CN117404823A - High-drop-height direct expansion machine - Google Patents
High-drop-height direct expansion machine Download PDFInfo
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- CN117404823A CN117404823A CN202311731920.6A CN202311731920A CN117404823A CN 117404823 A CN117404823 A CN 117404823A CN 202311731920 A CN202311731920 A CN 202311731920A CN 117404823 A CN117404823 A CN 117404823A
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- 230000005501 phase interface Effects 0.000 claims abstract description 93
- 239000007788 liquid Substances 0.000 claims abstract description 90
- 239000007791 liquid phase Substances 0.000 claims abstract description 86
- 239000003507 refrigerant Substances 0.000 claims description 168
- 239000003921 oil Substances 0.000 claims description 32
- 238000010438 heat treatment Methods 0.000 claims description 17
- 239000012071 phase Substances 0.000 claims description 16
- 238000004781 supercooling Methods 0.000 claims description 16
- 238000005057 refrigeration Methods 0.000 claims description 14
- 239000010721 machine oil Substances 0.000 claims description 10
- 238000011144 upstream manufacturing Methods 0.000 claims description 5
- 238000005086 pumping Methods 0.000 claims description 3
- 238000010168 coupling process Methods 0.000 description 7
- 238000005859 coupling reaction Methods 0.000 description 7
- 239000010687 lubricating oil Substances 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000012544 monitoring process Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
-
- 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
- F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing 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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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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)
- General Engineering & Computer Science (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Fluid Mechanics (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Combustion & Propulsion (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses a high-drop direct expansion machine, which comprises an outdoor unit, an indoor unit, a liquid phase connecting pipe and an air connecting pipe. The outdoor unit comprises a compressor, a four-way valve, a condenser, an outdoor unit expansion valve and a gas-liquid separator. The condenser is sequentially connected with the external machine expansion valve and the external machine liquid phase interface. The outlet of the gas-liquid separator is connected with the inlet of the compressor. The indoor unit comprises an indoor unit liquid pipe pressure sensor, an evaporator, an indoor unit expansion valve and a pressure equalizing valve. One end of the evaporator is connected with the gas phase interface of the internal machine, and the other end of the evaporator is sequentially connected with the expansion valve of the internal machine and the liquid phase interface of the internal machine. An inner machine liquid pipe pressure sensor is arranged between the inner machine expansion valve and the inner machine liquid phase interface so as to detect the pressure of an inner machine pipeline. One end of the pressure equalizing valve is connected with the liquid phase interface of the internal machine, and the other end of the pressure equalizing valve is connected with the gas phase interface of the internal machine. The high-drop direct expansion machine provided by the invention can be simultaneously suitable for use scenes with positive drop and negative drop.
Description
Technical Field
The invention relates to a high-drop-height direct expansion machine, and belongs to the technical field of air conditioners.
Background
The direct expansion air conditioning unit (simply referred to as direct expansion machine) is a compressor of the unit itself, and the liquid refrigerant in the refrigerating system is directly evaporated (expanded) in the evaporator coil, so as to absorb heat to the air outside the coil (i.e. the air inside the air conditioning room) to cool. A typical direct expansion machine includes an outdoor unit including a compressor and a condenser, and an indoor unit including an evaporator. The position of the outdoor unit above the indoor unit is called positive drop, the position of the outdoor unit below the indoor unit is called negative drop, and the positive drop or the negative drop under specific working conditions can reach 150m. Calculated by 100m drop, the gauge pressure difference of the refrigerant reaches 1.32MPa, and the liquid column pressure has a pressurizing effect on lower equipment and a depressurizing effect on upper equipment.
In the chinese patent application with application number CN202310260522.4, an active oil return system of an air conditioner with high positive drop and an air conditioner are disclosed. The compressor of the invention is connected with an air outlet pipe and an air suction pipe for connecting an indoor unit of an air conditioner; the oil return device comprises an oil storage tank, an air inlet pipe connected with the oil storage tank, an oil return pipe and an exhaust pipe used for connecting an outdoor unit of the air conditioner; the air inlet pipe is connected with the air outlet pipe, the oil return pipe is connected with the liquid pipe, and the oil return pipe is provided with an oil pump. According to the invention, the liquid lubricating oil from the air outlet pipe is deposited into the oil storage tank due to different weights of the gaseous refrigerant and the liquid lubricating oil, and the liquid lubricating oil in the oil storage tank is pumped into the liquid pipe through the oil pump, so that the refrigerant and the liquid lubricating oil can be recycled back to the compressor through the indoor unit and the air suction pipe together, and oil return of the compressor is completed.
In addition, in chinese patent application with application number CN201811333929.0, a high negative drop industrial air conditioning system is disclosed, including indoor unit and the off-premises station that connect gradually through the pipeline, be connected with negative drop part between indoor unit and the off-premises station, negative drop part is including control liquid refrigerant unidirectional flow's check valve and reservoir, and the check valve sets up at the entry end of reservoir, and indoor unit is connected to the exit end of reservoir, and negative drop part is in same level with indoor unit. The invention uses the compressor in the air conditioner to realize the refrigerant to be pressed into the negative drop part for storage, and then uses the liquid column in the liquid storage device to ensure the supercooling degree of the refrigerant before the throttling device. The input joint is arranged at the top end of the liquid storage device, and a pipeline is arranged in the input joint and extends to the bottom of the liquid storage device from the input joint. The output joint is arranged on the side surface of the lower end of the liquid storage device, so that a liquid column is formed conveniently, and the supercooling degree is ensured.
