CN112539572A - Quasi-three-stage compression super heat pump heat exchange device and cold and heat source temperature difference heat exchange method - Google Patents
Quasi-three-stage compression super heat pump heat exchange device and cold and heat source temperature difference heat exchange method Download PDFInfo
- Publication number
- CN112539572A CN112539572A CN202011535105.9A CN202011535105A CN112539572A CN 112539572 A CN112539572 A CN 112539572A CN 202011535105 A CN202011535105 A CN 202011535105A CN 112539572 A CN112539572 A CN 112539572A
- Authority
- CN
- China
- Prior art keywords
- working medium
- valve
- heat exchanger
- heat
- steam
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000007906 compression Methods 0.000 title claims abstract description 30
- 230000006835 compression Effects 0.000 title claims abstract description 25
- 238000000034 method Methods 0.000 title claims abstract description 16
- 239000007788 liquid Substances 0.000 claims description 36
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 11
- 238000010438 heat treatment Methods 0.000 claims description 3
- 238000010521 absorption reaction Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 2
- 239000000284 extract Substances 0.000 description 2
- 230000000704 physical effect Effects 0.000 description 2
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Images
Classifications
-
- 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
- F25B30/02—Heat pumps of the compression 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
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B31/00—Compressor arrangements
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
The invention discloses a quasi-tertiary compression super heat pump heat exchange device and a cold and heat source temperature difference heat exchange method, belonging to the technical field of energy utilization. The quasi-tertiary compression super heat pump heat exchange device is a heat pump heat exchange device for realizing large temperature difference between a low-temperature cold source and a high-temperature heat source, and consists of a heat exchanger A, a steam compressor, a heat exchanger B, a tuner, a controller, a motor, a valve A, a valve B, a valve C, a phase-change heat exchange tube, blades, a circulating working medium, a cold source inlet and outlet and a heat source inlet and outlet; wherein, the heat exchanger A, the vapor compressor, the heat exchanger B, the valve B and the distributor 4 are connected in series to form a loop; the distributor is connected with the vapor compressor through the valve A respectively. The invention automatically adjusts the vapor compression process according to the cold source temperature, thereby realizing the active adjustment of the cycle process under the large-range strong load variable working condition to improve the operating efficiency of the heat pump. The high-efficiency heat exchange under the operating condition that the temperature difference between the low-temperature cold source and the high-temperature heat source is higher than 100 ℃ can be realized.
Description
Technical Field
The invention belongs to the technical field of energy utilization, and particularly relates to a quasi-tertiary compression super heat pump heat exchange device and a cold and heat source temperature difference heat exchange method. In particular to a heat pump device which extracts heat in a cold source to heat the heat source and automatically adjusts the operation mode according to the temperature of the cold source.
Background
In the field of energy utilization, a large number of heat exchange processes exist in various industrial and civil processes. According to Newton's second law, heat can be spontaneously transferred from a high-temperature object to a low-temperature object, and the heat exchange working condition can be realized only by using a common heat exchanger; if heat needs to be transferred from a low temperature object to a high temperature object, a certain amount of high grade energy, such as electricity, high temperature steam or hot water, needs to be consumed. In the prior art, the heat pump technology is accepted and applied in the market by the characteristics of high efficiency and reliability. The heat pump technology is divided into absorption heat pumps or compression heat pumps according to the principle. The absorption heat pump is divided into a first type absorption heat pump and a second type absorption heat pump. The first type of absorption heat pump needs to consume high-grade energy, transfers a large amount of heat from a low-temperature object to a high-temperature object, generates heat with a temperature lower than the temperature of a driving heat source, is called a heat increasing type heat pump, extracts a small amount of heat from the low-temperature object, generates heat with a temperature higher than the temperature of the driving heat source, and is called a heating type heat pump; the compression heat pump consumes mechanical work, and realizes heat transfer from a low-temperature object to a high-temperature object through an inverse Carnot cycle. The absorption heat pump is limited by thermal cycle and physical properties of working medium, while the compression heat pump is limited by thermal cycle and physical properties of working medium, and can only work in respective temperature range, and cannot realize large-scale temperature increase. Meanwhile, the low-temperature cold source is often accompanied with temperature change in the production process, and the heat pump device is designed according to a rated working condition, so that the performance of the heat pump device is greatly attenuated when the operation working condition deviates from the design working condition, for example, in the air source heat pump technology, air at minus 5 ℃ is taken as the design working condition, and if the actual operation working condition is minus 15 to 10 ℃, the operation efficiency is obviously reduced.
In order to solve the application problem, a quasi-tertiary compression super heat pump device is provided, and a novel compressor and an operation regulation and control method are adopted to maintain the higher efficiency of a heat pump under a large-range variable working condition.
Disclosure of Invention
The invention aims to provide a quasi-tertiary compression super heat pump heat exchange device and a cold and heat source temperature difference heat exchange method, and is characterized in that the quasi-tertiary compression super heat pump heat exchange device is a heat pump heat exchange device for realizing large temperature difference between a low-temperature cold source and a high-temperature heat source, and the heat pump heat exchange device is composed of an A heat exchanger 1, a steam compressor 2, a B heat exchanger 3, a distributor 4, a controller 5, a motor 6, an A valve 7, a B valve 8, a C valve 9, a phase change heat exchange pipe 10, an A blade 11, a B blade 12, a circulating working medium, a cold source inlet 13, a cold source outlet 14, a heat source outlet 15 and a heat source inlet 16; wherein, the heat exchanger A1, the vapor compressor 2, the heat exchanger B3, the valve B8 and the distributor 4 are connected in series to form a loop; the distributor 4 is respectively connected with the vapor compressor 2 through an A valve 7 and connected on a communicating pipeline of the A heat exchanger 1 and the vapor compressor 2 through a C valve 9; the controller 5 is respectively connected with the valve A7, the valve B8 and the cold source inlet 13 of the heat exchanger A1 through communicating pipes; the heat exchanger A1 is also connected with a cold source outlet 14; the heat exchanger B3 is respectively provided with a heat source outlet 15 and a heat source inlet 16; the vapor compressor 2 is divided into a low pressure chamber 2a, a mixing chamber 2b and a high pressure chamber 2 c; wherein, a rotating shaft is fixed horizontally in the middle of the three cavities, on the rotating shaft, the blade B12 is arranged in the low-pressure cavity 2a, and the blade A11 is arranged in the high-pressure cavity 2 c; the motor 6 is fixed outside the low-pressure cavity 2a and connected with the rotating shaft to drive the blade B and the blade A to rotate.
Phase change heat exchange tubes 10 are arranged in the heat exchanger A1 and the heat exchanger B3.
The driving mode of the motor is electric driving or steam driving. The circulating working medium is water.
The vanes are of piston, scroll, screw or centrifugal type.
The cold source inlet and the cold source outlet of the heat pump are both air, the hot water inlet is hot water, and the steam outlet is steam.
The circulating working medium returns to the heat exchanger A1 after sequentially passing through the heat exchanger A1, the steam compressor 2, the heat exchanger B3, the valve B8 and the distributor 4; the valve 9 and the valve 7A are controlled by opening or closing states to realize a gas compression process that the circulating working medium enters or leaves the interior of the steam compressor 2, the circulating working medium steam from the outlet of the heat exchanger A1 is mixed with the working medium steam passing through the valve 9C and then sequentially passes through the low-pressure cavity 2a, the mixing cavity 2b and the high-pressure cavity 2c of the steam compressor 2, the working medium steam is mixed with the working medium passing through the valve 7A in the mixing cavity 2b or part of the working medium leaves through the valve 7A, and the controller 5 detects the temperature and flow control of the cold source inlet 13 and the opening or closing states of the valve 7A and the valve 9C.
A cold and heat source temperature difference heat exchange method of a quasi-three-stage compression super heat pump heat exchange device is characterized in that the cold and heat source temperature difference heat exchange method comprises the following modes:
(1) maximum load condition
When the flow of the cold source is increased or the temperature is reduced, and the heat exchange amount of the heat exchanger A1 is higher than the maximum load set value, the valve C9 is opened, the valve A7 is opened, the circulating working medium is heated by the cold source in the heat exchanger A1 through the phase change heat exchange pipe 10 to be changed into circulating working medium steam, the circulation working medium steam and the circulation working medium passing through the C valve 9 are mixed and then enter the steam compressor 2, the mixed circulation working medium steam enters the mixing cavity 2b after being compressed by the low pressure cavity 2a, the mixed gas and the circulating working medium which passes through the valve 7A are mixed again and then enter the high-pressure cavity 2c to be compressed again, the circulating working medium steam enters the heat exchanger 3B to heat the heat source medium to be changed into liquid, the liquid circulating working medium passes through the valve 8B and then enters the regulator 4, in the distributor 4, part of the working medium enters into circulation through the valve A7 and the valve C9, and the rest of the working medium enters into the heat exchanger A1 to complete the circulation.
(2) Sub-heavy load condition
When the flow of the cold source is increased or the temperature is reduced, and the heat exchange amount of the heat exchanger A1 is higher than the secondary load and lower than the maximum load set value, the valve C9 is closed, and the valve A7 is opened. The circulating working medium is heated by a cold source through a phase change heat exchange tube 10 in a heat exchanger A1 to become circulating working medium steam, the circulating working medium steam enters a mixing chamber 2B after being compressed by a low-pressure chamber 2a, is mixed with the circulating working medium passing through a valve A7 again and then enters a high-pressure chamber 2c to be compressed again, the circulating working medium steam enters a heat exchanger B3 and then heats a heat source medium to become liquid, the liquid circulating working medium enters a distributor 4 after passing through a valve B8, part of the working medium in the distributor 4 enters circulation through the valve A7, and the rest of the working medium enters the heat exchanger A1 to complete circulation.
(3) Greater load operating mode
When the flow of the cold source is increased or the temperature is reduced, and the heat exchange capacity of the heat exchanger A1 is higher than the design load and lower than the set value of the secondary heavy load, the valve C9 is closed, and the valve A7 is closed; the circulating working medium is heated by a cold source through a phase change heat exchange pipe 10 in a heat exchanger A1 to become circulating working medium steam, the circulating working medium steam is compressed by a low-pressure cavity 2a, then enters a mixing cavity 2B, then enters a high-pressure cavity 2c, and then is compressed again, the circulating working medium steam enters a heat exchanger B3, then heats a heat source medium and becomes liquid, the liquid circulating working medium enters a distributor 4 after passing through a valve B8, and all working media in the distributor 4 enter the heat exchanger A1 to complete circulation.
(4) Less loaded condition
When the flow of the cold source is reduced or the temperature is increased, and the heat exchange quantity of the heat exchanger A is smaller than the design load and larger than a set value of a smaller load, the valve C9 is opened, and the valve A7 is closed; the cycle working medium is heated by a cold source through a phase change heat exchange pipe 10 in a heat exchanger A1 to become cycle working medium steam, the cycle working medium steam is mixed with the cycle working medium passing through a C valve 9 and then enters a steam compressor 2, the mixed cycle working medium steam is compressed by a low-pressure cavity 2a and then enters a mixing cavity 2B, the mixed cycle working medium steam enters a high-pressure cavity 2C and then is compressed again, the cycle working medium steam enters a heat source medium after entering a heat exchanger B3 and then becomes liquid, the liquid cycle working medium enters a tuner 4 after passing through a valve B8, part of the working medium in the tuner 4 enters circulation through the C valve 9, and the rest of the working medium enters the heat exchanger A1 to complete.
(5) Sub-low load condition
When the flow of a cold source is reduced or the temperature is increased, and the heat exchange amount of the heat exchanger A is smaller than a small load and larger than a secondary small load set value, the C valve 9 is opened, the A valve 7 is opened, a circulating working medium is heated by the cold source in the heat exchanger A1 through the phase change heat exchange tube 10 to be changed into circulating working medium steam, the circulating working medium steam is mixed with the circulating working medium passing through the C valve 9 and then enters the steam compressor 2, the mixed circulating working medium steam is compressed by the low-pressure cavity 2a and then enters the mixing cavity 2B, part of the circulating working medium steam leaves the steam compressor 2 through the A valve 7, the rest of the circulating working medium steam enters the high-pressure cavity 2C and then is compressed again, the circulating working medium steam enters the B heat exchanger 3 and then heats a heat source medium and then is changed into a liquid state, the liquid circulating working medium enters the distributor 4 through the B valve 8 and then enters the distributor 4, and part of the circulating working medium from, and the rest working medium enters the heat exchanger A1 to complete circulation.
(6) Minimum load condition
When the flow of the cold source is reduced or the temperature is increased, and the heat exchange quantity of the heat exchanger A is smaller than the second small load set value, the valve c9 is closed, and the valve a7 is opened. The cycle working medium is heated by a cold source through a phase change heat exchange pipe 10 in a heat exchanger A1 to become cycle working medium steam, the cycle working medium steam enters a mixing cavity 2B after being compressed by a low-pressure cavity 2a, part of the cycle working medium steam leaves a steam compressor 2 through an A valve 7, the rest cycle working medium steam is compressed again after entering a high-pressure cavity 2c, the cycle working medium steam enters a heat exchanger B3 and then heats a heat source medium to become liquid, the liquid cycle working medium enters a distributor 4 after passing a B valve 8, and the cycle working medium passing the A valve 7 in the distributor 4 is mixed with the cycle working medium from the heat exchanger B3 and then enters the heat exchanger A1 to complete the cycle.
The invention has the beneficial effects that the vapor compression process is automatically adjusted according to the temperature of the cold source, and further the cycle process is actively adjusted under the large-range strong load variable working condition so as to improve the operation efficiency of the heat pump. The high-efficiency heat exchange under the operating condition that the temperature difference between the low-temperature cold source and the high-temperature heat source is higher than 100 ℃ can be realized.
Drawings
FIG. 1 is a diagram of a quasi-tertiary compression super heat pump apparatus system.
Detailed Description
The invention provides a quasi-tertiary compression super heat pump heat exchange device and a cold and heat source temperature difference heat exchange method.A cold source works in different running states under the self control of the temperature and the flow of a cold source, and the running loads are different according to the difference of the temperature and the flow of the cold source, and the loads are divided into a plurality of running working conditions of minimum load, secondary small load, smaller load, larger load, secondary large load and maximum load from small to large; the technical solution of the present invention will be described in more detail below with reference to the embodiments and the accompanying drawings. In fig. 1, the cold source inlet and outlet of the heat pump are both air, the heat source inlet is hot water, the heat source outlet is steam, and the circulating working medium is water.
FIG. 1 is a diagram of a quasi-three stage compression super heat pump apparatus. The quasi-tertiary compression super heat pump heat exchange device shown in the figure is a heat pump heat exchange device for realizing large temperature difference between a low-temperature cold source and a high-temperature heat source, and the heat pump heat exchange device is composed of a heat exchanger A1, a steam compressor 2, a heat exchanger B3, a tuner 4, a controller 5, a motor 6, a valve A7, a valve B8, a valve C9, a phase-change heat exchange tube 10, a blade A11, a blade B12, a circulating working medium, a cold source inlet 13, a cold source outlet 14, a heat source outlet 15 and a heat source inlet 16; wherein, the heat exchanger A1, the vapor compressor 2, the heat exchanger B3, the valve B8 and the distributor 4 are connected in series to form a loop, and the heat exchanger A1 and the heat exchanger B3 are internally provided with a phase change heat exchange tube 10. The distributor 4 is respectively connected with the vapor compressor 2 through an A valve 7 and connected on a communicating pipeline of the A heat exchanger 1 and the vapor compressor 2 through a C valve 9; the controller 5 is respectively connected with the valve A7, the valve B8 and the cold source inlet 13 of the heat exchanger A1 through communicating pipes; the heat exchanger A1 is also connected with a cold source outlet 14; the heat exchanger B3 is respectively provided with a heat source outlet 15 and a heat source inlet 16; the vapor compressor 2 is divided into a low pressure chamber 2a, a mixing chamber 2b and a high pressure chamber 2 c; wherein, a rotating shaft is fixed horizontally in the middle of the three cavities, on the rotating shaft, the blade B12 is arranged in the low-pressure cavity 2a, and the blade A11 is arranged in the high-pressure cavity 2 c; the motor 6 is fixed outside the low-pressure cavity 2a and connected with the rotating shaft to drive the blade B and the blade A to rotate.
The motor 6 is driven by electric power or steam. The circulating working medium is water.
The vanes are of piston, scroll, screw or centrifugal type.
The cold source inlet and the cold source outlet of the heat pump are both air, the hot water inlet is hot water, and the steam outlet is steam.
The circulating working medium returns to the heat exchanger A1 after sequentially passing through the heat exchanger A1, the steam compressor 2, the heat exchanger B3, the valve B8 and the distributor 4; the valve 9 and the valve 7A are controlled by opening or closing states to realize a gas compression process that the circulating working medium enters or leaves the interior of the steam compressor 2, the circulating working medium steam from the outlet of the heat exchanger A1 is mixed with the working medium steam passing through the valve 9C and then sequentially passes through the low-pressure cavity 2a, the mixing cavity 2b and the high-pressure cavity 2c of the steam compressor 2, the working medium steam is mixed with the working medium passing through the valve 7A in the mixing cavity 2b or part of the working medium leaves through the valve 7A, and the controller 5 detects the temperature and flow control of the cold source inlet 13 and the opening or closing states of the valve 7A and the valve 9C.
A cold and heat source temperature difference heat exchange method of a quasi-three-stage compression super heat pump heat exchange device comprises the following modes: firstly, dividing the load into a minimum load (a design load is 10-40%), a secondary small load (a design load is 40-70%), a small load (a design load is 70-100%), a large load (a design load is 100-130%), a secondary large load (a design load is 130-160%) and a maximum load (a design load is 160-200%), and specifically operating according to the following modes:
(1) maximum load condition
When the flow of the cold source is increased or the temperature is reduced, and the heat exchange amount of the heat exchanger A1 is higher than the maximum load set value, the valve C9 is opened, the valve A7 is opened, the circulating working medium is heated by the cold source in the heat exchanger A1 through the phase change heat exchange pipe 10 to be changed into circulating working medium steam, the circulation working medium steam and the circulation working medium passing through the C valve 9 are mixed and then enter the steam compressor 2, the mixed circulation working medium steam enters the mixing cavity 2b after being compressed by the low pressure cavity 2a, the mixed gas and the circulating working medium which passes through the valve 7A are mixed again and then enter the high-pressure cavity 2c to be compressed again, the circulating working medium steam enters the heat exchanger 3B to heat the heat source medium to be changed into liquid, the liquid circulating working medium passes through the valve 8B and then enters the regulator 4, in the distributor 4, part of the working medium enters into circulation through the valve A7 and the valve C9, and the rest of the working medium enters into the heat exchanger A1 to complete the circulation.
(2) Sub-heavy load condition
When the flow of the cold source is increased or the temperature is reduced, and the heat exchange amount of the heat exchanger A1 is higher than the secondary load and lower than the maximum load set value, the valve C9 is closed, and the valve A7 is opened. The circulating working medium is heated by a cold source through a phase change heat exchange tube 10 in a heat exchanger A1 to become circulating working medium steam, the circulating working medium steam enters a mixing chamber 2B after being compressed by a low-pressure chamber 2a, is mixed with the circulating working medium passing through a valve A7 again and then enters a high-pressure chamber 2c to be compressed again, the circulating working medium steam enters a heat exchanger B3 and then heats a heat source medium to become liquid, the liquid circulating working medium enters a distributor 4 after passing through a valve B8, part of the working medium in the distributor 4 enters circulation through the valve A7, and the rest of the working medium enters the heat exchanger A1 to complete circulation.
(3) Greater load operating mode
When the flow of the cold source is increased or the temperature is reduced, and the heat exchange capacity of the heat exchanger A1 is higher than the design load and lower than the set value of the secondary heavy load, the valve C9 is closed, and the valve A7 is closed; the circulating working medium is heated by a cold source through a phase change heat exchange pipe 10 in a heat exchanger A1 to become circulating working medium steam, the circulating working medium steam is compressed by a low-pressure cavity 2a, then enters a mixing cavity 2B, then enters a high-pressure cavity 2c, and then is compressed again, the circulating working medium steam enters a heat exchanger B3, then heats a heat source medium and becomes liquid, the liquid circulating working medium enters a distributor 4 after passing through a valve B8, and all working media in the distributor 4 enter the heat exchanger A1 to complete circulation.
(4) Less loaded condition
When the flow of the cold source is reduced or the temperature is increased, and the heat exchange quantity of the heat exchanger A is smaller than the design load and larger than a set value of a smaller load, the valve C9 is opened, and the valve A7 is closed; the cycle working medium is heated by a cold source through a phase change heat exchange pipe 10 in a heat exchanger A1 to become cycle working medium steam, the cycle working medium steam is mixed with the cycle working medium passing through a C valve 9 and then enters a steam compressor 2, the mixed cycle working medium steam is compressed by a low-pressure cavity 2a and then enters a mixing cavity 2B, the mixed cycle working medium steam enters a high-pressure cavity 2C and then is compressed again, the cycle working medium steam enters a heat source medium after entering a heat exchanger B3 and then becomes liquid, the liquid cycle working medium enters a tuner 4 after passing through a valve B8, part of the working medium in the tuner 4 enters circulation through the C valve 9, and the rest of the working medium enters the heat exchanger A1 to complete.
(5) Sub-low load condition
When the flow of a cold source is reduced or the temperature is increased, and the heat exchange amount of the heat exchanger A is smaller than a small load and larger than a secondary small load set value, the C valve 9 is opened, the A valve 7 is opened, a circulating working medium is heated by the cold source in the heat exchanger A1 through the phase change heat exchange tube 10 to be changed into circulating working medium steam, the circulating working medium steam is mixed with the circulating working medium passing through the C valve 9 and then enters the steam compressor 2, the mixed circulating working medium steam is compressed by the low-pressure cavity 2a and then enters the mixing cavity 2B, part of the circulating working medium steam leaves the steam compressor 2 through the A valve 7, the rest of the circulating working medium steam enters the high-pressure cavity 2C and then is compressed again, the circulating working medium steam enters the B heat exchanger 3 and then heats a heat source medium and then is changed into a liquid state, the liquid circulating working medium enters the distributor 4 through the B valve 8 and then enters the distributor 4, and part of the circulating working medium from, and the rest working medium enters the heat exchanger A1 to complete circulation.
(6) Minimum load condition
When the flow of the cold source is reduced or the temperature is increased, and the heat exchange quantity of the heat exchanger A is smaller than the second small load set value, the valve c9 is closed, and the valve a7 is opened. The cycle working medium is heated by a cold source through a phase change heat exchange pipe 10 in a heat exchanger A1 to become cycle working medium steam, the cycle working medium steam enters a mixing cavity 2B after being compressed by a low-pressure cavity 2a, part of the cycle working medium steam leaves a steam compressor 2 through an A valve 7, the rest cycle working medium steam is compressed again after entering a high-pressure cavity 2c, the cycle working medium steam enters a heat exchanger B3 and then heats a heat source medium to become liquid, the liquid cycle working medium enters a distributor 4 after passing a B valve 8, and the cycle working medium passing the A valve 7 in the distributor 4 is mixed with the cycle working medium from the heat exchanger B3 and then enters the heat exchanger A1 to complete the cycle.
Claims (7)
1. A quasi-tertiary compression super heat pump heat exchange device is characterized in that the quasi-tertiary compression super heat pump heat exchange device is a heat pump heat exchange device for realizing large temperature difference between a low-temperature cold source and a high-temperature heat source, and the heat pump heat exchange device is composed of an A heat exchanger (1), a steam compressor (2), a B heat exchanger (3), a distributor (4), a controller (5), a motor (6), an A valve (7), a B valve (8), a C valve (9), a phase-change heat exchange tube (10), an A blade (11), a B blade (12), a circulating working medium, a cold source inlet (13), a cold source outlet (14), a heat source outlet (15) and a heat source inlet (16), wherein the A heat exchanger (1), the steam compressor (2), the B heat exchanger (3), the B valve (8) and the distributor (4) are connected in series to form a loop, and the distributor (4) is respectively connected with the steam compressor (2) through the A valve (, is connected to a communicating pipeline of the heat exchanger A (1) and the steam compressor (2) through a valve C (9); the controller (5) is respectively connected with the valve A (7), the valve B (8) and a cold source inlet (13) of the heat exchanger A (1) through communicating pipes; the heat exchanger A (1) is also connected with a cold source outlet (14); the heat exchanger B (3) is respectively provided with a heat source outlet (15) and a heat source inlet (16); the vapor compressor (2) is divided into a low pressure chamber (2a), a mixing chamber (2b) and a high pressure chamber (2 c); wherein, a rotating shaft is horizontally fixed in the middle of the three cavities, on the rotating shaft, the blade B (12) is arranged in the low-pressure cavity (2a), and the blade A (11) is arranged in the high-pressure cavity (2 c); the motor (6) is fixed outside the low-pressure cavity 2a and is connected with the rotating shaft to drive the blade B (12) and the blade A (11) to rotate.
2. The heat exchange device of the quasi-tertiary compression super heat pump as claimed in claim 1, wherein phase change heat exchange tubes (10) are installed in the A heat exchanger 1 and the B heat exchanger 3.
3. The heat exchanger of a quasi-tertiary compression super heat pump according to claim 1, wherein the motor is driven by electric power or steam. The circulating working medium is water.
4. The quasi-tertiary compression super heat pump heat exchange device of claim 1, wherein the vanes are piston, scroll, screw or centrifugal.
5. The heat exchange device of the quasi-tertiary compression super heat pump of claim 1, wherein the cold source inlet and the outlet of the heat pump are both air, the hot source inlet is hot water, and the hot source outlet is steam.
6. The quasi-tertiary compression super heat pump heat exchange device according to claim 1, wherein the circulating working medium returns to the heat exchanger A (1) after sequentially passing through the heat exchanger A (1), the vapor compressor (2), the heat exchanger B (3), the valve B (8) and the distributor (4); the valve (9) and the valve A (7) are controlled through the opening or closing state to realize the gas compression process that the circulating working medium enters or leaves the interior of the steam compressor (2), the circulating working medium steam from the outlet of the heat exchanger A (1) and the working medium steam passing through the valve C (9) are mixed and then sequentially pass through the low-pressure cavity (2a), the mixing cavity (2b) and the high-pressure cavity (2c) of the steam compressor (2), the working medium steam is mixed with the working medium passing through the valve A (7) in the mixing cavity (2b) or part of the working medium leaves through the valve A (7), and the controller (5) detects the temperature and flow control of the cold source inlet (13) and the opening or closing state of the valve A (7) and the valve C (9).
7. A cold and heat source temperature difference heat exchange method of a quasi-three-stage compression super heat pump heat exchange device is characterized in that the cold and heat source temperature difference heat exchange method comprises the following modes:
(1) maximum load condition
When the flow of a cold source is increased or the temperature is reduced, and the heat exchange amount of the heat exchanger A (1) is higher than a maximum load set value, the valve C (9) is opened, the valve A (7) is opened, a circulating working medium is heated by the cold source in the heat exchanger A (1) through the phase change heat exchange tube (10) to be changed into circulating working medium steam, the circulating working medium steam is mixed with the circulating working medium passing through the valve C (9) and then enters the steam compressor (2), the mixed circulating working medium steam is compressed by the low-pressure cavity 2a and then enters the mixing cavity (2B), the mixed circulating working medium steam is mixed with the circulating working medium passing through the valve A (7) and then enters the high-pressure cavity (2C) and then is compressed again, the circulating working medium steam enters the heat exchanger B (3) and then heats a heat source medium and then becomes liquid, the liquid circulating working medium passes through the valve B (8) and then enters the distributor (4), and part of the working, and the rest working medium enters the heat exchanger A (1) to complete circulation.
(2) Sub-heavy load condition
When the flow of the cold source is increased or the temperature is reduced, and the heat exchange capacity of the heat exchanger A (1) is higher than the secondary load and lower than the maximum load set value, the valve C (9) is closed, and the valve A (7) is opened. The circulating working medium is heated by a cold source through a phase change heat exchange tube (10) in a heat exchanger A (1) to become circulating working medium steam, the circulating working medium steam is compressed by a low-pressure cavity (2a) and then enters a mixing cavity (2B), the circulating working medium steam is mixed with the circulating working medium passing through a valve A (7) again and then enters a high-pressure cavity (2c) and then is compressed again, the circulating working medium steam enters a heat source medium after entering a heat exchanger B (3) and then becomes liquid, the liquid circulating working medium enters a distributor (4) after passing through a valve B (8), part of the working medium in the distributor (4) enters circulation through the valve A (7), and the rest of the working medium enters the heat exchanger A (1.
