CN202328574U - Air supply system of central air conditioner with two cooling coils - Google Patents
Air supply system of central air conditioner with two cooling coils Download PDFInfo
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- CN202328574U CN202328574U CN2011202638432U CN201120263843U CN202328574U CN 202328574 U CN202328574 U CN 202328574U CN 2011202638432 U CN2011202638432 U CN 2011202638432U CN 201120263843 U CN201120263843 U CN 201120263843U CN 202328574 U CN202328574 U CN 202328574U
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Abstract
The utility model provides an air supply system of a central air conditioner with two cooling coils. The air supply system comprises a return air cooling coil and a fresh air cooling coil independent from each other, wherein the return air cooling coil is mounted in a return air cooling coil heat exchanging room; the return air cooling coil heat exchanging room is mounted in a return air circulating pipeline; the return air cooling coil is used for cooling return air flowing through the return air circulating pipeline by using first-temperature chilled water flowing in the coil; the fresh air cooling coil is mounted in a fresh air cooling coil heat exchanging room; the fresh air cooling coil heat exchanging room is mounted in a fresh air pipeline; the fresh air cooling coil is used for dehumidifying and cooling fresh air flowing-in from the fresh air pipeline by using second-temperature chilled water flowing in the coil; the temperature of the second-temperature chilled water is lower than that of the first-temperature chilled water; and the air amount of the return air circulating pipeline is larger than that of the fresh air pipeline. According to the air supply system provided by the utility model, the coefficient of refrigeration is improved, and the energy is saved.
Description
Technical field
The utility model relates to two cooling coil central air-conditioning air feed systems.
Background technology
Along with the continuous progress of society and the continuous development of science and technology, People more and more is concerned about the earth that we depend on for existence now, and most countries also has been fully recognized that the importance of environment to our human development in the world.Each state is all taking active and effective measure to improve environment, reduces and pollutes.This is wherein important also to be that the most urgent problem is exactly an energy problem, fundamentally solve energy problem, except seeking the new energy, energy-conservation be crucial also be the most effectively important measures at present.
In China's energy-consuming main body, building energy consumption account very big proportion.Statistics shows that the ratio of building energy consumption in China's energy-consuming reached 27.6%.In developed country, building energy consumption generally accounts for 30～40% of total energy consumption.Therefore, along with the raising of development and national economy and living standards of the people, the building energy consumption of China will inevitably continue to rise, and building energy conservation work is shouldered heavy responsibilities.
In building energy consumption, the central air conditioner system energy consumption generally accounts for 40～60% ratio.And in the energy consumption of central air conditioner system; About 50～60% power loads are consumed in the handpiece Water Chilling Units refrigeration; About 25～30% power loads are consumed on the transmission & distribution of chilled water pump and cooling water pump, and about 15～20% power loads are consumed on the transmission & distribution power consumption of various blower fans.Owing to lack advanced control technology means and equipment; Present central air conditioner system is still continued to use conventional artificial way to manage and simple and easy switching control device mostly; Can not realize that air conditioner coolant flow quantity follows variation and the dynamic adjustments of terminal load; When operation at part load, cause a large amount of energy wastes, make China's energy for building inefficiency, the developed country of the equal weather conditions of unit construction area ability loss-rate exceeds 2～3 times.So the power saving of central air conditioner system is an importance of building energy conservation, central air conditioner system energy saving optimization analysis and research are extremely important.
At present, big-and-middle-sized central air conditioner system generally adopts the indirect refrigeration mode, and diabatic process is made up of five circulations such as room air circulation, chilled water circulation, cold-producing medium circulation, cooling water circulation, outdoor air circulations.Cooling coil is the equipment of room air and chilled water generation heat exchange, is the important component part of central air conditioner system.
Traditional central air-conditioning air conditioning room air feed system all is to be made up of a cover cooling coil, and such cover cooling coil has been born two kinds of tasks: cooling air conditioning room return air with the explicit load that produces of various electric equipments; Removing the sensible heat and the latent heat that newly advance fresh air, also is the dehumidifying and the cooling of fresh air.The air quantity of a part is bigger wherein, accounts for 70～80% of whole air quantity.Usually our 7 ℃ of used chilled waters just are used as the dehumidifying of fresh air, and 15 ℃ of chilled waters have enough been accomplished the task of cooling air conditioning room return air.In existing central air conditioner system, 7 ℃ of chilled waters not only are used for the dehumidifying of fresh air, also are used for the cooling of air conditioning room return air, this means that a large amount of chilled water colds is wasted.
