US20190017712A1 - High-efficiency extra-large cooling capacity series chiller in energy station - Google Patents

High-efficiency extra-large cooling capacity series chiller in energy station Download PDF

Info

Publication number
US20190017712A1
US20190017712A1 US16/132,166 US201816132166A US2019017712A1 US 20190017712 A1 US20190017712 A1 US 20190017712A1 US 201816132166 A US201816132166 A US 201816132166A US 2019017712 A1 US2019017712 A1 US 2019017712A1
Authority
US
United States
Prior art keywords
evaporator
condenser
chiller
chilled water
cooling capacity
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.)
Abandoned
Application number
US16/132,166
Inventor
Ting ZHAN
Hao Sun
Pengyue JI
Junwu LU
Zhenfeng ZHU
Bin Pan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Jiangsu Quyu Energy Co Ltd
Original Assignee
Jiangsu Quyu Energy Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority to CN201810500187.XA priority Critical patent/CN108489132A/en
Priority to CN201810500187X priority
Application filed by Jiangsu Quyu Energy Co Ltd filed Critical Jiangsu Quyu Energy Co Ltd
Assigned to JIANGSU QUYU ENERGY CO., LTD. reassignment JIANGSU QUYU ENERGY CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JI, PENGYUE, LU, JUNWU, PAN, Bin, SUN, HAO, ZHAN, Ting, ZHU, ZHENFENG
Publication of US20190017712A1 publication Critical patent/US20190017712A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • F24F3/065Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units with a plurality of evaporators or condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30Arrangement or mounting of heat-exchangers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24HEATING; RANGES; VENTILATING
    • F24FAIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • F24F3/08Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units with separate supply and return lines for hot and cold heat-exchange fluids i.e. so-called "4-conduit" system
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/04Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00Details of evaporators; Details of condensers
    • F25B2339/02Details of evaporators
    • F25B2339/024Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0242Evaporators with refrigerant in a vessel in which is situated a heat exchanger having tubular elements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00Details of evaporators; Details of condensers
    • F25B2339/04Details of condensers
    • F25B2339/047Water-cooled condensers
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/06Several compression cycles arranged in parallel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25BREFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21Temperatures
    • F25B2700/2117Temperatures of an evaporator
    • F25B2700/21171Temperatures of an evaporator of the fluid cooled by the evaporator
    • F25B2700/21173Temperatures of an evaporator of the fluid cooled by the evaporator at the outlet

Abstract

A high-efficiency extra-large cooling capacity series water-cooled chiller in an energy station, comprising at least two evaporators, a condenser, a chilled water main pipe and a cooling water main pipe, all the evaporators form an evaporator series set in a series connection form, both ends of the evaporator series set are connected to the chilled water main pipe, and each evaporator is provided with a refrigerant channel for connecting the condenser. According to the present invention, the evaporators are set in series combination. When the load is very low, one compressor operates at a high load or at full load, that is, the compressor continuously operates in a high efficiency zone, which avoids multiple compressors operating in an inefficient zone, and high total power.

