CN117267981A - Gas-liquid hybrid power type heat pipe composite refrigeration system and refrigeration method - Google Patents
Gas-liquid hybrid power type heat pipe composite refrigeration system and refrigeration method Download PDFInfo
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- CN117267981A CN117267981A CN202311094986.9A CN202311094986A CN117267981A CN 117267981 A CN117267981 A CN 117267981A CN 202311094986 A CN202311094986 A CN 202311094986A CN 117267981 A CN117267981 A CN 117267981A
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 92
- 239000007788 liquid Substances 0.000 title claims abstract description 58
- 238000000034 method Methods 0.000 title claims abstract description 23
- 239000002131 composite material Substances 0.000 title claims abstract description 16
- YCKRFDGAMUMZLT-UHFFFAOYSA-N Fluorine atom Chemical compound [F] YCKRFDGAMUMZLT-UHFFFAOYSA-N 0.000 claims abstract description 82
- 229910052731 fluorine Inorganic materials 0.000 claims abstract description 82
- 239000011737 fluorine Substances 0.000 claims abstract description 82
- 238000001816 cooling Methods 0.000 claims abstract description 63
- 230000006835 compression Effects 0.000 claims abstract description 28
- 238000007906 compression Methods 0.000 claims abstract description 28
- 239000003507 refrigerant Substances 0.000 claims description 36
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 15
- 230000005494 condensation Effects 0.000 claims description 10
- 238000009833 condensation Methods 0.000 claims description 10
- 238000004378 air conditioning Methods 0.000 claims description 8
- 230000008859 change Effects 0.000 claims description 5
- 230000009977 dual effect Effects 0.000 claims description 2
- 238000005516 engineering process Methods 0.000 abstract description 31
- 230000009286 beneficial effect Effects 0.000 abstract description 11
- 238000009434 installation Methods 0.000 abstract description 9
- 230000000295 complement effect Effects 0.000 abstract description 4
- 150000001875 compounds Chemical class 0.000 abstract description 4
- 239000012071 phase Substances 0.000 description 28
- 238000001704 evaporation Methods 0.000 description 15
- 238000010586 diagram Methods 0.000 description 9
- 230000008020 evaporation Effects 0.000 description 9
- 230000008569 process Effects 0.000 description 9
- 230000008520 organization Effects 0.000 description 6
- 238000013459 approach Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000004134 energy conservation Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
- 239000012808 vapor phase 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
- F25B27/00—Machines, plants or systems, using particular sources of energy
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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
- F25B31/00—Compressor 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
Abstract
The invention relates to a gas-liquid hybrid power type heat pipe composite refrigeration system and a refrigeration method, comprising the following steps: the air conditioner comprises a pneumatic compressor, a condenser, a throttling device and an evaporator which are sequentially connected into a circulation loop, wherein a fluorine pump is further arranged on the circulation loop in parallel with the pneumatic compressor. The invention has the beneficial effects that the compound refrigerating unit has 4 operation modes: a fluorine pump refrigeration cycle mode, a fluorine pump refrigeration cycle+gas phase power type heat pipe cycle mode, a gas phase power type heat pipe cycle mode and a vapor compression refrigeration cycle mode, wherein the refrigeration unit automatically switches the cycle operation mode according to indoor and outdoor temperatures; the combined type refrigerating system integrates a fluorine pump technology, a gas phase power type heat pipe technology and a vapor compression refrigerating technology, forms a novel energy-saving cooling technology with complementary advantages of the fluorine pump technology, the gas phase power type heat pipe technology and the vapor compression refrigerating technology, fully utilizes a natural cold source, improves the operation efficiency, realizes energy-saving operation, and breaks through the limitation bottleneck of the installation positions of the indoor unit and the outdoor unit.
Description
Technical Field
The invention relates to the technical field of refrigeration, in particular to a gas-liquid hybrid power type heat pipe composite refrigeration system and a refrigeration method.
Background
The low-temperature low-pressure superheated gas in the traditional vapor compression refrigeration cycle enters the suction side of the pneumatic compressor, is compressed to become high-temperature high-pressure gas, is discharged and enters the condenser, is cooled by an external cold source into medium-temperature high-pressure supercooled liquid in the condenser, is throttled by a throttling device to become low-temperature low-pressure two-phase fluid, enters the evaporator, is changed into low-temperature low-pressure superheated gas after absorbing heat, is sucked into the pneumatic compressor, and is circulated again. The pressure-enthalpy diagram is shown in fig. 2, the absolute pressure is taken as an ordinate, the enthalpy value is taken as an abscissa, and the refrigeration cycle is a process of pressurizing and then depressurizing, and the process needs to consume larger energy consumption, so that the energy efficiency ratio COP (co-eff icient of performance) is lower. In fig. 2-3: letters represent the end state, the A-B process occurs in the compressor, the B-C process occurs in the condenser, the C-D process occurs in the expansion valve, and the D-A process occurs in the evaporator.