Desirable cold-producing medium circulation is called contrary Carnot cycle, supposes that promptly the temperature of low-temperature heat source (object promptly is cooled) does
T 0 , the temperature of high temperature heat source (being surrounding medium) does
T K , then refrigeration working medium (freon etc.) in endothermic process does
T 0 , in exothermic process do
T K , in heat absorption and exothermic process, there is not the temperature difference between working medium and low-temperature heat source and the high temperature heat source in other words, promptly conduct heat and under isothermal, carry out, compress and expansion process is carried out under the hot lotus damaed cordition not having.
The heat that refrigeration working medium is drawn from the low-temperature heat source that is cooled
Q 0 :
Refrigeration working medium is to the high temperature heat source liberated heat
Q K :
Wherein
S 1 =
S 2 ,
S 3 =
S 4 , be the entropy in isentropic Compression (outer bound pair system acting), constant entropy expansion (the system's recovery original state) process.
Can know the merit that the refrigeration working medium circulation is consumed by the conservation of energy
W 0 , the merit that equals to compress consumption deducts the merit that expansion obtains.
Coefficient of refrigerating performance
ε K : the value that consumes the refrigerating capacity that specific work obtained.Then contrary Carnot cycle coefficient of refrigerating performance
ε K For:
In the contrary Carnot cycle, refrigeration working medium only with two thermal source heat-shifts, visible by following formula, the coefficient of refrigerating performance of contrary Carnot cycle has nothing to do with the character of working medium, only depends on the temperature of low-temperature heat source (object promptly is cooled)
T 0 And the temperature of high temperature heat source (being surrounding medium)
T K Reduce
T K , improve
T 0 , all can improve coefficient of refrigerating performance.
Desirable cold-producing medium circulation should be contrary Carnot cycle.Though contrary Carnot cycle is actually and can't realizes, it can be used for assessing the refrigerating efficiency of actual cold-producing medium circulation.
Generally speaking, as far as the refrigerant-cycle systems of central air-conditioning, low-temperature heat source (object promptly is cooled) is a chilled water, and high temperature heat source (being surrounding medium) is a cooling water; According to above-mentioned analysis, reduce cooling water temperature or improve chilled water temperature, all can improve the actual coefficient of refrigerating performance of central air-conditioning refrigerant-cycle systems.
The utility model will through improve chilled water temperature (
T 0 ) improve refrigerating efficiency.
Summary of the invention
The utility model technical problem to be solved is to provide a kind of pair of cooling coil central air-conditioning air feed system; To overcome the shortcoming that existing central air-conditioning air feed system is wasted a large amount of chilled water colds; A kind of air feed system that effectively utilizes the chilled water cold is provided, for central air-conditioning energy provides design.For this reason, the utility model adopts following technical scheme:
Said pair of cooling coil central air-conditioning air feed system comprises the separate cooling coil of two covers: return air cooling coil and new air cooling coil pipe; Wherein, Said return air cooling coil is installed in the return air cooling coil heat-exchanging chamber; Return air cooling coil heat-exchanging chamber is installed in the return air circulating line, the return air cooling coil utilization first temperature chilled water in its coil pipe of flowing through, and cool stream is through the return air of return air circulating line; Said new air cooling coil pipe is installed in the new air cooling coil pipe heat-exchanging chamber; New air cooling coil pipe heat-exchanging chamber is installed in the fresh wind tube road; The new air cooling coil pipe utilization second temperature chilled water in its coil pipe of flowing through dehumidifies and cools off the fresh air that flows into from the fresh wind tube road; The temperature of the said second temperature chilled water is lower than the temperature of the said first temperature chilled water; The air quantity of said return air circulating line is greater than the air quantity in said fresh wind tube road.
Adopting on the basis of technique scheme, the utility model also can adopt or combined with following further technical scheme:
The temperature of the said first temperature chilled water is 11～17 ℃, and the temperature of the said second temperature chilled water is 4～10 ℃; The optimum temperature of the said first temperature chilled water is 15 ℃, and the optimum temperature of the said second temperature chilled water is 7 ℃; The said first temperature chilled water and the second temperature chilled water are carried through chilled water circulating pump separately respectively; Said chilled water circulating pump is a variable frequency pump, can regulate the chilled water circular flow through the frequency conversion mode.