Description

  • This application claims priority to Chinese Patent Application Ser. No. CN 201810500187X filed on May 23, 2018.
  • TECHNICAL FIELD
  • The present invention relates to a water-cooled chiller, and more particularly, to a high-efficiency extra-large cooling capacity series water-cooled chiller in an energy station using a multistage pipe embedded evaporator.
  • BACKGROUND
  • Present water-cooled chillers, compressors, evaporators, condensers and expansion valves are compactly assembled together. When multiple chillers are used in parallel, chilled water with higher temperature flew back at the tail end of the chiller will enter each parallel chiller along branches of chilled water return main pipes. After being cooled, the chilled water will be incorporated to the chilled water main supply pipes through each chilled water supply branch, and then supplied to the tail end. This type of chiller takes up a lot of space because of the connection of multiple branches and the reasonable installation space required by the chiller itself.
  • The chiller operates at high load rates with high efficiency and operates at low and medium loads with low efficiency. When the tail end load is small, that is, the cooling demand is small, but the chilled water flow demand is large because the cooling area is large, a single chiller can operate in the high efficiency zone when the existing chiller is used in the case that the number of operating chillers is small. The total power is lower, but due to the limitation of the pipe diameter of the evaporator, the flow of the chilled water delivered is small, such that there is insufficient chilled water flow at the tail end, and the cooling effect is poor in some areas. If the number of operating chillers is large, the chilled water delivered can meet the tail end demand, but a single chiller operates in a low-load, low-efficiency zone, which has a high total power. Because the chillers are selected according to the highest cooling load, the chillers operate under the above-mentioned low-load conditions in most of the time, and the energy consumption of a cold water host is high.
  • In order to ensure the safe operation of the chiller, no matter the chiller operates in high or low and medium loads, the chilled water pump must continue to provide a basic fixed head consumption for the chiller, generally no less than 80 kPa, resulting in high energy consumption of the chilled water pump.
  • The designed chilled water supply and return temperature difference of the existing chiller is generally 5 to 8□. When the actual temperature difference is higher or lower than the design value during operation, the efficiency of the chiller will decrease. In addition, the existing chillers cannot achieve a given chilled water return temperature by adjusting the chilled water supply temperature (6 to 12□) in a wide range. Therefore, for the project which requires frequently changed temperature difference at the tail end and can keep comfortable at a fixed return temperature, the existing chiller cannot provide the cooling capacity continuously, efficiently and effectively.
  • SUMMARY
  • Object of the present invention: in order to overcome the deficiencies in the prior art, a high-efficiency extra-large cooling capacity series water-cooled chiller in an energy station with high operating efficiency and small energy consumption and using a multistage pipe embedded evaporator is provided.
  • Technical solutions: in order to achieve the above object, the present invention provides a high-efficiency extra-large cooling capacity series water-cooled chiller in an energy station comprising at least two evaporators, a condenser, a chilled water main pipe and a cooling water main pipe. All the evaporators form an evaporator series set in a series connection form, both ends of the evaporator series set are connected to the chilled water main pipe, and each evaporator is provided with a refrigerant channel for connecting the condenser, the refrigerant channel is divided into two parts comprising a refrigerant supply channel and a refrigerant return channel, the refrigerant supply channel and the refrigerant return channel are respectively provided with a relief valve and the compressor, the evaporator is internally provided with a temperature sensor for collecting a temperature of chilled water leaving the evaporator, and the temperature sensor is connected to the corresponding compressor.
  • The design principle of the present invention is as follows: the evaporators are arranged in series combination, and each evaporator can reduce the temperature of the chilled water by about 3 degrees at the rated flow rate and the full load of the compressor. When the load is very low, one compressor operates at a high load or at full load, that is, the compressor continuously operates in a high efficiency zone, which avoids multiple compressors being operated in an inefficient zone, and high total power, so that the energy consumption of the chiller is greatly saved. Moreover, because the series structure is adopted, one evaporator operation can provide the same chilled water flow as that of three evaporator operation, which can meet the chilled water flow demand at the tail end.
  • Further, the evaporator series set is embedded in the chilled water main pipe.
  • Further, an evaporating shell pass of the evaporator serves as a refrigerant channel, and the evaporator is internally provided with a plurality of evaporating tube passes as chilled water channels. The evaporating tube pass is a single-pass structure, a water pressure drop of each evaporator is 6 to 8 kPa, and the water pressure drop is 18 to 24 kPa if three evaporators are connected in series, which is obviously smaller than a water pressure drop (50 to 100 kPa) of an evaporator of the current chiller, so that an energy consumption of a chilled water pump can be reduced.
