CN108131860B - Ultralow temperature air source heat pump based on single-machine double-stage compressor - Google Patents
Ultralow temperature air source heat pump based on single-machine double-stage compressor Download PDFInfo
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- CN108131860B CN108131860B CN201810104896.6A CN201810104896A CN108131860B CN 108131860 B CN108131860 B CN 108131860B CN 201810104896 A CN201810104896 A CN 201810104896A CN 108131860 B CN108131860 B CN 108131860B
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- 239000007788 liquid Substances 0.000 claims abstract description 84
- 238000010438 heat treatment Methods 0.000 claims abstract description 15
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 11
- 238000004378 air conditioning Methods 0.000 claims description 7
- 238000005057 refrigeration Methods 0.000 claims description 5
- 239000003507 refrigerant Substances 0.000 abstract description 62
- 230000006835 compression Effects 0.000 abstract description 11
- 238000007906 compression Methods 0.000 abstract description 11
- 230000000694 effects Effects 0.000 abstract description 4
- 229920006395 saturated elastomer Polymers 0.000 abstract description 4
- 239000003921 oil Substances 0.000 description 68
- 239000010687 lubricating oil Substances 0.000 description 20
- 239000000203 mixture Substances 0.000 description 7
- 238000010586 diagram Methods 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000001816 cooling Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 239000010725 compressor oil Substances 0.000 description 2
- 239000010726 refrigerant oil Substances 0.000 description 2
- 239000013526 supercooled liquid Substances 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000009897 systematic effect 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
- 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
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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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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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides an ultralow temperature air source heat pump based on a single-machine double-stage compressor, which belongs to the technical field of air source heat pumps and comprises a shell-and-tube heat exchanger, a liquid storage device, a gas-liquid separator, a plurality of groups of fin heat exchangers, a single-machine double-stage compressor, a horizontal oil separator, an oil cooler, an economizer, a pressure maintaining valve, a four-way reversing valve, a one-way valve, a plurality of electromagnetic valves, a plurality of expansion valves and a connecting pipeline. According to the invention, the single-machine double-stage compressor and the economizer are utilized to cool the overheated refrigerant discharged by the first-stage compressor to a nearly saturated gaseous state, and then the overheated refrigerant enters the second-stage compressor for compression, so that the power consumption of the compressor under the condition of large pressure ratio is reduced, and the heat supply can be stably carried out under the ultralow temperature environment. The air source heat pump has wide applicable environment temperature range; the problems that the air source heat pump has large power consumption and poor heating effect in cold areas and can not be used in severe cold areas are solved.
Description
Technical Field
The invention belongs to the technical field of air source heat pumps, and particularly relates to an ultralow temperature air source heat pump based on a single-machine double-stage compressor.
Background
At present, an air source heat pump product is mainly a single-stage compressor system, the influence of the ambient temperature on a unit is large during heating, and the minimum running temperature can only reach-15 ℃. Meanwhile, the system is limited by factors such as the compression ratio of a compressor, the characteristics of a refrigerant and the like, and can not effectively perform heating operation and even start up when the ambient temperature is very low.
The schematic diagram of the prior air source heat pump based on a single-stage compressor is shown in fig. 1, and the air source heat pump comprises a (single-stage) compressor 26, a shell-and-tube heat exchanger 17, a liquid reservoir 12, a gas-liquid separator 21, a plurality of groups of fin heat exchangers (1, 2 and 3, which are illustrated by taking three groups as examples, wherein the specific number of the groups is determined according to actual needs), a four-way reversing valve 16, a one-way valve 11, a plurality of electromagnetic valves, a plurality of expansion valves and connecting pipelines, and a first electromagnetic valve and a first expansion valve are respectively arranged at the first port of each group of fin heat exchangers; the connection relation of each device is as follows: the exhaust port of the compressor 26 is connected to the port D of the four-way reversing valve 16, the port E of the four-way reversing valve 16 is connected to the first port of the shell-and-tube heat exchanger 17, the second port of the shell-and-tube heat exchanger 17 is connected to the inlet of the one-way valve 11, the outlet of the one-way valve 11 is connected to the inlet of the liquid storage 12, the outlet pipeline of the liquid storage 12 is divided into two paths, the first pipeline is divided into three sub-pipelines and connected to the inlets of expansion valves (5, 7 and 9) arranged at the first ports of the fin heat exchangers of each group, the outlet pipeline of each expansion valve (5, 7 and 9) is divided into two paths and connected to the inlets of the corresponding electromagnetic valves (4, 6 and 8) and the first ports of the fin heat exchangers (1, 2 and 3), the outlets of each electromagnetic valve (4, 6 and 8) are converged into a pipeline section between the outlet of the one-way valve 11 and the inlet of the liquid storage 12, the second port of each fin heat exchanger (1, 2 and 3) is converged into a pipeline to the port C of the four-way reversing valve 16, the port S of the four-way valve 16 is connected to the inlet of the gas-liquid separator 21, the outlet of the gas-liquid separator 21 is connected to the inlet of the air-liquid storage 21, the outlet of the air separator 21 is connected to the inlet of the second pipeline of the air-liquid separator 26 through the second pipeline 18, and the inlet of the second pipeline of the air-way heat exchanger 18 is connected to the inlet of the one-way valve 11, and the inlet of the air-way valve 18 is connected to the inlet of the air-way valve 18.