Similarly, in the prior art, different schemes of the outdoor unit and the indoor unit are designed in a targeted manner so as to be respectively suitable for use scenes with positive fall or negative fall, and cannot be simultaneously suitable for use scenes with positive fall and negative fall.
Disclosure of Invention
The invention aims to solve the technical problem of providing a high-drop direct expansion machine which can be simultaneously suitable for use scenes with positive drop and negative drop.
In order to achieve the technical purpose, the invention adopts the following technical scheme:
a high-drop direct expansion machine comprises an outdoor unit, an indoor unit, a liquid phase connecting pipe and an air connecting pipe; wherein,
the outdoor unit comprises an outdoor unit liquid phase interface, an outdoor unit gas phase interface, a compressor, a four-way valve, a condenser, an outdoor unit expansion valve and a gas-liquid separator; the inlet of the compressor is connected with the outlet of the gas-liquid separator, and the outlet of the compressor is connected with one end of the four-way valve; one end of the four-way valve is connected with the outlet of the compressor, the other end of the four-way valve is connected with the gas phase interface of the external machine, the other end of the four-way valve is connected with the inlet of the gas-liquid separator, and the other end of the four-way valve is connected with one end of the condenser; the other end of the condenser is sequentially connected with the external machine expansion valve and the external machine liquid phase interface; the inlet of the gas-liquid separator is connected with the four-way valve, and the outlet of the gas-liquid separator is connected with the inlet of the compressor;
the indoor unit comprises an inner unit liquid phase interface, an inner unit gas phase interface, an inner unit liquid pipe pressure sensor, an evaporator, an inner unit expansion valve and a pressure equalizing valve; one end of the evaporator is connected with the gas phase interface of the internal machine, and the other end of the evaporator is sequentially connected with the expansion valve of the internal machine and the liquid phase interface of the internal machine; the pressure sensor of the liquid pipe of the inner machine is arranged between the expansion valve of the inner machine and the liquid phase interface of the inner machine so as to detect the pressure of the pipeline of the inner machine; one end of the pressure equalizing valve is connected with the liquid phase interface of the internal machine, and the other end of the pressure equalizing valve is connected with the gas phase interface of the internal machine;
the liquid phase connecting pipe comprises a refrigerant pump and an electromagnetic valve; the conveying direction of the refrigerant pump is from low height to high height; the refrigerant pump is connected in parallel with the electromagnetic valve.
Wherein preferably, the outdoor unit further comprises an outdoor unit economizer; the external machine economizer is arranged between the external machine expansion valve and the external machine liquid phase interface; and the inlet of the external machine economizer is connected with a pipeline between the external machine expansion valve and the external machine liquid phase interface, and the outlet of the external machine economizer is connected with the inlet of the gas-liquid separator.
Wherein preferably, the indoor unit further comprises an indoor unit economizer; the internal machine economizer is arranged between the internal machine expansion valve and the internal machine liquid phase interface; and the inlet of the internal machine economizer is connected with a pipeline between the internal machine expansion valve and the internal machine liquid phase interface, and the outlet of the internal machine economizer is connected with the internal machine gas phase interface.
Preferably, the outdoor unit is arranged above the indoor unit; the gas phase connecting pipe also comprises an oil return bend; the return bend is a bend with high and low drop height.
Wherein, preferably, the high-drop direct expansion machine is in a refrigeration working condition;
the inner engine liquid pipe pressure sensor is used for providing data for the outer engine expansion valve so as to control the opening degree of the outer engine expansion valve and further control the pressure of the refrigerant at the liquid phase interface of the inner engine to be not more than 4.3Mpa;
the pressure equalizing valve is used for being temporarily opened so as to release the high-pressure side refrigerant at the upstream of the internal machine expansion valve into the low-pressure side pipeline at the downstream of the evaporator, the flow speed of the refrigerant in the gas phase connecting pipe is improved, and the refrigerating machine oil in the oil return bend is conveyed upwards.
Wherein, preferably, the high-drop direct expansion machine is in a heating working condition;
the refrigerant pump is used for conveying the refrigerant upwards and reducing the pressure loss of the refrigerant;
the external economizer is used for reducing the temperature of the refrigerant to improve the supercooling degree of the refrigerant.
Preferably, the outdoor unit is disposed below the indoor unit.
Wherein, preferably, the high-drop direct expansion machine is in a refrigeration working condition;
the refrigerant is used for pumping the refrigerant upwards and reducing the pressure loss of the refrigerant;
the internal machine liquid pipe pressure sensor is used for providing data for the compressor so as to control the rotating speed of the compressor and further control the pressure of the refrigerant in front of the internal machine expansion valve to reach 2.5-3 MPa;
the internal economizer is used for reducing the temperature of the refrigerant to improve the supercooling degree of the refrigerant.
Wherein, preferably, the high-drop direct expansion machine is in a heating working condition;
the inner machine liquid pipe pressure sensor is used for providing data for the inner machine expansion valve so as to control the opening degree of the inner machine expansion valve and further control the pressure of the refrigerant at the liquid phase interface of the outer machine to be not more than 4.2MPa.
