CN210740796U - Cross-season energy storage type ice source heat pump system - Google Patents
Cross-season energy storage type ice source heat pump system Download PDFInfo
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Abstract
The utility model discloses a cross-season energy storage type ice source heat pump system, which comprises a heat pump host, wherein the heat pump host comprises a condenser and an evaporator, and a water outlet of the condenser is sequentially connected with a heat supply user end, a hot water pump and a water inlet of the condenser through pipelines; a liquid outlet of the evaporator is sequentially connected with the ethylene glycol pump, the dynamic ice slurry unit and a liquid inlet of the evaporator through pipelines; the water inlet of the dynamic ice slurry unit is sequentially connected with the cold water pump and a water source through pipelines, the water outlet of the dynamic ice slurry unit is connected with the seasonal ice storage pool through a pipeline, the water outlet of the dynamic ice slurry unit is also connected with the water inlet of a cooling user side, and the water outlet of the cooling user side is connected with the water inlet of the cold water pump; the water outlet of the condenser is also connected with the water inlet of the cross-season ice storage pool through a pipeline, and the water inlet of the condenser is sequentially connected with the cold water pump and the water outlet of the cross-season ice storage pool through pipelines. The utility model discloses stride energy storage type ice source heat pump system in season can improve the energy efficiency ratio under the cooling mode in summer.
Description
Technical Field
The utility model relates to a heat pump air conditioner technical field especially relates to a stride energy storage type ice source heat pump system in season.
Background
A heat pump is a device that transfers heat from a low temperature environment to a high temperature environment according to the principle of refrigeration. Every time the heat pump consumes 1 part of electric power (or other forms of energy), more than 3-4 parts of heat can be obtained, and the heat pump is a high-efficiency heat supply technical scheme. For water source heat pumps and ground source heat pumps which are widely applied, the basic principle is that heat is directly or indirectly extracted from surface water (water in rivers, lakes and seas) or underground water sources, and after the temperature grade is improved through the refrigeration cycle of a heat pump main machine, heat energy meeting the requirements of heat users is prepared, and the requirements of heating supply, domestic hot water and the like are met. Because the freezing point of water is 0 ℃, when the temperature of a water source after heat is extracted by the water and ground source heat pump devices is lower than 4 ℃, the risk of freezing the heat pump evaporator exists, the existing water and ground source heat pump units do not allow the temperature of a water outlet of the evaporator to be reduced to below 4 ℃ for operation, the temperature of a water inlet of the water source cannot be lower than 9 ℃ according to the calculation of a designed heat exchange temperature difference of 5 ℃, and the operation conditions of the water and ground source heat pump units are severely limited. In the Yangtze river basin of China, the climate of near freezing point with the surface water below 9 ℃ or even close to 0 ℃ in winter is a common climate phenomenon, particularly in the yellow river basin and the northern area, and the living areas of people in similar climate conditions in the world are also comparatively good. Although heat is extracted from underground water for a ground source heat pump, when cold and heat demands in winter and summer are greatly different, the temperature of underground water is gradually reduced along with the accumulation of the operation years of the heat pump, so-called cold accumulation occurs, and finally the temperature of an underground water source is lower than 9 ℃, so that the heat pump unit cannot be normally operated. The areas of North China, northwest China and northeast China all belong to areas with heat load far larger than cold load in summer, so that the phenomenon of cold accumulation of underground water is very common.
In conclusion, the water source heat pump is limited by the climate condition of near freezing point, and the ground source heat pump is limited by the phenomenon of cold accumulation, so that the heat pump system cannot normally operate when the heat demand is the most vigorous in winter, and temporary replacement means with higher energy consumption, such as electric heating, has to be adopted to make up the deficiency of the heat supply capacity, thereby not only increasing the energy consumption, but also improving the equipment and comprehensive construction investment of the heat supply system.
SUMMERY OF THE UTILITY MODEL
The utility model aims to overcome prior art's defect and not enough, provide and not restricted by "nearly freezing point" or "cold accumulation" climatic environment condition, and can improve the energy efficiency ratio of system under the cooling mode in summer and stride season energy storage type ice source heat pump system.