  • Further, the condenser is embedded in the cooling water main pipe, a condensing shell pass of the condenser serves as a refrigerant channel and the condenser is internally provided with a plurality of condensing tube passes as cooling water channels, such that both the refrigerant and the cooling water have respectively independent channels and will not contact and interfere with each other. The refrigerant flows between the separate evaporators and the overall condenser. No matter how many evaporators are operating, the refrigerant can maximize the heat exchange area in the condenser and improve the operating efficiency of each compressor.
  • Further, a total length of the refrigerant channel is no more than 200 meters, and a length of the refrigerant channel should not be too long, which may affect the using effect of the refrigerant.
  • Further, the condenser is placed on the ground, and the evaporator is suspended above the condenser. The evaporator does not occupy the floor space, which can reduce an area of a central air-conditioning room.
  • Further, the evaporator and the chilled water main pipe are connected by a reduction nipple, so that the evaporators of different pipe diameters can be perfectly jointed with the chilled water main pipe.
  • Further, a total cross-sectional area of the condensing tube passes is no less than a cross-sectional area of the chilled water main pipe, and a total cross-sectional area of the condensing tube passes is no less than a cross-sectional area of the cooling water main pipe, thus reducing the resistance for the chilled water and the cooling to flow in and out of the evaporator and the condenser respectively, and making the chilled water and the cooling water flow in and out more smoothly.
  • Beneficial effects: compared with the prior art, the present invention has the following advantages.
  • 1. The evaporators are set in series combination. When the load is very low, one compressor operates at a high load or at full load, that is, the compressor continuously operates in a high efficiency zone, which avoids multiple compressors being operated in an inefficient zone, and high total power, so that the energy consumption of the chiller is greatly saved.
  • 2. Both the tube passes and the shell passes are single-pass structures, so that the chilled water and the cooling water do not require a return stroke. Compared with the original return structure, the flow resistance of the chilled water and the cooling water is reduced, thereby reducing the energy consumption.
  • 3. Because of the series structure, one evaporator operation can provide the same chilled water flow as that of multiple evaporator operation, which can meet the chilled water flow demand at the tail end, so that each compressor can meet the chilled water demand at the tail end on the basis of keeping high efficiency operating, which not only guarantees the cooling effect, but also greatly saves the energy consumption and reduces the operating costs, thus being very suitable for large-area centralized cooling.
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • FIG. 1 is a structural schematic diagram of the present invention;
  • FIG. 2 is a sectional drawing of an evaporator;
  • FIG. 3 is a sectional drawing of a condenser;
  • FIG. 4 is a structural schematic diagram of a chiller in a second embodiment; and
  • FIG. 5 is a partial schematic diagram of a flow direction of cooling water.
  • DETAILED DESCRIPTION
  • The invention will be further clarified with reference to the accompanying drawings and specific embodiments. It should be appreciated that these embodiments are intended to illustrate the invention and not to limit the scope of the invention. Modifications of equivalent forms to the invention made by those skilled in the art after reading the invention all fall within the scope defined by the appended claims of the application.
  • First Embodiment
  • As shown in FIG. 1 to FIG. 3, the present invention provides a high-efficiency extra-large cooling capacity series water-cooled chiller in an energy station comprising three evaporators 1, a condenser 3, a chilled water main pipe 21 and a cooling water main pipe 31. The three evaporators 1 are embedded in the chilled water main pipe 21, each evaporator 1 is provided with a refrigerant channel 5 for connecting the condenser 3, each refrigerant channel 5 is divided into two parts comprising a refrigerant supply channel 51 and a refrigerant return channel 52, the refrigerant supply channel 51 and the refrigerant return channel 52 are respectively provided with a relief valve 4 and the compressor 2, the evaporator 1 is internally provided with a temperature sensor 10 for collecting a temperature of chilled water leaving the evaporator 1, and the temperature sensor 10 is connected to the corresponding compressor 2. The evaporator 1 adopts a structure of a full liquid evaporator, an evaporating shell pass 11 of the evaporator 1 serves as a refrigerant channel, and the evaporator 1 is internally provided with a plurality of evaporating tube passes 12 as chilled water channels, and the condenser 3 is embedded in the cooling water main pipe 31. The condenser 3 adopts a structure of a full liquid condenser, a condensing shell pass 32 of the condenser 3 serves as a refrigerant channel, and the condenser 3 is internally provided with a plurality of condensing tube passes 33 as cooling water channels, and a total length of the refrigerant channel 5 is 100 meters. The condenser 3 is placed on the ground and the evaporator 1 is suspended above the condenser 3. Both the evaporator 1 and the chilled water main pipe 21, and the condenser 3 and the cooling water main pipe 31 are connected by a reduction nipple. A total cross-sectional area of the evaporating tube passes 12 is no less than a cross-sectional area of the chilled water main pipe 21, and a total cross-sectional area of the condensing tube passes 33 is no less than a cross-sectional area of the cooling water main pipe 31.
  • Second Embodiment