Compared with the prior art, the high-drop direct expansion machine provided by the embodiment of the invention utilizes the structural schemes of the same outdoor unit and the same indoor unit, is matched with different on-line pipes of the indoor unit and the outdoor unit, is simultaneously suitable for use scenes with positive drop and negative drop, does not need to customize different outdoor units and indoor units for different use scenes, and reduces purchasing, distribution and inventory costs.
Drawings
FIG. 1 is a schematic diagram of a high-head direct expansion machine according to a first embodiment of the present invention;
FIG. 2 is a schematic view of the circulation flow of the high head direct expansion machine of FIG. 1 in a refrigeration mode;
FIG. 3 is a schematic view of a circulation flow of the high head direct expansion machine of FIG. 1 in a heating condition;
FIG. 4 is a schematic diagram of a high-head direct expansion machine according to a second embodiment of the present invention;
FIG. 5 is a schematic view of the circulation flow of the high head direct expansion machine of FIG. 4 in a refrigeration mode;
FIG. 6 is a schematic diagram of the circulation flow of the high head direct expansion machine of FIG. 4 in heating conditions.
Detailed Description
The technical contents of the present invention will be described in detail with reference to the accompanying drawings and specific examples.
The technical conception of the embodiment of the invention is that the same structural schemes of the outdoor unit and the indoor unit are utilized to be matched with different on-line pipes of the indoor unit and the outdoor unit so as to be simultaneously applicable to the use scenes of positive drop and negative drop. Specifically, although the structures between the outdoor unit and the indoor unit are different, the same indoor unit is suitable for a use scene with a positive drop and a use scene with a negative drop, and the same outdoor unit is also suitable for a use scene with a positive drop and a use scene with a negative drop. The difference between the use situations of the positive drop and the negative drop is limited to the difference between the inner machine connecting pipe and the outer machine connecting pipe, and the inner machine connecting pipe and the outer machine connecting pipe provided by the embodiment of the invention comprise a liquid connecting pipe and an air connecting pipe. The embodiment of the invention is suitable for use scenes with positive fall and negative fall of 0-130 m, wherein the fall is obviously superior to the prior art in the embodiment with the fall of 80-130 m.
Example 1
As shown in fig. 1, an embodiment of the present invention includes an outdoor unit 1, an indoor unit 2, a liquid-connected pipe 3, and an air-connected pipe 4. The outdoor unit is arranged at a position above the indoor unit, so that the outdoor unit is a use scene with a positive fall. The embodiment of the invention is illustrated by taking a positive drop height of 100m as an example.
1. High-drop-height direct expansion machine structure in embodiment of the invention
The outdoor unit 1 includes an outdoor unit liquid phase port 101, an outdoor unit gas phase port 102, a compressor 11, a four-way valve 12, a condenser 13, an outdoor unit expansion valve 14, a gas-liquid separator 15, and an outdoor unit economizer 16.
The inlet of the compressor 11 is connected with the outlet of the gas-liquid separator 15, and the outlet is connected with one end of the four-way valve 12. One end of the four-way valve 12 is connected with the outlet of the compressor 11, the other end is connected with the gas phase interface 102 of the external machine, the other end is connected with the inlet of the gas-liquid separator 15, and the other end is connected with one end of the condenser 13. The other end of the condenser 13 is connected with an external expansion valve 14 and an external liquid phase interface 101 in sequence. An external machine economizer 16 is connected between the external machine expansion valve 14 and the external machine liquid phase interface 101, an inlet of the external machine economizer 16 is connected with a pipeline between the external machine expansion valve 14 and the external machine liquid phase interface 101, and an outlet is connected with an inlet of the gas-liquid separator 15. The inlet of the gas-liquid separator 15 is connected with the outlet of the external economizer 16 and the four-way valve 12, and the outlet is connected with the inlet of the compressor 11. Preferably, the external expansion valve 14 is an electronic expansion valve.
The indoor unit 2 comprises an indoor unit liquid phase interface 201, an indoor unit gas phase interface 202, an indoor unit liquid pipe pressure sensor 203, an evaporator 21, an indoor unit expansion valve 22 and a pressure equalizing valve 23.
One end of the evaporator 21 is connected with an internal machine gas phase interface 202, and the other end is sequentially connected with an internal machine expansion valve 22 and an internal machine liquid phase interface 201. An indoor unit liquid pipe pressure sensor 203 is provided between the indoor unit expansion valve 22 and the indoor unit liquid interface 201 to detect the pressure of an indoor unit pipe (liquid pipe). One end of the pressure equalizing valve 23 is connected with the internal machine liquid phase interface 201, and the other end is connected with the internal machine gas phase interface 202. Preferably, the internal expansion valve 22 is an electronic expansion valve.
The liquid-coupling pipe 3 includes a refrigerant pump 31 and a solenoid valve 32. The liquid-phase connection pipe 3 is connected in series with a plurality of refrigerant pumps 31, and the conveying direction of each refrigerant pump 31 is from a low height to a high height. Each refrigerant pump 31 is connected in parallel with a solenoid valve 32.
The air-coupling tube 4 comprises an oil return bend 41. The gas-phase pipe 4 is connected in series with a plurality of return bends 41. The oil return bend 41 is a bend with a height difference, which is not described in detail in the present invention.
The upper end of the liquid phase connecting pipe 3 is connected with the outer machine liquid phase interface 101, and the lower end is connected with the inner machine liquid phase interface 201.
The upper end of the gas connection pipe 4 is connected with the outer machine gas phase interface 102, and the lower end is connected with the inner machine gas phase interface 202.
2. Application of embodiment of the invention in refrigeration working condition
2.1 The operating principle of the embodiment of the invention under the refrigeration working condition
As shown in fig. 2, the high-temperature and high-pressure gaseous refrigerant output from the compressor 11 enters the condenser 13 through the four-way valve 12, and the condenser 13 cools and condenses the refrigerant. The refrigerant is depressurized while passing through the outdoor unit expansion valve 14 and is again cooled while passing through the outdoor unit economizer 16.
The principle of the external economizer 16 is that the branch refrigerant is led out from the main refrigerant, so that the branch refrigerant throttles, evaporates and absorbs heat, and the main refrigerant is cooled by evaporation and heat absorption, and the cooling amplitude can reach 20 ℃. The evaporated bypass refrigerant enters the gas-liquid separator 15. The construction and operation of the external unit economizer 16 is well known in the industry and will not be described in detail herein.
The refrigerant enters the liquid-connected pipe 3 through the liquid-phase interface 101 of the external machine. The liquid-coupling pipe 3 turns off the refrigerant pump 31 and turns on the electromagnetic valve 32 during the cooling operation. The liquid refrigerant in the liquid-phase connecting pipe 3 enters the indoor unit 2 through the electromagnetic valve 32 and the liquid-phase interface 201 of the indoor unit, enters the evaporator 21 to evaporate and absorb heat after being throttled and expanded by the expansion valve 22 of the indoor unit, and refrigerates the indoor environment.
The refrigerant with phase change into gas state enters the gas-connected pipe 4 from the gas-phase interface 202 of the internal machine and flows through the oil return bend 41. At this time, the gaseous refrigerant and the liquid refrigerator oil are separated, and the refrigerator oil is likely to remain in the return oil bend 41. The pressure equalizing valve 23 is opened to discharge the high-pressure side refrigerant upstream of the inner machine expansion valve 22 into the low-pressure side line downstream of the evaporator 21, thereby increasing the flow rate of the refrigerant in the gas-phase linkage pipe 4 and the return bend 41 to bring the refrigerating machine oil back into the outdoor machine 1.
The source of the refrigerator oil is the compressor 11, which is well known in the industry and will not be described in detail in this patent.
The gaseous refrigerant enters the outdoor unit 1 from the gas-phase interface 102 of the outdoor unit and enters the gas-liquid separator 15 through the four-way valve 12. The gaseous refrigerant in the gas-liquid separator 15 enters the compressor 11 to be pressurized, and participates in the cycle again.
2.2 Difficulty in application of the prior art in refrigeration working condition
Taking a positive drop of 100m as an example, the pressure of the refrigerant entering the indoor unit 2 is the sum of the pressure at the outdoor unit liquid phase interface 101 and the pressure of the 100m refrigerant liquid column (1.32 MPa). Because the pressure of the indoor unit 2 of the direct expansion machine adopting the R410A refrigerant cannot exceed 4.3MPa, but the highest pressure at the liquid phase interface 101 of the outdoor unit can reach 4.1MPa, and at the moment, the liquid column pressure of the overlapped refrigerant can reach 5.42MPa which is far higher than the highest pressure of the indoor unit 2 by 4.3MPa. Therefore, a pressure reducing device needs to be arranged at the outer machine liquid phase interface 101 to ensure that the pressure at the inner machine liquid phase interface 201 is not higher than 4.3MPa.
The refrigerator oil is generally returned to the outdoor unit 1 by the refrigerant having a high flow rate. Because the indoor unit is arranged below and the outdoor unit is arranged above, the refrigerator oil is influenced by gravity and accumulated in the indoor unit 1 and the air connecting pipe, and cannot return to the outdoor unit arranged above. When the refrigerating machine oil is accumulated to a certain amount, the compressor runs short of oil, so that the compressor lacks lubrication and is worn.
2.3 The embodiment of the invention aims at solving the difficulty of refrigeration working conditions
By monitoring the pressure value of the internal machine liquid pipe pressure sensor 203, the opening degree of the external machine expansion valve 14 is controlled to reduce the pressure of the refrigerant, and then the pressure of the refrigerant at the external machine liquid phase interface 101 is reduced. After the refrigerant liquid column pressure is overlapped to be 1.32MPa, the pressure value of the liquid pipe pressure sensor 203 of the indoor unit is controlled to be 2.75-3.4 MPa so as to limit the pressure of the indoor unit 2 to be not more than 4.3MPa.
Opening control logic of the external expansion valve 14: (1) when the pressure value of the internal machine liquid pipe pressure sensor 203 is more than 3.8MPa, the opening of the external machine expansion valve 14 is 80PLS, and the internal machine liquid pipe pressure sensor is kept for thirty seconds; (2) when the pressure value of the internal machine liquid pipe pressure sensor 203 is less than or equal to 3.8MPa and is less than 3.4MPa, the opening of the external machine expansion valve 14 is closed at the speed of three seconds and one step; (3) when the pressure value of the internal unit liquid pipe pressure sensor 203 is less than 2.75MPa, the opening of the external unit expansion valve 14 is opened at a rate of three seconds and one step. The minimum opening of the external expansion valve 14 is 60PLS.
The air-coupling pipe 4 is provided with an oil return bend 41 every ten meters in the height direction to store refrigerating machine oil. When the refrigerating machine oil accumulates to a certain amount, the pressure equalizing valve 23 is opened, the high-pressure side refrigerant upstream of the internal expansion valve 22 is released into the low-pressure side pipeline downstream of the evaporator 21, and the refrigerant flow rate in the air-connected pipe 4 is increased by reducing the pipeline cross-sectional area, so that the refrigerating machine oil is delivered upward.
In the embodiment of the invention, the equalizing valve 23 of the indoor unit is opened once every thirty minutes, and the opening time lasts for one minute. The purpose is to release a large amount of liquid refrigerant from the high pressure side of the indoor unit 2 to the low pressure side directly, and drive the refrigerator oil in the gas phase connecting pipe 4 to enter the gas-liquid separator 15 of the outdoor unit 1 entirely. The refrigerating machine oil in the gas-liquid separator 15 can be effectively returned to the compressor 11.
3. Application of embodiment of the invention in heating working conditions
3.1 The embodiment of the invention is based on the operation principle under the heating working condition.
As shown in fig. 3, the high-temperature and high-pressure gaseous refrigerant output by the compressor 11 enters the air-connection pipe 4 through the outer machine gas phase interface 102, enters the indoor machine 2 through the inner machine gas phase interface 202, is cooled and condensed through the evaporator 21, and heats the indoor environment. By controlling the opening degree of the internal expansion valve 22, the amount of refrigerant passing through the internal expansion valve 22 is reduced, so that the refrigerant remains in the evaporator 21, and the refrigerant continues to dissipate heat in the evaporator 21, thereby increasing the supercooling degree of the liquid refrigerant formed by condensation.
The cooled refrigerant passes through the internal expansion valve 22 and enters the liquid-connected pipe 3 through the internal liquid phase interface 201. The liquid-connected pipe 3 turns on the refrigerant pump 31 and turns off the electromagnetic valve 32 during heating conditions. The liquid refrigerant in the liquid-phase connection pipe 3 is delivered upward by the refrigerant pump 31.
The refrigerant enters the outdoor unit 1 from the outdoor unit liquid phase interface 101, is cooled by the outdoor unit economizer 16, throttled and expanded by the outdoor unit expansion valve 14, and enters the condenser 13 to absorb heat and raise temperature. The heating principle of the direct expansion machine is well known in the industry, and the invention is not repeated.
The refrigerant after temperature rise enters the gas-liquid separator 15 through the four-way valve 12. The gaseous refrigerant in the gas-liquid separator 15 enters the compressor 11 to be pressurized, and participates in the cycle again.
3.2 The prior art has the application difficulty when in heating working condition
Taking a positive drop of 100m as an example, the pressure of the refrigerant entering the outdoor unit 1 is the difference between the pressure at the liquid phase interface 201 of the indoor unit and the pressure of the 100m refrigerant liquid column (1.32 MPa). The outdoor unit 1 of the direct expansion machine using the R410A refrigerant has a design pressure of typically 2.75MPa before the outdoor expansion valve 14, and a suction pressure of the compressor 11 of typically 0.3 to 0.65MPa. When the indoor unit 2 is a fresh air machine, the pressure at the liquid phase interface 201 of the indoor unit can be reduced to 2.0MPa, and only 0.68MPa is generated after the pressure of the liquid column of the refrigerant is counteracted by 1.32 MPa. Then, the pressure before the external expansion valve 14 is 0.68MPa, the pressure after the external expansion valve 14 is 0.3 to 0.65MPa, and the front-rear pressure difference is too small, and at this time, the external expansion valve 14 cannot ensure that sufficient refrigerant enters the condenser 13 to exchange heat even if it is fully opened.
The saturation temperature of the R410a refrigerant at a gauge pressure of 0.68MPa is-1 c, and if the refrigerant temperature is higher than-1 c, gaseous refrigerant is present before the inlet of the external expansion valve 14. The gaseous refrigerant occupies a large number of passages of the external expansion valve 14, further reducing the ability of the refrigerant to pass through the external expansion valve 14.
3.3 The embodiment of the invention aims at solving the difficulty of heating working conditions
The liquid-connected pipe 3 is provided with a large-lift refrigerant pump 31 for pumping up the refrigerant every ten meters in the height direction and reducing the pressure loss of the refrigerant to ensure that the refrigerant pressure after passing through the external expansion valve 14 (before entering the condenser 13) reaches 1.2MPa or more.
It is noted that the refrigerant pump 31 cannot handle the gaseous refrigerant, so a plurality of large-lift refrigerant pumps 31 are provided according to the lifting height to reduce the pressure loss of the refrigerant and avoid the vaporization of the refrigerant due to the saturation temperature being reduced to the ambient temperature. Meanwhile, the opening degree of the indoor unit expansion valve 22 of the indoor unit 2 is controlled to control the degree of supercooling of the refrigerant at the indoor unit liquid phase interface 201. For example, the temperature of the refrigerant at the liquid phase interface 201 of the indoor unit is 3-8 ℃ higher than the temperature of the air intake of the indoor unit 2, so as to ensure the supercooling degree of the refrigerant at the liquid phase interface 201 of the indoor unit.
After the refrigerant enters the external machine liquid phase interface 101, the external machine economizer 16 cools the refrigerant to improve the supercooling degree before the external machine expansion valve 14.
The external expansion valve 14 adopts a plurality of expansion valves connected in parallel, so that the control precision of single opening in small opening is ensured, and the passing flow in double opening is ensured.
Example two
As shown in fig. 4, the embodiment of the present invention includes an outdoor unit 1, an indoor unit 2, a liquid-connected pipe 3, and an air-connected pipe 4. The outdoor unit is arranged at a position below the indoor unit, namely, a negative drop use scene. The embodiment of the invention is illustrated by taking a negative drop height of 100m as an example.
1. High-drop-height direct expansion machine structure in embodiment of the invention
The outdoor unit 1 and the liquid phase connecting pipe 3 provided in the embodiment of the present invention are identical to those in the embodiment, and are not described in detail. The embodiment of the present invention provides an air-coupled tube 4 that, unlike the first embodiment, does not include an oil return bend 41.
The indoor unit 2 according to the embodiment of the present invention further includes an indoor unit economizer 23, unlike the first embodiment. An internal machine economizer 23 is connected in parallel between the internal machine expansion valve 22 and the internal machine liquid phase interface 201, an inlet of the internal machine economizer 23 is connected with a pipeline between the internal machine expansion valve 22 and the internal machine liquid phase interface 201, and an outlet is connected with an internal machine gas phase interface 202.
The lower end of the liquid phase connecting pipe 3 is connected with the outer machine liquid phase interface 101, and the upper end is connected with the inner machine liquid phase interface 201.
The lower end of the gas connection pipe 4 is connected with the outer machine gas phase interface 102, and the upper end is connected with the inner machine gas phase interface 202.
2. Application of embodiment of the invention in refrigeration working condition
2.1 The operating principle of the embodiment of the invention under the refrigeration working condition
As shown in fig. 5, the high-temperature and high-pressure gaseous refrigerant output from the compressor 11 enters the condenser 13 through the four-way valve 12, and the condenser 13 cools and condenses the refrigerant. The refrigerant is depressurized while passing through the outdoor unit expansion valve 14 and is again cooled while passing through the outdoor unit economizer 16.
The refrigerant enters the liquid-connected pipe 3 through the liquid-phase interface 101 of the external machine. The liquid-coupling pipe 3 turns on the refrigerant pump 31 and turns off the electromagnetic valve 32 during the cooling operation. The liquid refrigerant in the liquid-phase connection pipe 3 is delivered upward by the refrigerant pump 31.
The refrigerant enters the indoor unit 2 from the liquid phase interface 201 of the indoor unit, is cooled by the economizer 23 of the indoor unit, is throttled and expanded by the expansion valve 22 of the indoor unit, and then enters the evaporator 21 to evaporate and absorb heat, thus refrigerating the indoor environment.
The refrigerant with phase change into gas state enters the gas-connected pipe 4 from the gas-phase interface 202 of the inner machine, enters the outdoor unit 1 from the gas-phase interface 102 of the outer machine, and enters the gas-liquid separator 15 through the four-way valve 12. The gaseous refrigerant in the gas-liquid separator 15 enters the compressor 11 to be pressurized, and participates in the cycle again.
2.2 Difficulty in application of the prior art in refrigeration working condition
Taking a negative drop of 100m as an example, the pressure of the refrigerant entering the indoor unit 2 is the difference between the pressure at the outdoor unit liquid phase interface 101 and the pressure of the 100m refrigerant liquid column (1.32 MPa). In the outdoor unit 1 of the direct expansion machine adopting the R410A refrigerant, the design pressure at the liquid phase interface 101 of the outdoor unit is generally 2.7MPa of gauge pressure, and after the offset of the liquid column pressure is 1.32MPa, the refrigerant pressure at the liquid phase interface 201 of the indoor unit is 1.38MPa. The pressure behind the internal expansion valve 22 is typically 0.7MPa, and the pressure in front of the internal expansion valve 22 is 1.38MPa, which is the same as the pressure at the internal liquid interface 201, so that the pressure difference between the front and back of the internal expansion valve 22 is too small, which affects the ability of the refrigerant to pass through the internal expansion valve 22.
The saturation temperature of the R410a refrigerant at a gauge pressure of 1.38MPa is 21 ℃, and if the refrigerant temperature is close to 21 ℃, there is no supercooling of the refrigerant, and a gaseous refrigerant exists before the inlet of the internal expansion valve 22. The gaseous refrigerant occupies a large number of passages of the internal expansion valve 22, further reducing the ability of the refrigerant to pass through the internal expansion valve 22.
2.3 The embodiment of the invention aims at solving the difficulty of refrigeration working conditions
The liquid-coupling pipe 3 is provided with a large-lift refrigerant pump 31 every ten meters in the height direction, lifting up the refrigerant and reducing the pressure loss of the refrigerant. Meanwhile, the pressure value of the internal machine liquid pipe pressure sensor 203 is monitored, the rotation speed of the compressor 11 is controlled, the pressure in front of the internal machine expansion valve 22 is guaranteed to reach 2.5-3 MPa, and 2.75MPa is preferable, so that the supercooling degree of the refrigerant in front of the internal machine expansion valve 22 is guaranteed. It is noted that the outlet pressure of the compressor 11 is generally 2.75 to 3.4MPa, and must not be greater than 3.4MPa.
After the refrigerant enters the inner machine liquid phase interface 201, the inner machine economizer 23 cools the refrigerant to improve the supercooling degree of the refrigerant before the inner machine expansion valve 22.