At present, environmental protection is increasingly focused in various areas, high-pollution and high-energy-consumption equipment is eliminated continuously, an air source heat pump is promoted widely at present to supply heat and warm, a large market space exists in the north of China, but the places of China are wide, the air temperature is obviously different, and if the air source heat pump is promoted in northeast and other places, the common air source heat pump cannot be used. To ensure comfortable heating temperature in severe cold areas, the heat pump refrigerating system needs to have larger high-low pressure span and can be completed by a multi-stage compression system, but the multi-stage compression system can cause higher equipment cost, difficult control and other problems.
Disclosure of Invention
The invention aims to overcome the defects of the prior art, and provides an ultralow-temperature air source heat pump based on a single-machine double-stage compressor, which can stably heat at a large range of ambient temperature (-30-15 ℃), has lower equipment cost and is simple in unit control.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
an ultralow-temperature air source heat pump based on a single-machine double-stage compressor comprises a shell-and-tube heat exchanger (17), a liquid reservoir (12), a gas-liquid separator (21), a plurality of groups of fin heat exchangers (1, 2 and 3), a four-way reversing valve (16), a one-way valve (11), a plurality of electromagnetic valves, a plurality of expansion valves and a connecting pipeline; a first electromagnetic valve and a first expansion valve are respectively arranged at the first ports of each group of fin heat exchangers; the air source heat pump also comprises a single-machine double-stage compressor (22), a horizontal oil separator (23), an oil cooler (24), an economizer (14) and a pressure maintaining valve (20); the connection relation of each device is as follows:
the exhaust port of the single-machine double-stage compressor (22) is connected into the D port of the four-way reversing valve (16) sequentially through the horizontal oil separator (23) and the pressure maintaining valve (20), the E port of the four-way reversing valve (16) is connected into the first port (a) of the shell-and-tube heat exchanger (17), the second port (b) of the shell-and-tube heat exchanger (17) is connected into the inlet of the liquid reservoir (12) through the one-way valve (11), and the outlet of the liquid reservoir (12) is connected into the third port (c) of the economizer (14);
the fourth port (d) pipeline of the economizer (14) is divided into two paths, wherein the first pipeline is divided into a plurality of sub-paths which are respectively connected with corresponding fin heat exchangers through first expansion valves of first ports of all the fin heat exchangers, second ports of all the fin heat exchangers are combined into a pipeline which is connected with a C port of a four-way reversing valve (16), an S port of the four-way reversing valve (16) is connected with an air suction port of a single-stage two-stage compressor (22) through a gas-liquid separator (21), a pipeline section between an air outlet of the single-stage compressor (22) and an air inlet of a horizontal oil separator (23) and a pipeline section between the air suction port of the single-stage two-stage compressor (22) and an outlet of the gas-liquid separator (21) are provided with a fifth electromagnetic valve (15), inlets of the first electromagnetic valves (4, 6, 8) arranged at the first ports of all the fin heat exchangers are connected with pipeline sections between the first ports of the corresponding fin heat exchangers and the outlets of the first expansion valves, and outlet pipelines of all the first electromagnetic valves (4, 6, 8) are combined into a pipeline which is connected with an outlet of a one-stage valve (11) and an inlet of a liquid accumulator (12); a second pipeline of a fourth port (d) pipeline of the economizer (14) sequentially passes through a second electromagnetic valve (19) and a second expansion valve (18) and is connected into a pipe section between a second port (b) of the shell-and-tube heat exchanger (17) and an inlet of the one-way valve (11);
the first port (a) pipeline of the economizer (14) is divided into two paths which are respectively connected with an economizer port of the single-machine double-stage compressor (22) and a balance pipe of the pressure maintaining valve (20), and the second port (b) port of the economizer (14) sequentially passes through the third expansion valve (13) and the third electromagnetic valve (10) and then is connected with a pipe section between the outlet of the liquid storage device (12) and the third port (c) port of the economizer (14);
an oil outlet pipeline of the horizontal oil separator (23) is divided into two paths which are respectively connected with a first port (a) of the oil cooler (24) and an inlet of the fourth electromagnetic valve (25), an outlet of the fourth electromagnetic valve (25) and a second port (b) of the oil cooler (24) are combined into a pipeline which is connected with an oil inlet of the single-machine double-stage compressor (22), and a fourth port (d) of the oil cooler (24) is connected with a third port (c) of the shell-and-tube heat exchanger (17); air conditioning system water flows in from a third port (c) of the oil cooler (24) and flows out from a fourth port (d) of the shell-and-tube heat exchanger (17).
Further, the fifth electromagnetic valve (15) is opened for a period of time when the single-machine double-stage compressor (22) is started for pressure balance; the third electromagnetic valve (10) is switched on according to the low-pass high-low pressure difference judgment switch, when the high-low pressure difference is larger than or equal to a set pressure value, the third electromagnetic valve is switched off when the high-low pressure difference is smaller than the set pressure value; the fourth electromagnetic valve (25) judges a switch according to the detected oil temperature in the pipeline, and is closed when the oil temperature is higher than the set temperature and is opened when the oil temperature is lower than the set temperature;
when the air source heat pump is in a heating mode: the electromagnetic valves (4, 6, 8) of the first ports of each group of fin heat exchangers and the second electromagnetic valve (19) are normally closed; the four-way reversing valve (16) is in an electricity-obtaining state, the D port is communicated with the E port, and the C port is communicated with the S port;
when the air source heat pump is in a refrigeration mode: the electromagnetic valves (4, 6, 8) of the first ports of each group of fin heat exchangers and the second electromagnetic valve (19) are normally open; the four-way reversing valve (16) is in a power-off state, the D port is communicated with the C port, and the E port is communicated with the S port.
The invention has the characteristics and beneficial results that:
the invention utilizes the single-machine double-stage compressor for the air source heat pump product, and uses the economizer in the system design, the overheated refrigerant discharged by the first-stage compressor is cooled to be close to the saturated gaseous state and then enters the second-stage compressor for compression, thereby reducing the power consumption of the compressor under the condition of large pressure ratio and being capable of stably supplying heat in the ultralow temperature environment.
The air source heat pump has wide applicable environment temperature range; the problems that the air source heat pump has large power consumption and poor heating effect in cold areas and can not be used in severe cold areas are solved. Provides more choices for central heating in the north, and is economical and environment-friendly.
Drawings
FIG. 1 is a schematic diagram of an air source heat pump based on a single stage compressor;
fig. 2 is a schematic diagram of an air source heat pump according to an embodiment of the present invention.
Detailed Description
The invention provides an ultralow temperature air source heat pump based on a single-machine double-stage compressor, which is described in detail below by combining with the accompanying drawings and embodiments:
the schematic diagram of the embodiment of the invention is shown in fig. 2, and the air source heat pump comprises a shell-and-tube heat exchanger 17, a liquid reservoir 12, a gas-liquid separator 21, a plurality of groups of fin heat exchangers (1, 2 and 3, and 3 groups of fin heat exchangers are arranged in the embodiment), a four-way reversing valve 16, a one-way valve 11, a plurality of electromagnetic valves, a plurality of expansion valves and connecting pipelines; a first electromagnetic valve (4, 6, 8) and a first expansion valve (5, 7, 9) are respectively arranged at the first ports of each group of fin heat exchangers; the air source heat pump further includes a stand-alone two-stage compressor 22, a horizontal oil separator 23, an oil cooler 24, an economizer 14, and a pressure maintenance valve 20; the connection relation of each device is as follows:
the exhaust port of the single-machine double-stage compressor 22 is connected with the air inlet of the horizontal oil separator 23, the air outlet of the horizontal oil separator 23 is connected with the inlet of the pressure maintaining valve 20, the outlet of the pressure maintaining valve 20 is connected with the D port of the four-way reversing valve 16, the E port of the four-way reversing valve 16 is connected with the a port of the shell-and-tube heat exchanger 17, the b port of the shell-and-tube heat exchanger 17 is connected with the inlet of the one-way valve 11, the outlet of the one-way valve 11 is connected with the inlet of the liquid accumulator 12, and the outlet of the liquid accumulator 12 is connected with the c port of the economizer 14;
the d-port pipeline of the economizer 14 is divided into two paths, wherein the first pipeline is divided into a plurality of sub-paths which are respectively connected with the corresponding fin heat exchangers through the first expansion valves of the first ports of each group of fin heat exchangers (in the embodiment, the first pipeline is divided into three sub-paths which are respectively connected with the first ports of the fin heat exchanger 1, the fin heat exchanger 2 and the fin heat exchanger 3 through the expansion valves 5, the expansion valve 7 and the expansion valve 9), the second ports of each group of fin heat exchangers are combined into one pipeline to be connected with the C port of the four-way reversing valve 16, the S port of the four-way reversing valve 16 is connected with the inlet of the gas-liquid separator 21, the outlet of the gas-liquid separator 21 is connected with the air suction port of the single-stage two-stage compressor 22, the electromagnetic valve 15 is arranged on a pipe section between an exhaust port of the single-unit double-stage compressor 22 and an air inlet of the horizontal oil separator 23 and a pipe section between an air suction port of the single-unit double-stage compressor 22 and an outlet of the gas-liquid separator 21, an electromagnetic valve inlet arranged at a first port of each group of fin heat exchangers is connected with a pipe section between a corresponding first port of the fin heat exchanger and a first expansion valve outlet (in the embodiment, an electromagnetic valve 4, an electromagnetic valve 6 and an electromagnetic valve 8 inlet are respectively connected with a pipe section between a first port of the fin heat exchanger 1 and an outlet of the expansion valve 5, a first port of the fin heat exchanger 2 and an outlet of the expansion valve 7 and an outlet of the fin heat exchanger 3 and an outlet of the expansion valve 9), and outlet pipelines of the electromagnetic valves (4, 6 and 8) are combined into a pipe section between an outlet of the one-way valve 11 and an inlet of the liquid reservoir 12; the second pipeline of the d-port pipeline of the economizer 14 is connected with the inlet of the electromagnetic valve 19, the outlet of the electromagnetic valve 19 is connected with the inlet of the expansion valve 18, and the outlet of the expansion valve 18 is connected with a pipe section between the b port of the shell-and-tube heat exchanger 17 and the inlet of the one-way valve 11;
the a-port pipeline of the economizer 14 is divided into two paths which are respectively connected with an economizer port of the single-machine double-stage compressor 22 and a balance pipe of the pressure maintaining valve 20, the b-port of the economizer 14 is connected with an inlet of the expansion valve 13, an outlet of the expansion valve 13 is connected with an inlet of the electromagnetic valve 10, and an outlet of the electromagnetic valve 10 is connected with a pipe section between an outlet of the liquid storage 12 and a c-port of the economizer 14;
the oil outlet pipeline of the horizontal oil separator 23 is divided into two paths which are respectively connected with an a port of the oil cooler 24 and an inlet of the electromagnetic valve 25, an outlet of the electromagnetic valve 25 and a b port pipeline of the oil cooler 24 are combined into a pipeline which is connected with an oil inlet of the single-machine double-stage compressor 22, and a d port of the oil cooler 24 is connected with a c port of the shell-and-tube heat exchanger 17; air conditioning system water flows in from port c of the oil cooler 24 and flows out from port d of the shell and tube heat exchanger 17.
The air source heat pump has two working modes of refrigeration and heating, and is respectively described as follows:
when the air source heat pump is in a heating mode, the electromagnetic valve 4, the electromagnetic valve 6, the electromagnetic valve 8 and the electromagnetic valve 19 are normally closed; the electromagnetic valve 10 judges a switch according to the high-low pressure difference of the system, and is opened when the high-low pressure difference is more than or equal to 10bar, and is closed when the high-low pressure difference is less than 10 bar; the solenoid valve 15 is opened for 10 seconds when the compressor is started for pressure balance; the four-way reversing valve 16 is in a power-on state, the D port is communicated with the E port, and the C port is communicated with the S port; the solenoid valve 25 determines the switch according to the detected oil temperature in the pipe, and is closed when the oil temperature is higher than 70 ℃ and opened when the oil temperature is lower than 50 ℃. The mixed gas of the high-temperature and high-pressure refrigerant and lubricating oil in the heat pump system enters the air inlet of the horizontal oil separator 23 from the air outlet of the single-machine two-stage compressor 22, and the high-temperature and high-pressure refrigerant gas and lubricating oil in the horizontal oil separator 23 are separated; the high-temperature high-pressure refrigerant gas enters the inlet of the pressure maintaining valve 20 from the gas outlet of the horizontal oil separator 23, and the pressure maintaining valve 20 has the function of ensuring that the system exhaust gas reaches the preset pressure to be discharged and maintaining the high-low pressure ratio of the compressor 22; the high-temperature high-pressure refrigerant gas enters the D port of the four-way reversing valve 16 from the outlet of the pressure maintaining valve 20, and the four-way reversing valve 16 has the function of switching the flow direction of the refrigerant to realize the switching of a refrigerating mode and a heating mode; in the heating mode, the port D of the four-way reversing valve 16 is communicated with the port E, and the high-temperature and high-pressure refrigerant gas entering the port D of the four-way reversing valve from the pressure maintaining valve 20 enters the port a of the shell-and-tube heat exchanger 17 from the port E of the four-way reversing valve; the high-temperature and high-pressure refrigerant exchanges heat with the air-conditioning circulating water in the shell-and-tube heat exchanger 17, heat is released into the air-conditioning circulating water, meanwhile, the high-temperature and high-pressure refrigerant gas is condensed into high-temperature and high-pressure refrigerant liquid, and the high-temperature and high-pressure refrigerant liquid is discharged from the port b of the shell-and-tube heat exchanger 17 and enters the one-way valve 11, and the one-way valve 11 can be opened only in one direction, flows forward and is not opened in the opposite direction; the high-temperature high-pressure refrigerant liquid enters the liquid storage device 12 through the one-way valve 11, and the liquid storage device is used for storing excessive refrigerant in the system and ensuring that the refrigerant can be effectively sealed in liquid before the expansion valve throttles, so that the influence of flash refrigerant vapor on the throttling effect is avoided; the high-temperature high-pressure refrigerant liquid is discharged from the liquid storage device 12, enters the port C of the economizer 14 through the main liquid pipeline, a branch pipeline is taken from the main liquid pipeline in front of the liquid storage device 12 and the economizer 14 and passes through the electromagnetic valve 10 and the expansion valve 13, a small part of the high-temperature high-pressure refrigerant liquid is throttled into a gas-liquid two-phase mixture with medium temperature and medium pressure through the branch pipeline, enters the port b of the economizer 14, the two refrigerants exchange heat, the high-temperature high-pressure refrigerant liquid of the main liquid pipeline passes through the economizer 14 and is cooled into high-pressure supercooled liquid, the throttled medium-temperature medium-pressure refrigerant of the branch pipeline passes through the economizer 14 and is evaporated into a saturated gaseous refrigerant with medium pressure, the medium-pressure cavity flowing out of the port a of the economizer 14 and entering the single-machine two-stage compressor 22 is mixed with medium-pressure overheated refrigerant exhaust gas of the first-stage compressor, the exhaust gas temperature after the first-stage compression is cooled, the mixed exhaust gas temperature is sent into the second-stage compressor for compression, the high-pressure refrigerant liquid after being supercooled by the economizer 14 is discharged from the port d of the economizer 14 and is divided into three branches to be throttled into a low-temperature low-pressure gas-liquid two-phase mixture through the expansion valve 5, the expansion valve 7 and the expansion valve 9), and the gas-liquid two-phase mixture enters the first fin heat exchanger, the second fin heat exchanger, the third fin heat exchanger (1, 2 and 3) respectively and exchanges heat with the outside air, the low-temperature low-pressure refrigerant is evaporated into low-pressure overheated gas through absorbing heat in the air, and then is converged into a pipeline to enter the port C of the four-way reversing valve 16; at this time, the C port and the S port of the four-way reversing valve 16 are communicated; the low-pressure superheated refrigerant gas is discharged from the S port of the four-way reversing valve 16 and enters the gas-liquid separator 21, the gas-liquid separator has the function of separating the refrigerant liquid which is not completely evaporated, the refrigerant liquid is prevented from entering the compressor to cause wet compression, the refrigerant liquid is separated in the gas-liquid separator 21, and the discharged low-pressure refrigerant gas is sucked by the air suction port of the stand-alone two-stage compressor 22, so that the circulation of the refrigerant is completed. The flow process of lubricating oil is that after the lubricating oil is separated by the horizontal oil separator 23, the lubricating oil flows out from an oil outlet of the horizontal oil separator 23, in order to prevent the lubricating oil from being too high in temperature, the system is provided with the oil cooler 24, the lubricating oil discharged from the oil outlet of the horizontal oil separator 23 enters an a port of the oil cooler 24, the lubricating oil exchanges heat with air-conditioning circulating water in the oil cooler, and is discharged from a b port of the oil cooler 24 to enter a compressor oil inlet after being cooled, when the lubricating oil temperature is not high in system design, an oil way bypass is arranged, unnecessary oil cooling is avoided, and the electromagnetic valve 25 plays a role of the oil way bypass. The above is the flow process of the refrigerant and the lubricating oil in the heating mode.