The purpose of the utility model can be realized by the following technical scheme: a cross-season energy storage type ice source heat pump system comprises a heat pump host, wherein the heat pump host comprises a condenser and an evaporator, and a water outlet of the condenser is sequentially connected with a heat supply user side, a hot water pump and a water inlet of the condenser through pipelines; a liquid outlet of the evaporator is sequentially connected with the ethylene glycol pump, the dynamic ice slurry unit and a liquid inlet of the evaporator through pipelines; the water inlet of the dynamic ice slurry unit is sequentially connected with the cold water pump and a water source through pipelines, the water outlet of the dynamic ice slurry unit is connected with the seasonal ice storage pool through a pipeline, the water outlet of the dynamic ice slurry unit is also connected with the water inlet of a cooling user side, and the water outlet of the cooling user side is connected with the water inlet of the cold water pump; the water outlet of the condenser is also connected with a water inlet of the cross-season ice storage pool through a pipeline, and the water inlet of the condenser is sequentially connected with a cold water pump and the water outlet of the cross-season ice storage pool through pipelines.
As a preferable technical scheme, a filter is arranged between a water outlet of the water source and a water inlet of the cold water pump, and a valve is arranged between the water outlet of the filter and the water inlet of the cold water pump.
As the preferred technical scheme, the water outlet of the cooling user end is connected with the water outlet of the valve arranged between the filter and the cold water pump.
As a preferable technical scheme, a valve is arranged between a water outlet of the dynamic ice slurry unit and a water inlet of the seasonal ice storage tank.
As the preferred technical scheme, a valve is arranged between the water outlet of the dynamic ice slurry machine set and the water inlet of the cooling user side.
As a preferred technical scheme, a valve is arranged between the water outlet of the condenser and the water inlet of the heat supply user side.
As a preferable technical scheme, the water outlet of the condenser is also connected with the water inlet of the cooling tower, and the water outlet of the cooling tower is connected with the water inlet of the hot water pump.
As a preferable technical scheme, a valve is arranged between the water outlet of the condenser and the water inlet of the cooling tower, and a valve is arranged between the water outlet of the cooling tower and the water inlet of the hot water pump.
As the preferred technical scheme, a valve is arranged between the water outlet of the condenser and a valve water inlet arranged between the condenser and the heat supply user side and the cooling tower, and a valve is arranged between the water inlet of the condenser and the water outlet of the hot water pump.
As a preferable technical scheme, a valve is arranged between a water outlet of the condenser and a water inlet of the seasonal ice storage pool, and a valve is arranged between the water inlet of the condenser and a water outlet of the cold water pump.
Compared with the prior art, the utility model, following advantage and beneficial effect have:
1. the utility model discloses an introduce dynamic ice slurry machine group in the heat pump system, because the ethylene glycol solution has lower freezing point temperature in the ethylene glycol circulation, can avoid freezing of heat pump evaporator. And the ice stored in the cross-season ice storage tank in winter or the melted low-temperature water is directly used as an excellent cooling cold source of the condenser of the refrigerating system, which is equivalent to the fact that the cold energy discharged to the environment by the system in winter is stored and transferred to the requirement of air conditioning refrigeration in summer, so that the operation energy efficiency ratio (COP) of the refrigerating system in summer is greatly improved, and the annual comprehensive operation energy consumption of cooling and heating is greatly reduced.
2. The utility model discloses an ice source heat pump system has possessed the ability of all-weather stable high-efficient operation under various climatic conditions, has thoroughly solved traditional water, the technological problem that ground source heat pump can't move under "nearly freezing point" weather or "cold accumulation" condition, increases the application scope of weather and environment by a wide margin.
Drawings
Fig. 1 is a schematic structural diagram of an energy storage type ice source heat pump system across seasons in an embodiment of the present invention.