The said first temperature chilled water and the needed refrigerating capacity of cooling of the second temperature chilled water are respectively from first parallelly connected in the refrigerant circulation line refrigerant evaporator and second refrigerant evaporator; Said refrigerant circulation line is connected with coolant compressor, refrigerant condenser in turn; Be divided into the first refrigerant evaporator parallel branch and the second refrigerant evaporator parallel branch then, be connected to the entrance point of coolant compressor after two parallel branches are converged; Be connected with first expansion valve, first refrigerant evaporator and first evaporating pressure regulating valve in turn on the said first refrigerant evaporator parallel branch; Be connected with second expansion valve, second refrigerant evaporator and check-valves in turn on the said second refrigerant evaporator parallel branch; Through the regulating action of said first evaporating pressure regulating valve, make the evaporating pressure of first refrigerant evaporator be higher than the evaporating pressure of second refrigerant evaporator; Through the one-way flow effect of said check-valves, prevent that the higher gas refluence of the first refrigerant evaporator outlet pressure from getting into second refrigerant evaporator; Said first expansion valve, second expansion valve are electric expansion valve or heating power expansion valve.
Said pair of cooling coil central air-conditioning air feed system adopts the wind endless form to regulate indoor temperature; Said wind endless form comprises: through total cold wind that main intake stack blower fan is carried, be diverted to the air conditioning room air inlet of each air conditioning room after, the air conditioning room and flow out from the air conditioning room air outlet of flowing through becomes return air and imports main return air duct; By all import total return air that the return air of main return air duct forms carry through main return air duct blower fan and arrive at the end of main return air duct after shunt; Air-valve is discharged to the external world by discarded airduct road to total return air below 30% through discarded airduct road, and the total return air more than 70% becomes cold return air after return air circulating line air-valve gets into the return air circulating line and the return air cooling coil heat-exchanging chamber of flowing through; Air-valve becomes cold new wind by the fresh air that the fresh wind tube road flows into behind the new air cooling coil pipe heat-exchanging chamber of flowing through through the fresh wind tube road from the external world; Total cold wind by said cold return air and said cold new wind mix gets into main intake stack, carries through main intake stack blower fan.
Said main intake stack blower fan and said main return air duct blower fan are frequency conversion fan, can regulate air circulation through the frequency conversion mode.
Therefore, most chilled water all is the first temperature chilled water, and the second temperature chilled water only accounts for sub-fraction.The raising of chilled water temperature means chilled water (temperature
T 0 ) and cooling water (temperature
T K ) the temperature difference reduce, also just mean the raising of refrigerating efficiency.
The said pair of temperature that cooling coil central air-conditioning air feed system adopts the variable air rate mode to regulate air conditioning room; Said variable air rate mode is for regulating ventilation temperature, but regulates the air conditioning room temperature through the mode of regulating wind supply quantity; The mode of said adjusting wind supply quantity realizes in the following manner: main intake stack is connected with main return air duct through air conditioning room air inlet, air conditioning room, air conditioning room air outlet; But be separately installed with the air conditioning room air inlet air-valve of independent operating at each air conditioning room air inlet, regulate the wind supply quantity of each air conditioning room through the aperture that changes air conditioning room air inlet air-valve.
The utility model is on the single cooling coil air feed system of original central air-conditioning basis; Increased by one and overlapped independently cooler pan manage-style loop; Realized the separating of dehumidifying, cooling of the cooling of air conditioning room return air and the fresh air that replenishes from the external world; Improve the temperature of return air cooling coil chilled water (the first temperature chilled water), thereby improved the coefficient of refrigerating performance of system, reached energy-conservation effect.In order to realize the separation in two cover wind loops; Need to generate the chilled water of two kinds of different temperatures; The i.e. first temperature chilled water and the second temperature chilled water; The utility model is provided with different evaporating pressures and realizes that a coolant compressor drives two refrigerant evaporators simultaneously and produces the different temperatures chilled water through assembling evaporating pressure regulating valve and check-valves.Simultaneously,, adopt the variable air rate control mode, better meet user's demand, also reduced pipeline from chilled water to air conditioning room that carry, reduced the initial stage of system and dropped into through to the air conditioning room transporting cold wind.
The air conditioning room air feed system of the utility model uses when especially being fit to the central air-conditioning refrigeration, can realize the energy saving optimizing of system, for the user provides better service.
Description of drawings
Fig. 1 is the structural representation of the two cooling coil central air-conditioning air feed systems of the utility model.
Label is represented respectively as follows among the figure: 1, return air cooling coil, 2, return air cooling coil heat-exchanging chamber, 3, the first temperature chilled water circulation line, 4, new air cooling coil pipe; 5, new air cooling coil pipe heat-exchanging chamber, 6, the second temperature chilled water circulation line, 7, the first temperature chilled water circulating pump, 8, the second temperature chilled water circulating pump; 9, first refrigerant evaporator, 10, second refrigerant evaporator, 11, refrigerant circulation line, 12, the first refrigerant evaporator parallel branch; 13, the second refrigerant evaporator parallel branch, 14, first expansion valve, 15, second expansion valve, 16, first evaporating pressure regulating valve; 17, second evaporating pressure regulating valve, 18, check-valves, 19, coolant compressor, 20, refrigerant condenser; 21, main intake stack, 22, main intake stack blower fan, 23, main intake stack air velocity transducer, 24, main return air duct; 25, main return air duct blower fan, 26, discarded airduct road, 27, discarded airduct road air-valve, 28, the return air circulating line; 29, return air circulating line air-valve, 30, the fresh wind tube road, 31, fresh wind tube road air-valve, 32, fresh wind tube road air velocity transducer; 33, air conditioning room, 34, the air conditioning room air inlet, 35, air conditioning room air inlet air-valve, 36 air conditioning room air outlets.
The specific embodiment
Below in conjunction with accompanying drawing the utility model is further specified.
Shown in accompanying drawing 1; A kind of pair of cooling coil central air-conditioning air feed system; Its course of work is: refrigerant circulation line 11 is connected with coolant compressor 19, refrigerant condenser 20 in turn; Be divided into the entrance point that is connected to coolant compressor 19 after the first refrigerant evaporator parallel branch 12 and 13, two parallel branches of the second refrigerant evaporator parallel branch are converged then; The first refrigerant evaporator parallel branch 12 is connected with first expansion valve 14, first refrigerant evaporator 9 and first evaporating pressure regulating valve, 16, the second refrigerant evaporator parallel branches 13 in turn and is connected with second expansion valve 15, second refrigerant evaporator 10, second evaporating pressure regulating valve 17 and check-valves 18 in turn.
Evaporating pressure is under the certain situation of refrigerant temperature, the maximum pressure when cold-producing medium becomes gaseous state by liquid state.For a kind of cold-producing medium; When certain pressure, evaporating temperature immobilizes, and that is to say; Can produce different evaporating temperatures through the evaporating pressure that changes the refrigerant evaporator downstream; To obtain different refrigeration, produce the chilled water of different temperatures, to satisfy the water temperature requirements of return air cooling coil 1 and new air cooling coil pipe 4.
Be higher than the evaporating pressure with pairing second refrigerant evaporator 10 of the second temperature chilled water with the evaporating pressure of pairing first refrigerant evaporator 9 of the first temperature chilled water; Evaporating pressure through first evaporating pressure regulating valve, 16 configurations, first refrigerant evaporator 9 is the evaporating pressure that produces 15 ℃ of chilled waters; Evaporating pressure through second evaporating pressure regulating valve, 17 configurations, second refrigerant evaporator 10 is the evaporating pressure that produces 7 ℃ of chilled waters; Prevent that through check-valves 18 is set cold-producing medium from flowing to the second refrigerant evaporator parallel branch 13 (low pressure) by the first refrigerant evaporator parallel branch 12 (high pressure), the pressure behind the check-valves 18 is the pressure of inspiration(Pi) of coolant compressor 19.What deserves to be mentioned is that when the evaporating pressure after we need set second refrigerant evaporator 10 equated with the pressure of inspiration(Pi) of coolant compressor 19, second evaporating pressure regulating valve 17 became selectable unit (SU).
Heat exchange action takes place in cooling water and cold-producing medium in refrigerant condenser 20, the refrigerant gas of high temperature, high pressure is condensed into the refrigerant liquid of low temperature, high pressure in refrigerant condenser 20, and release heat.Low temperature, high pressure refrigerant liquid change the refrigerant liquid of low temperature, low pressure into after first expansion valve 14 and 15 throttlings of second expansion valve; And respectively in first refrigerant evaporator 9 and second refrigerant evaporator 10 with the first temperature chilled water and the second temperature chilled water generation heat exchange action; The cold-producing medium evaporation absorbs heat; Change the refrigerant gas of low temperature, low pressure into; In first refrigerant evaporator 9, produce 15 ℃ of first temperature chilled water simultaneously, in second refrigerant evaporator 10, produce 7 ℃ of first temperature chilled water.Coolant compressor 19 compression low temperature, low pressure refrigerant gas; Make it to become refrigerant condenser 20 acceptable high temperature, higher pressure refrigerant gas; Coolant compressor 19 is power sources of cold-producing medium circulation; Also be the main power consumption parts of whole cold-producing medium circulation,, can produce different refrigeration to satisfy the demand under the different cooling loads through changing the frequency of coolant compressor 19.
