WO2017045458A1 - 重力热管式地冷冷源蓄冷系统及冷水机组 - Google Patents

重力热管式地冷冷源蓄冷系统及冷水机组 Download PDF

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Publication number
WO2017045458A1
WO2017045458A1 PCT/CN2016/088061 CN2016088061W WO2017045458A1 WO 2017045458 A1 WO2017045458 A1 WO 2017045458A1 CN 2016088061 W CN2016088061 W CN 2016088061W WO 2017045458 A1 WO2017045458 A1 WO 2017045458A1
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Prior art keywords
cold storage
cold
arc
pipe
storage system
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PCT/CN2016/088061
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English (en)
French (fr)
Inventor
张卫星
张宗勤
田俊
袁祎
王凌云
Original Assignee
南京佳力图机房环境技术股份有限公司
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Priority to US15/751,482 priority Critical patent/US10295206B2/en
Publication of WO2017045458A1 publication Critical patent/WO2017045458A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0046—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater using natural energy, e.g. solar energy, energy from the ground
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/0017—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning using cold storage bodies, e.g. ice
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24T—GEOTHERMAL COLLECTORS; GEOTHERMAL SYSTEMS
    • F24T10/00—Geothermal collectors
    • F24T10/10—Geothermal collectors with circulation of working fluids through underground channels, the working fluids not coming into direct contact with the ground
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B23/00—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect
    • F25B23/006—Machines, plants or systems, with a single mode of operation not covered by groups F25B1/00 - F25B21/00, e.g. using selective radiation effect boiling cooling systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/06—Heat pumps characterised by the source of low potential heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/025—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes having non-capillary condensate return means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0266—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • H—ELECTRICITY
    • H05—ELECTRIC TECHNIQUES NOT OTHERWISE PROVIDED FOR
    • H05K—PRINTED CIRCUITS; CASINGS OR CONSTRUCTIONAL DETAILS OF ELECTRIC APPARATUS; MANUFACTURE OF ASSEMBLAGES OF ELECTRICAL COMPONENTS
    • H05K7/00—Constructional details common to different types of electric apparatus
    • H05K7/20—Modifications to facilitate cooling, ventilating, or heating
    • H05K7/20709—Modifications to facilitate cooling, ventilating, or heating for server racks or cabinets; for data centers, e.g. 19-inch computer racks
    • H05K7/208—Liquid cooling with phase change
    • H05K7/20827—Liquid cooling with phase change within rooms for removing heat from cabinets, e.g. air conditioning devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B10/00—Integration of renewable energy sources in buildings
    • Y02B10/40—Geothermal heat-pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/10—Geothermal energy
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the invention relates to a gravity heat pipe type cold and cold source cold storage system.
  • the data center has a relatively high requirement for the continuous cooling capacity of the chiller.
  • the UPS can be used for power supply of the IT equipment, and generally cannot supply power to the air conditioner with the same large power consumption, but can give the fan, Power is supplied by devices with low power consumption such as pumps.
  • the data center has added a large-scale cold storage tank in the water system, which is bulky and takes up a lot of space, which brings trouble to the heat preservation work and the load-bearing work; and the system cannot save energy. From the perspective of providing the angle of cooling after power failure and reducing the volume of the cold storage device.
  • the present invention is directed to the defects of the prior art chiller, and provides an energy-saving and efficient gravity-heat-cooled cold-source cold storage system and a chiller, which effectively utilizes a natural cold source and can continuously supply a cold source.
  • the gravity heat pipe type cold source cold storage system of the present invention adopts the following technical scheme: a chiller gravity heat pipe type cold cold source cold storage system, the chiller is provided with a cold water pipe, and the cold storage is provided.
  • the system includes a gravity heat pipe, a cold storage tank, and a condensing heat exchange device; the heat exchange pipe is buried in the ground, the heat exchange pipe includes an inlet pipe and a return pipe, and the upper ends of the inlet pipe and the return pipe respectively pass through the heat insulating pipe Connecting the inlet and the outlet of the condensing heat exchange device, the outer wall of the inlet pipe is connected to the outer wall of the return pipe, the inlet pipe and the return pipe are parallel to each other, and the inlet pipe comprises 4 horizontal pipes.