When the air source heat pump is in a refrigeration mode, the electromagnetic valve 4, the electromagnetic valve 6, the electromagnetic valve 8 and the electromagnetic valve 19 are normally open; the electromagnetic valve 10 is switched on according to the low-pass high-low pressure difference judgment switch, when the high-low pressure difference is more than or equal to 10bar, the electromagnetic valve is switched off when the high-low pressure difference is less than 10 bar; the solenoid valve 15 is opened for 10 seconds when the compressor is started for pressure balance; the four-way reversing valve 16 is in a power-off state, the port D is communicated with the port C, and the port E is communicated with the port S; the solenoid valve 25 determines the switch according to the detected oil temperature in the pipe, and is closed when the oil temperature is higher than 70 ℃ and opened when the oil temperature is lower than 50 ℃. The mixed gas of the high-temperature and high-pressure refrigerant and lubricating oil in the heat pump system enters the air inlet of the horizontal oil separator 23 from the air outlet of the single-machine two-stage compressor 22, and the high-temperature and high-pressure refrigerant gas and lubricating oil in the horizontal oil separator 23 are separated; the high-temperature high-pressure refrigerant gas enters the inlet of the pressure maintaining valve 20 from the gas outlet of the horizontal oil separator 23, and the pressure maintaining valve 20 has the function of ensuring that the system exhaust gas reaches the preset pressure and can be discharged, and maintaining the high-low pressure ratio of the compressor; the high-temperature high-pressure refrigerant gas enters the D port of the four-way reversing valve 16 from the outlet of the pressure maintaining valve 20, and the four-way reversing valve 16 has the function of switching the flow direction of the refrigerant to realize the switching of a refrigerating mode and a heating mode; in the refrigeration mode, the port D of the four-way reversing valve 16 is communicated with the port C, the high-temperature and high-pressure refrigerant gas entering the port D of the four-way reversing valve from the pressure maintaining valve 20 is separated into three branches from the port C of the four-way reversing valve and enters the first, second and third fin heat exchangers (1, 2 and 3) respectively, exchanges heat with the outside air, releases heat into the air, and condenses the high-temperature and high-pressure refrigerant into high-pressure refrigerant liquid; then respectively passing through the electromagnetic valve 4, the electromagnetic valve 6 and the electromagnetic valve 8) and then converging into a pipeline to enter the liquid storage device 12, wherein the liquid storage device is used for storing excessive refrigerant of the system and ensuring that the refrigerant can be effectively sealed before the expansion valve throttles so as to avoid the influence of flash refrigerant steam on the throttling effect; the high-temperature high-pressure refrigerant liquid is discharged from the liquid storage device 12, enters the c port of the economizer 14 through the main liquid pipeline, a branch pipeline is taken from the main liquid pipeline before the liquid storage device 12 and the economizer 14, passes through the electromagnetic valve 10 and the expansion valve 13, a small part of the high-temperature high-pressure refrigerant liquid is throttled into a gas-liquid two-phase mixture with medium temperature and medium pressure through the branch pipeline, enters the b port of the economizer 14, the two-way refrigerant is subjected to heat exchange, the high-temperature high-pressure refrigerant liquid of the main liquid pipeline passes through the economizer 14 and is cooled into high-pressure supercooled liquid, the throttled medium-temperature medium-pressure refrigerant of the branch pipeline passes through the economizer 14 and is evaporated into medium-pressure saturated gaseous refrigerant, the medium-pressure cavity entering the single-stage two-stage compressor 22 is mixed with medium-pressure overheated refrigerant exhaust gas of the first-stage compressor, the mixed high-pressure refrigerant liquid is discharged from the d port of the economizer 14 after being fed into the two-stage compressor for compression, the high-pressure refrigerant liquid mixture is throttled into the low-temperature low-pressure two-phase mixture enters the heat exchange shell 17 b of the economizer 14 through the electromagnetic valve 19 and the expansion valve 18, the low-pressure refrigerant mixture is evaporated into the low-temperature circulating water through the heat exchange valve 16, and the heat exchange water of the low-pressure circulating water is cooled through the low-pressure circulation valve is cooled into the low-temperature air-pressure circulation valve; at this time, the E port and the S port of the four-way reversing valve 16 are communicated; the low-pressure superheated refrigerant gas is discharged from the S port of the four-way reversing valve 16 and enters the gas-liquid separator 21, the gas-liquid separator has the function of separating the refrigerant liquid which is not completely evaporated, the refrigerant liquid is prevented from entering the compressor to cause wet compression, the refrigerant liquid is separated in the gas-liquid separator 21, and the discharged low-pressure refrigerant gas is sucked by the air suction port of the stand-alone two-stage compressor 22, so that the circulation of the refrigerant is completed. The flow process of lubricating oil is that after the lubricating oil is separated by the horizontal oil separator 23, the lubricating oil flows out from an oil outlet of the horizontal oil separator 23, in order to prevent the lubricating oil from being too high in temperature, the system is provided with the oil cooler 24, the lubricating oil discharged from the oil outlet of the horizontal oil separator 23 enters an a port of the oil cooler 24, the lubricating oil exchanges heat with air-conditioning circulating water in the oil cooler, and is discharged from a b port of the oil cooler 24 to enter a compressor oil inlet after being cooled, when the lubricating oil temperature is not high in system design, an oil way bypass is arranged, unnecessary oil cooling is avoided, and the electromagnetic valve 25 plays a role of the oil way bypass. The above is the flow process of the refrigerant and the lubricating oil in the cooling mode.