The first temperature chilled water circulating pump 7 drives the circulation of the first temperature chilled water at the first temperature chilled water circulation line 3; Return air cooling coil 1 is installed in the return air cooling coil heat-exchanging chamber 2; Return air cooling coil heat-exchanging chamber 2 is installed in the return air circulating line 28; The first temperature chilled water that return air cooling coil 1 utilizes in its coil pipe of flowing through, cool stream is through the return air of return air circulating line 28; In return air cooling coil heat-exchanging chamber 2; Flow through the first temperature chilled water and the return air generation heat exchange action that reclaims and discharge the return air circulating line 28 of flowing through behind a certain amount of discarded wind by main return air duct 24 in the return air cooling coil 1 through discarded airduct road 26; The first temperature chilled water temperature raises; The return air of return air circulating line 28 of flowing through obtains cooling, becomes cold return air.Be provided with main return air duct blower fan 25 in the main return air duct 24, for the conveying of the total return air of air conditioning room provides power.
The second temperature chilled water circulating pump 8 drives the circulation of the second temperature chilled water at the second temperature chilled water circulation line 6; New air cooling coil pipe 4 is installed in the new air cooling coil pipe heat-exchanging chamber 5; New air cooling coil pipe heat-exchanging chamber 5 is installed in the fresh wind tube road 30; The second temperature chilled water that new air cooling coil pipe 4 utilizes in its coil pipe of flowing through is to 30 fresh airs that flow into dehumidify and cool off from the fresh wind tube road; In new air cooling coil pipe heat-exchanging chamber 5; Flow through the second temperature chilled water and air-valve 31 is flowed into by fresh wind tube road 30 through the fresh wind tube road from the external world fresh air generation heat exchange action in the new air cooling coil pipe 4; The second temperature chilled water temperature raises; Play cooling and the effect that dehumidifies to newly advancing fresh air, produce cold new wind.
Total cold wind by said cold return air and said cold new wind mix gets into main intake stack 21, carries through main intake stack blower fan 22.
Through total cold wind that main intake stack blower fan 22 is carried, be diverted to the air conditioning room air inlet 34 of each air conditioning room 33 after, the air conditioning room 33 and flow out from air conditioning room air outlet 35 of flowing through becomes return air and imports main return air duct 24; By all import total return air that the return air of main return air duct 24 forms carry through main return air duct blower fan 25 and arrive at the end of main return air duct 24 after shunt; Air-valve 27 is discharged to the external world by discarded airduct road 26 to total return air below 30% through discarded airduct road, and the total return air more than 70% is through return air circulating line air-valve 29 entering return air circulating lines 28.
Be provided with fresh wind tube road air velocity transducer 32 in the fresh wind tube road 30 and can change the fresh wind tube road air-valve 31 that newly advances amount of fresh air, 30 cross-sectional areas in the fresh wind tube road
A 1 Under the known condition, through the new wind speed degree that records
v 1 (t)Can calculate in the certain hour
(t1～t2)The resh air requirement that gets into
Q 1 , calculating formula is:
Newly advance what of fresh air through regulating fresh wind tube road air-valve 31 apertures, can changing.Corresponding therewith; Be provided with discarded airduct road air-valve 27 in the discarded airduct road 26; Be provided with return air circulating line air-valve 29 in the return air circulating line 28; Through changing the aperture of discarded airduct road air-valve 27 and return air circulating line air-valve 29, can change discarded air quantity what and return air air circulation how much; In main intake stack 21, be provided with main intake stack air velocity transducer 23, at main intake stack 21 cross-sectional areas
A 2 Under the known condition, through the intake velocity that records
v 2 (t)Can calculate in the certain hour
(t1～t2)Get into total wind supply quantity of air conditioning room
Q 2 , calculating formula is:
New wind ratio is the proportion that resh air requirement accounts for total wind supply quantity, and calculating formula is:
Through the aperture of discarded airduct road air-valve 27, return air circulating line air-valve 29 and fresh wind tube road air-valve 31 is set, can realize different new wind ratios.For instance, we can be provided with resh air requirement and account for 20% of total intake, and at this moment discarded air quantity accounts for 20% of total wind supply quantity, and the return air amount accounts for 80% of total wind supply quantity.This ratio is not changeless, can regulate according to specific circumstances, to obtain best effect.
