CN203454447U - Intermediate inadequacy cooling double operating conditions refrigeration system in secondary throttling - Google Patents
Intermediate inadequacy cooling double operating conditions refrigeration system in secondary throttling Download PDFInfo
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- CN203454447U CN203454447U CN201320395153.1U CN201320395153U CN203454447U CN 203454447 U CN203454447 U CN 203454447U CN 201320395153 U CN201320395153 U CN 201320395153U CN 203454447 U CN203454447 U CN 203454447U
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Abstract
The utility model discloses an intermediate inadequacy cooling double operating conditions refrigeration system in secondary throttling, which is the system for realization of both the variable-flow singe-stage vapor compression cycle and the variable-flow intermediate inadequacy cooling two-stage compression cycle in the secondary throttling, and comprises a plurality of sets of variable-flow compression condenser sets connected in parallel among a low-temperature inspiration pipeline, a high-temperature inspiration pipeline and a middle-pressure feeding pipeline; and each of the variable-flow compression condenser sets comprises low-pressure constant-flow compressor, a low-pressure variable-flow compressor, a high-temperature variable-flow compressor, a first check valve, a second check valve, a third check valve, a first valve, as second valve, a third valve, a forth valve, a fifty valve, a sixth valve, a condenser, an intermediate cooler and a throttle valve. By controlling opening and closing of each of the valves, both the liquid feeding by a single-stage compression refrigeration circle to the middle-pressure feeding pipeline through inspiration of the high-temperature inspiration pipeline and the liquid feeding to the middle-pressure feeding pipeline by a two-stage compression refrigeration circle through the inspiration of the low-temperature pipeline can be realized.
Description
Technical field
The utility model relates to refrigeration technology field, particularly relates to a kind of middle incomplete cooling Double-working-condition double-stage compressive refrigerating system of second throttle that carries out refrigerating capacity adjusting by changing refrigerant flow.
Background technology
The existing double-stage compressive refrigerating system for cold storage freezer adopts temperature to control the start-stop of compressor conventionally, and when temperature of ice house reaches temperature controller set temperature, refrigeration system quits work; When temperature rises on temperature controller set temperature, prescribe a time limit, 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 in cold storage freezer, store food is brought due to freezing rate difference, and food quality declines; 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.In addition existing double-stage compressive refrigerating system high and low pressure volumetric ratio is fixing 1:3 or 1:2, the refrigeration system constantly changing for condensation temperature, and because high and low pressure volumetric ratio is non-adjustable, refrigeration system is not to work under optimum, energy consumption is high.
The multi-connected air conditioning system being comprised of many Condensing units and Duo Tai indoor evaporator is realized the control of refrigerating capacity by changing refrigerant flow, system flexible operation is easy to control, and is widely used in field of air conditioning.But existing multi-gang air conditioner is all single-stage compression refrigeration system, is only applicable to field of air conditioning, be not suitable for the cold storage refrigeration storage system that temperature is lower.
For cold storage freezer, (suction temperature is lower; conventionally need Two-stage Compression system) and (suction temperature is higher to refrigerate freezer; conventionally need one-stage steam compression system) system in parallel; usually need single/double stage vapor compression system to configure separately; system one-time investment is large, and refrigerating capacity adjusting relies on startup-shutdown to realize completely.
Utility model content
The purpose of this utility model is to regulate for the refrigerating capacity existing in prior art the technological deficiency that relies on startup-shutdown to realize completely; and provide a kind of many group variable-flow compression freezing machine groups in parallel; both the one-stage steam compressed circulation of variable-flow can be realized, the refrigeration system of the middle not exclusively cooling Two-stage Compression circulation of variable-flow second throttle can be realized again.
For realizing the technical scheme that the purpose of this utility model adopts, be:
An incomplete cooling Double-working-condition refrigeration system in the middle of second throttle, is characterized in that, comprises the many groups variable-flow compression freezing machine group being connected to side by side between low temperature suction line, high temperature suction line and middle pressure liquid feeding pipeline, described in every group, 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 described in every group in 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 compression machine air entry is connected with described 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, described the first check valve outlet and described the second check valve export in parallel after respectively with described the 3rd valve inlet, described the 5th valve inlet is connected with described the 6th valve export, described the 3rd valve export with after described the 4th valve export parallel connection, be connected with described high voltage variable flow compressor air entry, described high voltage variable flow compressor exhaust outlet is connected with described the 3rd check valve inlet, described the 3rd check valve outlet is connected with described condenser inlet with after described the 5th valve export parallel connection, described condensator outlet is connected with described intercooler import through described choke valve, described intercooler gas vent is connected with described the 6th valve inlet, by controlling the unlatching of described the first valve, the second valve, the 3rd valve, the 4th valve, the 5th valve and the 6th valve or closing, both can be from the air-breathing single stage compress kind of refrigeration cycle that realizes of described high temperature suction line to pressure liquid feeding pipeline feed flow described, can realize in the middle of second throttle incomplete cooling Two-stage Compression kind of refrigeration cycle to pressure liquid feeding pipeline feed flow described from described low temperature suction line is air-breathing again.
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, 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 adopt 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 beneficial effects of the utility model are:
1, energy-conservation: refrigeration system of the present utility model 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 need to regulate according to load; overcome refrigerating capacity and regulated the technological deficiency that relies on startup-shutdown to realize completely, refrigeration system can frequently not opened.
2, temperature of ice house is constant: owing to can adjusting the refrigerant flow of refrigeration system, system can be adjusted refrigerant flow automatically according to the load variations of cold storage freezer, after reaching design temperature, refrigeration system can be with lower refrigerant flow work, maintain the temperature of cold storage freezer and refrigeration freezer, avoid the fluctuation of cool house internal temperature, effectively reduced the dehydration drying loss of the food bringing due to temperature fluctuation.
3, one-time investment is few: refrigeration system of the present utility model, both can realize the one-stage steam compressed circulation of variable-flow, and can realize again the middle not exclusively cooling Two-stage Compression circulation of variable-flow second throttle, a tractor serves several purposes, has reduced one-time investment.
4, unit can be realized optimum condition: refrigeration system of the present utility model 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 prior art the fixedly shortcoming of high and low pressure volumetric ratio, realized the adjustable of volumetric ratio, no matter how operating mode changes, refrigeration system is always 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.
Accompanying drawing explanation
Figure 1 shows that the schematic diagram of the middle incomplete cooling Double-working-condition refrigeration system of the utility model second throttle.
In figure: 1. high temperature suction line, 2. low temperature suction line, presses 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 utility model is described in further detail.
Figure 1 shows that the middle incomplete cooling Double-working-condition refrigeration system schematic diagram of the utility model second throttle, comprise the many groups variable-flow compression freezing machine group being connected to side by side between high temperature suction line 1, low temperature suction line 2 and middle pressure liquid feeding pipeline 3.Described in every group, 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 described in every group in 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 compression machine 5 air entries are connected with described the 4th valve 8-4 import, 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 is connected with described the 6th valve 8-6 outlet, after described the 3rd valve 8-3 outlet is in parallel with described the 4th valve 8-4 outlet, be connected with described high voltage variable flow compressor 6 air entries, described high voltage variable flow compressor 6 exhaust outlets are connected with described the 3rd check valve 7-3 import, after described the 3rd check valve 7-3 outlet is in parallel with described the 5th valve 8-5 outlet, be connected with described condenser 9 imports, described condenser 9 outlets are connected with described intercooler 10 imports through described choke valve 11, described intercooler 10 gas vents are connected with described the 6th valve 8-6 import.
Variable-flow compression freezing machine group in the middle of second throttle of the present utility model in incomplete cooling Double-working-condition refrigeration system is by controlling the unlatching of 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 or closing, both can from described high temperature suction line 1 air-breathing realize single stage compress kind of refrigeration cycle to pressure liquid feeding pipeline 3 feed flows, again can from described low temperature suction line 2 air-breathing realize in the middle of second throttle incomplete cooling Two-stage Compression kind of refrigeration cycle to pressure liquid feeding pipeline 3 feed flows.Variable-flow compression freezing machine group nonintervention mutually at work in parallel, and all can realize variable-flow operation.
1, from high temperature suction line 1 air-breathing realize single stage compress kind of refrigeration cycle to pressure liquid feeding pipeline 3 feed flows:
In variable-flow compression freezing machine group, the second valve 8-2, the 3rd valve 8-3 and the 6th valve 8-6 close, 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 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 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, and at choke valve 11, carrying out a throttling is to refrigeration freezer feed flow during the saturated gas-liquid two phase refrigerant of middle pressure enters middle pressure liquid feeding pipeline 3 by intercooler 10.
2, from low temperature suction line 2 air-breathing realize Two-stage Compression kind of refrigeration cycle to pressure liquid feeding pipeline 3 feed flows:
In variable-flow compression freezing machine group, the first valve 8-1, the 4th valve 8-4 and the 5th valve 8-5 close, 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 cold storage freezer enters respectively low pressure constant flow compressor 4 and low pressure variable-flow compression machine 5 and carries out one-level compression through low temperature suction line 2, middle pressure superheated vapor cold-producing medium after compression respectively through the first check valve 7-1 and the second check valve 7-2 with from intercooler 10 gas vents out pressure saturated vapor refrigerant mixed be that middle pressure superheated vapor cold-producing medium enters and in high voltage variable flow compressor 6, carries out second level compression, high pressure superheater vaporous cryogen after compression is condensed into high pressure liquid refrigerant through condenser 9, in choke valve 11, throttling is to enter in intercooler 10 after the saturated gas-liquid two phase refrigerant of middle pressure, middle pressure saturated vapor cold-producing medium participates in second level compression, middle pressure saturated liquid cold-producing medium presses liquid feeding pipeline 3 to cold storage freezer feed flow in warp.
In above-mentioned single stage compress kind of refrigeration cycle, the combination of compressing machine 5, high voltage variable flow compressor 6 by low pressure constant flow compressor 4, low pressure variable-flow meets the control to refrigerant flow in single stage compress kind of refrigeration cycle under different load condition.
In above-mentioned Two-stage Compression kind of refrigeration cycle, when cold storage freezer load hour, low pressure variable-flow compression machine 5 is worked with high voltage variable flow compressor 6 simultaneously, by adjusting the refrigerant flow of high voltage variable flow compressor 6, low pressure variable-flow compression machine 5, realizes the best high and low pressure volumetric ratio of system; 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 the system that realizes.System can be carried out according to the load variations of cold storage freezer the adjusting of refrigerant flow in Two-stage Compression kind of refrigeration cycle.
In above-described embodiment, 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 while preventing that associated compressors from not working.
Low pressure constant flow compressor described in the utility model 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, 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 adopt 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 orifice throttle, can be also the throttling arrangement that other can step-down power.Described intercooler can be plate type heat exchanger, double pipe heat exchanger or other pattern heat exchanger.
Valve described in the utility model can be that manually-operated gate can be also electrically operated valve, and also available triple valve or cross valve replace.
In the middle of second throttle of the present utility model, incomplete cooling Double-working-condition refrigeration system is when concrete 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 is only preferred embodiment of the present utility model; it should be noted that; for those skilled in the art; do not departing under the prerequisite of the utility model principle; can also make some improvements and modifications, these improvements and modifications also should be considered as protection domain of the present utility model.
Claims (6)
1. an incomplete cooling Double-working-condition refrigeration system in the middle of second throttle, is characterized in that, comprises the many groups variable-flow compression freezing machine group being connected to side by side between low temperature suction line, high temperature suction line and middle pressure liquid feeding pipeline, described in every group, 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 described in every group in 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 compression machine air entry is connected with described 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, described the first check valve outlet and described the second check valve export in parallel after respectively with described the 3rd valve inlet, described the 5th valve inlet is connected with described the 6th valve export, described the 3rd valve export with after described the 4th valve export parallel connection, be connected with described high voltage variable flow compressor air entry, described high voltage variable flow compressor exhaust outlet is connected with described the 3rd check valve inlet, described the 3rd check valve outlet is connected with described condenser inlet with after described the 5th valve export parallel connection, described condensator outlet is connected with described intercooler import through described choke valve, described intercooler gas vent is connected with described the 6th valve inlet, by controlling the unlatching of described the first valve, the second valve, the 3rd valve, the 4th valve, the 5th valve and the 6th valve or closing, both can be from the air-breathing single stage compress kind of refrigeration cycle that realizes of described high temperature suction line to pressure liquid feeding pipeline feed flow described, can realize in the middle of second throttle incomplete cooling Two-stage Compression kind of refrigeration cycle to pressure liquid feeding pipeline feed flow described from described low temperature suction line is air-breathing again.
2. incomplete cooling Double-working-condition refrigeration system in the middle of 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. incomplete cooling Double-working-condition refrigeration system in the middle of 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, variable-flow mode is by regulating to the frequency conversion of alternating current generator or by the time variant voltage to direct current generator, or adopts cold-producing medium unloading and load mode to realize the Flow-rate adjustment of cold-producing medium.
4. incomplete cooling Double-working-condition refrigeration system in the middle of second throttle according to claim 1, is characterized in that, described condenser is air-cooled condenser, water-cooled condenser or evaporative condenser.
5. incomplete cooling Double-working-condition refrigeration system in the middle of second throttle according to claim 1, is characterized in that, described choke valve is electric expansion valve, heating power expansion valve, capillary or orifice plate.
6. incomplete cooling Double-working-condition refrigeration system in the middle of second throttle according to claim 1, is characterized in that, described intercooler is plate type heat exchanger or double pipe heat exchanger.
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| CN201320395153.1U CN203454447U (en) | 2013-07-04 | 2013-07-04 | Intermediate inadequacy cooling double operating conditions refrigeration system in secondary throttling |
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| CN201320395153.1U CN203454447U (en) | 2013-07-04 | 2013-07-04 | Intermediate inadequacy cooling double operating conditions refrigeration system in secondary throttling |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103322718A (en) * | 2013-07-04 | 2013-09-25 | 天津商业大学 | Two-stage-throttling incomplete-intercooling double-duty refrigerating system |
| CN106218360A (en) * | 2016-08-24 | 2016-12-14 | 常州市武进南夏墅苏南锻造有限公司 | Vapour-compression refrigeration cycle arrangement |
| CN112484351A (en) * | 2020-12-03 | 2021-03-12 | 苏州电器科学研究院股份有限公司 | Large-span low-temperature refrigerating system for test box |
-
2013
- 2013-07-04 CN CN201320395153.1U patent/CN203454447U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103322718A (en) * | 2013-07-04 | 2013-09-25 | 天津商业大学 | Two-stage-throttling incomplete-intercooling double-duty refrigerating system |
| CN106218360A (en) * | 2016-08-24 | 2016-12-14 | 常州市武进南夏墅苏南锻造有限公司 | Vapour-compression refrigeration cycle arrangement |
| CN112484351A (en) * | 2020-12-03 | 2021-03-12 | 苏州电器科学研究院股份有限公司 | Large-span low-temperature refrigerating system for test box |
| WO2022116133A1 (en) * | 2020-12-03 | 2022-06-09 | 苏州电器科学研究院股份有限公司 | Wide-range low-temperature refrigeration system for test chamber |
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