CN116123747A - Overlapping type cold and hot source unit - Google Patents
Overlapping type cold and hot source unit Download PDFInfo
- Publication number
- CN116123747A CN116123747A CN202310396972.6A CN202310396972A CN116123747A CN 116123747 A CN116123747 A CN 116123747A CN 202310396972 A CN202310396972 A CN 202310396972A CN 116123747 A CN116123747 A CN 116123747A
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- Prior art keywords
- temperature
- low
- compressor
- source unit
- compression cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Sorption Type Refrigeration Machines (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Separation By Low-Temperature Treatments (AREA)
Abstract
The cascade type cold and hot source unit adopts the cascade type compression technology, and not only realizes the simultaneous refrigeration and heating by optimizing a refrigeration cycle system, but also mainly realizes the heating, is assisted by the refrigeration, does not discharge waste heat to the environment, greatly improves the effective utilization rate of energy sources, and simplifies the system design.
Description
Technical Field
The invention relates to the field of cold and heat source units, in particular to the field of simultaneous refrigeration and heating.
Background
In industrial production, many processes are not separated from cold and heat, in order to improve the energy utilization rate, various large cold and heat source supply companies are wanting to improve the efficiency of energy equipment, different cold and heat source supply modes are provided by different companies, but most of the large cold and heat source supply modes supply different heat, and patent publication No. CN 213713606U discloses a cold and heat combined supply double-effect board exchange unit which, although realizing refrigeration and heating, also needs to discharge a part of heat to the environment, the energy utilization rate is not improved to the maximum extent, and the system design is complex.
Disclosure of Invention
The invention adopts the cascade compression technology, and by optimizing the refrigeration cycle system, not only realizes simultaneous refrigeration and heating, but also realizes that the refrigeration is mainly used for heating and the refrigeration is auxiliary, does not discharge waste heat to the environment, and greatly improves the effective utilization rate of energy sources.
The cascade cold-heat source unit is formed by coupling two refrigeration compression cycles through an intermediate heat exchanger, wherein the first refrigeration compression cycle is responsible for outputting cold energy outwards, the second refrigeration compression cycle is responsible for outputting heat outwards, the first refrigeration compression cycle is preferably used for refrigerating agent R134a and is called a low-temperature stage, and the second refrigeration compression cycle is preferably used for refrigerating agent R123 and is called a high-temperature stage.
The exhaust port of the low-temperature-level low-temperature compressor is connected with the low-temperature-level secondary oil separator, the upper part of the low-temperature-level secondary oil separator is connected with a pipeline on the hot side of the intermediate heat exchanger, the lower part of the low-temperature-level secondary oil separator is connected with the air suction port of the low-temperature compressor, the other pipeline on the hot side of the intermediate heat exchanger is connected to the low-temperature-level liquid storage device, and then the low-temperature-level angle valve, the low-temperature-level dry filter, the low-temperature-level electromagnetic valve, the low-temperature-level liquid-showing mirror, the low-temperature-level electronic expansion valve, the evaporator and finally the low-temperature-level electronic expansion valve return to the air inlet of the low-temperature compressor are sequentially connected to form a refrigerant loop.
And the oil inlet and outlet of the low-temperature compressor is connected with a low-temperature oil cooler in parallel, when the oil temperature is too high, a part of refrigerant can be separated from the front of the low-temperature level liquid reservoir and enters the low-temperature level oil cooler to be evaporated, fed and cooled through a fluorine path electromagnetic valve and a low-temperature level expansion valve of the low-temperature level oil cooling system.
In addition, a part of refrigerant is separated from the front of the low-temperature-stage liquid reservoir and forms a liquid spraying device through the low-temperature-stage liquid spraying electromagnetic valve and the low-temperature-stage throttle valve, and low-temperature freon is sprayed to cool the low-temperature compressor when the low-temperature compressor needs to cool.
The high temperature compressor exhaust port of the high temperature level is connected with the high temperature level secondary oil separator, the upper part of the high temperature level secondary oil separator is connected with a pipeline on the hot side of the condenser, the lower part of the high temperature level secondary oil separator is connected with the air suction port of the high temperature compressor, the other side pipeline on the hot side of the condenser is connected to the high temperature level liquid storage device, and then is sequentially connected to the high temperature level angle valve, the high temperature level dry filter, the high temperature level electromagnetic valve, the high temperature level liquid display mirror, the high temperature level electronic expansion valve, the intermediate heat exchanger and finally returns to the air inlet of the high temperature compressor to form another refrigerant loop.
The oil inlet and outlet of the high-temperature compressor is connected with a high-temperature oil cooler in parallel, and when the oil temperature is too high, part of refrigerant can be separated from the front of the high-temperature level liquid storage device and enter the high-temperature oil cooler for evaporation, oil feeding and cooling.
And a part of refrigerant is separated out before the high-temperature-stage liquid reservoir, and the high-temperature-stage liquid-jet electromagnetic valve and the high-temperature-stage throttle valve form a liquid-jet device, so that the high-temperature compressor is cooled by the jet refrigerant when the high-temperature compressor needs to be cooled.
Advantageous effects
The heat generated by the low-temperature stage is completely transferred to the high-temperature stage through the intermediate heat exchanger, and finally, the heat energy is provided for the materials to be heated through the high-temperature condenser, so that the energy utilization rate is improved; the system structure is simplified, auxiliary equipment is reduced, and equipment cost is reduced.
Drawings
Fig. 1 is a schematic diagram of an cascade heat source unit.
The low-temperature compressor 2, the low-temperature secondary oil separator 3, the intermediate heat exchanger 4, the low-temperature level liquid reservoir 5, the low-temperature level angle valve 6, the low-temperature level dry filter 7, the low-temperature level electromagnetic valve 8, the low-temperature level liquid indicator 9, the low-temperature level electronic expansion valve 10, the evaporator 11, the low-temperature level oil cooler 12, the low-temperature level expansion valve 13, the low-temperature level oil cooling system fluorine-way electromagnetic valve 14, the low-temperature level throttle valve 15, the low-temperature level liquid injection electromagnetic valve 16, the low-temperature level oil way electromagnetic valve 17, the high-temperature compressor 18, the high-temperature level secondary oil separator 19, the high-temperature condenser 20, the high-temperature level liquid reservoir 21, the high-temperature level angle valve 22, the high-temperature level dry filter 23, the high-temperature level oil cooler 24, the high-temperature level electromagnetic valve 25, the high-temperature level liquid indicator 26, the high-temperature level electronic expansion valve 27, the high-temperature level oil cooling system fluorine-way electromagnetic valve 28, the high-temperature level liquid injection electromagnetic valve 29, the high-temperature level expansion valve 30, the high-temperature level throttle valve 31 and the high-temperature level oil way electromagnetic valve.
Detailed Description
The application of the cascade heat source unit of the present invention will be described by taking a case of providing cold water at 20 c and hot fluid at 120 c as an example with reference to fig. 1.
The low-temperature level R134a of the cascade cold and heat source unit is compressed by the low-temperature compressor 1, the exhaust temperature reaches 86 ℃, enters the low-temperature level secondary oil separator 2, enters the intercooler 3 after lubricating oil is separated, realizes condensation at 65-70 ℃ in the intercooler, then enters the low-temperature level electronic expansion valve 9 through the low-temperature level liquid storage device 4, the low-temperature level angle valve 5, the low-temperature level drying filter 6, the low-temperature level electromagnetic valve 7 and the low-temperature level liquid display lens 8, enters the evaporator 10 for evaporation after throttling and depressurization, and finally returns to the air suction port of the low-temperature compressor 1. The evaporating temperature of R134a in evaporator 10 is about 15-18 deg.C, so that the outside cold water can be easily cooled to 20 deg.C.
When the low-temperature-stage exhaust gas temperature is high, for example, more than 90 ℃, the low-temperature-stage liquid injection electromagnetic valve 15 is opened, and a small part of R134a is injected to the inlet of the compressor to evaporate, so that the low-temperature-stage exhaust gas temperature is reduced.
When the temperature of the low-temperature oil exceeds a set value, the fluorine-path electromagnetic valve 13 of the low-temperature oil cooling system is opened, R134a is sprayed to the low-temperature oil cooler 11, and the temperature of the lubricating oil is reduced.
The high-temperature level R123 completely absorbs heat released by condensation of R134a from the intermediate heat exchanger, the heat is evaporated at 60-65 ℃ and enters the high-temperature compressor 17, the exhaust temperature after compression reaches 130 ℃, the heat is separated and lubricated by the high-temperature level secondary oil separator 18 and enters the high-temperature condenser 19, the heat is condensed under the working condition of 125 ℃, and finally the heat is condensed by the high-temperature level liquid storage 20, the high-temperature level angle valve 21, the high-temperature level dry filter 22, the high-temperature level electromagnetic valve 24, the high-temperature level liquid display mirror 25 and the high-temperature level electronic expansion valve 26, and the heat enters the intermediate heat exchanger 3 to complete a cycle. Because the high temperature condenser condenses to a temperature of 125 c, it is easy to heat the hot fluid to 120 c.
When the high temperature stage discharge temperature is high, such as in excess of 140 c, the high temperature stage fluid injection solenoid valve 28 is opened to allow a small portion of R123 to be injected into the compressor inlet for evaporation, thereby reducing the discharge temperature.
When the temperature of the high-temperature oil exceeds a set value, a fluorine-path electromagnetic valve 27 of the high-temperature oil cooling system is opened, R123 is sprayed to the oil cooler, and cooling of lubricating oil is achieved.