  • A target temperature value of a chilled water supply temperature of the chiller was preset. As shown in FIGS. 2 and 4, three evaporators 1 were respectively recorded as an evaporator a, an evaporator b and an evaporator c, and chilled water return water 6 entered an evaporating tube pass 12 of the evaporator a through a chilled water main pipe 21, a refrigerant was located in an evaporating shell pass 11 of the evaporator a, and the refrigerant exchanged heat with the chilled water return water 6 in the evaporating tube pass 12 to become a gaseous state, the temperature of the chilled water return water 6 dropped, a relief valve 4 a was opened, the gaseous refrigerant entered a refrigerant supply channel 51 a, and then flowed into a condenser 3. The gaseous refrigerant flew in a condensing shell pass 32 of the condenser 3, and the gaseous refrigerant was turned into a liquid state by the compression of a compressor 2 a and returned to the evaporator a through a refrigerant circuit channel 52 a. The process was circulated in this way.
  • Therefore, when the compressor 2 a and the condenser 3 were operating, the refrigerant flew between the evaporator 1 and the entire condenser 3, completing the process of transferring heat from the evaporator 1 to the condenser 3, and the temperature of the chilled water dropped. A temperature sensor 10 a collected a temperature value of the chilled water leaving the evaporator a as the operation basis for a compressor 2 b. When the temperature value collected by the temperature sensor 10 a was higher than the preset target temperature value, the temperature sensor 10 a sent a start instruction to the compressor 2 b.
  • The chilled water return water 6 entered the evaporator b, a relief valve 4 b was in an opened state. The gaseous refrigerant entered a refrigerant supply channel 51 b, and then flew into the condenser 3. The gaseous refrigerant flew in the condensing shell pass 32 of the condenser 3, and the gaseous refrigerant was turned into a liquid state by the compression of a compressor 2 b and returned to the evaporator b through a refrigerant return channel 52 b. The process was circulated in this way.
  • Therefore, when the compressor 2 b and the condenser 3 were operating, the refrigerant flew between the evaporator 1 and the entire condenser 3, completing the process of transferring heat from the evaporator 1 to the condenser 3, and the temperature of the chilled water dropped again. A temperature sensor 10 b collected a temperature value of the chilled water leaving the evaporator b as the operation basis for a compressor 2 c. When the temperature value collected by the temperature sensor 10 b was higher than the preset target temperature value, the temperature sensor 10 b sent a start instruction to the compressor 2 c.
  • The chilled water return water 6 entered the evaporator c, a relief valve 4 c was in an opened state. The gaseous refrigerant entered a refrigerant supply channel 51 c, and then flew into the condenser 3. The gaseous refrigerant flew in the condensing shell pass 32 of the condenser 3, and the gaseous refrigerant was turned into a liquid state by a compressor 2 c and returned to the evaporator c through a refrigerant return channel 52 c. When the compressor 2 c and the condenser 3 were operating, the refrigerant flew between the evaporator 1 and the entire condenser 3, completing the process of transferring heat from the evaporator 1 to the condenser 3, and the temperature of the chilled water dropped again. A temperature sensor 10 c collected a temperature value of the chilled water leaving the evaporator c, and the chilled water was outputted through the chilled water main pipe 21 as chilled water supply water 7.
  • Third Embodiment
  • A target temperature value of a chilled water supply temperature of the chiller was preset. As shown in FIGS. 2 and 4, three evaporators 1 were respectively recorded as an evaporator a, an evaporator b and an evaporator c, and chilled water return water 6 entered an evaporating tube pass 12 of the evaporator a through a chilled water main pipe 21, a refrigerant was located in an evaporating shell pass 11 of the evaporator a, and the refrigerant exchanged heat with the chilled water return water 6 in the evaporating tube pass 12 to become a gaseous state, the temperature of the chilled water return water 6 dropped, a relief valve 4 a was in opened state, the gaseous refrigerant entered a refrigerant supply channel 51 a, and then flowed into a condenser 3. The gaseous refrigerant flew in a condensing shell pass 32 of the condenser 3, and the gaseous refrigerant was turned into a liquid state by a compressor 2 a and returned to the evaporator a through a refrigerant return channel 52 a. When the compressor 2 a and the condenser 3 were operating, the refrigerant flew between the evaporator 1 and the entire condenser 3, completing the process of transferring heat from the evaporator 1 to the condenser 3, and the temperature of the chilled water dropped. A temperature sensor 10 a collected a temperature value of the chilled water leaving the evaporator a as the operation basis for a compressor 2 b; when the temperature value collected by the temperature sensor 10 a was lower than the preset target temperature value, a relief valve 4 b, a relief valve 4 c, the compressor 2 b and a compressor 2 c were all in a closed and stopped state, which did not cool the chilled water return water 6. The chilled water return water 6 passed through the evaporator b and the evaporator c in sequence, and was finally outputted through the chilled water main pipe 21 as chilled water supply water 7.
  • Fourth Embodiment
  • As shown in FIG. 1 and FIG. 5, a condenser 3 was connected to a cooling water main pipe 31, and was powered by a cooling pump. Cooling water return water 8 cooled by a cooling tower entered the condenser 3 to cool the condenser 3, and take away the heat of the condenser 3. Cooling water effluent 9 flew to the cooling tower 91, and the process was circulated in this way.
  • It can be known from the second embodiment and the second embodiment that no matter how many compressors 2 are compressor, each compressor 2 can maintain full load operation, avoiding the compressor 2 in a low load operating state. The operating efficiency of the chiller is very efficient, and the energy consumption is reduced.

