liquid state from gaseous state, liquid refrigerant enters Intermediate Heat Exchanger 14 by low-temperature level condenser 13 and cools, after cooling, the lower liquid refrigerant of temperature enters into low-temperature level reservoir 16 by Intermediate Heat Exchanger 14, makes cold-producing medium excessively cold from low-temperature level reservoir 16 cold-producing medium out through low-temperature level economizer 17; Cross cold cold-producing medium and enter low-temperature level evaporimeter 19 through expansion valve 18, in low-temperature level evaporimeter 19, cold-producing medium evaporation absorbs the heat of extraneous refrigerating medium.Last cold-producing medium enters low-temperature level gas-liquid separator 20 through low-temperature level evaporimeter 19, finally gets back to the inlet end of low-temperature level compressor 11.
Claims (10)
1. temperature in a kind, the superposition type handpiece Water Chilling Units that low temperature is dual-purpose, described superposition type handpiece Water Chilling Units comprises high-temperature level system and 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 is by low-temperature level compressor, low-temperature level condenser, Intermediate Heat Exchanger and low-temperature level evaporimeter are in turn connected to form loop, 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. the superposition type handpiece Water Chilling Units that middle temperature according to claim 1, low temperature are dual-purpose, 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 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; Described high-temperature level gas-liquid separator is located between high-temperature level evaporimeter and high-temperature level compressor, and 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. the superposition type handpiece Water Chilling Units that middle temperature according to claim 2, low temperature are dual-purpose, 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. the superposition type handpiece Water Chilling Units that middle temperature according to claim 2, low temperature are dual-purpose, 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 of the outlet side being located at high-temperature level compressor.
5. the superposition type handpiece Water Chilling Units that middle temperature according to claim 1, low temperature are dual-purpose, 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 gas-liquid separator and expansion drum; Described low-temperature level oil eliminator top is connected with the outlet side of low-temperature level compressor and the inlet end of low-temperature level condenser; Described low-temperature level reservoir liquid feeding end is connected with the low-temperature level outlet end of Intermediate Heat Exchanger, the outlet end of low-temperature level reservoir 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 gas-liquid separator is located between low-temperature level evaporimeter and low-temperature level compressor, and 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, described expansion drum and two ends pipeline on be also provided with throttling arrangement.
6. the superposition type handpiece Water Chilling Units that middle temperature according to claim 5, low temperature are dual-purpose, 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. the superposition type handpiece Water Chilling Units that middle temperature according to claim 5, low temperature are dual-purpose, 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 of the outlet side being located at low-temperature level compressor.
8. the superposition type handpiece Water Chilling Units that the middle temperature according to any one of claim 1 ~ 7, low temperature are dual-purpose, is characterized in that, described superposition type handpiece Water Chilling Units is run 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 temperature pattern or low temperature mode;
Under middle temperature pattern, 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. the superposition type handpiece Water Chilling Units that middle temperature according to claim 1, low temperature are dual-purpose, is characterized in that,
Described high-temperature level compressor is screw compressor; Low-temperature level compressor is screw machine compressor or piston compressor.
10. the superposition type handpiece Water Chilling Units that middle temperature according to claim 8, low temperature are dual-purpose, it is characterized in that, the throttling arrangement in described superposition type handpiece Water Chilling Units is electric expansion valve, heating power expansion valve, orifice plate or capillary.
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106403409A (en) * | 2016-10-26 | 2017-02-15 | 广东高而美制冷设备有限公司 | Low-temperature enthalpy increasing and refrigerating system and working mode |
| CN110243035A (en) * | 2019-06-06 | 2019-09-17 | 深圳市云科设计咨询服务有限公司 | A kind of warm and humid sub-control air-conditioning system of the big temperature difference of multi-freezing pipe |
| CN111928523A (en) * | 2020-08-04 | 2020-11-13 | 松下冷机***（大连）有限公司 | CO (carbon monoxide)2Transcritical cold and heat comprehensive utilization system |
| CN113720031A (en) * | 2021-08-25 | 2021-11-30 | 北京京仪自动化装备技术股份有限公司 | Double-channel temperature control device with supercooling enthalpy increase function, control method and electronic equipment |
| CN113720032A (en) * | 2021-08-25 | 2021-11-30 | 北京京仪自动化装备技术股份有限公司 | Double-channel temperature control device with supercooling enthalpy increase function, control method and electronic equipment |
| 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 |
| CN115289704A (en) * | 2022-06-23 | 2022-11-04 | 北京京仪自动化装备技术股份有限公司 | Temperature control device and temperature control method |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20120216551A1 (en) * | 2009-11-03 | 2012-08-30 | E.I. Du Pont De Nemours And Company | Cascade refrigeration system with fluoroolefin refrigerant |
| CN202420018U (en) * | 2012-01-13 | 2012-09-05 | 重庆市威尔试验仪器有限公司 | Energy-saving mixed cascade refrigeration system |
| CN202869066U (en) * | 2012-10-25 | 2013-04-10 | 南京五洲制冷集团有限公司 | Efficient dual-element-overlapped copious cooling unit with pre-cooling and temperature adjustment functions |
| 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 |
-
2015
- 2015-07-31 CN CN201510461862.9A patent/CN105004088A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20120216551A1 (en) * | 2009-11-03 | 2012-08-30 | E.I. Du Pont De Nemours And Company | Cascade refrigeration system with fluoroolefin refrigerant |
| CN202420018U (en) * | 2012-01-13 | 2012-09-05 | 重庆市威尔试验仪器有限公司 | Energy-saving mixed cascade refrigeration system |
| CN202869066U (en) * | 2012-10-25 | 2013-04-10 | 南京五洲制冷集团有限公司 | Efficient dual-element-overlapped copious cooling unit with pre-cooling and temperature adjustment functions |
| 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 |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106403409A (en) * | 2016-10-26 | 2017-02-15 | 广东高而美制冷设备有限公司 | Low-temperature enthalpy increasing and refrigerating system and working mode |
| CN110243035A (en) * | 2019-06-06 | 2019-09-17 | 深圳市云科设计咨询服务有限公司 | A kind of warm and humid sub-control air-conditioning system of the big temperature difference of multi-freezing pipe |
| CN111928523A (en) * | 2020-08-04 | 2020-11-13 | 松下冷机***（大连）有限公司 | CO (carbon monoxide)2Transcritical cold and heat comprehensive utilization system |
| CN113720031A (en) * | 2021-08-25 | 2021-11-30 | 北京京仪自动化装备技术股份有限公司 | Double-channel temperature control device with supercooling enthalpy increase function, control method and electronic equipment |
| CN113720032A (en) * | 2021-08-25 | 2021-11-30 | 北京京仪自动化装备技术股份有限公司 | Double-channel temperature control device with supercooling enthalpy increase function, control method and electronic equipment |
| CN113720031B (en) * | 2021-08-25 | 2022-12-13 | 北京京仪自动化装备技术股份有限公司 | Double-channel temperature control device with supercooling enthalpy increase function, control method and electronic equipment |
| CN113720032B (en) * | 2021-08-25 | 2022-12-13 | 北京京仪自动化装备技术股份有限公司 | Double-channel temperature control device with supercooling enthalpy increase function, control method and electronic equipment |
| 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 |
| CN115289704A (en) * | 2022-06-23 | 2022-11-04 | 北京京仪自动化装备技术股份有限公司 | Temperature control device and temperature control method |
| CN115289704B (en) * | 2022-06-23 | 2023-10-13 | 北京京仪自动化装备技术股份有限公司 | Temperature control device and temperature control method |
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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 Environmental Systems 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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Application publication date: 20151028 |