When the external environment of the refrigeration cycle is gradually improved, for example, natural cooling can be used for replacing or partially replacing mechanical compression refrigeration when the temperature of the outdoor environment is reduced, so that the condensation pressure is reduced, namely, the condensation pressure line of the whole cycle chart is gradually reduced, the evaporation pressure line is basically maintained unchanged, the cycle chart gradually approaches to the heat pipe cycle (shown in fig. 3) and even reaches the heat pipe cycle state, so that the heat pipe cycle is understood to be the most ideal and original state of the refrigeration cycle, and also is the state with the minimum energy consumption, and the original heat pipe cycle is required to deviate from the original cycle in a way of pressurizing and then depressurizing due to the insufficient outdoor environment, but the refrigeration cycle gradually approaches to the heat pipe cycle as long as the external environment is enough. How to fully utilize natural cold sources, improve the operation efficiency, realize energy-saving operation, and break through the limitation bottleneck of the installation positions of indoor units and outdoor units is a problem which needs to be solved at present.
Disclosure of Invention
The invention aims to solve the technical problems of providing a gas-liquid hybrid power type heat pipe composite refrigerating system and a refrigerating method, which integrate a fluorine pump technology, a gas phase power type heat pipe technology and a vapor compression refrigerating technology to form a novel energy-saving cooling technology with complementary advantages, thereby solving the problems of how to fully utilize a natural cold source, improve the operation efficiency, realize energy-saving operation and break through the bottleneck of limiting the installation positions of an indoor unit and an outdoor unit.
The technical scheme for solving the technical problems is as follows: a gas-liquid hybrid heat pipe composite refrigeration system comprising: the air conditioner comprises a pneumatic compressor, a condenser, a throttling device and an evaporator which are sequentially connected into a circulation loop, wherein a fluorine pump is further arranged on the circulation loop in parallel with the pneumatic compressor.
The beneficial effects of the invention are as follows: the compound refrigeration unit has 4 modes of operation: fluorine pump refrigeration cycle mode (abbreviated as fluorine pump mode), fluorine pump refrigeration cycle+gas phase power type heat pipe cycle mode (abbreviated as fluorine pump+pneumatic heat pipe mode), gas phase power type heat pipe cycle mode (abbreviated as pneumatic heat pipe mode) and vapor compression refrigeration cycle mode (abbreviated as mechanical refrigeration mode), the refrigerating unit automatically switches the cycle operation mode according to indoor and outdoor temperatures. The combined type refrigerating system integrates a fluorine pump technology, a gas phase power type heat pipe technology and a vapor compression refrigerating technology, forms a novel energy-saving cooling technology with complementary advantages of the fluorine pump technology, the gas phase power type heat pipe technology and the vapor compression refrigerating technology, fully utilizes a natural cold source, improves the operation efficiency, realizes energy-saving operation, and breaks through the limitation bottleneck of the installation positions of the indoor unit and the outdoor unit.
On the basis of the technical scheme, the invention can be improved as follows.
Further, the throttle device includes: the electromagnetic valve is arranged in parallel with the expansion valve.
The beneficial effects of adopting the further scheme are as follows: the electromagnetic valve and the expansion valve are arranged in parallel, so that the switching of different modes is realized by switching the electromagnetic valve and the opening or closing of the expansion valve.
Further, the throttling device, the pneumatic compressor and the fluorine pump which are arranged in parallel are integrated into a whole to form a refrigerating unit.
The beneficial effects of adopting the further scheme are as follows: the throttling device, the pneumatic compressor and the fluorine pump are integrated into a whole, so that the structure is more compact, and the throttle device can be directly installed in different application scenes.
Further, the condenser is a water cooling tower, an air cooling tower or an evaporation cooling tower;
the evaporator includes: room-level precision air conditioning, inter-column air conditioning, back-plate precision air conditioning and/or overhead refrigerant phase change ends;
the evaporator is connected with one end of the refrigerating unit through a pair of refrigerant pipes respectively, and the other end of the refrigerating unit is connected with the condenser through another pair of refrigerant pipes respectively.
The beneficial effects of adopting the further scheme are as follows: the refrigerating system can be coupled with three cold sources of air cooling, water cooling and evaporative cooling, is matched with different end forms, has wide application range and multiple application areas, and has better energy-saving effect in different climatic regions.
The invention also discloses a gas-liquid hybrid power type heat pipe composite refrigeration method, which uses the refrigeration system and comprises the following steps:
connecting the pneumatic compressor, the condenser, the throttling device and the evaporator in series to form a circulation loop, and connecting the fluorine pump and the pneumatic compressor in parallel;
the refrigeration system switches different circulation modes according to the outdoor air dry bulb temperature.
The beneficial effects of adopting the further scheme are as follows: according to indoor and outdoor temperatures, the refrigerating system selectively operates in one mode, the aim of energy-saving operation is achieved on the premise that the indoor cooling requirement is guaranteed, meanwhile, the adaptability is higher, and the applicability is wider.
Further, the step of switching different circulation modes of the refrigeration system according to the outdoor air dry bulb temperature comprises the following steps:
when the outdoor air dry bulb temperature tw is less than or equal to 0 ℃, the refrigerating system is switched into a fluorine pump refrigerating cycle mode;
when the temperature of the outdoor air dry bulb is more than 0 ℃ and less than or equal to 4 ℃, the refrigerating system is switched into a fluorine pump refrigerating cycle and gas phase power type heat pipe cycle mode;
when the outdoor air dry bulb temperature is 4 ℃ < tw <30 ℃, the refrigerating system is switched to a gas-phase power type heat pipe circulation mode;
when the temperature tw of the outdoor air dry bulb is more than or equal to 30 ℃, the refrigerating system is switched into a vapor compression refrigerating cycle mode.