Claims (13)

What is claimed is:
1. A high-efficiency extra-large cooling capacity series chiller in an energy station, comprising at least two evaporators (1), a condenser (3), a chilled water main pipe (21) and a cooling water main pipe (31), wherein all the evaporators (1) form an evaporator series set in a series connection form, both ends of the evaporator series set are connected to the chilled water main pipe (21), and each evaporator (1) is provided with a refrigerant channel (5) for connecting the condenser (3), the refrigerant channel (5) is divided into two parts comprising a refrigerant supply channel (51) and a refrigerant return channel (52), the refrigerant supply channel (51) and the refrigerant return channel (52) are respectively provided with a relief valve (4) and the compressor (2), the evaporator (1) is internally provided with a temperature sensor (10) for collecting a temperature of chilled water leaving the evaporator (1), and the temperature sensor (10) is connected to the corresponding compressor (2).
2. The high-efficiency extra-large cooling capacity series water-cooled chiller in an energy station according to claim 1, wherein the evaporator series set is embedded in the chilled water main pipe (21).
3. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 1, wherein an evaporating shell pass (11) of the evaporator (1) serves as a refrigerant channel, and the evaporator (1) is internally provided with a plurality of evaporating tube passes (12) as chilled water channels.
4. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 1, wherein the condenser (3) is embedded in the cooling water main pipe (31), a condensing shell pass (32) of the condenser (3) serves as a refrigerant channel, and the condenser (3) is internally provided with a plurality of condensing tube passes (33) as cooling water channels.
5. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 1, wherein a total length of the refrigerant channel (5) is no more than 200 meters.
6. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 1, wherein the condenser (3) is placed on the ground and the evaporator (1) is suspended above the condenser (3).
7. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 1, wherein the evaporator (1) and the chilled water main pipe (21) are connected by a reduction nipple.
8. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 3, wherein a total cross-sectional area of the evaporating tube passes (12) is no less than a cross-sectional area of the chilled water main pipe (21).
9. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 4, wherein a total cross-sectional area of the condensing tube passes (33) is no less than a cross-sectional area of the cooling water main pipe (31).
10. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 2, wherein the condenser (3) is placed on the ground and the evaporator (1) is suspended above the condenser (3).
11. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 3, wherein the condenser (3) is placed on the ground and the evaporator (1) is suspended above the condenser (3).
12. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 4, wherein the condenser (3) is placed on the ground and the evaporator (1) is suspended above the condenser (3).
13. The high-efficiency extra-large cooling capacity series chiller in an energy station according to claim 5, wherein the condenser (3) is placed on the ground and the evaporator (1) is suspended above the condenser (3).
US16/132,166 2018-05-23 2018-09-14 High-efficiency extra-large cooling capacity series chiller in energy station Abandoned US20190017712A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201810500187.XA CN108489132A (en) 2018-05-23 2018-05-23 The efficiently especially big cold series connection handpiece Water Chilling Units of energy source station
CN201810500187X 2018-05-23