Two cooling coil central air-conditioning air feed systems of the utility model can be realized distributing rationally of the overall situation.Throttling arrangement that the central air-conditioning cold-producing medium recycles first expansion valve 16, second expansion valve 17 are preferably electric expansion valve, and the coolant compressor 19 of use is for realizing the frequency-changeable compressor of variable frequency adjustment.The central air-conditioning first temperature chilled water circulating pump 7, the second temperature chilled water circulating pump 8 are variable frequency pump, can change the freezing water yield through changing the water pump frequency of supply; Said main intake stack blower fan 22 is a frequency conversion fan with main return air duct blower fan 25, can change main intake stack 21 wind supply quantities through changing the blower fan frequency of supply.When customer charge changes; Through changing the frequency of coolant compressor 19, the first temperature chilled water circulating pump 7, the second temperature chilled water circulating pump 8, main intake stack blower fan 22 and main return air duct blower fan 25; Can avoid system on fixing operating point, to work; The reduction of frequency means the minimizing of energy consumption, under the prerequisite of meeting consumers' demand, reaches best energy-saving effect.Simultaneously, this is distributing rationally of a kind of integral body, and the application intelligent optimized Algorithm is confirmed the operating frequency of each variable ratio frequency changer equipment, and other consumer energy consumption improves the influence that is brought when avoiding a certain equipment energy consumption to reduce, and makes the whole energy consumption minimized of system.
The above-mentioned specific embodiment is used for the utility model of explaining; Be merely the preferred embodiment of the utility model; Rather than the utility model limited; In the protection domain of the spirit of the utility model and claim, any modification that the utility model is made, be equal to replacement, improvement etc., all fall into the protection domain of the utility model.
Claims (4)
1. two cooling coil central air-conditioning air feed systems is characterized in that it comprises the separate cooling coil of two covers: return air cooling coil and new air cooling coil pipe; Said return air cooling coil is installed in the return air cooling coil heat-exchanging chamber, and return air cooling coil heat-exchanging chamber is installed in the return air circulating line, the return air cooling coil utilization first temperature chilled water in its coil pipe of flowing through, and cool stream is through the return air of return air circulating line; Said new air cooling coil pipe is installed in the new air cooling coil pipe heat-exchanging chamber; New air cooling coil pipe heat-exchanging chamber is installed in the fresh wind tube road; The new air cooling coil pipe utilization second temperature chilled water in its coil pipe of flowing through dehumidifies and cools off the fresh air that flows into from the fresh wind tube road; The temperature of the said second temperature chilled water is lower than the temperature of the said first temperature chilled water; The air quantity of said return air circulating line is greater than the air quantity in said fresh wind tube road.
2. according to claim 1 pair of cooling coil central air-conditioning air feed system, the temperature that it is characterized in that the said first temperature chilled water is 11～17 ℃, the temperature of the said second temperature chilled water is 4～10 ℃; The optimum temperature of the said first temperature chilled water is 15 ℃, and the optimum temperature of the said second temperature chilled water is 7 ℃; The said first temperature chilled water and the second temperature chilled water are carried through chilled water circulating pump separately respectively; Said chilled water circulating pump is a variable frequency pump, can regulate the chilled water circular flow through the frequency conversion mode.
3. according to claim 2 pair of cooling coil central air-conditioning air feed system is characterized in that the said first temperature chilled water and the needed refrigerating capacity of cooling of the second temperature chilled water are respectively from first parallelly connected in the refrigerant circulation line refrigerant evaporator and second refrigerant evaporator; Refrigerant circulation line is connected with coolant compressor, refrigerant condenser in turn, is divided into the first refrigerant evaporator parallel branch and the second refrigerant evaporator parallel branch then, is connected to the entrance point of coolant compressor after two parallel branches are converged; Be connected with first expansion valve, first refrigerant evaporator and first evaporating pressure regulating valve in turn on the said first refrigerant evaporator parallel branch; Be connected with second expansion valve, second refrigerant evaporator and check-valves in turn on the said second refrigerant evaporator parallel branch; Through the regulating action of said first evaporating pressure regulating valve, make the evaporating pressure of first refrigerant evaporator be higher than the evaporating pressure of second refrigerant evaporator; Through the one-way flow effect of said check-valves, prevent that the higher gas refluence of the first refrigerant evaporator outlet pressure from getting into second refrigerant evaporator; Said first expansion valve, second expansion valve are electric expansion valve or heating power expansion valve.
4. according to claim 1,2 or 3 described pairs of cooling coil central air-conditioning air feed systems, it is characterized in that said main intake stack blower fan and said main return air duct blower fan are frequency conversion fan, can regulate air circulation through the frequency conversion mode.
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| Application Number | Priority Date | Filing Date | Title |
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| CN2011202638432U CN202328574U (en) | 2011-07-25 | 2011-07-25 | Air supply system of central air conditioner with two cooling coils |
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| CN2011202638432U CN202328574U (en) | 2011-07-25 | 2011-07-25 | Air supply system of central air conditioner with two cooling coils |
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| CN102278795A (en) * | 2011-07-25 | 2011-12-14 | 浙江大学 | Central air-conditioning air supply system adopting double cooling coils |
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2011
- 2011-07-25 CN CN2011202638432U patent/CN202328574U/en not_active Withdrawn - After Issue
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| CN102278795A (en) * | 2011-07-25 | 2011-12-14 | 浙江大学 | Central air-conditioning air supply system adopting double cooling coils |
| CN103105015A (en) * | 2013-03-07 | 2013-05-15 | 西南科技大学 | Energy-saving type double-evaporator two-stage compression refrigerating equipment used for floor radiant cooling |
| CN103267321A (en) * | 2013-05-30 | 2013-08-28 | 深圳中元宏康科技有限公司 | Operating room air purifying system |
| CN103267321B (en) * | 2013-05-30 | 2016-08-10 | 深圳橙果医疗科技有限公司 | Operating room air cleaning system |
| CN106440267A (en) * | 2016-12-02 | 2017-02-22 | 青岛海尔空调器有限总公司 | Energy-saving control method for air conditioner |
| CN106524355A (en) * | 2016-12-02 | 2017-03-22 | 青岛海尔空调器有限总公司 | Air-conditioner energy-saving control method |
| CN106594871A (en) * | 2016-12-02 | 2017-04-26 | 青岛海尔空调器有限总公司 | Air conditioner energy-saving control method |
| CN106594988A (en) * | 2016-12-02 | 2017-04-26 | 青岛海尔空调器有限总公司 | Energy-saving control method for air conditioner |
| CN106642559A (en) * | 2016-12-02 | 2017-05-10 | 青岛海尔空调器有限总公司 | Energy-saving method for air conditioner |
| CN106705358A (en) * | 2016-12-02 | 2017-05-24 | 青岛海尔空调器有限总公司 | Energy-saving control method for air conditioner |
| CN106765563A (en) * | 2016-12-02 | 2017-05-31 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106765915A (en) * | 2016-12-02 | 2017-05-31 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106765914A (en) * | 2016-12-02 | 2017-05-31 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
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| CN106765910A (en) * | 2016-12-02 | 2017-05-31 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106594988B (en) * | 2016-12-02 | 2019-09-03 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106524355B (en) * | 2016-12-02 | 2019-10-01 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106765563B (en) * | 2016-12-02 | 2019-11-05 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106594871B (en) * | 2016-12-02 | 2019-11-05 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106642559B (en) * | 2016-12-02 | 2019-11-05 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106765914B (en) * | 2016-12-02 | 2019-11-05 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106765915B (en) * | 2016-12-02 | 2019-11-05 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106765908B (en) * | 2016-12-02 | 2019-11-05 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106705358B (en) * | 2016-12-02 | 2019-11-05 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN106440267B (en) * | 2016-12-02 | 2019-11-05 | 青岛海尔空调器有限总公司 | Air conditioner energy saving control method |
| CN113375293A (en) * | 2021-06-01 | 2021-09-10 | 青岛海尔空调器有限总公司 | Display method and device for air conditioner and air conditioner |
| WO2022252655A1 (en) * | 2021-06-01 | 2022-12-08 | 青岛海尔空调器有限总公司 | Display method and apparatus for use in air conditioner, and air conditioner |
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