  • a pipe having a circular cross section wherein the cross section of the return pipe is formed by first and second ends of the first arc, the second arc, the third arc and the fourth arc, wherein the second arc and the fourth arc are S-shaped arcs
  • the radius of the first arc is greater than the radius of the third arc, and the centers of the first arc and the third arc are both located in a cross section of the return tube, and the inlet tube is disposed around the third arc.
  • the inlet tubes have equal cross-sectional areas.
  • the sum of the cross-sectional areas of the inlet tubes is greater than the cross-sectional area of the return tubes.
  • the heat exchanger tube has an overall outer diameter of 80 ⁇ 0.5 mm, and the wall thickness of the return tube and the outer tube are both 3 ⁇ 0.5 mm.
  • the return pipe is insulated from the inner wall of one end of the ground or a heat insulating sleeve is disposed on the inner wall thereof.
  • cross-sectional area of the return pipe is 50-60% of the sum of the cross-sectional areas of the inlet pipes.
  • the refrigerant is water, an aqueous solution of ethylene glycol, an aqueous solution of 30% to 45% calcium chloride, or a 20% to 40% aqueous solution of sodium sulfate decahydrate and 15% to 25% sodium acetate trihydrate, or an aqueous solution containing 20% to 40% sodium sulfate decahydrate and 15% to 30% calcium chloride.
  • the cold storage medium has a phase transition temperature of 5 to 20 ° C, thereby effectively utilizing the latent heat of phase change in a high temperature environment.
  • the condensing heat exchange device is a water cooling device, an air cooling device or a spray evaporation condensing heat exchange device.
  • Various cooling methods for the gravity heat pipe can be realized by the heat exchange tube of the present invention.
  • the water cooling device can be realized only by a cold water pool.
  • the gravity heat pipe type cold source cold storage system of the present invention uses a heat exchange tube to provide a cold source for a gravity heat pipe, and the heat exchange tube can fully utilize the heat exchange area in the borehole to maintain a large area contact between the heat exchange tube and the well wall. , effectively improve the heat absorption efficiency of the heat exchange tube.
  • the invention also discloses a gravity heat pipe type cold and cold source cold storage system chiller, comprising the gravity heat pipe type cold cooling source cold storage system according to any one of claims 1-7, wherein the cold storage tank is connected in parallel with the chiller .
  • the cold storage tank is connected to the chiller through a three-way valve. This design makes it easy to control the passage of control media from a chiller or a cold storage tank.
  • the gravity heat pipe type cold source cold storage system chiller of the present invention provides a cold storage system for a chiller by using a gravity heat pipe type cold source cold storage system, and the gravity heat pipe type cold source cold storage system of the present invention uses a heat exchange tube to provide a gravity heat pipe
  • the cold source and the heat exchange tube can make full use of the heat exchange area in the borehole, so that the heat exchange tube maintains a large area contact with the well wall, and effectively improves the heat absorption efficiency of the heat exchange tube.
  • FIG. 1 is a schematic structural view of a gravity heat pipe type gravity heat pipe type ground cooling and cooling source cold storage system according to the present invention
  • FIG. 2 is a schematic structural view of a gravity heat pipe of the present invention
  • FIG. 3 is a schematic view showing the structure of the heat exchange tube of the present invention.
  • the gravity heat pipe type cold source cold storage system of the present invention is applied to a cold water unit.
  • the chiller is provided with a cold water pipe, including a gravity heat pipe 5, a cold storage tank 4, a condensing heat exchange device 3, and a heat exchange pipe.
  • the inlet and outlet of the cold storage tank are connected in parallel with the cold water pipe of the chiller, and are connected or broken through a control valve.
  • the gravity heat pipe is a separate heat pipe, and the evaporation section is disposed in the cold storage tank 4, and the condensation section is disposed in the condensing heat exchange device 3.
  • the cold storage system includes a gravity heat pipe 5, a cold storage tank 4, a condensing heat exchange device 3, and a heat exchange tube.
  • the lower end of the gravity heat pipe 5 is disposed in the cold storage tank 4, and the upper end of the gravity heat pipe 5 is disposed in the condensing heat exchange device 3.
  • the cold storage tank 4 is connected in parallel with the chiller. When the chiller fails or is powered off, the cold storage tank 4 can be used to continuously supply the cooling capacity.
  • the cold storage tank 4 stores a cold storage medium, which is water, 5% to 25% aqueous calcium chloride solution, or an aqueous solution containing 3% to 10% sodium sulfate decahydrate and 5% to 12% sodium acetate trihydrate. Or an aqueous solution containing 5% to 15% calcium chloride and 5% to 10% sodium phosphate.
  • the cold storage medium has a phase transition temperature of 5 to 20 ° C, thereby effectively utilizing the latent heat of phase change in a high temperature environment.
  • the heat exchange tube of the present invention is buried in the underground, including the inlet pipe 2 and the return pipe 1, and the upper ends of the inlet pipe 2 and the return pipe 1 are respectively connected to both ends of the condensation heat exchange device 3 through the heat insulating pipe, and the outer wall of the inlet pipe 2 Connected to the outer wall of the return pipe 1, the inlet pipe 2 and the return pipe 1 are parallel to each other, and the inlet pipe 2 comprises four tubes having a circular cross section, and the cross section of the return pipe 1 is composed of a first arc 11 and a second arc 12
  • the third arc 13 and the fourth arc 14 are connected end to end in sequence, wherein the second arc 12 and the fourth arc 14 are S-shaped arcs, and the radius of the first arc 11 is larger than the radius of the third arc 13 , the first arc Both ends of the first arc 11 and the third arc 13 are connected by a second arc 12 and a fourth arc 14, respectively, and the centers of the first arc 11 and the third
  • the above design enables the heat exchange tube to fully utilize the heat exchange area in the borehole, so that the heat exchange tube maintains a large area contact with the well wall, thereby effectively improving the suction efficiency of the heat exchange tube.
  • the cross-sectional areas of the return pipes 1 are all equal.
  • the sum of the areas of the cross sections of the inlet pipe 2 is larger than the cross sectional area of the return pipe 1.
  • the outer diameter of the heat exchange tube is 80 ⁇ 0.5mm, and the thickness of the tube of the return tube 1 and the inlet tube 2 is 3 ⁇ 0.5mm.
  • the inner wall of one end of the return pipe 1 near the ground is insulated or a heat insulating sleeve is provided on the inner wall thereof.
  • the cross-sectional area of the return pipe 1 is 50-60% of the sum of the cross-sectional areas of the inlet pipe 2. This design can greatly reduce the inlet pipe pressure of the heat exchange tubes. It ensures a slower flow of fluid during inflow, a longer residence time and more heat.
  • the reflux cross section is small, and the liquid passing through the bottom heat exchange can quickly flow back to the ground to prevent the return liquid from being thermally disturbed by the inlet pipe.
  • the cross-sectional area of the center tube 1 is 50-60% of the sum of the cross-sectional areas of the outer tubes 1.
  • the outer tube wall of the inlet tube 2 and the return tube 1 is provided with a groove.
  • the grooves may be arranged along the axial direction of the inlet pipe 2 and the return pipe 1. Among them, the grooves are evenly distributed on the outer tube wall of the inlet tube 2 and the return tube 1. The length of the groove is equal to the length of the inlet pipe 2 and the return pipe 1. Grooves are provided in the inlet pipe 2 and the return pipe 1 for enlarging the surface areas of the inlet pipe 2 and the return pipe 1, which can absorb heat more efficiently and improve the heat exchange efficiency of the heat exchange tubes.
  • the heat exchange area in the borehole can be fully utilized to maintain a large area contact between the heat exchange tube and the well wall, thereby effectively improving the heat absorption efficiency of the heat exchange tube.
  • the inner tube 1 is insulated from the inner wall of one end of the ground or a heat insulating sleeve is disposed on the inner wall thereof. Near the surface of the earth, the thermal interference between the inlet pipe and the return pipe is large, and the cavity contact surface of the upper end of the return pipe close to the ground is insulated or inserted. Insulation sleeves increase heat exchange efficiency.
  • the heat exchange tube is made of high density polyethylene or polypropylene.
  • the overall outer diameter of the heat exchange tube is 80 ⁇ 0.5 mm, and the wall thickness of the inlet tube 2 and the return tube 1 are both 3 ⁇ 0.5 mm.
  • the invention also discloses a gravity heat pipe type cold source cold storage system chiller, which adopts the gravity heat pipe type cold source cold storage system as described above, and the cold storage tank 4 is connected in parallel with the chiller unit.
  • the cold storage tank 4 is connected to the chiller through a three-way valve. This design makes it easy to control the passage of the control medium from the chiller or the cold storage tank.
  • the gravity heat pipe type cold source cold storage system chiller of the present invention uses a gravity heat pipe type cold source cold storage system to provide a cold storage system for the chiller, and the gravity heat pipe type cold source cold storage system of the present invention uses the heat exchange tube to provide a cold source for the gravity heat pipe.
  • the heat exchange tube can make full use of the heat exchange area in the borehole, so that the heat exchange tube maintains a large area contact with the well wall, effectively improves the suction efficiency of the heat exchange tube, and at the same time, the heat exchange tube inlet tube and the return tube of the present invention. Both can be in contact with the well wall to absorb cold, which can greatly extend the working distance of the heat exchange tube and improve the effect of sucking cold.
  • Cool storage process When the gravity heat pipe works, the refrigerant in the heat pipe (the working medium, generally adopts Freon) circulates between the outdoor condensing heat exchange device and the cold storage tank 4, and discharges heat in the condensing heat exchange device 3, and stores the cold.
  • the pool 4 absorbs heat, thereby lowering the temperature of the cold storage medium in the cold storage tank 4, and even causing a phase change of the refrigerant medium to store heat.
  • the process of releasing the cold amount when the cooling capacity needs to be released, the water inlet of the chiller flows through the cold storage tank 4 by opening the on-off valve, and the water exchanges heat with the medium in the cold storage tank 4, thereby reducing the cold water.
  • the water temperature of the unit The process of releasing the cooling capacity.
  • the gravity heat pipe type cold source cold storage system chiller of the present invention uses a gravity heat pipe type cold source cold storage system to provide a cold storage system for the chiller, and the gravity heat pipe type cold source cold storage system of the present invention uses the heat exchange tube to provide a cold source for the gravity heat pipe.
  • the heat exchange tube can make full use of the heat exchange area in the borehole, so that the heat exchange tube maintains a large area contact with the well wall, effectively improves the heat absorption efficiency of the heat exchange tube, and maximizes the utilization of the underground cold source.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Sustainable Energy (AREA)
  • Computer Hardware Design (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

一种重力热管式地冷冷源蓄冷系统及包含该蓄冷系统的冷水机组，蓄冷系统包括重力热管（5）、蓄冷池（4）、冷凝换热装置（3）和换热管，蓄冷池（4）的进口和出口与冷水机组的冷水管道并联连接，并通过控制阀实现接入或断开。换热管埋设在地下，包括进流管（2）和回流管（1），回流管（1）的横截面由第一弧（11）、第二弧（12）、第三弧（13）和第四弧（14）依次首尾相接而成，其中，第二弧（12）和第四弧（14）为S形弧，第一弧（11）的半径大于第三弧（13）的半径且二者的圆心均位于回流管（1）的横截面内，进流管（2）包括4个横截面为圆形的管且围绕第三弧（13）设置。

Description

重力热管式地冷冷源蓄冷系统及冷水机组 技术领域
本发明涉及一种重力热管式地冷冷源蓄冷系统。
背景技术
现有技术中，数据中心对冷水机组持续制冷能力要求比较高，当外部电源断电后，UPS可以用于IT设备供电，一般无法给同样耗电巨大的空调设备进行供电，但是可以给风机、水泵等功耗小的设备进行供电。此外，数据中心为解决蓄冷事宜，在水系统中增设大型蓄冷罐，体积庞大，占据空间巨大，给保温工作，承重工作带来麻烦；并且这种系统并不能节能。出于断电后提供冷量的角度以及减少蓄冷设备体积的角度考虑。
因此，需要一种新的蓄冷系统以解决上述问题。
发明内容
发明目的：本发明针对现有技术中冷水机组的缺陷，提供一种节能高效的重力热管式地冷冷源蓄冷系统及冷水机组，有效利用了自然冷源并能持续供给冷源。
技术方案：为解决上述技术问题，本发明的重力热管式冷源蓄冷系统采用如下技术方案：一种冷水机组重力热管式地冷冷源蓄冷系统，所述冷水机组设有冷水管道，所述蓄冷系统包括重力热管、蓄冷池、冷凝换热装置中；所述换热管埋设在地下，所述换热管包括进流管和回流管，所述进流管和回流管的上端分别通过绝热管联通所述冷凝换热装置的进口和出口，所述进流管的外壁与所述回流管的外壁连接，所述进流管与所述回流管相互平行，所述进流管包括4个横截面为圆形的管子，所述回流管的横截面由第一弧、第二弧、第三弧和第四弧依次首尾相接而成，其中，第二弧和第四弧为S形弧，第一弧的半径大于第三弧的半径，所述第一弧和第三弧的圆心均位于所述回流管的横截面内，所述进流管围绕所述第三弧设置。
更进一步的，所述进流管的横截面面积均相等。
更进一步的，所述进流管的横截面的面积总和大于所述回流管的横截面面积。
更进一步的，所述换热管整体外直径为80±0.5mm，所述回流管和所述外侧管的管壁厚度均为3±0.5mm。
更进一步的，所述回流管靠近地面的一端内壁绝热或在其内壁设置绝热管套。
更进一步的，所述回流管的截面积为所述进流管截面积之和的50-60％。
更进一步的，所述冷媒是水、乙二醇水溶液、30％～45％的氯化钙水溶液、或者是含 20％～40％十水合硫酸钠和15％～25％三水合醋酸钠的水溶液，或者是含20％～40％十水合硫酸钠和15％～30％氯化钙的水溶液。
此蓄冷介质具有5～20℃下相变温度，从而在温度较高的环境下有效利用其相变潜热。
更进一步的，所述冷凝换热装置为水冷装置、风冷装置或者喷淋蒸发冷凝换热装置。可以利用本发明的换热管实现对重力式热管的各种冷却方式。其中，水冷装置只需一个冷水池即可实现。
有益效果：本发明的重力热管式冷源蓄冷系统利用换热管为重力热管提供冷源，换热管能够充分利用钻孔井内的热交换面积，使换热管与井壁保持大面积的接触，有效提高换热管的吸冷效率。
本发明还公开了一种重力热管式地冷冷源蓄冷系统冷水机组，包括如权利要求1-7任一项所述的重力热管式地冷冷源蓄冷系统，所述蓄冷池与冷水机组并联。
更进一步的，所述蓄冷池通过三通阀连接冷水机组。此种设计可简单方便实现控制介质从冷水机组或者蓄冷池通过。
有益效果：本发明的重力热管式冷源蓄冷系统冷水机组，利用重力热管式冷源蓄冷系统为冷水机组提供蓄冷系统，且本发明的重力热管式冷源蓄冷系统利用换热管为重力热管提供冷源，换热管能够充分利用钻孔井内的热交换面积，使换热管与井壁保持大面积的接触，有效提高换热管的吸冷效率。
附图说明
图1本发明的重力热管式重力热管式地冷冷源蓄冷系统的结构示意图；
图2本发明的重力热管的结构示意图；
图3本发明的换热管的结构示意图。
具体实施方式
下面结合附图和具体实施例，进一步阐明本发明，应理解这些实施例仅用于说明本发明而不用于限制本发明的范围，在阅读了本发明之后，本领域技术人员对本发明的各种等价形式的修改均落于本申请所附权利要求所限定的范围。
请参阅图1、图2和图3所示，本发明的重力热管式冷源蓄冷系统，蓄冷系统应用于冷水机组上。冷水机组设有冷水管道，包括重力热管5、蓄冷池4、冷凝换热装置3和换热管，蓄冷池的进口和出口与冷水机组的冷水管道并联连接，并通过控制阀实现接入或断开；重力热管为分离式热管，其蒸发段设在蓄冷池4中，冷凝段则设在冷凝换热装置3中。
蓄冷系统包括重力热管5、蓄冷池4、冷凝换热装置3和换热管，重力热管5的下端设置在蓄冷池4中，重力热管5的上端设置在冷凝换热装置3中。其中，蓄冷池4与冷水机组并联。当冷水机组出现故障或者停电时，可以利用蓄冷池4持续提供冷量。
蓄冷池4中存储有蓄冷介质，蓄冷介质是水、5％～25％的氯化钙水溶液、或者是含3％～10％十水合硫酸钠和5％～12％三水合醋酸钠的水溶液，或者是含5％～15％氯化钙和5％～10％磷酸钠的水溶液。此蓄冷介质具有5～20℃下相变温度，从而在温度较高的环境下有效利用其相变潜热。
本发明的换热管埋设在地下，包括进流管2和回流管1，进流管2和回流管1的上端分别通过绝热管联通冷凝换热装置3的两端，进流管2的外壁与回流管1的外壁连接，进流管2与回流管1相互平行，进流管2包括4个横截面为圆形的管子，回流管1的横截面由第一弧11、第二弧12、第三弧13和第四弧14依次首尾相接而成，其中，第二弧12和第四弧14为S形弧，第一弧11的半径大于第三弧13的半径，第一弧11的两端和第三弧13的两端分别通过第二弧12和第四弧14连接，第一弧11和第三弧13的圆心均位于回流管1的横截面内，进流管2围绕第三弧13设置。
上述设计能够使换热管充分利用钻孔井内的热交换面积，使换热管与井壁保持大面积的接触，有效提高换热管的吸冷效率。本实施例中，回流管1的横截面面积均相等。进流管2的横截面的面积总和大于回流管1的横截面面积。
换热管整体外直径为80±0.5mm，回流管1和进流管2的管壁厚度均为3±0.5mm。回流管1靠近地面的一端内壁绝热或在其内壁设置绝热管套。
回流管1的截面积为进流管2截面积之和的50-60％。此设计可使换热管的进流管管压大大降低。可保证进流时流体较缓慢流动，停留时间长，吸收更多的热量。回流截面小，经过底部热交换的液体能快速流回地面，避免回流液体受进流管的热干扰。优选的，中心管1的截面积为外侧管1截面积之和的50-60％。
优选的，进流管2和回流管1的外管壁上设置有凹槽。凹槽可以沿进流管2和回流管1的轴线方向设置。其中，凹槽均匀分布在进流管2和回流管1的外管壁。凹槽的长度与进流管2和回流管1的长度相等。在进流管2和回流管1上设置凹槽用来扩大进流管2和回流管1的表面积，可以更有效的吸收热量，提高换热管的热交换效率。能够充分利用钻孔井内的热交换面积，使换热管与井壁保持大面积的接触，有效提高换热管的吸冷效率。中心管1靠近地面的一端内壁绝热或者在其内壁设置绝热管套。靠近地表的部分，进流管和回流管之间热干扰大，对回流管靠近地面的上端的管腔接触面绝热或插入 绝热套管就可提高热交换效率。为保证使用寿命大于50年，换热管的材质为高密度聚乙烯或聚丙烯。换热管的整体外直径为80±0.5mm，进流管2和回流管1的管壁厚度均为3±0.5mm。
本发明还公开了一种重力热管式冷源蓄冷系统冷水机组，采用如上所述的重力热管式冷源蓄冷系统，蓄冷池4与冷水机组并联。蓄冷池4通过三通阀连接冷水机组。此种设计，简单方便实现控制介质从冷水机组或者蓄冷池通过。
本发明的重力热管式冷源蓄冷系统冷水机组，利用重力热管式冷源蓄冷系统为冷水机组提供蓄冷系统，且本发明的重力热管式冷源蓄冷系统利用换热管为重力热管提供冷源，换热管能够充分利用钻孔井内的热交换面积，使换热管与井壁保持大面积的接触，有效提高换热管的吸冷效率，同时本发明的换热管进流管和回流管均可与井壁接触吸冷，可以大大延长换热管的作用距离，提高吸冷效果。
原理如下：
蓄冷过程：重力热管工作时，热管中的载冷剂(工质，一般采用氟利昂)在室外的冷凝换热装置和蓄冷池4之间进行循环，在冷凝换热装置3中排放热量，在蓄冷池4中吸收热量，从而降低蓄冷池4中蓄冷介质的温度，甚至使得制冷剂介质发生相变，从而储存热量。
释放冷量的过程：当需要释放冷量的时候，通过开启通断阀的方式，使得冷水机组的进水先流经蓄冷池4，这些水和蓄冷池4中介质发生热量交换，降低了冷水机组的水温。实现释放冷量的过程。
本发明的重力热管式冷源蓄冷系统冷水机组，利用重力热管式冷源蓄冷系统为冷水机组提供蓄冷系统，且本发明的重力热管式冷源蓄冷系统利用换热管为重力热管提供冷源，换热管能够充分利用钻孔井内的热交换面积，使换热管与井壁保持大面积的接触，有效提高换热管的吸冷效率，最大化的利用地下冷源。

Claims (10)

  1. 一种重力热管式地冷冷源蓄冷系统，所述冷水机组设有冷水管道，其特征在于：所述蓄冷系统包括重力热管(5)、蓄冷池(4)、冷凝换热装置(3)和换热管，所述蓄冷池的进口和出口与冷水机组的冷水管道并联连接，并通过控制阀实现接入或断开；所述重力热管为分离式热管，其蒸发段设在蓄冷池中，冷凝段则设在冷凝换热装置(3)中；所述换热管埋设在地下，包括进流管(2)和回流管(1)，所述进流管(2)和回流管(1)的上端分别通过绝热管联通所述冷凝换热装置(3)的进口和出口形成循环，所述进流管(2)的外壁与所述回流管(1)的外壁连接，所述进流管(2)与所述回流管(1)相互平行，所述进流管(2)包括4个横截面为圆形的管子，所述回流管(1)的横截面由第一弧(11)、第二弧(12)、第三弧(13)和第四弧(14)依次首尾相接而成，其中，第二弧(12)和第四弧(14)为S形弧，第一弧(11)的半径大于第三弧(13)的半径，所述第一弧(11)和第三弧(13)的圆心均位于所述回流管(1)的横截面内，所述进流管(2)围绕所述第三弧(13)设置。
  2. 如权利要求1所述的重力热管式地冷冷源蓄冷系统，其特征在于，所述进流管(2)的横截面面积均相等。
  3. 如权利要求1所述的重力热管式地冷冷源蓄冷系统，其特征在于，所述进流管(2)的横截面的面积总和大于所述回流管(1)的横截面面积。
  4. 如权利要求1所述的重力热管式地冷冷源蓄冷系统，其特征在于，所述换热管整体外直径为80±0.5mm，所述进流管(2)和回流管(1)的管壁厚度均为3±0.5mm。
  5. 如权利要求1所述的重力热管式地冷冷源蓄冷系统，其特征在于，所述回流管(1)靠近地面的一端内壁绝热或在其内壁设置绝热管套。
  6. 如权利要求1所述的重力热管式地冷冷源蓄冷系统，其特征在于，所述回流管(1)的截面积为所述进流管(2)截面积之和的50-60％。
  7. 如权利要求1所述的重力热管式地冷冷源蓄冷系统，其特征在于，所述蓄冷池(5)中存储有蓄冷介质，所述蓄冷介质是水、乙二醇水溶液、30％～45％的氯化钙水溶液、或者是含20％～40％十水合硫酸钠和15％～25％三水合醋酸钠的水溶液，或者是含20％～40％十水合硫酸钠和15％～30％氯化钙的水溶液。
  8. 如权利要求1所述的重力热管式地冷冷源蓄冷系统，其特征在于，所述冷凝换热装置为水冷装置、风冷装置或者喷淋蒸发冷凝换热装置。
  9. 一种重力热管式地冷冷源蓄冷系统冷水机组，其特征在于，包括如权利要求1-7任一项所述的重力热管式地冷冷源蓄冷系统，所述蓄冷池(4)与冷水机组并联。
  10. 如权利要求8所述的重力热管式冷源蓄冷系统冷水机组，其特征在于，所述蓄冷池(4)通过三通阀连接冷水机组。
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