Publications (1)

Publication Number Publication Date
US20190017712A1 true US20190017712A1 (en) 2019-01-17

Family

ID=63352195

Family Applications (1)

Application Number Title Priority Date Filing Date
US16/132,166 Abandoned US20190017712A1 (en) 2018-05-23 2018-09-14 High-efficiency extra-large cooling capacity series chiller in energy station

Country Status (2)

Country Link
US (1) US20190017712A1 (en)
CN (1) CN108489132A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3926253A3 (en) * 2020-06-17 2022-04-20 Carrier Corporation Vapor compression system and method for operating heat exchanger

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111947259B (en) * 2020-08-19 2021-07-02 江苏区宇能源有限公司 Regional energy station jointly built with transformer substation
CN113587467A (en) * 2021-07-29 2021-11-02 江苏区宇能源有限公司 Multi-machine-head single-return-stroke segmented compression type water chilling unit

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3926253A3 (en) * 2020-06-17 2022-04-20 Carrier Corporation Vapor compression system and method for operating heat exchanger

Also Published As

Publication number Publication date
CN108489132A (en) 2018-09-04

Similar Documents

Publication Publication Date Title
US20190017712A1 (en) High-efficiency extra-large cooling capacity series chiller in energy station
CN101334203B (en) Method for enhancing cold-storage density of cold storage air conditioner system and cold storage air conditioner system
CN210197600U (en) Secondary pump variable flow chilled water system with energy storage device
CN102313331B (en) Ice storage refrigeration system and refrigeration method thereof
CN102155772A (en) Cascaded ice-storage air conditioning system and method utilizing same to supply cold air for air conditioner
CN104791925A (en) Energy-saving type open cold supply system for cooling tower
CN202254480U (en) Multifunctional water-heating air-conditioning system
KR20110076527A (en) The regenerative system air-conditioning apparatus
CN104896641A (en) Double-evaporator dynamic ice cold storage system
CN204730381U (en) Double evaporators dynamic ice cold storage system
CN102384551B (en) External-ice-melting-type ice cold storage refrigerating system and refrigerating method thereof
CN102506473B (en) Direct-evaporating type ice cold accumulation refrigerating system and refrigerating method thereof
CN207350607U (en) A kind of ice-storage air-conditioning structure
CN203848732U (en) Chilled water and circulating cooling water combined heat exchange system
CN107355926A (en) High-temperature refrigeration coupling accumulation of energy cold source air conditioning system and its control method based on independent temperature-humidity control
CN106839481B (en) Cooling unit with auxiliary cold source
CN202915596U (en) Double-system water cooling screw machine set water fluorine series reverse flow system
CN102734878A (en) High-efficiency dual-temperature air source heat pump assembly dedicated to capillary radiation air-conditioning system
CN205156454U (en) Freezer heat recovery is towards white system
CN210602351U (en) Condenser capable of improving supercooling degree, water chilling unit and air conditioner
CN208567190U (en) The efficiently especially big cooling capacity series connection water cooler of energy source station
CN102506474B (en) Parallel ice cold accumulation refrigerating system and refrigerating method thereof
CN201259287Y (en) Cold storage air conditioner system for enhancing cold-storage density
CN216123342U (en) Data center mixes cold source economizer system
CN212320115U (en) Refrigerating system for data center

Legal Events

Date Code Title Description
AS Assignment

Owner name: JIANGSU QUYU ENERGY CO., LTD., CHINA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:ZHAN, TING;SUN, HAO;JI, PENGYUE;AND OTHERS;REEL/FRAME:046882/0599

Effective date: 20180807

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION