CN103322718A - Two-stage-throttling incomplete-intercooling double-duty refrigerating system - Google Patents
Two-stage-throttling incomplete-intercooling double-duty refrigerating system Download PDFInfo
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- CN103322718A CN103322718A CN2013102785257A CN201310278525A CN103322718A CN 103322718 A CN103322718 A CN 103322718A CN 2013102785257 A CN2013102785257 A CN 2013102785257A CN 201310278525 A CN201310278525 A CN 201310278525A CN 103322718 A CN103322718 A CN 103322718A
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Abstract
The invention discloses a two-stage-throttling incomplete-intercooling double-duty refrigerating system and provides a system which allows for variable-flow single-stage steam compression cycle and which also allows for variable-flow two-stage-throttling incomplete-intercooling two-stage compression cycle. The system comprises a plurality of variable-flow compression condensing units parallelly connected among a low-temperature suction pipeline, a high-temperature suction pipeline and a medium-pressure liquid supply pipeline. Each variable-flow compression condensing unit comprises a low-pressure constant-flow compressor, a low-voltage variable-flow compressor, a high-pressure variable-flow compressor, a first one-way valve, a second one-way valve, a third one-way valve, a first valve, a second valve, a third valve, a fourth valve, a fifth valve, a sixth valve, a condenser, an intercooler and a throttle valve. By controlling the valves to open or close, the high-temperature suction pipeline can take in air to allow for single-stage-compression refrigerating cycle so that liquid is supplied to the medium-pressure liquid supply pipeline, and the low-temperature suction pipeline can take in the air to allow for two-stage-compression refrigerating cycle so that the liquid is supplied to the medium-pressure liquid supply pipeline.
Description
Technical field
The present invention relates to refrigeration technology field, particularly relate to a kind of middle not exclusively cooling of second throttle Double-working-condition double-stage compressive refrigerating system that carries out the refrigerating capacity adjusting by changing refrigerant flow.
Background technology
The existing double-stage compressive refrigerating system that is used for the cold storage freezer adopts the start-stop of temperature control compressor usually, and when temperature of ice house reached the temperature controller set temperature, refrigeration system quit work; Prescribe a time limit when temperature rises on the temperature controller set temperature, refrigeration system is opened.There is a contradiction in such system, when needs startup-shutdown Temperature Difference Ratio is larger, can cause the food dehydration drying loss that store food is brought owing to the freezing rate difference in the cold storage freezer, and food quality descends; When needs startup-shutdown Temperature Difference Ratio hour, refrigeration system is opened frequently, not only power consumption increase, and the service life that can reduce refrigeration system.Existing double-stage compressive refrigerating system high and low pressure volumetric ratio is fixing 1:3 or 1:2 in addition, and for the refrigeration system that condensation temperature constantly changes, because the high and low pressure volumetric ratio is non-adjustable, refrigeration system is not to work under optimum, and energy consumption is high.
The multi-connected air conditioning system that is comprised of many Condensing units and Duo Tai indoor evaporator is realized the control of refrigerating capacity by changing refrigerant flow, system's flexible operation is easy to control, is widely used in field of air conditioning.But existing multi-gang air conditioner all is single-stage compression refrigeration system, is only applicable to field of air conditioning, is not suitable for the lower cold storage refrigeration storage system of temperature.
(suction temperature is lower for the cold storage freezer; usually need the Two-stage Compression system) and (suction temperature is higher to refrigerate freezer; usually need the one-stage steam compression system) system in parallel; usually need the single/double stage vapor compression system is configured separately; system's one-time investment is large, and the refrigerating capacity adjusting relies on startup-shutdown to realize fully.
Summary of the invention
The objective of the invention is to regulate the technological deficiency that relies on startup-shutdown to realize fully for the refrigerating capacity that exists in the prior art; and provide a kind of many group variable-flow compression freezing machine groups in parallel; both can realize the one-stage steam compressed circulation of variable-flow, can realize again the refrigeration system of the Two-stage Compression circulation of the middle not exclusively cooling of variable-flow second throttle.
For realizing that the technical scheme that purpose of the present invention adopts is:
Not exclusively cool off the Double-working-condition refrigeration system in the middle of a kind of second throttle, it is characterized in that, comprise the many groups variable-flow compression freezing machine group that is connected to side by side between low temperature suction line, high temperature suction line and the middle pressure liquid feeding pipeline; Every group of described variable-flow compression freezing machine group is comprised of low pressure constant flow compressor, low pressure variable-flow compression machine, high voltage variable flow compressor, the first check valve, the second check valve, the 3rd check valve, the first valve, the second valve, the 3rd valve, the 4th valve, the 5th valve, the 6th valve, condenser, intercooler and choke valve; Described the first valve inlet in every group of described variable-flow compression freezing machine group is connected with described high temperature suction line, described the second valve inlet is connected with described low temperature suction line, described intercooler liquid outlet is connected with described middle pressure liquid feeding pipeline, described the first valve export and described the second valve export respectively with described low pressure constant flow compressor air suction mouth, described low pressure variable-flow compresses the machine air entry and is connected the connection of the 4th valve inlet, described low pressure constant flow exhaust outlet of compressor is connected with described the first check valve inlet, described low pressure variable-flow compression machine exhaust outlet is connected with described the second check valve inlet, the outlet of described the first check valve and described the second check valve export in parallel after respectively with described the 3rd valve inlet, described the 5th valve inlet be connected the 6th valve export and connect, be connected with described high voltage variable flow compressor air entry after described the 3rd valve export and described the 4th valve export parallel connection, described high voltage variable flow compressor exhaust outlet is connected with described the 3rd check valve inlet, be connected with described condenser inlet after the outlet of described the 3rd check valve and described the 5th valve export parallel connection, described condensator outlet is connected with described intercooler import through described choke valve, and described intercooler gas vent is connected with described the 6th valve inlet; Unlatching by controlling described the first valve, the second valve, the 3rd valve, the 4th valve, the 5th valve and the 6th valve or close, both can be from the air-breathing realization single stage compress of described high temperature suction line kind of refrigeration cycle pressure liquid feeding pipeline feed flow to described, again can be in the middle of the air-breathing realization second throttle of described low temperature suction line incomplete cooling Two-stage Compression kind of refrigeration cycle pressure liquid feeding pipeline feed flow to described.
Described low pressure constant flow compressor be screw compressor, rotor compressor, helical-lobe compressor, piston compressor any.
Described low pressure variable-flow compression machine and described high voltage variable flow compressor be screw compressor, rotor compressor, helical-lobe compressor, piston compressor any, the variable-flow mode can be by regulating to the frequency conversion of alternating current generator or by the time variant voltage to direct current generator, also can adopting cold-producing medium unloading and load mode to realize the Flow-rate adjustment of cold-producing medium.
Described condenser is air-cooled condenser, water-cooled condenser, evaporative condenser or other pattern condenser.
Described choke valve is electric expansion valve, heating power expansion valve, capillary or orifice plate.
Described intercooler is plate type heat exchanger or double pipe heat exchanger.
Compared with prior art, the invention has the beneficial effects as follows:
1, energy-conservation: refrigeration system of the present invention is comprised of variable-flow compression freezing machine group parallel with one another; every group of variable-flow compression freezing machine group comprises low pressure constant flow compressor, low pressure variable-flow compression machine and high voltage variable flow compressor; the refrigerant flow that is input to cold storage freezer and refrigeration freezer can be regulated according to the load needs; overcome refrigerating capacity and regulated the technological deficiency that relies on startup-shutdown to realize fully, refrigeration system can frequently not opened.
2, temperature of ice house is constant: owing to can adjust the refrigerant flow of refrigeration system, system can adjust refrigerant flow automatically according to the load variations of cold storage freezer, refrigeration system can be with lower refrigerant flow work after reaching design temperature, keep the temperature of cold storage freezer and refrigeration freezer, avoided the fluctuation of cool house internal temperature, effectively reduced because the dehydration drying loss of the food that temperature fluctuation brings.
3, one-time investment is few: refrigeration system of the present invention, both can realize the one-stage steam compressed circulation of variable-flow, and can realize that again the Two-stage Compression that not exclusively cools off in the middle of the variable-flow second throttle circulates, a tractor serves several purposes has reduced one-time investment.
4, unit can be realized optimum condition: refrigeration system of the present invention is comprised of variable-flow compression freezing machine group parallel with one another, every group of variable-flow compression freezing machine group comprises low pressure constant flow compressor, low pressure variable-flow compression machine and high voltage variable flow compressor, overcome in the prior art the fixedly shortcoming of high and low pressure volumetric ratio, realized regulating of volumetric ratio, no matter how operating mode changes, refrigeration system always is in optimum state work, and energy consumption is low.
5, modularization: high voltage variable flow compressor and low pressure variable-flow compression machine can adopt the compressor of same rated input power, are conducive to the adjustment of system and are convenient to maintenance and maintenance, more easily realize the modularization of system simultaneously.
Description of drawings
Figure 1 shows that the schematic diagram of the middle not exclusively cooling of second throttle of the present invention Double-working-condition refrigeration system.
Among the figure: 1. high temperature suction line, 2. low temperature suction line is pressed liquid feeding pipeline in 3., 4. low pressure constant flow compressor, 5. low pressure variable-flow compression machine, 6. high voltage variable flow compressor, 7-1. the first check valve, 7-2. the second check valve, 7-3. the 3rd check valve, 8-1. the first valve, 8-2. the second valve, 8-3. the 3rd valve, 8-4. the 4th valve, 8-5. the 5th valve, 8-6. the 6th valve, 9. condenser, 10. intercooler, 11. choke valves.
The specific embodiment
Below in conjunction with the drawings and specific embodiments the present invention is described in further detail.
Not exclusively cool off Double-working-condition refrigeration system schematic diagram in the middle of Figure 1 shows that second throttle of the present invention, comprise the many groups variable-flow compression freezing machine group that is connected to side by side between high temperature suction line 1, low temperature suction line 2 and the middle pressure liquid feeding pipeline 3.Every group of described variable-flow compression freezing machine group comprises low pressure constant flow compressor 4, low pressure variable-flow compression machine 5, high voltage variable flow compressor 6, the first check valve 7-1, the second check valve 7-2, the 3rd check valve 7-3, the first valve 8-1, the second valve 8-2, the 3rd valve 8-3, the 4th valve 8-4, the 5th valve 8-5, the 6th valve 8-6, condenser 9, intercooler 10 and choke valve 11.Described the first valve 8-1 import in every group of described variable-flow compression freezing machine group is connected with described high temperature suction line 1, described the second valve 8-2 import is connected with described low temperature suction line 2, and the liquid outlet of described intercooler 10 is connected with described middle pressure liquid feeding pipeline 3.Described the first valve 8-1 outlet and described the second valve 8-2 export respectively and described low pressure constant flow compressor 4 air entries, described low pressure variable-flow compresses machine 5 air entries and is connected the 4th valve 8-4 import connection, described low pressure constant flow compressor 4 exhaust outlets are connected with described the first check valve 7-1 import, described low pressure variable-flow compression machine 5 exhaust outlets are connected with described the second check valve 7-2 import, described the first check valve 7-1 outlet and described the second check valve 7-2 export in parallel after respectively with described the 3rd valve 8-3 import, described the 5th valve 8-5 import be connected the 6th valve 8-6 outlet and connect, described the 3rd valve 8-3 outlet is connected with described high voltage variable flow compressor 6 air entries with described the 4th valve 8-4 outlet parallel connection is rear, described high voltage variable flow compressor 6 exhaust outlets are connected with described the 3rd check valve 7-3 import, described the 3rd check valve 7-3 outlet is connected with described condenser 9 imports with described the 5th valve 8-5 outlet parallel connection is rear, described condenser 9 outlets are connected with described intercooler 10 imports through described choke valve 11, and described intercooler 10 gas vents are connected with described the 6th valve 8-6 import.
In the middle of the second throttle of the present invention not exclusively the variable-flow compression freezing machine group in the cooling Double-working-condition refrigeration system by controlling described the first valve 8-1, the second valve 8-2, the 3rd valve 8-3, the 4th valve 8-4, the 5th valve 8-5 and the 6th valve 8-6 unlatching or close, both can from described high temperature suction line 1 air-breathing realization single stage compress kind of refrigeration cycle to pressure liquid feeding pipeline 3 feed flows, again can be in the middle of described low temperature suction line 2 air-breathing realization second throttles not exclusively cooling Two-stage Compression kind of refrigeration cycle to pressure liquid feeding pipeline 3 feed flows.At work mutually nonintervention of variable-flow compression freezing machine group in parallel, and all can realize the variable-flow operation.
1, from high temperature suction line 1 air-breathing realization single stage compress kind of refrigeration cycle to pressure liquid feeding pipeline 3 feed flows:
The second valve 8-2, the 3rd valve 8-3 and the 6th valve 8-6 close in the variable-flow compression freezing machine group, and the first valve 8-1, the 4th valve 8-4 and the 5th valve 8-5 open.The low-pressure refrigerant vapor of getting back to variable-flow compression freezing machine group from the refrigeration freezer enters respectively low pressure constant flow compressor 4, low pressure variable-flow compression machine 5 and high voltage variable flow compressor 6 through high temperature suction line 1 and compresses, high-pressure refrigerant vapor after the compression is condensed into highly pressurised liquid through the first check valve 7-1, the second check valve 7-2 and the 3rd check valve 7-3 respectively to condenser 9, carrying out a throttling at choke valve 11 is that the saturated gas-liquid two phase refrigerant of middle pressure enters by intercooler 10 in the middle pressure liquid feeding pipeline 3 to refrigeration freezer feed flow.