Wherein: 1: a heat pump host; 1 a: a condenser; 1 b: an evaporator; 2: a dynamic ice slurry machine set; 3: a heat supply user side; 4: a cooling tower; 5: a cooling user terminal; 6: a cross-season ice storage pool; 7: a water source; 8: an ethylene glycol pump; 9: a hot water pump; 10: a cold water pump; 11: a cooling pump; 12-21: a valve; 22: and (3) a filter.
Detailed Description
The present invention will be described in further detail with reference to the following examples and drawings, but the present invention is not limited thereto.
As shown in fig. 1, an ice source heat pump system of a cross-season energy storage type includes a heat pump main machine 1 including a condenser 1a and an evaporator 1 b. The water outlet of the condenser 1a is connected with the heat supply user end 3, the hot water pump 9 and the water inlet of the condenser 1a in sequence through pipelines to form a closed loop. A valve 12 is arranged between the water outlet of the condenser 1a and the water inlet of the heat supply user end 3. The water outlet of the condenser 1a is also connected with the water inlet of the cooling tower 4, and the water outlet of the cooling tower 4 is connected with the water inlet of the hot water pump 9. A valve 13 is arranged between the water outlet of the condenser 1a and the water inlet of the cooling tower 4, and a valve 14 is arranged between the water outlet of the cooling tower 4 and the water inlet of the hot water pump 9. A valve 15 is arranged between the water outlet of the condenser 1a and the water inlets of the valve 12 and the valve 13, and a valve 16 is arranged between the water inlet of the condenser 1a and the water outlet of the hot water pump 9.
The liquid outlet of the evaporator 1b is connected with the glycol pump 8, the dynamic ice slurry unit 2 and the liquid inlet of the evaporator 1b in sequence through pipelines to form a closed loop. The dynamic ice slurry machine set is a special equipment for preparing 0 ℃ ice slurry, has no restriction requirement on the temperature of a water source, and can be directly, stably and efficiently prepared into the ice slurry no matter the temperature is higher than 9 ℃ or lower than 9 ℃ (even the temperature is as low as 0 ℃) as long as liquid water is used. The utility model discloses in can adopt the developments ice thick liquid unit among the prior art, like the developments ice thick liquid unit that chinese patent CN201520443800.0 disclosed.
The water inlet of the dynamic ice slurry machine set 2 is sequentially connected with the cold water pump 10 and the water source 7 through pipelines, a filter 22 is arranged between the water outlet of the water source 7 and the water inlet of the cold water pump 10, and a valve 21 is arranged between the water outlet of the filter 22 and the water inlet of the cold water pump 10.
The water outlet of the dynamic ice slurry machine set 2 is respectively connected with the water inlet of the seasonal ice storage tank 6 and the water inlet of the cooling user end 5 through pipelines, and the water outlet of the cooling user end 5 is connected with the water outlet of the valve 21. A valve 20 is arranged between the water outlet of the dynamic ice slurry machine set 2 and the water inlet of the seasonal ice storage tank 6, and a valve 19 is arranged between the water outlet of the dynamic ice slurry machine set 2 and the water inlet of the cold supply user end 5. The cooling user end 5 can be a fan coil, a combined air cabinet or other heat exchangers. The water outlet of the condenser 1a is connected with the water inlet of the cross-season ice storage pool 6 through a pipeline, and the water inlet of the condenser 1a is sequentially connected with the cold water pump 11 and the water outlet of the cross-season ice storage pool 6 through pipelines. A valve 17 is arranged between the water outlet of the condenser 1a and the water inlet of the seasonal ice storage pool, and a valve 18 is arranged between the water inlet of the condenser 1a and the water outlet of the cold water pump 11.