The beneficial effects of adopting the further scheme are as follows: according to the different refrigeration cycle modes of switching of outdoor air dry bulb temperature, realize the goal of energy-conserving operation under the prerequisite of guaranteeing indoor cooling requirement, the suitability is higher simultaneously, and the applicability is wider.
Further, when the outdoor air dry bulb temperature tw is less than or equal to 0 ℃, the step of switching the refrigeration system to the fluorine pump refrigeration cycle mode is as follows:
the electromagnetic valve in the throttling device is opened, and the electronic expansion valve is closed; the pneumatic compressor is closed, and the refrigerant circulation is powered by the fluorine pump;
the low-temperature low-pressure liquid working medium absorbs heat and evaporates in the evaporator to become a low-temperature low-pressure gaseous working medium, and the low-temperature low-pressure liquid working medium flows into the condenser to release heat and condense into a low-temperature low-pressure liquid working medium under the driving of the fluorine pump, returns to the evaporator again to absorb heat and evaporate through the electromagnetic valve, and circulates reciprocally.
The beneficial effects of adopting the further scheme are as follows: the air conditioner adopts a fluorine pump refrigeration cycle mode, fully utilizes an outdoor natural cold source, achieves the aim of energy-saving operation on the premise of guaranteeing indoor cooling requirements, simultaneously provides power for heat pipe circulation by the fluorine pump, breaks through the limitation bottleneck of the installation position of the heat pipe, and is higher in adaptability and wider in applicability.
Further, when the outdoor air dry bulb temperature is 0 ℃ < tw less than or equal to 4 ℃, the step of switching the refrigerating system into a fluorine pump refrigerating cycle and gas phase power type heat pipe circulating mode is as follows:
the electromagnetic valve in the throttling device is opened, and the expansion valve is opened; the pneumatic compressor and the fluorine pump are all started;
the pneumatic compressor operates at a low pressure ratio, the low-temperature low-pressure liquid working medium absorbs heat in the evaporator and evaporates to become a low-temperature low-pressure gaseous working medium, and the low-temperature low-pressure liquid working medium flows into the condenser to release heat and condense to become a low-temperature low-pressure liquid working medium under the dual drive of the pneumatic compressor and the fluorine pump which are arranged in parallel, and returns to the evaporator again to absorb heat and evaporate through the electromagnetic valve and the expansion valve which are arranged in parallel, and the reciprocating cycle is performed.
The beneficial effects of adopting the further scheme are as follows: the pneumatic compressor and the fluorine pump jointly provide power required by gas flow, the heat exchange capacity of the condenser is controlled to be matched with indoor heat load, natural cooling time is widened, natural cold sources in transitional seasons are more fully utilized, and energy conservation is realized.
Further, when the outdoor air dry bulb temperature is 4 ℃ < tw <30 ℃, the step of switching the refrigeration system to the gas-phase power heat pipe circulation mode is as follows:
the electromagnetic valve in the throttling device is closed, and the expansion valve is kept open; the fluorine pump is closed, and the pneumatic compressor is started;
the low-temperature low-pressure liquid working medium absorbs heat and evaporates in the evaporator to become a low-temperature low-pressure gaseous working medium, the low-temperature low-pressure gaseous working medium is compressed by a pneumatic compressor operated by a low-pressure ratio and then becomes a medium-temperature medium-pressure gaseous working medium, the medium-temperature medium-pressure gaseous working medium flows into a condenser to release heat and condense to become a medium-temperature medium-pressure liquid working medium, and the medium-temperature medium-pressure liquid working medium becomes the low-temperature low-pressure liquid working medium after being throttled by an expansion valve and returns to the evaporator again to absorb heat and evaporate and is recycled.
The beneficial effects of adopting the further scheme are as follows: the compression ratio of the pneumatic compressor is adjusted to meet the requirement of refrigerating operation with a small pressure ratio, so that the power consumption of the compressor is reduced, and the COP of the unit is improved.
Further, when the outdoor air dry bulb temperature tw is more than or equal to 30 ℃, the step of switching the refrigeration system to the vapor compression refrigeration cycle mode is as follows:
an expansion valve in the throttling device is opened, and an electromagnetic valve is closed; the pneumatic compressor is started, and the fluorine pump is closed;
the low-temperature low-pressure liquid working medium absorbs heat and evaporates in the evaporator to become a low-temperature low-pressure gaseous working medium, the low-temperature low-pressure gaseous working medium is compressed by a pneumatic compressor operated by a high-pressure ratio to become a high-temperature high-pressure gaseous working medium, the high-temperature high-pressure gaseous working medium flows into a condenser to release heat and condense to become a high-temperature high-pressure liquid working medium, and the high-temperature high-pressure liquid working medium is throttled by an expansion valve to become the low-temperature low-pressure liquid working medium to return to the evaporator again for absorbing heat and evaporating and reciprocating circulation.
The beneficial effects of adopting the further scheme are as follows: the pressure ratio of the pneumatic compressor is improved to carry out refrigeration cycle, and the pressure ratio of the pneumatic compressor and the heat exchange capacity of the heat exchanger are always matched with the load, so that the normal cooling of the tail end is ensured.
Drawings
FIG. 1 is a schematic diagram of a vapor compression refrigeration cycle of the prior art;
fig. 2 is a prior art vapor compression refrigeration cycle pressure enthalpy diagram;
FIG. 3 is a prior art heat pipe refrigeration cycle pressure enthalpy diagram;
FIG. 4 is a schematic diagram of a compound refrigeration cycle of the present invention;
FIG. 5 is a schematic diagram of a water-cooled system according to the present invention;
FIG. 6 is a schematic diagram of an air-cooled system according to the present invention;
FIG. 7 is a schematic diagram of an evaporative cooling system according to the present invention.
In the drawings, the list of components represented by the various numbers is as follows:
1. solenoid valve 2, expansion valve, 3, evaporimeter, 4, pneumatic compressor, 5, fluorine pump, 6, condenser, 7, throttling arrangement, 8, refrigerant pipe, 9, condenser pipe, 10, compressor.
Detailed Description
The principles and features of the present invention are described below with examples given for the purpose of illustration only and are not intended to limit the scope of the invention.
In a first aspect, in one embodiment of the present invention, as shown in fig. 4, a gas-liquid hybrid heat pipe composite refrigeration system includes: the pneumatic compressor 4, the condenser 6, the throttling device 7 and the evaporator 3 are sequentially connected into a circulation loop, and the circulation loop and the pneumatic compressor 4 are also connected in parallel and provided with a fluorine pump 5; during operation, the pneumatic compressor 4 and the fluorine pump 5 can be started simultaneously or not simultaneously according to the use requirement.
The fluorine pump technology, the gas phase power type heat pipe technology and the vapor compression refrigeration technology are combined, the fluorine pump technology adopts the refrigeration cycle of the fluorine pump 5, the gas phase power type heat pipe technology and the vapor compression refrigeration technology adopt the refrigeration cycle of the pneumatic compressor 4, and the schematic diagram is shown in figure 4.
Compared with the traditional vapor compression refrigeration air conditioning system shown in fig. 1, the scheme updates and optimally arranges the components such as the pipeline, the condenser, the valve and the like of the refrigeration system, and adds the fluorine pump 5 to realize the fluorine pump refrigeration cycle, so that the structure of the fluorine pump refrigeration cycle is changed into a fluorine pump circulation branch and a pneumatic compressor circulation branch. In this embodiment, the pneumatic compressor 4 may also be used as a gas booster pump, and the compressor is operated at a low pressure ratio to provide circulating power for the gas-phase power type heat pipe system when the outdoor temperature is low by utilizing the pressure ratio characteristic of the compressor. When the outdoor temperature is high, the vapor compression refrigeration cycle is operated at a high pressure ratio. In the present embodiment, the low pressure ratio and the high pressure ratio are both relative values, and the evaporator 3, the condenser 6, and the throttle device 7 are shared by the fluorine pump refrigeration cycle, the gas-phase power heat pipe cycle, and the vapor compression refrigeration cycle.
The compound refrigerating unit in the scheme has 4 operation modes: fluorine pump refrigeration cycle mode (abbreviated as fluorine pump mode), fluorine pump refrigeration cycle+gas phase power type heat pipe cycle mode (abbreviated as fluorine pump+pneumatic heat pipe mode), gas phase power type heat pipe cycle mode (abbreviated as pneumatic heat pipe mode) and vapor compression refrigeration cycle mode (abbreviated as mechanical refrigeration mode), the refrigerating unit automatically switches the cycle operation mode according to indoor and outdoor temperatures. The combined type refrigerating system integrates a fluorine pump technology, a gas phase power type heat pipe technology and a vapor compression refrigerating technology, forms a novel energy-saving cooling technology with complementary advantages of the fluorine pump technology, the gas phase power type heat pipe technology and the vapor compression refrigerating technology, fully utilizes a natural cold source, improves the operation efficiency, realizes energy-saving operation, and breaks through the limitation bottleneck of the installation positions of the indoor unit and the outdoor unit.
Specifically, in order to utilize an outdoor natural cooling source, in a conventional refrigeration system, no equipment is installed on a parallel branch of a compressor, only a bypass pipe is provided, and refrigerant is contained therein, and in the circulation process, gravity circulation is required, so that an outdoor condenser is required to be provided higher than an indoor evaporator, so that the refrigerant flows downstream through gravity, and then returns to the outdoor condenser through evaporation phase change or the like. In conventional refrigeration systems, it is necessary to ensure that the outdoor condenser is taller than the indoor evaporator, while the length between them is not too long.
In this embodiment, the circulating power is increased by the arrangement of the fluorine pump 5, so that the installation height of the outdoor condenser and the indoor evaporator and the distance are not required to be limited, i.e. the limitation bottleneck of the installation positions of the indoor unit and the outdoor unit is broken through.
As shown in fig. 4, the throttle device 7 includes: the electromagnetic valve 1 and the expansion valve 2 are arranged in parallel, and the electromagnetic valve 1 and the expansion valve 2 are connected in parallel.
In the above-described scheme, the solenoid valve 1 is provided in parallel with the expansion valve 2, so that switching of different modes is achieved by switching the opening or closing of the solenoid valve 1 and the expansion valve 2.
As shown in fig. 4, in a specific manufacturing process, the throttle device 7, the pneumatic compressor 4 and the fluorine pump 5 which are arranged in parallel can be integrated into a whole, and the integrated components form a composite refrigerating unit which can be directly applied.
In the scheme, the throttling device 7, the pneumatic compressor 4 and the fluorine pump 5 are integrated into a whole, the structure is more compact, and the device can be directly installed in different application scenes.
As shown in fig. 5-7, three cold sources of air cooling, water cooling and evaporative cooling can be coupled in the system, wherein the cold source is the condenser 6, and in this embodiment, the condenser 6 is a water cooling tower, an air cooling tower or an evaporative cooling tower.
The specific connection mode is as follows: the evaporator 3 is connected to one end of the refrigerating unit through a pair of refrigerant pipes 8, and the other end of the refrigerating unit is also connected to the condenser 6 through another pair of refrigerant pipes 8, wherein the flowing direction and the temperature of the refrigerant in each pair of refrigerant pipes 8 are different.
As shown in fig. 5, when the cold source adopts a water cooling tower, a heat exchanger is further arranged between the water cooling tower and the refrigerating unit, the water cooling tower is connected with one end of the heat exchanger through a cooling water pipe 9, and the other end of the heat exchanger is connected with the refrigerating unit through a refrigerant pipe 8; in this embodiment, the heat exchanger may be an external plate heat exchanger or an external shell and tube heat exchanger.
The limiting temperature of natural cooling of the cooling tower is outdoor wet bulb temperature, the water-cooled system uses water as a heat transfer medium and is connected with an external heat exchanger, and the refrigerant from the unit is cooled in a temperature difference heat transfer mode, so that heat is transferred to the outside.
Specifically, when the cold source adopts an air-cooled cooling tower, the limiting temperature of natural cooling of the cooling tower is outdoor dry bulb temperature, the air-cooled refrigeration system uses a refrigerant as a heat transfer medium, and external cold air is used as the cold source. The air-cooled condenser is connected with the combined refrigerating unit, takes away the heat of the refrigerant in a temperature difference heat transfer mode, and cools the refrigerant.
Specifically, when the cold source adopts evaporative cooling, the limiting temperature of natural cooling of the cooling tower is the outdoor wet bulb temperature, the evaporative condensing refrigeration system adopts a refrigerant as a heat transfer medium, heat dissipation and refrigerant condensation are realized by utilizing latent heat generated by water evaporation, namely water sprayed on the surface of the condenser is contacted with outdoor dry and cold air, liquid water is evaporated into a vapor state, heat on the surface of the condenser is taken away, and therefore the refrigerant in the condenser is cooled.
Wherein, the terminal form also has a plurality of choices, and the indoor set of terminal is the evaporimeter 3 promptly, and evaporimeter 3 includes: the room-level precise air conditioner, the inter-column air conditioner, the back-plate type precise air conditioner and/or the overhead refrigerant phase change terminal can be used in one or more modes according to the requirement. For example:
form one: room-level precise air conditioner
The common residual pressure (Pa) is 150-200Pa;
energy efficiency ratio (kW/kW): 16;
airflow organization form: the room-level airflow organization is a heat treatment method of cooling the room environment and then cooling the cabinet, and the whole room is refrigerated and supplied with air. The most common open channel raised floor air supply of data center adopts high-power precision air conditioner to refrigerate, and the rack adopts face-to-face, back-to-back arrangement, through setting up the air conditioner supply port inside raised floor, send into room and rack air intake department with cold wind via the floor grid, and the hot-blast accurate air conditioner of room return is got back to rack exhaust hot-blast, and whole refrigeration process is accomplished through the room.
Form two: air conditioner between rows
The common residual pressure (Pa) is 20-50Pa;
energy efficiency ratio (kW/kW): 25, a step of selecting a specific type of material;
airflow organization form: compared with the room level, the row-column air conditioner air supply is closer to the cabinet, and the refrigerating air conditioner and the cabinet can be connected through the closed channel, so that the refrigerating air supply mode is adopted for refrigerating and supplying air to the cabinets in the same row and column. The air conditioner between the columns is additionally provided with a closed cold channel for air supply, so that raised floors and precise air conditioners are omitted, the air conditioner between the columns is directly arranged between the cabinets, an air conditioner air supply port and an air inlet of the cabinet are closed in a closed channel mode, cold and hot air flows are separated, cooling efficiency is effectively improved, and in addition, the air conditioner air outlet and an air conditioner air return port are connected in a closed hot channel air supply mode.
Form three: back plate type precise air conditioner
The common residual pressure (Pa) is 0-20Pa;
energy efficiency ratio (kW/kW): 60;
airflow organization form: the back plate type precise air conditioner firstly cools the inside of the cabinet and then cools the room, is directly arranged in the cabinet to refrigerate IT equipment, and the whole air supplying and returning process is completed in the cabinet.
Form four: overhead refrigerant phase change terminal
The common residual pressure (Pa) is 30-50Pa;
energy efficiency ratio (kW/kW): 20, a step of;
airflow organization form: overhead is a form of room-level airflow organization that utilizes the original air-conditioning headspace, mounted on top of it, with the addition of a cold source heat exchanger. The original terminal air supply mode is not changed, and the double cold sources are formed with the original system, so that the safety is high and the practicability is high.
The refrigerating system in the scheme can be used for coupling three cold sources of air cooling, water cooling and evaporative cooling, is matched with different tail end forms, has wide application range and multiple application areas, and has better energy-saving effect in different climatic regions.
In a second aspect, a gas-liquid hybrid power type heat pipe composite refrigeration method is also disclosed, which comprises the following specific steps:
the pneumatic compressor 4, the condenser 6, the throttling device 7 and the evaporator 3 are connected in series to form a circulation loop, and the fluorine pump 5 is arranged in parallel with the pneumatic compressor 4;
the refrigeration system switches different circulation modes according to the outdoor air dry bulb temperature.
According to the scheme, the refrigerating system selectively operates in one mode according to the indoor and outdoor temperatures, and the aim of energy-saving operation is fulfilled on the premise of guaranteeing the indoor cooling requirement.
Further, the step of switching different circulation modes of the refrigeration system according to the outdoor air dry bulb temperature comprises the following steps:
when the outdoor air dry bulb temperature tw is less than or equal to 0 ℃, the refrigerating system is switched to a fluorine pump refrigerating cycle mode;
when the temperature of the outdoor air dry bulb is more than 0 ℃ and less than or equal to 4 ℃, the refrigerating system is switched into a fluorine pump refrigerating cycle and gas phase power type heat pipe cycle mode;
when the outdoor air dry bulb temperature is 4 ℃ < tw <30 ℃, the refrigerating system is switched to a gas-phase power type heat pipe circulation mode;
when the temperature tw of the outdoor air dry bulb is more than or equal to 30 ℃, the refrigerating system is switched into a vapor compression refrigerating cycle mode.
In the scheme, different refrigeration cycle modes are switched according to the difference of the temperature of the outdoor air dry bulb, the aim of energy-saving operation is achieved on the premise of guaranteeing the indoor cooling requirement, meanwhile, the suitability is higher, and the applicability is wider.
Specifically, as shown in fig. 5, when the outdoor air dry bulb temperature tw is less than or equal to 0 ℃, the step of switching the refrigeration system to the fluorine pump refrigeration cycle mode is:
the electromagnetic valve 1 in the throttling device 7 is opened, and the expansion valve 2 is closed; the pneumatic compressor 4 is closed, the fluorine pump 5 is opened, and the fluorine pump 5 is used for providing power for the refrigerant circulation;
the low-temperature low-pressure liquid working medium absorbs heat and evaporates in the evaporator 3 to become a low-temperature low-pressure gaseous working medium, and the low-temperature low-pressure liquid working medium is driven by the fluorine pump 5 to overcome the resistance of a pipeline, flows into the condenser 6 to release heat and condense to become the low-temperature low-pressure liquid working medium, and returns to the evaporator 3 again to absorb heat and evaporate through the electromagnetic valve 1 to circulate reciprocally.
In this step, the working medium is a commonly accepted refrigerant, for example: r134a, R22, R32, R410A, etc. can be selected as required.
In the scheme, the outdoor natural cold source is fully utilized by adopting the fluorine pump refrigeration cycle mode, the aim of energy-saving operation is fulfilled on the premise of ensuring the indoor cooling requirement, and meanwhile, the fluorine pump 5 provides power for the heat pipe circulation, so that the limitation bottleneck of the installation position of the heat pipe is broken through, the suitability is higher, and the applicability is wider.
Specifically, as shown in fig. 5, when the outdoor air dry bulb temperature is 0 ℃ < tw less than or equal to 4 ℃, the steps of switching the refrigeration system to the fluorine pump refrigeration cycle+gas phase power type heat pipe cycle mode are as follows:
the electromagnetic valve 1 in the throttling device 7 is opened, and the expansion valve 2 is opened; the pneumatic compressor 4 and the fluorine pump 5 are all started;
on the basis of a fluorine pump refrigeration cycle mode, a pneumatic compressor system is started, a pneumatic compressor 4 operates at a low pressure ratio, a low-temperature low-pressure liquid working medium absorbs heat and evaporates in an evaporator 3 to form a low-temperature low-pressure gaseous working medium, the pneumatic compressor 4 and a fluorine pump 5 which are arranged in parallel are driven in a double mode, the resistance of a pipeline is overcome, the low-temperature low-pressure liquid working medium flows into a condenser 6 to be subjected to heat release and condensation, and the low-temperature low-pressure liquid working medium returns to the evaporator 3 again to absorb heat and evaporate through an electromagnetic valve 1 and an expansion valve 2 which are arranged in parallel, and is circulated in a reciprocating mode.
In the scheme, the pneumatic compressor 4 and the fluorine pump 5 jointly provide power required by gas flow, the heat exchange capacity of the condenser 3 is controlled to be matched with indoor heat load, natural cooling time is widened, natural cold sources in transitional seasons are more fully utilized, and energy conservation is achieved.
Specifically, as shown in fig. 5, when the outdoor air dry bulb temperature is 4 ℃ < tw <30 ℃, the steps of switching the refrigeration system to the vapor-phase power heat pipe circulation mode are:
the electromagnetic valve 1 in the throttling device 7 is kept closed, and the expansion valve 2 is kept open; the fluorine pump 5 is closed, and the pneumatic compressor 4 is started;
the fluorine pump 5 is turned off in the circulation mode of the fluorine pump refrigeration cycle and the gas phase power type heat pipe, the low-temperature low-pressure liquid working medium absorbs heat in the evaporator 3 to evaporate to become a low-temperature low-pressure gaseous working medium, the low-temperature low-pressure gaseous working medium is compressed by the pneumatic compressor 4 operated by a low-pressure ratio to become a medium-temperature medium-pressure gaseous working medium, the medium-temperature medium-pressure gaseous working medium flows into the condenser 6 to release heat and condense to become a medium-temperature medium-pressure liquid working medium, and the medium-temperature medium-pressure liquid working medium is throttled by the expansion valve 2 to become a low-temperature low-pressure liquid working medium to return to the evaporator 3 again to absorb heat to evaporate, and the reciprocating cycle is performed.
In the scheme, the compression ratio of the pneumatic compressor 4 is adjusted to meet the requirement of refrigerating operation with a small pressure ratio, so that the power consumption of the compressor is reduced, and the COP of the unit is improved.
Specifically, as shown in fig. 5, when the outdoor air dry bulb temperature tw is greater than or equal to 30 ℃, the step of switching the refrigeration system to the vapor compression refrigeration cycle mode is:
the expansion valve 2 in the throttling device 7 is opened, and the electromagnetic valve 1 is closed; the pneumatic compressor 4 is started, and the fluorine pump 5 is kept closed;
the low-temperature low-pressure liquid working medium absorbs heat and evaporates in the evaporator 3 to become a low-temperature low-pressure gaseous working medium, the low-temperature low-pressure gaseous working medium is compressed by the pneumatic compressor 4 operated by high-pressure ratio to become a high-temperature high-pressure gaseous working medium, the high-temperature high-pressure gaseous working medium flows into the condenser 6 to be subjected to heat release and condensation to become a high-temperature high-pressure liquid working medium, and the high-temperature high-pressure liquid working medium is throttled by the expansion valve 2 to become a low-temperature low-pressure liquid working medium to be returned to the evaporator 3 again for absorbing heat and evaporating and reciprocating circulation.
In the scheme, the pressure ratio of the pneumatic compressor 4 is improved to carry out refrigeration cycle, and the pressure ratio of the pneumatic compressor and the heat exchange capacity of the heat exchanger are always matched with the load, so that the normal cooling of the tail end is ensured.
In this example, the high temperature, high pressure or low temperature, low pressure are relative values under undefined conditions. The low temperature and low pressure may correspond to the refrigerant evaporating temperature and pressure, and the high temperature and high pressure may correspond to the refrigerant condensing temperature and pressure. The evaporating temperature is related to the set indoor temperature of the air conditioner, the condensing temperature is related to the outdoor environment temperature of the application place and the cold source form (namely air cooling, water cooling or evaporation cooling), after the evaporating temperature and the condensing temperature are determined, the temperature and the pressure of different refrigerants have one-to-one correspondence, and the compressor pressure ratio is the condensing pressure divided by the evaporating pressure.
For example: the refrigeration system in the scheme is generally applied to a data center, and the evaporation temperature of the refrigerant is about 14 ℃ in the form of the direct cooling tail end of each refrigerant; taking Beijing area as an example, a cold source form of water cooling is adopted, the temperature difference between the outdoor temperature and the corresponding condensing temperature is about 14 ℃, namely the outdoor temperature is 0 ℃, and the condensing temperature is about 14 ℃. Table 1 gives the corresponding pressures of the refrigerant at the different evaporation temperatures.
Table 1 common refrigerant saturation pressure gauge
The operation mode of the gas-liquid hybrid power type heat pipe composite refrigeration system is as follows:
1) The outdoor dry bulb temperature tw is less than or equal to 0 ℃, and the fluorine pump refrigeration cycle mode;
2) The outdoor dry bulb temperature is more than 0 ℃ and less than or equal to 4 ℃, and the fluorine pump refrigeration cycle and gas phase power type heat pipe cycle mode are adopted;
3) A gas phase power type heat pipe circulation mode with the temperature of more than 4 ℃ and less than 30 ℃;
4) tw is greater than or equal to 30 ℃, and vapor compression refrigeration cycle mode.
The pressure ratio ranges of the compressors in each of the operation modes are shown in table 2 below.
Table 2 range of pressure ratios for refrigerant compressors in general use
In the present embodiment, the high pressure ratio and the low pressure ratio are both relative values, for example: for R22, < 2.203 is low pressure, and no less than 2.203 is high pressure; this value corresponds only to the division of the R22 refrigerant at an evaporation temperature of 14 degrees and a condensation temperature of 44 degrees at high and low pressures, with the division changing when the evaporation condensation temperature changes.
While embodiments of the present invention have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the invention, and that variations, modifications, alternatives and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the invention.
Claims (10)
1. A gas-liquid hybrid heat pipe composite refrigeration system, comprising: the air conditioner comprises a pneumatic compressor (4), a condenser (6), a throttling device (7) and an evaporator (3) which are sequentially connected into a circulation loop, wherein the circulation loop and the pneumatic compressor (4) are further connected in parallel and provided with a fluorine pump (5).
2. A gas-liquid hybrid heat pipe composite refrigeration system according to claim 1, wherein the throttling device (7) comprises: the device comprises an electromagnetic valve (1) and an expansion valve (2), wherein the electromagnetic valve (1) and the expansion valve (2) are arranged in parallel.
3. A gas-liquid hybrid heat pipe composite refrigeration system according to claim 2, characterized in that the throttling device (7) is integrated with the pneumatic compressor (4) and the fluorine pump (5) arranged in parallel to form a refrigeration unit.
4. A gas-liquid hybrid heat pipe composite refrigeration system according to claim 3, wherein the condenser (6) is a water cooling tower, an air cooling tower or an evaporative cooling tower;
the evaporator (3) comprises: room-level precision air conditioning, inter-column air conditioning, back-plate precision air conditioning and/or overhead refrigerant phase change ends;
the evaporator (3) is connected with one end of the refrigerating unit through a pair of refrigerant pipes (8) respectively, and the other end of the refrigerating unit is connected with the condenser (6) through another pair of refrigerant pipes (8) respectively.