3. Application of embodiment of the invention in heating working conditions
3.1 The embodiment of the invention is based on the operation principle under the heating working condition.
As shown in fig. 6, the high-temperature and high-pressure gaseous refrigerant output by the compressor 11 enters the air-connection pipe 4 through the outer machine gas phase interface 102, enters the indoor machine 2 through the inner machine gas phase interface 202, is cooled and condensed through the evaporator 21, and heats the indoor environment. By controlling the opening degree of the internal expansion valve 22, the amount of refrigerant passing through the internal expansion valve 22 is reduced, so that the refrigerant remains in the evaporator 21, and the refrigerant continues to dissipate heat in the evaporator 21, thereby increasing the supercooling degree of the liquid refrigerant formed by condensation. Meanwhile, by controlling the opening degree of the internal machine expansion valve 22, the pressure at the external machine liquid phase interface 101 can also be controlled.
The cooled refrigerant passes through the internal expansion valve 22 and enters the liquid-connected pipe 3 through the internal liquid phase interface 201. The liquid-connected pipe 3 turns off the refrigerant pump 31 and turns on the electromagnetic valve 32 during heating operation. The refrigerant in the liquid-phase connection pipe 3 is sent downward through the solenoid valve 32.
The refrigerant enters the outdoor unit 1 from the outdoor unit liquid phase interface 101, is cooled by the outdoor unit economizer 16, throttled and expanded by the outdoor unit expansion valve 14, and enters the condenser 13 to absorb heat and raise temperature.
The refrigerant after temperature rise enters the gas-liquid separator 15 through the four-way valve 12. The gaseous refrigerant in the gas-liquid separator 15 enters the compressor 11 to be pressurized, and participates in the cycle again.
3.2 The prior art has the application difficulty when in heating working condition
Taking a negative drop of 100m as an example, the pressure of the refrigerant entering the outdoor unit 1 is the sum of the pressure at the liquid phase interface 201 of the indoor unit and the pressure of the 100m refrigerant liquid column (1.32 MPa). Because the pressure of the outdoor unit 1 of the direct expansion machine adopting the R410A refrigerant must not exceed 4.2MPa, but the design pressure at the liquid phase interface 201 of the indoor unit is generally 2.7MPa, at this time, the pressure of the superimposed refrigerant liquid column is 1.32MPa and reaches 4.02MPa, which is close to the protection pressure of the outdoor unit 1, 4.2MPa. Therefore, a pressure reducing device needs to be arranged at the liquid phase interface 201 of the inner machine to ensure that the pressure at the liquid phase interface 101 of the outer machine is not higher than 4.2MPa.
3.3 The embodiment of the invention aims at solving the difficulty of heating working conditions
By monitoring the pressure value of the internal machine liquid pipe pressure sensor 203, the opening degree of the internal machine expansion valve 22 is controlled to reduce the pressure of the refrigerant, and then the pressure of the refrigerant at the internal machine liquid phase interface 201 is reduced. For example, the pressure value of the inner-unit liquid-pipe pressure sensor 203 is controlled to be not more than 1.8MPa, and after the pressure of the superimposed refrigerant liquid column is 1.32MPa, the pressure at the outer-unit liquid-phase interface 101 is not more than 3.12MPa and is lower than the protection pressure of the outdoor unit 1 by 4.2MPa, so as to protect the continuous and stable operation of the outdoor unit 1.
In summary, according to the high-drop direct expansion machine provided by the embodiment of the invention, the economizer, the expansion valve, the pressure sensor and the pressure equalizing valve 23 are arranged in the outdoor unit 1 and the indoor unit 2, the refrigerant pump 31 and the electromagnetic valve 32 are arranged in the liquid phase connecting pipe 3, and the oil return bend 41 is arranged in the gas phase connecting pipe 4, so that the outdoor unit 1 and the indoor unit 2 are simultaneously suitable for use scenes with positive and negative drops, different outdoor units 1 and indoor units 2 do not need to be customized for different use scenes, and purchasing, distributing and inventory costs are reduced.
Wherein the outer economizer 16 and the inner economizer 23 serve to cool down the refrigerant to increase the supercooling degree of the refrigerant.
The indoor unit 1 and the outdoor unit 2 are controlled by controlling the opening of the outdoor unit expansion valve 14 or the indoor unit expansion valve 22 by the indoor unit liquid pipe pressure sensor 203 under different working conditions.
The refrigerant pump 31 serves to convey the liquid refrigerant from a low level to a high level and maintain the pressure and supercooling degree of the refrigerant. When the refrigerant passes through the liquid-phase connection pipe 3 from the high level to the low level, the refrigerant pump 31 is bypassed via the solenoid valve 32. Therefore, the refrigerant can smoothly pass through the liquid-coupling tube 3 in both directions.
The return oil 41 stores the refrigerating machine oil separated from the refrigerant, the pressure equalizing valve 23 is opened to introduce the high-pressure refrigerant into the gas phase connecting pipe 4, and the refrigerating machine oil stored in the return oil 41 is sent back to the outdoor unit 1.
It should be noted that the above embodiments are only examples, and the technical solutions of the embodiments may be combined, which are all within the protection scope of the present invention.
The terms "front," "rear," and the like indicate orientations or positional relationships described based on the conduit flow direction shown in the drawings, and are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention. Where "forward" is the upstream direction of flow and "aft" is the downstream direction of flow.