The utility model discloses a abandon ice type ice source heat pump system can divide into two kinds of modes operation of winter heat supply and summer cooling. The specific working principle is as follows:
(1) winter heating mode
The valves 12, 15 and 16 are opened, the valves 13, 14, 17 and 18 are closed, the condenser 1a, the valve 15, the valve 12, the heat supply user end 3, the hot water pump 9 and the valve 16 of the heat pump host 1 are sequentially connected through pipelines to form hot water circulation, the cooling tower 4 is shielded and does not participate in operation, and a refrigeration cycle consisting of the cross-season ice storage pool 6 and the cooling pump 11 is cut off and does not participate in operation. The low-temperature hot water is sent to a condenser 1a of the heat pump host 1 through a water pump 9, is heated to high-temperature hot water (for example, 40 ℃ or more than 45 ℃) meeting the heat supply target temperature, and then flows into a heat supply user end 3, the heat supply user end 3 is a fan coil, a radiator or other heat exchangers, the high-temperature hot water transfers heat to indoor air or domestic hot water and other heat user ends, the temperature is reduced to be low-temperature hot water (for example, 30 ℃ or 35 ℃), and then the low-temperature hot water is sent to the condenser 1a of the heat pump host 1 through the hot water pump 9 in a circulating mode to be.
The evaporator 1b of the heat pump main unit 1, the ethylene glycol pump 8 and the dynamic ice slurry unit 2 are connected in sequence to form an ethylene glycol cycle, and because the working temperature of the cycle is possibly lower than 0 ℃, the circulating medium adopts an ethylene glycol aqueous solution with a lower freezing point temperature and a mass concentration of 20%. The glycol water solution is cooled to-3 ℃ in the evaporator 1b of the heat pump main machine 1 (the standard parameter value of the dynamic ice slurry machine set disclosed in the Chinese patent CN 201520443800.0), then is sent into the dynamic ice slurry machine set 2 under the drive of the glycol pump 8, the temperature is raised to-1 ℃ after heat exchange with water in an ice making cycle in the dynamic ice slurry machine set 2, then the glycol water solution returns to the evaporator 1b through a pipeline, and is cooled to-3 ℃ in the evaporator 1b, and the circulation is repeated, so that the purpose of continuously obtaining heat from the dynamic ice slurry machine set 2 is achieved by the evaporator 1b of the heat pump main machine 1.
The valves 20 and 21 are opened, the valve 19 is closed, the water source 7, the filter 22, the valve 21, the cold water pump 10, the dynamic ice slurry unit 2, the valve 20 and the seasonal ice storage tank 6 are sequentially connected to form an ice making cycle, and the cold supply user end 5 is shielded and does not participate in operation. The water source 7 is a water source which can ensure that liquid water can be obtained under any temperature condition, such as tap water, reclaimed water, rivers, lakes and seas and the like. The cross-season ice storage pool 6 is a natural cave, a cellar, a pool, a large artificially-built pool or the like, solid ice can be stored in the cross-season ice storage pool for a long time in summer, and a cold source pool with low-temperature water can be formed even if melting loss occurs. The water source 7 and the seasonal ice storage pool 6 can be communicated (even the same pool, cellar, river, lake, sea, etc.) or isolated. Liquid water is pumped out from a water source 7 through a cold water pump 10, is filtered through a filter 22 and then is sent to a dynamic ice slurry unit 2, is cooled into fluidized ice slurry at 0 ℃ by glycol water solution at-3 ℃ in the glycol circulation, and the ice slurry is conveyed to a season-crossing ice storage tank 6 through a pipeline and is stored for a long time to wait for the cold supply season in summer for reuse.
The complete ice source heat pump heating operation mode is realized. In winter, even in the extremely cold weather of ice, snow and land, the liquid water can be conveniently taken out from the ice layer of water sources such as rivers, lakes and seas, and therefore the water source 7 meeting the requirements of the utility model is easy to find or configure. Therefore, no matter how low the ambient temperature is in winter, the energy storage type ice source heat pump system can continuously and stably operate for a long time in a cross-season manner, so that the energy storage type ice source heat pump system in the cross-season manner has the capability of all-weather stable and efficient operation under various climatic conditions, the technical problem that the traditional water and ground source heat pump cannot operate under the condition of 'near freezing point' climate or 'cold accumulation' is thoroughly solved, and the byproduct ice in winter is also stored for cooling in summer, thereby realizing great energy-saving benefits.