The air source heat pump can realize double-stage compression of a single compressor, has large high-low pressure ratio of the system, can adapt to low-temperature environment, can stably heat at-30 ℃ and has obvious economic benefit.
The specific implementation modes of the main components of the invention are as follows:
the main components of the invention are a stand-alone two-stage compressor, a horizontal oil separator, a four-way reversing valve, a shell-and-tube heat exchanger, a gas-liquid separator, a liquid reservoir, an economizer, a fin heat exchanger, an oil cooler, an electromagnetic valve, an expansion valve, a pressure maintaining valve and a one-way valve which are all commercially available mature products.
Examples:
1. the single-machine double-stage compressor determines the type of the selected compressor according to the mass flow rate of the refrigerating system and the displacement of the compressor determined by the unit load, and the selected compressor is a double-brand SRT413 single-machine double-stage compressor;
2. a horizontal oil separator, wherein the model is selected and determined according to the exhaust gas amount of the compressor and the average flow speed in the horizontal oil separator;
3. the four-way reversing valve is used for selecting a type according to the refrigerating capacity of the refrigerating system;
4. the shell-tube heat exchanger calculates the shape according to the heating capacity of the heat pump host, the physical characteristics of heat exchange media at two sides of the heat exchanger and the heat transfer properties of heat exchange materials;
5. the gas-liquid separator is used for selecting a proper model according to the refrigerant filling amount and the refrigerating capacity of a system refrigerating system;
6. the liquid accumulator is used for selecting a proper model according to the quantity of refrigerant filling quantity of a system refrigerating system and the size of a system pipeline;
7. the economizer calculates the type selection according to the medium-pressure heat exchange amount of the refrigerating system and the temperatures of the two sides of heat exchange;
8. the fin heat exchanger calculates the shape selection according to the refrigerating capacity of the refrigerating system, the physical characteristics of heat exchange media at two sides of the heat exchanger, heat exchange materials, fin materials and fin spacing;
9. an oil cooler for calculating and selecting the heat transfer attribute of the heat exchange tube material according to the oil quantity and the heat exchange temperature difference and the water side temperature difference;
10. electromagnetic valve, expansion valve, check valve, according to systematic load and pipeline structure type selection;
11. the pressure maintaining valve is a compressor fitting, and manufacturers are matched;
12. other pipeline valves are determined according to pipeline and need.
The foregoing description of the preferred embodiments of the invention is not intended to limit the scope of the invention, but is intended to cover any modifications, equivalents, improvements or the like within the spirit and scope of the present invention.
Claims (2)
1. An ultralow-temperature air source heat pump based on a single-machine double-stage compressor comprises a shell-and-tube heat exchanger (17), a liquid reservoir (12), a gas-liquid separator (21), a plurality of groups of fin heat exchangers (1, 2 and 3), a four-way reversing valve (16), a one-way valve (11), a plurality of electromagnetic valves, a plurality of expansion valves and a connecting pipeline; a first electromagnetic valve and a first expansion valve are respectively arranged at the first ports of each group of fin heat exchangers; the air source heat pump is characterized by further comprising a single-machine double-stage compressor (22), a horizontal oil separator (23), an oil cooler (24), an economizer (14) and a pressure maintaining valve (20); the connection relation of each device is as follows:
the exhaust port of the single-machine double-stage compressor (22) is connected into the D port of the four-way reversing valve (16) sequentially through the horizontal oil separator (23) and the pressure maintaining valve (20), the E port of the four-way reversing valve (16) is connected into the first port (a) of the shell-and-tube heat exchanger (17), the second port (b) of the shell-and-tube heat exchanger (17) is connected into the inlet of the liquid reservoir (12) through the one-way valve (11), and the outlet of the liquid reservoir (12) is connected into the third port (c) of the economizer (14);
the fourth port (d) pipeline of the economizer (14) is divided into two paths, wherein the first pipeline is divided into a plurality of sub-paths which are respectively connected with corresponding fin heat exchangers through first expansion valves of first ports of all the fin heat exchangers, second ports of all the fin heat exchangers are combined into a pipeline which is connected with a C port of a four-way reversing valve (16), an S port of the four-way reversing valve (16) is connected with an air suction port of a single-stage two-stage compressor (22) through a gas-liquid separator (21), a pipeline section between an air outlet of the single-stage compressor (22) and an air inlet of a horizontal oil separator (23) and a pipeline section between the air suction port of the single-stage two-stage compressor (22) and an outlet of the gas-liquid separator (21) are provided with a fifth electromagnetic valve (15), inlets of the first electromagnetic valves (4, 6, 8) arranged at the first ports of all the fin heat exchangers are connected with pipeline sections between the first ports of the corresponding fin heat exchangers and the outlets of the first expansion valves, and outlet pipelines of all the first electromagnetic valves (4, 6, 8) are combined into a pipeline which is connected with an outlet of a one-stage valve (11) and an inlet of a liquid accumulator (12); a second pipeline of a fourth port (d) pipeline of the economizer (14) sequentially passes through a second electromagnetic valve (19) and a second expansion valve (18) and is connected into a pipe section between a second port (b) of the shell-and-tube heat exchanger (17) and an inlet of the one-way valve (11);
the first port (a) pipeline of the economizer (14) is divided into two paths which are respectively connected with an economizer port of the single-machine double-stage compressor (22) and a balance pipe of the pressure maintaining valve (20), and the second port (b) port of the economizer (14) sequentially passes through the third expansion valve (13) and the third electromagnetic valve (10) and then is connected with a pipe section between the outlet of the liquid storage device (12) and the third port (c) port of the economizer (14);
an oil outlet pipeline of the horizontal oil separator (23) is divided into two paths which are respectively connected with a first port (a) of the oil cooler (24) and an inlet of the fourth electromagnetic valve (25), an outlet of the fourth electromagnetic valve (25) and a second port (b) of the oil cooler (24) are combined into a pipeline which is connected with an oil inlet of the single-machine double-stage compressor (22), and a fourth port (d) of the oil cooler (24) is connected with a third port (c) of the shell-and-tube heat exchanger (17); air conditioning system water flows in from a third port (c) of the oil cooler (24) and flows out from a fourth port (d) of the shell-and-tube heat exchanger (17).
2. The air source heat pump according to claim 1, characterized in that the fifth solenoid valve (15) is opened for a period of time for pressure equalization when the stand-alone two-stage compressor (22) is started; the third electromagnetic valve (10) is switched on according to the low-pass high-low pressure difference judgment switch, when the high-low pressure difference is larger than or equal to a set pressure value, the third electromagnetic valve is switched off when the high-low pressure difference is smaller than the set pressure value; the fourth electromagnetic valve (25) judges a switch according to the detected oil temperature in the pipeline, and is closed when the oil temperature is higher than the set temperature and is opened when the oil temperature is lower than the set temperature;
when the air source heat pump is in a heating mode: the first electromagnetic valve (4, 6, 8) and the second electromagnetic valve (19) of the first port of each group of fin heat exchangers are normally closed; the four-way reversing valve (16) is in an electricity-obtaining state, the D port is communicated with the E port, and the C port is communicated with the S port;
when the air source heat pump is in a refrigeration mode: the first electromagnetic valves (4, 6, 8) and the second electromagnetic valves (19) of the first ports of each group of fin heat exchangers are normally open; the four-way reversing valve (16) is in a power-off state, the D port is communicated with the C port, and the E port is communicated with the S port.
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Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108954914A (en) * | 2018-08-08 | 2018-12-07 | 广东欧亚制冷设备制造有限公司 | A kind of low ambient temperature net for air-source heat pump units |
| CN109210827A (en) * | 2018-08-30 | 2019-01-15 | 北京工业大学 | A kind of heat pipe-type air source heat pump with lubrication oil circulation |
| CN111023620A (en) * | 2018-10-09 | 2020-04-17 | 山东新华能节能科技有限公司 | Vortex type air source heat pump two-stage system |
| CN110220326B (en) * | 2019-02-26 | 2024-01-23 | 北京华电东晟科技有限公司 | Automatic variable-load air source heat pump for preparing high-temperature hot water from ultralow-temperature air |
| CN110411054B (en) * | 2019-07-09 | 2021-02-02 | 南京天加环境科技有限公司 | Gas heat pump air conditioning system capable of reducing temperature of lubricating oil and control method |
| CN110260560B (en) * | 2019-07-19 | 2024-06-11 | 北京金茂绿建科技有限公司 | High-power single-machine two-stage vortex type ultralow-temperature air source heat pump |
| CN114576880A (en) * | 2022-03-24 | 2022-06-03 | 山东阿尔普尔节能装备有限公司 | Single-machine two-stage screw compression ultra-large ultralow temperature air source heat pump unit |
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