2, from low temperature suction line 2 air-breathing realization Two-stage Compression kind of refrigeration cycle to pressure liquid feeding pipeline 3 feed flows:
The first valve 8-1, the 4th valve 8-4 and the 5th valve 8-5 close in the variable-flow compression freezing machine group, and the second valve 8-2, the 3rd valve 8-3 and the 6th valve 8-6 open.The low-pressure refrigerant vapor of getting back to variable-flow compression freezing machine group from the cold storage freezer enters respectively low pressure constant flow compressor 4 and the low pressure variable-flow compression machine 5 through low temperature suction line 2 carries out the one-level compression, middle pressure superheated vapor cold-producing medium after the compression respectively through the first check valve 7-1 and the second check valve 7-2 with from middle cooler 10 gas vents out pressure saturated vapor refrigerant mixed be that middle pressure superheated vapor cold-producing medium enters and carries out second level compression in the high voltage variable flow compressor 6, high pressure superheater vaporous cryogen after the compression is condensed into high pressure liquid refrigerant through condenser 9, throttling is to enter in the intercooler 10 after the saturated gas-liquid two phase refrigerant of middle pressure in choke valve 11, middle pressure saturated vapor cold-producing medium participates in second level compression, and middle pressure saturated liquid cold-producing medium then presses liquid feeding pipeline 3 to cold storage freezer feed flow in the warp.
In the above-mentioned single stage compress kind of refrigeration cycle, satisfy under the different load condition control to refrigerant flow in the single stage compress kind of refrigeration cycle by the combination of low pressure constant flow compressor 4, low pressure variable-flow compression machine 5, high voltage variable flow compressor 6.
In the above-mentioned Two-stage Compression kind of refrigeration cycle, when cold storage freezer load hour, low pressure variable-flow compression machine 5 is worked simultaneously with high voltage variable flow compressor 6, realizes the best high and low pressure volumetric ratio of system by the refrigerant flow of adjusting high voltage variable flow compressor 6, low pressure variable-flow compression machine 5; When cold storage freezer load is larger, low pressure constant flow compressor 4, low pressure variable-flow compression machine 5 and high voltage variable flow compressor 6 are worked simultaneously, by adjusting the refrigerant flow of low pressure variable-flow compression machine 5 and high voltage variable flow compressor 6, the best high and low pressure volumetric ratio of realization system.System can carry out according to the load variations of cold storage freezer the adjusting of refrigerant flow in the Two-stage Compression kind of refrigeration cycle.
The effect of the first check valve 6-1, the second check valve 6-2 and the 3rd check valve 6-3 is the backflow when preventing that associated compressors from not working in above-described embodiment.
Low pressure constant flow compressor of the present invention be screw compressor, rotor compressor, helical-lobe compressor, piston compressor any, or other pattern compressor.Described low pressure variable-flow compression machine and described high voltage variable flow compressor be screw compressor, rotor compressor, helical-lobe compressor, piston compressor any, or other pattern compressor, the variable-flow mode can be by regulating to the frequency conversion of alternating current generator or by the time variant voltage to direct current generator, also can adopting cold-producing medium unloading and load mode to realize the Flow-rate adjustment of cold-producing medium.Described condenser is air-cooled condenser, water-cooled condenser, evaporative condenser or other pattern condenser.Described choke valve is any in electric expansion valve, heating power expansion valve, capillary or the orifice throttle, but also can be the throttling arrangement of other step-down power.Described intercooler can be plate type heat exchanger, double pipe heat exchanger or other pattern heat exchanger.
Valve of the present invention can be that manually-operated gate also can be electrically operated valve, and also available triple valve or cross valve replace.
Not exclusively cool off the Double-working-condition refrigeration system in the middle of the second throttle of the present invention when concrete the utilization, high voltage variable flow compressor and low pressure variable-flow compression machine can adopt the compressor of same rated input power, be conducive to the adjustment of system and be convenient to maintenance and maintenance, more easily realize the modularization of system simultaneously.
The above only is preferred embodiment of the present invention; should be pointed out that for those skilled in the art, under the prerequisite that does not break away from the principle of the invention; can also make some improvements and modifications, these improvements and modifications also should be considered as protection scope of the present invention.
Claims (6)
1. not exclusively cool off the Double-working-condition refrigeration system in the middle of a second throttle, it is characterized in that, comprise the many groups variable-flow compression freezing machine group that is connected to side by side between low temperature suction line, high temperature suction line and the middle pressure liquid feeding pipeline; Every group of described variable-flow compression freezing machine group is comprised of low pressure constant flow compressor, low pressure variable-flow compression machine, high voltage variable flow compressor, the first check valve, the second check valve, the 3rd check valve, the first valve, the second valve, the 3rd valve, the 4th valve, the 5th valve, the 6th valve, condenser, intercooler and choke valve; Described the first valve inlet in every group of described variable-flow compression freezing machine group is connected with described high temperature suction line, described the second valve inlet is connected with described low temperature suction line, described intercooler liquid outlet is connected with described middle pressure liquid feeding pipeline, described the first valve export and described the second valve export respectively with described low pressure constant flow compressor air suction mouth, described low pressure variable-flow compresses the machine air entry and is connected the connection of the 4th valve inlet, described low pressure constant flow exhaust outlet of compressor is connected with described the first check valve inlet, described low pressure variable-flow compression machine exhaust outlet is connected with described the second check valve inlet, the outlet of described the first check valve and described the second check valve export in parallel after respectively with described the 3rd valve inlet, described the 5th valve inlet be connected the 6th valve export and connect, be connected with described high voltage variable flow compressor air entry after described the 3rd valve export and described the 4th valve export parallel connection, described high voltage variable flow compressor exhaust outlet is connected with described the 3rd check valve inlet, be connected with described condenser inlet after the outlet of described the 3rd check valve and described the 5th valve export parallel connection, described condensator outlet is connected with described intercooler import through described choke valve, and described intercooler gas vent is connected with described the 6th valve inlet; Unlatching by controlling described the first valve, the second valve, the 3rd valve, the 4th valve, the 5th valve and the 6th valve or close, both can be from the air-breathing realization single stage compress of described high temperature suction line kind of refrigeration cycle pressure liquid feeding pipeline feed flow to described, again can be in the middle of the air-breathing realization second throttle of described low temperature suction line incomplete cooling Two-stage Compression kind of refrigeration cycle pressure liquid feeding pipeline feed flow to described.
2. incomplete cooling Double-working-condition refrigeration system in the middle of the second throttle according to claim 1 is characterized in that, described low pressure constant flow compressor be screw compressor, rotor compressor, helical-lobe compressor, piston compressor any.
3. not exclusively cool off the Double-working-condition refrigeration system in the middle of the second throttle according to claim 1, it is characterized in that, described low pressure variable-flow compression machine and described high voltage variable flow compressor be screw compressor, rotor compressor, helical-lobe compressor, piston compressor any, the variable-flow mode is for by regulating to the frequency conversion of alternating current generator or by the time variant voltage to direct current generator, or adopts the Flow-rate adjustment of cold-producing medium unloading and load mode realization cold-producing medium.
4. not exclusively cool off the Double-working-condition refrigeration system in the middle of the second throttle according to claim 1, it is characterized in that, described condenser is air-cooled condenser, water-cooled condenser or evaporative condenser.
5. not exclusively cool off the Double-working-condition refrigeration system in the middle of the second throttle according to claim 1, it is characterized in that, described choke valve is electric expansion valve, heating power expansion valve, capillary or orifice plate.
6. not exclusively cool off the Double-working-condition refrigeration system in the middle of the second throttle according to claim 1, it is characterized in that, described intercooler is plate type heat exchanger or double pipe heat exchanger.
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Cited By (1)
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| US11131491B1 (en) | 2020-08-07 | 2021-09-28 | Emerson Climate Technologies, Inc. | Systems and methods for multi-stage operation of a compressor |
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| SG11202012506VA (en) | 2018-11-12 | 2021-05-28 | Carrier Corp | Compact heat exchanger assembly for a refrigeration system |
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Effective date of registration: 20151120 Address after: 300000, Tianjin free trade zone (Airport Economic Zone) air route 1, aviation industry support center, room 645AB43 Patentee after: Tianjin Yi Ding Engineering Design Co., Ltd. Address before: Tianjin highway 300134 East Tianjin District of Beichen City Patentee before: Tianjin University Of Commerce |