(2) Summer cooling mode
In summer, when cooling is performed, on the evaporator 1b side of the heat pump main unit 1, a glycol cycle is formed by sequentially connecting the evaporator 1b of the heat pump main unit 1, a glycol pump 8 and a dynamic ice slurry unit 2, wherein a circulating medium glycol aqueous solution is responsible for transmitting cooling capacity generated in the evaporator 1b of the heat pump main unit 1 in operation aiming at cooling to the dynamic ice slurry unit 2 through the glycol cycle, and the dynamic ice slurry unit 2 transmits the cooling capacity to the following cooling cycle.
The valve 19 is opened, the valve 20 is closed, the valve 21 is normally closed, and the valve 21 is opened for water supplement only when water supplement is needed in the pipeline of the cooling circulation system. The refrigeration system is characterized in that a dynamic ice slurry set 2, a valve 19, a refrigeration user side 5 and a cold water pump 10 are sequentially connected to form refrigeration circulation, chilled water (for example, 7 ℃) cooled by the ethylene glycol circulation in the dynamic ice slurry set 2 is sent to the refrigeration user side 5, cold energy is transferred to indoor air of a refrigeration user through heat exchange, air conditioning refrigeration is achieved, the temperature rises (for example, 12 ℃) after refrigeration, the chilled water is pumped into the dynamic ice slurry set 2 through the cold water pump 10 to be cooled through circulation, and the refrigeration circulation is repeated to achieve a refrigeration operation mode. The cooling user end can be a fan coil, a combined air cabinet or other heat exchangers.
For the common comfortable air conditioner cooling application occasions, the inlet and outlet water temperatures of the chilled water of the cooling user end 5 are generally 7 ℃ and 12 ℃, and the chilled water circulation side of the dynamic ice slurry unit 2 does not need to enter the working condition of preparing ice slurry, so that the dynamic ice slurry unit 2 is only equivalent to a heat exchanger under the direct cooling operation working condition in the summer cooling mode.
In summer, the heat pump main unit 1 is divided into the following 3 operation conditions on the condenser 1a side according to different environmental conditions:
(a) cooling circulation cooling
(b) Cooling by cooling tower
The valves 13 to 16 are opened, the valves 12, 17 and 18 are closed, the condenser 1a, the valve 15, the valve 13, the cooling tower 4, the valve 14, the hot water pump 9 and the valve 16 of the heat pump host 1 are sequentially connected to form a cooling water circulation (namely the hot water circulation), the heat supply user end 3 is shielded and does not participate in the operation, and the cooling circulation is also cut off and does not participate in the operation. The cooling water circulation at this time is a cooling water circulation of a general central air conditioning system, and the condensation heat generated in the condenser 1a of the heat pump main unit 1 in the operation for cooling is transferred to the cooling tower 4 through the cooling water circulation and discharged to the atmosphere.
(c) Combined cooling
Namely, the cooling circulation cooling and the cooling tower cooling are simultaneously and jointly operated. The valves 15 to 18 are now fully open and the open or closed state of the remaining valves, depending on whether or not the cycle in which they are operating, is as described above for each cycle. Under the operation condition of combined cooling, the cooling of the condenser 1b of the heat pump main unit 1 is respectively partially undertaken by the cooling circulation cooling and the cooling tower cooling, and the discharge of the condensation heat generated in the condenser 1b is jointly completed.
The choice of the 3 different operating conditions on the condenser side is determined for energy saving purposes. Generally, the cooling circulation cooling with the best energy efficiency is preferably selected, the cooling circulation cooling is equivalent to indirectly recycling cold discharged in winter, the operation energy efficiency of a cooling system is the highest, and the cooling system is switched to a combined cooling or even pure cooling tower cooling working condition only when the water temperature of the cross-season ice storage pool is increased to be insufficient to efficiently operate the cooling system (for example, the water temperature is higher than 30 ℃).
The above-mentioned embodiments only represent some embodiments of the present invention, and the description thereof is specific and detailed, but not to be construed as limiting the scope of the present invention. It should be noted that, for those skilled in the art, without departing from the spirit of the present invention, several variations and modifications can be made, which are within the scope of the present invention. Therefore, the protection scope of the present invention should be subject to the appended claims.
Claims (10)
1. A cross-season energy storage type ice source heat pump system is characterized by comprising a heat pump host machine, wherein the heat pump host machine comprises a condenser and an evaporator,
the water outlet of the condenser is sequentially connected with a heat supply user end, a hot water pump and the water inlet of the condenser through pipelines;
a liquid outlet of the evaporator is sequentially connected with the ethylene glycol pump, the dynamic ice slurry unit and a liquid inlet of the evaporator through pipelines;
the water inlet of the dynamic ice slurry unit is sequentially connected with the cold water pump and a water source through pipelines, the water outlet of the dynamic ice slurry unit is connected with the seasonal ice storage pool through a pipeline, the water outlet of the dynamic ice slurry unit is also connected with the water inlet of a cooling user side, and the water outlet of the cooling user side is connected with the water inlet of the cold water pump;
the water outlet of the condenser is also connected with a water inlet of the cross-season ice storage pool through a pipeline, and the water inlet of the condenser is sequentially connected with a cold water pump and the water outlet of the cross-season ice storage pool through pipelines.
2. The ice source heat pump system of claim 1, wherein a filter is arranged between a water outlet of the water source and a water inlet of the cold water pump, and a valve is arranged between the water outlet of the filter and the water inlet of the cold water pump.
3. The ice source heat pump system of claim 2, wherein the water outlet of the cold supply user end is connected with the water outlet of the valve arranged between the filter and the cold water pump.
4. The ice source heat pump system of claim 1, wherein a valve is arranged between the water outlet of the dynamic ice slurry unit and the water inlet of the seasonal ice storage tank.
5. The ice source heat pump system of claim 4, wherein a valve is arranged between the water outlet of the dynamic ice slurry unit and the water inlet of the cooling user end.
6. The ice source heat pump system of claim 1, wherein a valve is arranged between the water outlet of the condenser and the water inlet of the heat supply user side.
7. The ice source heat pump system of claim 6, wherein the water outlet of the condenser is further connected with the water inlet of the cooling tower, and the water outlet of the cooling tower is connected with the water inlet of the hot water pump.
8. The ice source heat pump system of claim 7, wherein a valve is arranged between the water outlet of the condenser and the water inlet of the cooling tower, and a valve is arranged between the water outlet of the cooling tower and the water inlet of the hot water pump.
9. The ice source heat pump system of claim 8, wherein a valve is provided between the water outlet of the condenser and a water inlet of a valve provided between the condenser and the heating user side and the cooling tower, and a valve is provided between the water inlet of the condenser and the water outlet of the hot water pump.
10. The ice source heat pump system of claim 1, wherein a valve is arranged between the water outlet of the condenser and the water inlet of the seasonal ice storage tank, and a valve is arranged between the water inlet of the condenser and the water outlet of the cold water pump.
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| CN201921752549.0U CN210740796U (en) | 2019-10-18 | 2019-10-18 | Cross-season energy storage type ice source heat pump system |
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| CN201921752549.0U CN210740796U (en) | 2019-10-18 | 2019-10-18 | Cross-season energy storage type ice source heat pump system |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111780303A (en) * | 2020-07-21 | 2020-10-16 | 南京工程学院 | Efficient heat source tower heat pump system for southern areas |
| CN115614859A (en) * | 2022-09-28 | 2023-01-17 | 清华大学 | Cross-season heat and cold supply system for hot summer, cold winter and summer |
-
2019
- 2019-10-18 CN CN201921752549.0U patent/CN210740796U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111780303A (en) * | 2020-07-21 | 2020-10-16 | 南京工程学院 | Efficient heat source tower heat pump system for southern areas |
| CN111780303B (en) * | 2020-07-21 | 2021-07-27 | 南京工程学院 | Efficient heat source tower heat pump system for southern areas |
| CN115614859A (en) * | 2022-09-28 | 2023-01-17 | 清华大学 | Cross-season heat and cold supply system for hot summer, cold winter and summer |
| CN115614859B (en) * | 2022-09-28 | 2024-07-19 | 清华大学 | Cross-season heat and cold supply system for summer heat and winter and summer |
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