The orientation or positional relationship indicated by the terms "upper", "lower", "top", "bottom", etc. are based on the orientation or positional relationship shown in the drawings, are merely for convenience in describing the present invention and simplifying the description, and are not indicative or implying that the apparatus or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as limiting the present invention.
Furthermore, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.
The high-drop-height direct expansion machine provided by the invention is described in detail above. Any obvious modifications to the present invention, without departing from the spirit thereof, would constitute an infringement of the patent rights of the invention and would take on corresponding legal liabilities.
Claims (9)
1. The high-drop direct expansion machine is characterized by comprising an outdoor unit, an indoor unit, a liquid phase connecting pipe and an air connecting pipe; wherein,
the outdoor unit comprises an outdoor unit liquid phase interface, an outdoor unit gas phase interface, a compressor, a four-way valve, a condenser, an outdoor unit expansion valve and a gas-liquid separator; the inlet of the compressor is connected with the outlet of the gas-liquid separator, and the outlet of the compressor is connected with one end of the four-way valve; one end of the four-way valve is connected with the outlet of the compressor, the other end of the four-way valve is connected with the gas phase interface of the external machine, the other end of the four-way valve is connected with the inlet of the gas-liquid separator, and the other end of the four-way valve is connected with one end of the condenser; the other end of the condenser is sequentially connected with the external machine expansion valve and the external machine liquid phase interface; the inlet of the gas-liquid separator is connected with the four-way valve, and the outlet of the gas-liquid separator is connected with the inlet of the compressor;
the indoor unit comprises an inner unit liquid phase interface, an inner unit gas phase interface, an inner unit liquid pipe pressure sensor, an evaporator, an inner unit expansion valve and a pressure equalizing valve; one end of the evaporator is connected with the gas phase interface of the internal machine, and the other end of the evaporator is sequentially connected with the expansion valve of the internal machine and the liquid phase interface of the internal machine; the pressure sensor of the liquid pipe of the inner machine is arranged between the expansion valve of the inner machine and the liquid phase interface of the inner machine so as to detect the pressure of the pipeline of the inner machine; one end of the pressure equalizing valve is connected with the liquid phase interface of the internal machine, and the other end of the pressure equalizing valve is connected with the gas phase interface of the internal machine;
the liquid phase connecting pipe comprises a refrigerant pump and an electromagnetic valve; the conveying direction of the refrigerant pump is from low height to high height; the refrigerant pump is connected in parallel with the electromagnetic valve.
2. The high head direct expansion machine according to claim 1, wherein said outdoor unit further comprises an outdoor unit economizer;
the external machine economizer is arranged between the external machine expansion valve and the external machine liquid phase interface; and the inlet of the external machine economizer is connected with a pipeline between the external machine expansion valve and the external machine liquid phase interface, and the outlet of the external machine economizer is connected with the inlet of the gas-liquid separator.
3. The high head direct expansion machine of claim 2, wherein said indoor unit further comprises an indoor unit economizer;
the internal machine economizer is arranged between the internal machine expansion valve and the internal machine liquid phase interface; and the inlet of the internal machine economizer is connected with a pipeline between the internal machine expansion valve and the internal machine liquid phase interface, and the outlet of the internal machine economizer is connected with the internal machine gas phase interface.
4. The high head direct expansion machine of claim 2, wherein:
the outdoor unit is arranged above the indoor unit;
the gas phase connecting pipe also comprises an oil return bend; the return bend is a bend with high and low drop height.
5. The high head direct expansion machine of claim 4, wherein said high head direct expansion machine is in a refrigeration condition;
the inner engine liquid pipe pressure sensor is used for providing data for the outer engine expansion valve so as to control the opening degree of the outer engine expansion valve and further control the pressure of the refrigerant at the liquid phase interface of the inner engine to be not more than 4.3Mpa;
the pressure equalizing valve is used for being temporarily opened so as to release the high-pressure side refrigerant at the upstream of the internal machine expansion valve into the low-pressure side pipeline at the downstream of the evaporator, the flow speed of the refrigerant in the gas phase connecting pipe is improved, and the refrigerating machine oil in the oil return bend is conveyed upwards.
6. The high-head direct expansion machine according to claim 4, wherein the high-head direct expansion machine is in a heating condition;
the refrigerant pump is used for conveying the refrigerant upwards and reducing the pressure loss of the refrigerant;
the external economizer is used for reducing the temperature of the refrigerant to improve the supercooling degree of the refrigerant.
7. A high head direct expansion machine as claimed in claim 3, wherein:
the outdoor unit is arranged below the indoor unit.
8. The high head direct expansion machine of claim 7, wherein said high head direct expansion machine is in a refrigeration condition;
the refrigerant is used for pumping the refrigerant upwards and reducing the pressure loss of the refrigerant;
the internal machine liquid pipe pressure sensor is used for providing data for the compressor so as to control the rotating speed of the compressor and further control the pressure of the refrigerant in front of the internal machine expansion valve to reach 2.5-3 MPa;
the internal economizer is used for reducing the temperature of the refrigerant to improve the supercooling degree of the refrigerant.
9. The high-head direct expansion machine according to claim 7, wherein the high-head direct expansion machine is in a heating condition;
the inner machine liquid pipe pressure sensor is used for providing data for the inner machine expansion valve so as to control the opening degree of the inner machine expansion valve and further control the pressure of the refrigerant at the liquid phase interface of the outer machine to be not more than 4.2MPa.
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