(3) Greater load operating mode
When the flow of the cold source is increased or the temperature is reduced, and the heat exchange capacity of the heat exchanger A (1) is higher than the design load and lower than the set value of the secondary large load, the valve C (9) is closed, and the valve A (7) is closed; the circulating working medium is heated by a cold source through a phase change heat exchange pipe (10) in a heat exchanger A (1) to become circulating working medium steam, the circulating working medium steam is compressed by a low-pressure cavity (2a), then enters a mixing cavity (2B), then enters a high-pressure cavity (2c), and then is compressed again, the circulating working medium steam enters a heat source medium after entering a heat exchanger B (3) and then becomes liquid, the liquid circulating working medium enters a distributor (4) after passing through a valve B (8), and all working media in the distributor (4) enter the heat exchanger A (1) to complete circulation.
(4) Less loaded condition
When the flow of the cold source is reduced or the temperature is increased, and the heat exchange quantity of the heat exchanger A is smaller than the design load and larger than a set value of a smaller load, the valve C (9) is opened, and the valve A (7) is closed; the cycle working medium is heated by a cold source through a phase change heat exchange pipe (10) in a heat exchanger A (1) to become cycle working medium steam, the cycle working medium steam is mixed with the cycle working medium passing through a valve C (9) and then enters a steam compressor (2), the mixed cycle working medium steam is compressed by a low-pressure cavity (2a) and then enters a mixing cavity (2B), the mixed cycle working medium steam enters a high-pressure cavity (2C) and is compressed again, the cycle working medium steam enters a heat source medium after entering a heat exchanger B (3) and then becomes liquid, the liquid cycle working medium enters a tuner (4) after passing through a valve B (8), part of the working medium in the tuner (4) enters the cycle through the valve C (9), and the rest of the working medium enters the heat exchanger A (1).
(5) Sub-low load condition
When the flow of a cold source is reduced or the temperature is increased, and the heat exchange capacity of the heat exchanger A is smaller than a small load and larger than a secondary small load set value, the valve C (9) is opened, the valve A (7) is opened, a circulating working medium is heated by the cold source to be changed into circulating working medium steam in the heat exchanger A (1) through the phase change heat exchange pipe (10), the circulating working medium steam is mixed with the circulating working medium passing through the valve C (9) and then enters the steam compressor (2), the mixed circulating working medium steam enters the low-pressure cavity (2a) to be compressed and then enters the mixing cavity (2B), part of the circulating working medium steam leaves the steam compressor (2) through the valve A (7), the rest of the circulating working medium steam enters the high-pressure cavity (2C) to be compressed again, the circulating working medium steam enters the heat exchanger B (3) to be heated and then changed into a liquid state, the liquid circulating working medium enters, after the circulating working medium passing through the valve A (7) in the distributor (4) is mixed with the circulating working medium from the heat exchanger B (3), part of the working medium circulates through the valve C (9), and the rest of the working medium enters the heat exchanger A (1) to complete circulation.
(6) Minimum load condition
When the cold source flow is reduced or the temperature is increased and the heat exchange quantity of the heat exchanger A is less than the second small load set value, c, closing a valve (9), opening a valve (7), heating the circulating working medium in a heat exchanger A (1) through a phase-change heat exchange pipe (10) by a cold source to form circulating working medium steam, compressing the circulating working medium steam through a low-pressure cavity (2a) and then entering a mixing cavity (2B), allowing part of the circulating working medium steam to leave a steam compressor (2) through the valve A (7), re-compressing the rest of the circulating working medium steam after entering a high-pressure cavity (2c), heating a heat source medium after the circulating working medium steam enters a heat exchanger B (3) and then changing the circulating working medium into liquid, allowing the liquid circulating working medium to enter a distributor (4) through a valve B (8), the circulating working medium passing through the valve A (7) in the distributor (4) is mixed with the circulating working medium from the heat exchanger B (3) and then enters the heat exchanger A (1) to complete circulation.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011535105.9A CN112539572A (en) | 2020-12-23 | 2020-12-23 | Quasi-three-stage compression super heat pump heat exchange device and cold and heat source temperature difference heat exchange method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011535105.9A CN112539572A (en) | 2020-12-23 | 2020-12-23 | Quasi-three-stage compression super heat pump heat exchange device and cold and heat source temperature difference heat exchange method |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112539572A true CN112539572A (en) | 2021-03-23 |