Claims (5)
1. The cascade cold and heat source unit is formed by coupling two refrigeration compression cycles through an intermediate heat exchanger, wherein the first refrigeration compression cycle is responsible for outputting cold energy outwards, and the second refrigeration compression cycle is responsible for outputting heat outwards, and is characterized in that the first refrigeration compression cycle is formed by connecting the upper part of a low-temperature compressor (1) with a low-temperature secondary oil separator (2), connecting the upper part of the low-temperature secondary oil separator (2) with a pipeline on the hot side of the intermediate heat exchanger (3), connecting the other pipeline on the hot side of the intermediate heat exchanger (3) with a low-temperature angle valve (5), sequentially connecting a low-temperature dry filter (6), a low-temperature electromagnetic valve (7), a low-temperature liquid indicator mirror (8), a low-temperature electronic expansion valve (9), an evaporator (10) and finally returning to an air inlet of the low-temperature compressor (1), so as to form a refrigerant loop; the second refrigeration compression cycle is characterized in that the upper part of a high-temperature compressor (17) is connected with a high-temperature secondary oil separator (18), the upper part of the high-temperature secondary oil separator (18) is connected with a pipeline on the hot side of a high-temperature condenser (19), the other pipeline on the hot side of the high-temperature condenser (19) is connected with a high-temperature angle valve (21), and then is sequentially connected with a high-temperature dry filter (22), a high-temperature electromagnetic valve (24), a high-temperature liquid indicator mirror (25), a high-temperature electronic expansion valve (26), a pipeline on the cold side of an intermediate heat exchanger (3) and finally returns to the air inlet of the high-temperature compressor (17) to form another refrigerant loop, and the intermediate heat exchanger (3) completely releases heat generated by the first refrigeration compression cycle to the second refrigeration compression cycle.
2. The cascade heat and cold source unit as set forth in claim 1, wherein the high temperature compressor and the low temperature compressor are connected in parallel with an oil cooler.
3. The cascade heat and cold source unit of claim 2, wherein the oil cooler is cooled by freon.
4. The cascade heat and cold source unit as claimed in claim 1, wherein the liquid spraying devices are arranged in front of the high-temperature compressor and the low-temperature compressor.
5. The cascade heat and cold source unit as set forth in claim 1, wherein a low-temperature-stage liquid reservoir is provided between the first refrigeration compression cycle intermediate heat exchanger and the low-temperature-stage angle valve, and a high-temperature-stage liquid reservoir is provided between the second refrigeration compression cycle high-temperature condenser and the high-temperature-stage angle valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310396972.6A CN116123747A (en) | 2023-04-14 | 2023-04-14 | Overlapping type cold and hot source unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310396972.6A CN116123747A (en) | 2023-04-14 | 2023-04-14 | Overlapping type cold and hot source unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116123747A true CN116123747A (en) | 2023-05-16 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310396972.6A Pending CN116123747A (en) | 2023-04-14 | 2023-04-14 | Overlapping type cold and hot source unit |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116123747A (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN204006763U (en) * | 2014-06-03 | 2014-12-10 | 云南道精制冷科技有限责任公司 | The large temperature difference unit of Double-working-condition of 1～2 ℃ of frozen water of a kind of system |
| WO2014199445A1 (en) * | 2013-06-11 | 2014-12-18 | 三菱電機株式会社 | Refrigerating device |
| US20160334143A1 (en) * | 2015-05-12 | 2016-11-17 | Shanghai Ocean University | Switchable two-stage and cascade marine energy-saving ultralow-temperature refrigeration system |
| CN108662811A (en) * | 2018-03-16 | 2018-10-16 | 广州德能热源设备有限公司 | Air-source overlapping type heat pump device |
| CN112254366A (en) * | 2020-11-10 | 2021-01-22 | 云南道精制冷科技有限责任公司 | Cold and hot combined supply double-effect plate replacement machine set |
| CN213713606U (en) * | 2020-11-10 | 2021-07-16 | 云南道精制冷科技有限责任公司 | Cold and hot combined supply double-effect plate replacement machine set |
| CN214841769U (en) * | 2021-06-01 | 2021-11-23 | 徐州极子能源管理有限公司 | Overlapping heat pump convenient for adjusting load rate change |
-
2023
- 2023-04-14 CN CN202310396972.6A patent/CN116123747A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014199445A1 (en) * | 2013-06-11 | 2014-12-18 | 三菱電機株式会社 | Refrigerating device |
| 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 |
| CN204006763U (en) * | 2014-06-03 | 2014-12-10 | 云南道精制冷科技有限责任公司 | The large temperature difference unit of Double-working-condition of 1～2 ℃ of frozen water of a kind of system |
| US20160334143A1 (en) * | 2015-05-12 | 2016-11-17 | Shanghai Ocean University | Switchable two-stage and cascade marine energy-saving ultralow-temperature refrigeration system |
| CN108662811A (en) * | 2018-03-16 | 2018-10-16 | 广州德能热源设备有限公司 | Air-source overlapping type heat pump device |
| CN112254366A (en) * | 2020-11-10 | 2021-01-22 | 云南道精制冷科技有限责任公司 | Cold and hot combined supply double-effect plate replacement machine set |
| CN213713606U (en) * | 2020-11-10 | 2021-07-16 | 云南道精制冷科技有限责任公司 | Cold and hot combined supply double-effect plate replacement machine set |
| CN214841769U (en) * | 2021-06-01 | 2021-11-23 | 徐州极子能源管理有限公司 | Overlapping heat pump convenient for adjusting load rate change |
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