5. A gas-liquid hybrid heat pipe composite refrigeration method using the refrigeration system according to any one of claims 2 to 4, characterized by comprising the steps of:
the pneumatic compressor (4), the condenser (6), the throttling device (7) and the evaporator (3) are connected in series to form a circulation loop, and the fluorine pump (5) and the pneumatic compressor (4) are arranged in parallel;
the refrigeration system switches different circulation modes according to the outdoor air dry bulb temperature.
6. The method of claim 5, wherein the step of switching different circulation modes of the refrigeration system according to the outdoor air dry bulb temperature comprises:
when the outdoor air dry bulb temperature tw is less than or equal to 0 ℃, the refrigerating system is switched into a fluorine pump refrigerating cycle mode;
when the temperature of the outdoor air dry bulb is more than 0 ℃ and less than or equal to 4 ℃, the refrigerating system is switched into a fluorine pump refrigerating cycle and gas phase power type heat pipe cycle mode;
when the outdoor air dry bulb temperature is 4 ℃ < tw <30 ℃, the refrigerating system is switched to a gas-phase power type heat pipe circulation mode;
when the temperature tw of the outdoor air dry bulb is more than or equal to 30 ℃, the refrigerating system is switched into a vapor compression refrigerating cycle mode.
7. The method for hybrid heat pipe cooling according to claim 6, wherein when the outdoor air dry bulb temperature tw is less than or equal to 0 ℃, the step of switching the cooling system to a fluorine pump cooling cycle mode is:
the electromagnetic valve (1) in the throttling device (7) is opened, and the expansion valve (2) is closed; the pneumatic compressor (4) is closed, and the fluorine pump (5) is used for providing power for the refrigerant circulation;
the low-temperature low-pressure liquid working medium absorbs heat and evaporates in the evaporator (3) to become a low-temperature low-pressure gaseous working medium, and flows into the condenser (6) to be exothermic and condensed into a low-temperature low-pressure liquid working medium under the driving of the fluorine pump (5), and returns to the evaporator (3) again to absorb heat and evaporate through the electromagnetic valve (1) to circulate reciprocally.
8. The method for hybrid heat pipe cooling according to claim 6, wherein when the outdoor air dry bulb temperature is 0 ℃ < tw < 4 ℃, the step of switching the cooling system to the fluorine pump cooling cycle+gas phase power heat pipe cycle mode is:
the electromagnetic valve (1) in the throttling device (7) is opened, and the expansion valve (2) is opened; the pneumatic compressor (4) and the fluorine pump (5) are all started;
the pneumatic compressor (4) operates at a low pressure ratio, the low-temperature low-pressure liquid working medium absorbs heat and evaporates in the evaporator (3) to become a low-temperature low-pressure gaseous working medium, and the low-temperature low-pressure liquid working medium flows into the condenser (6) to be subjected to heat release and condensation to become a low-temperature low-pressure liquid working medium under the dual driving of the pneumatic compressor (4) and the fluorine pump (5) which are arranged in parallel, and returns to the evaporator (3) again to absorb heat and evaporate through the electromagnetic valve (1) and the expansion valve (2) which are arranged in parallel, and the reciprocating cycle is performed.
9. The method as set forth in claim 6, wherein when the outdoor air dry bulb temperature is 4 ℃ < tw <30 ℃, the step of switching the refrigeration system to the gas phase power type heat pipe circulation mode is:
the electromagnetic valve (1) in the throttling device (7) is closed, and the expansion valve (2) is kept open; the fluorine pump (5) is closed, and the pneumatic compressor (4) is opened;
the low-temperature low-pressure liquid working medium absorbs heat and evaporates in the evaporator (3) to become a low-temperature low-pressure gaseous working medium, the low-temperature low-pressure gaseous working medium is compressed by the pneumatic compressor (4) operated by a low-pressure ratio and then becomes a medium-temperature medium-pressure gaseous working medium, the medium-temperature medium-pressure gaseous working medium flows into the condenser (6) to be subjected to heat release and condensation to become a medium-temperature medium-pressure liquid working medium, and the medium-temperature medium-pressure liquid working medium becomes the low-temperature low-pressure liquid working medium after being throttled by the expansion valve (2) and returns to the evaporator (3) to absorb heat and evaporate again, and the medium-temperature medium-pressure liquid working medium circulates reciprocally.
10. The method for hybrid heat pipe cooling according to claim 6, wherein when the outdoor air dry bulb temperature tw is greater than or equal to 30 ℃, the step of switching the cooling system to a vapor compression cooling cycle mode is as follows:
an expansion valve (2) in the throttling device (7) is opened, and the electromagnetic valve (1) is closed; the pneumatic compressor (4) is started, and the fluorine pump (5) is closed;
the low-temperature low-pressure liquid working medium absorbs heat and evaporates in the evaporator (3) to become a low-temperature low-pressure gaseous working medium, the low-temperature low-pressure gaseous working medium is compressed by the pneumatic compressor (4) operated by high-pressure ratio and becomes a high-temperature high-pressure gaseous working medium, the high-temperature high-pressure gaseous working medium flows into the condenser (6) to be subjected to exothermic condensation to become a high-temperature high-pressure liquid working medium, the high-temperature high-pressure liquid working medium becomes a low-temperature low-pressure liquid working medium after being throttled by the expansion valve (2) and returns to the evaporator (3) again to absorb heat and evaporate, and the reciprocating circulation is performed 。
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