Family
ID=75017607
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011535105.9A Pending CN112539572A (en) | 2020-12-23 | 2020-12-23 | Quasi-three-stage compression super heat pump heat exchange device and cold and heat source temperature difference heat exchange method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112539572A (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101055133A (en) * | 2007-05-30 | 2007-10-17 | 李兴荣 | Electrically water-heated solid adsorption type air source heat pump system |
| CN110057127A (en) * | 2019-05-29 | 2019-07-26 | 华北电力大学 | A kind of coupling heat pump heat exchanger |
| CN110500910A (en) * | 2019-08-26 | 2019-11-26 | 华北电力大学 | A kind of caloic decoupling heat exchanger and its caloic decoupling method |
| CN110567189A (en) * | 2019-09-10 | 2019-12-13 | 华北电力大学 | Steam compression type absorption heat pump |
| CN111442553A (en) * | 2020-05-08 | 2020-07-24 | 华北电力大学 | Air source super heat pump and method for extracting heat by using same |
| US20200318836A1 (en) * | 2019-04-03 | 2020-10-08 | The Marley-Wylain Company | System and Method for Controlling a Variable-Speed Appliance Circulator |
| CN214333101U (en) * | 2020-12-23 | 2021-10-01 | 华北电力大学 | Super heat pump heat transfer device of quasi-tertiary compression |
-
2020
- 2020-12-23 CN CN202011535105.9A patent/CN112539572A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101055133A (en) * | 2007-05-30 | 2007-10-17 | 李兴荣 | Electrically water-heated solid adsorption type air source heat pump system |
| US20200318836A1 (en) * | 2019-04-03 | 2020-10-08 | The Marley-Wylain Company | System and Method for Controlling a Variable-Speed Appliance Circulator |
| CN110057127A (en) * | 2019-05-29 | 2019-07-26 | 华北电力大学 | A kind of coupling heat pump heat exchanger |
| CN110500910A (en) * | 2019-08-26 | 2019-11-26 | 华北电力大学 | A kind of caloic decoupling heat exchanger and its caloic decoupling method |
| CN110567189A (en) * | 2019-09-10 | 2019-12-13 | 华北电力大学 | Steam compression type absorption heat pump |
| CN111442553A (en) * | 2020-05-08 | 2020-07-24 | 华北电力大学 | Air source super heat pump and method for extracting heat by using same |
| CN214333101U (en) * | 2020-12-23 | 2021-10-01 | 华北电力大学 | Super heat pump heat transfer device of quasi-tertiary compression |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107939460B (en) | Expansion unit for high-power-level compressed air energy storage system | |
| CN113137293B (en) | Supercritical carbon dioxide circulation system and turbine adjusting and emergency shutdown method | |
| CN111594283A (en) | Two-stage turbine gas suspension ORC power generation system and control method | |
| CN111255720A (en) | Temperature control variable working condition operation system based on heat accumulation type compressed air energy storage | |
| CN209637831U (en) | A kind of system of thermal power plant's hot press in conjunction with space division system | |
| CN214333101U (en) | Super heat pump heat transfer device of quasi-tertiary compression | |
| CN113027552A (en) | Supercritical carbon dioxide power generation control system and operation mode | |
| CN108104887A (en) | The therrmodynamic system of double reheat | |
| CN103335440B (en) | Secondary throttling middle complete cooling double-working-condition refrigeration system | |
| CN116557094A (en) | Thermoelectric cooperative system integrating compressed air energy storage and operation method | |
| CN214371068U (en) | Large-temperature-rise super heat pump heat exchange device | |
| CN109751652B (en) | High back pressure and heat pump combined heat supply system of 300MW and above grade wet cooling unit | |
| CN112539572A (en) | Quasi-three-stage compression super heat pump heat exchange device and cold and heat source temperature difference heat exchange method | |
| CN114439563B (en) | Compressed air energy storage system and method for sliding pressure expansion | |
| CN114483231B (en) | Compressed air energy storage system and control method thereof | |
| CN203454447U (en) | Intermediate inadequacy cooling double operating conditions refrigeration system in secondary throttling | |
| CN111503703B (en) | Heat supply method of cogeneration unit and cogeneration unit | |
| CN212837970U (en) | Two-stage turbine gas suspension ORC power generation system | |
| CN210531098U (en) | Energy-efficient air compressor unit circulation system | |
| CN114635797A (en) | Control system for inlet air temperature of gas turbine | |
| CN103322718B (en) | Two-stage-throttling incomplete-intercooling double-duty refrigerating system | |
| CN109441785B (en) | Compressed air energy storage compressor system and control method thereof | |
| CN114922705B (en) | System and method for circulating split-flow repressing supercritical carbon dioxide | |
| CN111578555A (en) | Steam waste heat recovery compression refrigeration system and working method thereof | |
| CN113266441B (en) | Method and system for controlling starting operation of supercritical carbon dioxide recompression power generation system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |