WO2020238207A1 - 一种环保型热管工质 - Google Patents

一种环保型热管工质 Download PDF

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Publication number
WO2020238207A1
WO2020238207A1 PCT/CN2019/130393 CN2019130393W WO2020238207A1 WO 2020238207 A1 WO2020238207 A1 WO 2020238207A1 CN 2019130393 W CN2019130393 W CN 2019130393W WO 2020238207 A1 WO2020238207 A1 WO 2020238207A1
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WO
WIPO (PCT)
Prior art keywords
hfo
heat pipe
working fluid
1336mzz
gravity heat
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PCT/CN2019/130393
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English (en)
French (fr)
Inventor
权恒道
郭智恺
赵升
欧阳洪生
杨会娥
孙华峰
杨刚
罗霞
Original Assignee
浙江省化工研究院有限公司
中化蓝天集团有限公司
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Application filed by 浙江省化工研究院有限公司, 中化蓝天集团有限公司 filed Critical 浙江省化工研究院有限公司
Priority to KR1020217039287A priority Critical patent/KR20220002631A/ko
Priority to US17/614,464 priority patent/US20220235253A1/en
Priority to EP19931178.8A priority patent/EP3978731A4/en
Priority to JP2021571302A priority patent/JP7478170B2/ja
Publication of WO2020238207A1 publication Critical patent/WO2020238207A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
    • C09K5/02—Materials undergoing a change of physical state when used
    • C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
    • 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
    • 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
    • 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
    • H05K7/2029—Modifications to facilitate cooling, ventilating, or heating using a liquid coolant with phase change in electronic enclosures
    • 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
    • H05K7/2029—Modifications to facilitate cooling, ventilating, or heating using a liquid coolant with phase change in electronic enclosures
    • H05K7/20309—Evaporators
    • 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
    • H05K7/2029—Modifications to facilitate cooling, ventilating, or heating using a liquid coolant with phase change in electronic enclosures
    • H05K7/20318—Condensers
    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
    • C09K2205/22—All components of a mixture being fluoro compounds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F01K25/10—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours the vapours being cold, e.g. ammonia, carbon dioxide, ether
    • 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
    • F25B2400/00—General 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
    • F25B2400/12—Inflammable refrigerants

Definitions

  • the invention relates to a cooling medium, in particular to a cooling medium of a gravity heat pipe.
  • IDC's energy consumption includes IT equipment, refrigeration equipment, power distribution systems and other auxiliary equipment. Among them, the energy consumption of refrigeration equipment accounts for 40% of IDC's total energy consumption. Therefore, it is necessary to adopt energy-saving refrigeration technology to reduce the PUE value of the data center, which is one of the effective ways to build a green energy-saving data center in my country.
  • refrigeration equipment traditional precision air conditioners have the problems of low energy utilization and uneven air distribution. With the increase in heat generation and the sharp rise of heat density, they cannot meet the heat dissipation requirements of server cabinets.
  • Gravity heat pipe is a kind of energy saving and emission reduction refrigeration equipment, with good refrigeration effect and low energy consumption.
  • Gravity heat pipe is a kind of sealed pipe, which contains working fluid in liquid and gas phase at the same time.
  • the liquid working fluid is transformed into a gaseous state by absorbing the latent heat of the evaporation zone.
  • the gas enters the condensing zone and transforms into a liquid working fluid while releasing latent heat.
  • the liquid working fluid relies on gravity to return to the evaporation zone to complete the cycle.
  • the size of the gravity heat pipe is small and can be installed on the back of the rack or as the side panel of the base station. Gravity heat pipes can not only realize one-to-one cooling, avoid local overheating, but also improve the utilization rate of equipment.
  • the commonly used working fluids for gravity heat pipes include water, ammonia, methanol, acetone, HCFC-22, HFC-134a, R410a, etc. In terms of safety and environmental protection requirements, these working fluids all have insurmountable defects.
  • the starting temperature of water is high, and the equipment must be well protected to prevent potential leakage; ammonia water has strong irritation and will cause poisoning if it leaks; methanol and acetone are flammable compounds and are not suitable for large-dose use; HCFC-22 can destroy the ozone layer, and its global warming potential (GWP) is 1810; although HFC-134a and R410a will not destroy the ozone layer, their GWP values have reached 1300 or higher, and the high system pressure leads to manufacturing costs high.
  • GWP global warming potential
  • HFC-245fa is a safe and feasible alternative to the working fluid of gravity heat pipes. It is non-flammable and has low system pressure, which can meet the needs of related applications. However, HFC-245fa has a GWP value of 1050 and may be replaced in the future. Therefore, it is necessary to develop an environmentally friendly working fluid for gravity heat pipes to replace HFC-245fa for heat pipe cooling.
  • the purpose of the present invention is to provide a gravity heat pipe working fluid for cooling the gravity heat pipe.
  • the embodiment of the present invention relates to a gravity heat pipe whose working fluid is selected from HFO-1234ze(Z), HFO-1234ze(E), HFO-1336mzz(Z), HFO-1336mzz(E), HFO- 1224yd (Z), HFO-1233zd (E) and mixtures thereof.
  • the working fluid is selected from HFO-1234ze (Z), HFO-1234yf, HFO-1233zd (E), HFO-1224yd (Z) or mixtures thereof.
  • the working fluid is HFO-1234ze(Z).
  • HFO-1234ze(Z) that is, cis-1,3,3,3-tetrafluoropropene, molecular formula is CHFCHCF3, molecular weight is 114.04, standard boiling point is 9.72°C, critical temperature is 150.12°, critical pressure is 3.53MPa .
  • the present invention provides a method of using a gravity heat pipe working fluid, in which a working fluid containing HFO-1234ze (Z) is used.
  • the working fluid consists only of HFO-1234ze (Z).
  • the gravity heat pipe operates at a temperature of 0°C to 100°C.
  • the working fluid of the present invention is suitable for directly replacing the gravity heat pipe originally designed to use HFC-245fa, HFC-134a or R410a as the working fluid.
  • the gravity heat pipe device of the present invention adopts the design of separate evaporation section and condensation section, and the evaporation section and condensation section are connected by pipelines.
  • the gravity heat pipe device of the present invention can realize long-distance heat transmission, and can adjust the heat exchange area ratio according to requirements to meet the cooling requirements of IDCs of different scales.
  • the gravity heat pipe of the present invention is a flat gravity heat pipe.
  • the gravity heat pipe device of the present invention is particularly suitable for cooling electronic equipment, such as computers, communication base stations, servers or data centers.
  • the gravity heat pipe working fluid of the present invention has the following advantages:
  • the working fluid criterion number M'representing the comprehensive performance of reaction thermal physics and heat transfer is higher than HFC-245fa, which is currently the preferred working fluid for cooling IDC;
  • thermosyphon The specific expression of the working fluid criterion number M'of the gravity heat pipe (ie thermosyphon) of the present invention is as follows:
  • the dimension of the criterion number M' is L is the latent heat of vaporization, in units (KJ/Kg); ⁇ l is the density of saturated liquid, in kg/m 3 ; k l is the thermal conductivity of saturated liquid, in W/(m ⁇ K); ⁇ l is the dynamic viscosity of the liquid, The unit is Pa ⁇ s.
  • the ODP value of the gravity heat pipe working fluid of the present invention is obtained by testing CFC-11 as a reference value of 1.0, and the GWP value is obtained by using CO2 as a reference value of 1.0 (100 years).
  • Figure 1 shows the saturated vapor pressure of the gravity heat pipe working fluid in the temperature range of 0°C-100°C;
  • Figure 2 is the criterion number M’ of the working fluid of the gravity heat pipe in the temperature range of 0°C-100°C;
  • Figure 3 is a schematic diagram of the process flow of the gravity heat pipe device.
  • Embodiments of the present invention relate to working fluids for heat pipes (eg, gravity heat pipes), especially working fluids for cooling electronic devices such as computers, communication base stations, servers, or Internet data centers (IDCs).
  • the heat pipe uses the phase change of the working fluid (such as the phase change between the liquid phase and the gas phase) to transfer heat from one area to another.
  • the normal operation of the heat pipe requires saturated working fluid.
  • the working fluid absorbs latent heat (evaporation heat) in the evaporation area and evaporates from the liquid state to the gas state, and condenses from the gas state to the liquid state in the condensation area to release the latent heat.
  • the working temperature range which is between three times the freezing point and criticality of the working fluid Between points.
  • the operating temperature range of any given fluid is relatively small, because the heat that the heat pipe can carry drops sharply when it approaches the freezing point and critical temperature. If the working temperature is too high, the working fluid may not be able to condense; however, if the working temperature is too low, the working fluid will not evaporate.
  • the operating temperature range is usually between 0°C and 150°C, and more commonly between 0°C and 100°C.
  • the working fluids that meet the requirements include HFO-1234yf, HFO-1234ze(Z), HFO-1234ze(E), HFO-1233zd(E), HCFO-1224yd(Z), HFO-1336mzz(Z) , HFO-1336mzz(E), and some of their mixed working fluids.
  • HFC-22 0.05 1810 HFC-245fa 0 1050 HFO-1234yf 0 ⁇ 1 HFO-1234ze(Z) 0 ⁇ 1 HFO-1234ze(E) 0 ⁇ 1 HFO-1233zd(E) 0.00034 1 HCFO-1224yd(Z) 0.00012 ⁇ 1 HFO-1336mzz(Z) 0 2 HFO-1336mzz(E) 0 7
  • the working fluid Since the heat pipe uses the phase change (liquid and gas) of the working fluid to transfer heat, the working fluid should have sufficient saturated vapor pressure within the working temperature range to conduct enough heat. In addition, the saturated vapor pressure of the working fluid should not be too high in the working range, otherwise it will produce too high pressure on the shell. Therefore, a good working fluid should have a suitable saturated vapor pressure within the working temperature range. In addition, the pressure change as a function of temperature should not be too drastic.
  • Figure 1 shows the saturation vapor pressure curve of different candidate working fluids at different temperatures.
  • most of the working fluids meet the saturated vapor pressure requirements within the working temperature range of 0-100°C, and some of them have Better pressure and temperature correlation performance.
  • the saturated vapor pressure of HFO-1336mzz(E), HFO-1234ze(Z), HFO-1233zd(E), HCFO-1224yd(Z) and HFO-1336mzz(E) at the same temperature is close to that of HFC-245fa.
  • R410a, HCFC-22, HFC-134a, HFO-1234yf and HFO-1234ze(E) at the same temperature have a significantly higher saturated vapor pressure than HFC-245fa, and also have a higher pressure and temperature correlation These characteristics mean that these working fluids cannot be used as working fluids to replace HFC-245fa.
  • R134a and HFC-1234yf have similar properties, and HFC-1234yf can be used as a substitute for R134a.
  • the trans isomer HFO-1234ze (E) has a higher saturation vapor pressure and temperature dependence than its cis isomer HFO-1234ze (Z).
  • working fluids with better properties include: HFO-1336mzz(E), HFO-1234ze(Z), HFC-245fa, HCFO-1224yd(Z), HFO-1233zd(E) and HFO-1336mzz(Z) ), the saturated vapor pressure of these working fluids at 100°C is lower or only slightly higher than 1.0MPa, HFO-1336mzz(E), HFO-1234ze(Z), HFC-245fa, HCFO-1224yd(Z), HFO-1233zd (E) and HFO-1336mzz(Z) have lower saturated vapor pressures, which means lower requirements on the strength of the shell, thus reducing the manufacturing cost of the system.
  • HFC-245fa which is currently the most commonly used heat pipe working fluid.
  • the similar pressure-temperature distributions of these working fluids indicate that these working fluids can be "alternatives" to the HFC-245fa in the current heat pipe system, and there are no or only minor changes to the current system.
  • criterion number (or criterion map) can be used to evaluate the relative performance of a series of candidate working fluids.
  • M criterion number
  • the dimension of the criterion number M' is Where L is the latent heat of vaporization, in units (kJ/kg); ⁇ l is the density of saturated liquids, in kg/m3; ⁇ l is the hydrodynamic viscosity, in Pa ⁇ s.
  • Figure 2 shows the criterion number (M') of several candidate working fluids in the temperature range of 15 ⁇ 95°C.
  • M' criterion number
  • HFO-1234ze(Z) is not only suitable for replacing HFC-245fa in current heat pipe systems, but also has higher performance than HFC-245fa.
  • Other working fluids with higher criterion numbers include HFO-1233ze(E), HFO-1224yd(Z), HFO-1336mzz(Z) and HFO-1234ze(E).
  • HFO-1234ze(E) which is a cooling fluid for modern automobiles, has a significantly lower standard number in this temperature range than other working fluids.
  • the advantages of the cis isomer HFO-1234ze (Z) are significantly higher than the trans isomer HFO-1234ze (E). Therefore, HFO-1234ze(z) will be a better working fluid than HFO-1234ze(e) because of its lower pressure-temperature dependence and larger criterion number.
  • Latent heat of evaporation relates to the amount of heat transfer per unit mass of working fluid (for example, from the liquid phase to the gas phase in the evaporation zone). As shown in the above criterion number formula, the higher the latent heat of evaporation of the working fluid, the greater the criterion number. high. Therefore, under the same other conditions, working fluids with higher latent heat are preferred because they can transfer the same heat with less working fluid than working fluids with lower latent heat of vaporization. Table 2 below shows the latent heat of evaporation of several working fluids and mixed working fluids:
  • the cooling performance of the working fluid of the present invention was tested with a gravity heat pipe device.
  • the gravity heat pipe device consists of two sets of heat pipe systems close to each other and independent of each other.
  • One gravity heat pipe system uses HFC-245fa as a comparison, and the other gravity heat pipe system Use the working fluid involved in the present invention for testing.
  • the close system can clearly compare the two working fluids.
  • the single-tube gravity heat pipe system is also used for working fluid performance testing. The test results of both systems will be uploaded to the computer for modeling and calculation.
  • the process flow chart of the gravity heat pipe device is shown in Figure 3.
  • the indoor inlet air dry bulb temperature is 35°C
  • the indoor inlet air wet bulb temperature is 22°C.
  • the air circulation is the same, both The circulating water temperature of the system is also consistent (inlet: 15°C, outlet: 20°C).
  • the thermal cycle performance parameters of the working fluid are shown in Table 3 below. Under the same inlet and outlet water temperature, the heat exchange capacity and the performance coefficient of several alternative working fluids are better than those of HFC-245fa and can be maintained The temperature of the air inlet area of the cold aisle meets the requirements of the national standard 18 ⁇ 27°C.
  • the performance parameters of the working fluid involved in the present invention are overall better than those used in the prior art, such as HFC-245fa.
  • alternative working fluids require less charge to achieve the same heat transfer.
  • the refrigeration performance coefficient of the working fluid is better than HFC-245fa, which means that these working fluids have better performance than HFC-245fa. Effect.
  • most of these working fluids have lower system pressures, such as HFO-1234yf and HFO-1234ze(E), which means that the process safety of their use in place of HFC-245fa can be guaranteed, and there is no need for heat pipes. Carry out reinforcement improvements.
  • the working fluid of the present invention has a lower optimal demand (quality) and is more environmentally friendly.
  • the above data indicate that the HFO and HCFO compounds of the present invention are excellent working fluids for heat pipes, especially gravity heat pipes.
  • the working fluid of the present invention includes HFO-1234ze (Z), HFO-1234ze (E), HFO-1234yf, HFO-1336mzz (Z), HFO-1336mzz (E), HFO-1224yd (Z) and HFO-1233zd (E ), and its mixed working fluid.
  • the preferred working fluids of the present invention include HFO-1234ze (Z), HFO-1233zd (E), HFO-1234yf, HFO-1336mzz (E) and HFO-1224yd (Z), and mixed working fluids thereof.
  • the mixture of these working fluids can include two components in a ratio of 1:99, preferably 10:90, or 20:80, or 30:70, or 40:60, or 50:50, and any between them proportion.
  • HFO-1234ze (Z), HFO-1233zd (E) or HFO-1336mzz (E) is used as one of the components.
  • the mixed fluid involved in the present invention includes:
  • HCFO-1233zd(E)/HCFO-1224yd is mixed in an appropriate ratio (such as 10/90);
  • HFO-1336mzz(E)/HCFO-1224yd is mixed in an appropriate ratio (such as 10/90).
  • HFO working fluid of the present invention has better performance parameters than HFO-1234ze(E) and HFC-245fa.
  • HFC-245fa is considered to be a good alternative working fluid for gravity heat pipes. Due to its thermophysical properties, it is suitable for a variety of heat transfer and working fluid applications, such as centrifugal coolers, organic Rankine cycles for energy recovery, cryogenic refrigeration and passive Sensible heat transfer in cooling devices.
  • the trans-isomer HFO-1234ze(E) was developed as a fourth-generation refrigerant to replace refrigerants such as HFC-134a.
  • GWP ⁇ 1 extremely low global warming potential
  • HFO-1234ze(E) has been used as a working fluid in coolers, heat pumps and supermarket refrigeration systems.
  • the cis isomer HFO-1234ze (Z) is actually more suitable than the trans isomer HFO-1234ze (E) for heat pipes (especially gravity heat pipes) used to cool electronic equipment, Internet data centers, etc. . Because the cis-isomer HFO-1234ze(Z) has a lower system pressure, and at the same time, it requires less working fluid when transferring the same heat.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Physics & Mathematics (AREA)
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Abstract

一种重力热管，所述重力热管的工作流体选自HFO-1234ze(Z)、HFO-1234ze(E)、HFO-1336mzz(Z)、HFO-1336mzz(E)、HFO-1224yd(Z)、HFO-1233zd(E)及其混合物。该重力热管具有环保、冷却性能好、制造成本低等优点，适用于通信基站、服务器或数据中心的冷却。

Description

一种环保型热管工质 技术领域
本发明涉及一种冷却介质，特别涉及一种重力热管冷却工质。
背景技术
近年来，随着互联网产业的快速发展，互联网数据中心(IDC)迅速崛起，IDC市场需求迅速增长。2016年，中国IDC市场规模达到714.5亿元，预计到2019年，中国IDC市场规模将达到1800亿元。数据中心的能耗也迅速增加，2016年，中国数据中心的用电量突破1000亿千瓦时，超过整个三峡电站的年发电量(900亿千瓦时)，占全国总用电量的1％，达到全球总用电量的2％。
IDC的能耗包括IT设备、制冷设备、配电系统和其他辅助设备，其中，制冷设备的能耗占IDC总能耗的40％。因此，需要采用节能制冷技术来降低数据中心的PUE值，这是我国建设绿色节能数据中心的有效途径之一。就制冷设备而言，传统的精密空调存在能量利用率低、气流组织分布不均的问题，随着发热量的增加和热密度的急剧上升，无法满足服务器机柜的散热需求。
重力热管是一种节能减排的制冷设备，具有良好的制冷效果且能耗低。重力热管是一种密封管，管内同时含有液相和气相状态的工作流体。液态工作流体通过吸收蒸发区的潜热转化为气态，气体进入冷凝区转化成液态工作流体同时释放潜热，液态工作流体依靠重力返回蒸发区完成循环。通常，重力热管的尺寸较小，可以安装在机架背面或作为基站的侧板。重力热管不仅可以实现一对一冷却，避免局部过热，还可以提高设备间的利用率。
在0-100℃的工作温度范围内，重力热管常用的工作流体包括水、氨水、甲醇、丙酮、HCFC-22、HFC-134a、R410a等。从安全性和环保要求方面考虑，这些工作流体都具有无法 克服的缺陷。如：水的起始温度高，必须对设备进行良好的保护，以防止潜在的泄漏；氨水具有强烈的刺激性，一旦泄漏会引起中毒；甲醇和丙酮是易燃化合物，不适合大剂量使用；HCFC-22可以破坏臭氧层，其全球变暖潜能值(GWP)为1810；HFC-134a和R410a虽然不会破坏臭氧层，但它们的GWP值也达到了1300或更高，且系统压力高导致制造成本高。
目前，HFC-245fa是重力热管工作流体的一种安全可行的替代品，具有不可燃性且系统压力低，可以满足相关应用的需求。然而，HFC-245fa的GWP值为1050，在将来也可能被替代。因此，有必要开发一种环保型重力热管工作流体，以替代HFC-245fa用于热管冷却。
发明内容
本发明的目的是提供一种重力热管工作流体，用于重力热管冷却。
本发明的实施方式涉及一种重力热管，所述重力热管的工作流体选自HFO-1234ze(Z)、HFO-1234ze(E)、HFO-1336mzz(Z)、HFO-1336mzz(E)、HFO-1224yd(Z)、HFO-1233zd(E)及其混合物。在优选的实施方案中，所述工作流体选自HFO-1234ze(Z)、HFO-1234yf、HFO-1233zd(E)、HFO-1224yd(Z)或其混合物。在更优选的实施方案中，所述工作流体为HFO-1234ze(Z)。
HFO-1234ze(Z)，也即，顺式-1,3,3,3-四氟丙烯，分子式为CHFCHCF3，分子量为114.04，标准沸点为9.72℃，临界温度为150.12°，临界压力为3.53MPa。
本发明提供一种使用重力热管工作流体的方法，在所述重力热管中使用包含HFO-1234ze(Z)的工作流体。
在优选的实施例中，所述工作流体仅由HFO-1234ze(Z)组成。
在优选实施例中，重力热管在0℃到100℃的温度下工作。
本发明的工作流体适用于直接替代最初设计使用HFC-245fa，HFC-134a或R410a作为工作流体的重力热管。
本发明的重力热管装置采用分离的蒸发段和冷凝段的设计，所述蒸发段和冷凝段通过管道连接。本发明的重力热管装置可实现远距离热量传输，并且可根据需求调节热交换面积比 以满足不同规模IDC的制冷要求。作为优选，本发明的重力热管为平板重力热管。
本发明的重力热管装置特别适用于电子设备的冷却，例如计算机、通信基站、服务器或数据中心。
与现有技术相比，本发明的重力热管工作流体具有以下优势：
(1)具有优良的环境性能，ODP值为0，GWP值<1；
(2)具有良好的传热性能，其代表反应热物理和传热综合性能的工质准则数M'均高于HFC-245fa，而HFC-245fa是目前冷却IDC的首选工作流体；
(3)在0℃-100℃的工作温度范围内，具有良好的热交换性能和较低的饱和蒸气压，可以降低使用该工作流体的系统的制造成本；
(4)稳定性好，安全性高。
本发明的重力式热管(即热虹吸管)工作流体准则数M'的具体表达式如下：
Figure PCTCN2019130393-appb-000001
其中，准则数M'的量纲为
Figure PCTCN2019130393-appb-000002
L为汽化潜热，单位(KJ/Kg)；ρ l为饱和液体密度，单位kg/m 3；k l为饱和液体热导率，单位W/(m·K)；μ l为液体动力黏度，单位Pa·s。
本发明重力热管工作流体的ODP值通过测试CFC-11作为参考值1.0而获得，GWP值通过使用CO2作为参考值1.0(100年)而获得。
附图说明
图1为重力热管工作流体在0℃-100℃的温度范围内的饱和蒸汽压；
图2为重力热管工作流体在0℃-100℃的温度范围内的准则数M’；
图3为重力热管装置的工艺流程示意图。
具体实施方式
下面结合具体实施例来对本发明进行进一步说明，但并不将本发明局限于这些具体实施方式。本领域技术人员应该认识到，本发明涵盖了权利要求书范围内所可能包括的所有备选 方案、改进方案和等效方案。
本发明的实施例涉及用于热管(例如重力型热管)的工作流体，特别是用于冷却如计算机、通信基站、服务器或互联网数据中心(IDC)之类的电子设备的工作流体。热管利用工作流体的相变(如液相和气相之间的相变)将热量从一个区域转移到另一个区域。热管正常工作需要饱和的工作流体，工作流体在蒸发区域吸收潜热(蒸发热)从液态蒸发成气态，在冷凝区域从气态冷凝成液态释放潜热。
由于热管在饱和条件下工作(即热管中的液相和气相共存)，选择工作流体时要考虑的第一个因素就是工作温度范围，所述工作温度范围介于工作流体的三倍冰点和临界点之间。实际上，任何给定流体的工作温度范围都较小，因为热管所能携带的热量在接近冰点和临界温度时急剧下降。如果工作温度过高，工作流体可能无法冷凝；但是，如果工作温度过低，工作流体将无法蒸发。对于冷却电子设备的应用，例如IDC中的应用，工作温度范围通常在0℃-150℃之间，更常见的是在0℃-100℃之间。
许多潜在的工作流体可以在该温度范围内起作用，对工作流体的正确选择将取决于与工作流体特性相关的许多因素。
气候变化是急迫的问题，任何工作流体都不应该产生或很少产生环境影响，即臭氧破坏潜能(ODP)为0，全球温室潜能(GWP)较低。基于ODP和GWP值，几种备选工作流体如表1所示。从表1可以看出，所有的工作流体ODP值均较低或为0。一部分工作流体含有较高的GWP值，一部分工作流体GWP值较低。基于环境影响因素考虑，符合要求的工作流体包括HFO-1234yf、HFO-1234ze(Z)、HFO-1234ze(E)、HFO-1233zd(E)、HCFO-1224yd(Z)、HFO-1336mzz(Z)、HFO-1336mzz(E)，以及一些它们的混合工质。
表1.不同工质的ODP和GWP值
工质 ODP GWP
HFC-134a 0 1430
R410a 0 2100
HCFC-22 0.05 1810
HFC-245fa 0 1050
HFO-1234yf 0 <1
HFO-1234ze(Z) 0 <1
HFO-1234ze(E) 0 <1
HFO-1233zd(E) 0.00034 1
HCFO-1224yd(Z) 0.00012 <1
HFO-1336mzz(Z) 0 2
HFO-1336mzz(E) 0 7
由于热管采用工作流体发生相变(液体和气体)的方式使热量发生转移，工作流体应在工作温度范围内具有足够的饱和蒸汽压，以传导足够的热量。除此之外，工作流体的饱和蒸气压在工作范围内不应过高，否则会对管壳产生过高的压力。因此，好的工作流体在工作温度范围内应该具有合适的饱和蒸汽压。此外，作为温度函数的压力变化不应太剧烈。
图1给出了不同备选工作流体作为不同温度下的饱和蒸汽压变化曲线，如图1所示，大部分的工作流体在工作温度0-100℃范围内满足饱和蒸汽压要求，其中一部分有更好的压力和温度关联表现。例如，HFO-1336mzz(E)、HFO-1234ze(Z)、HFO-1233zd(E)、HCFO-1224yd(Z)和HFO-1336mzz(E)在相同温度下的饱和蒸气压与HFC-245fa接近，这些特性表明，这些工作液可以是HFC-245fa的替代物，也可以说，当用任何这些工作液体替换HFC-245fa时，没有必要对管道进行修改。
另一方面，相同温度下R410a、HCFC-22、HFC-134a、HFO-1234yf和HFO-1234ze(E)对比HFC-245fa具有明显更高的饱和蒸汽压，也拥有较高的压力和温度关联度，这些特性意味着这些工作流体不能作为工作流体代替HFC-245fa，其中，R134a和HFC-1234yf有相似的性质，HFC-1234yf可以作为R134a的替代品。有趣的是，反式异构体HFO-1234ze(E)与其顺式异构体HFO-1234ze(Z)相比，具有更高的饱和蒸气压和温度依赖性。
可以看出，拥有更好性质的工作流体包括：HFO-1336mzz(E)、HFO-1234ze(Z)、HFC-245fa、HCFO-1224yd(Z)、HFO-1233zd(E)和HFO-1336mzz(Z)，这些工作流体在100℃时的饱和蒸汽压低于或仅仅略高于1.0MPa，HFO-1336mzz(E)、HFO-1234ze(Z)、HFC-245fa、HCFO-1224yd(Z)、HFO-1233zd(E)和HFO-1336mzz(Z)的饱和蒸气压较低即对管壳强度要求低，因此降低了系统的制造成本。更重要的是，这些工作液体的蒸汽压与温度关联性与HFC-245fa非常相似，HFC-245fa是目前最常用的热管工作流体。这些工作流体的类似的压力-温度分布，表明这些工作流体可以是当前热管系统中的HFC-245fa的“可替代物”，并且对于当前系统没有或仅需要很小的改动。
除了上述考虑之外，工作流体中固有的几个特性会影响其作为热管工作流体的性能。例如，高的液体密度和高蒸发潜热减少了输送给定功率所需的流体流量(即所需的工作流体的量)，低的液体粘度使液体压降降低。
考虑到工作流体的这些特性，可以使用一个准则数(或准则图)来评估一系列备选工作流体的相对性能。对于重力式热管(无管芯热管或热虹吸管)，其准则数(M’)定义如下：
Figure PCTCN2019130393-appb-000003
式中准则数M’的量纲为
Figure PCTCN2019130393-appb-000004
其中L为汽化潜热，单位(kJ/kg)；ρ l为饱和液体密度，单位kg/m3；μ l为液体动力粘度，单位Pa·s。
图2给出了几个备选工作流体在温度为15～95℃范围内的准则数(M’)，如图所示，HFO-1234ze(Z)温度范围内的准则数最高，甚至高于HFC-245fa。因此，HFO-1234ze(Z)不仅适用于替代目前热管系统中HFC-245fa，而且与HFC-245fa相比，具有较高的性能。其他工作流体拥有较高准则数的包括HFO-1233ze(E)、HFO-1224yd(Z)、HFO-1336mzz(Z)和HFO-1234ze(E)。相比较而言，作为现代汽车冷却液的HFO-1234ze(E)，其在该温度范围下的准则数明显低于其他工作流体。有趣的是，在此温度范围内，顺式异构体HFO-1234ze(Z)的优点明显高于其反式异构体HFO-1234ze(E)。因此，HFO-1234ze(z)将是比HFO-1234ze(e) 更优的工作流体，因为其具有较低的压力-温度依赖性和较大的准则数。
蒸发潜热涉及单位质量的工作流体发生相变(例如，从蒸发区的液相到气相)时的热传递量，如上述准则数公式所示，工作流体的蒸发潜热越高，其准则数也越高。因此，在其他条件相同的情况下，具有较高潜热的工作流体是首选的，因为与蒸发潜热较低的工作流体相比，它们用较少的工作流体即可传递相同的热量。下表2给出了几种工作流体和混合工质的蒸发潜热：
表2.不同工质蒸发潜热
工作流体 蒸发潜热23℃(KJ/Kg)
HFC-245fa 192.4
HFO-1234ze(Z) 207.4
HFO-1336mzz(E) 160.00
HCFO-1233zd(E) 192.2
HFO-1234yf 147.0
HFO-1234ze(E) 168.4
HCFO-1224yd 164.9
HFO-1336mzz(Z) 169.4
R1234ze(Z)/R1336mzz(E)＝80/20 199.0
R1234ze(Z)/R1336mzz(E)＝20/80 169.6
R1234ze(Z)/R1224yd＝90/10 202.3
R1234ze(Z)/R1224yd＝10/90 168.1
R1234ze(Z)/R1233zd(E)＝90/10 204.9
R1234ze(Z)/R1233zd(E)＝10/90 192.7
R1233zd(E)/R1224yd＝90/10 188.9
R1233zd(E)/R1224yd＝10/90 167.0
R1336mzz(E)/R1224yd＝90/10 188.9
R1336mzz(E)/R1224yd＝10/90 165.3
如上表2所示，几种工作液体具有很高的蒸发潜热，使用这些工作流体，用较少的量(质量)就能达到同样的传热量。
用重力热管装置测试了本发明工作流体的冷却性能，所述重力热管装置由两套紧靠在一起且相互独立的热管系统组成，一个重力热管系统使用HFC-245fa作为对比，另一个重力热管系统使用本发明涉及的工作流体进行测试。该紧靠的系统可以清晰对比两种工作流体，此外，单管重力热管系统也被使用进行工作流体性能测试。两种系统的测试结果都将被上传到计算机中进行建模和计算。
重力热管装置的工艺流程图如图3所示，实验过程中，同时开启内外侧背板进行热管循环实验。实验工况：室内进风干球温度为35℃，室内进风湿球温度为22℃，对于测试组(HFO-1234ze)系统和对比组(HFC-245fa)系统，空气循环量是相同的，两个系统的循环水温度也保持一致(进口：15℃，出口：20℃)。
与HFC-245fa相比，工作流体的热循环性能参数见下表3，在相同的进出口水温度下，热交换能力和几种备选工作流体的表现系数均优于HFC-245fa，且能维持冷通道进风区域温度符合国家标准规定要求的18～27℃。
表3重力热管循环测试结果
Figure PCTCN2019130393-appb-000005
Figure PCTCN2019130393-appb-000006
如上表3所示，本发明涉及工作流体的性能参数整体优于现有技术使用的工作流体，像HFC-245fa。例如，备选工作流体需要更少的充注量就可以达到相同的换热量，工作流体的制冷性能系数优于HFC-245fa，这意味着这些工作流体相比于HFC-245fa具有更好的使用效果。除此之外，这些工作流体大多拥有更低的系统压力，例如HFO-1234yf和HFO-1234ze(E)，这意味着其代替HFC-245fa使用的过程安全性是可以保证的，不需要对热管进行加固改良。
此外，相较于HFC-245fa，本发明的工作流体具有更低的最优需求量(质量)，更加环保。
上述数据表明本发明的HFO和HCFO化合物是热管，特别是重力式热管的优良工作流体。本发明的工作流体包括HFO-1234ze(Z)、HFO-1234ze(E)、HFO-1234yf、HFO-1336mzz(Z)、HFO-1336mzz(E)、HFO-1224yd(Z)和HFO-1233zd(E)，及其混合工作流体。本发明的首选工作流体包括HFO-1234ze(Z)、HFO-1233zd(E)、HFO-1234yf、HFO-1336mzz(E)和HFO-1224yd(Z)，及其混合工作流体。
这些工作流体的混合物可以包括两种组分，其比例为1∶99，优选10∶90，或20∶80，或30∶70，或40∶60，或50∶50，以及它们之间的任何比例。作为优选，HFO-1234ze(Z)，HFO-1233zd(E)或HFO-1336mzz(E)作为其中一个组分。本发明涉及的混合流体包括：
HFO-1234ze(Z)/HFO-1336mzz(E)在合适的比例下混合(如80/20)；
HFO-1234ze(Z)/HFO-1336mzz(E)在合适的比例下混合(如20/80)；
HFO-1234ze(Z)/HCFO-1224yd在合适的比例下混合(如90/10)；
HFO-1234ze(Z)/HCFO-1224yd在合适的比例下混合(如10/90)；
HFO-1234ze(Z)/HCFO-1233zd(E)在合适的比例下混合(如10/90)；
HFO-1234ze(Z)/HCFO-1233zd(E)在合适的比例下混合(如90/10)；
HCFO-1233zd(E)/HCFO-1224yd在合适的比例下混合(如10/90)；
HCFO-1233zd(E)/HCFO-1224yd在合适的比例下混合(如90/10)；
HFO-1336mzz(E)/HCFO-1224yd在合适的比例下混合(如90/10)；
HFO-1336mzz(E)/HCFO-1224yd在合适的比例下混合(如10/90)。
出乎意料的是，本发明的HFO工作流体比HFO-1234ze(E)和HFC-245fa具有更好的性能参数。HFC-245fa被认为是重力热管的良好替代工作流体,因其热物理性质使其适用于多种传热和工作流体应用，如离心式冷却器、能量回收的有机朗肯循环、低温制冷和被动冷却装置中的显热传递。
此外，反式异构体HFO-1234ze(E)被开发为第四代制冷剂以替代诸如HFC-134a等制冷剂。HFO-1234ze(E)具有零臭氧消耗潜能(ODP＝0)、极低的全球升温潜能(GWP＜1)，甚至低于 CO2。HFO-1234ze(E)已经被用作冷却器、热泵和超市制冷系统中的工作流体。然而，我们发现顺式异构体HFO-1234ze(Z)实际上比反式异构体HFO-1234ze(E)更适用于用于冷却电子设备、互联网数据中心等的热管(特别是重力热管)。因为顺式异构体HFO-1234ze(Z)拥有更低的系统压力，同时当转移相同热量时所需的工作流体量更少。
本发明的具体案例已经利用上述几组例子进行说明。本领域的技术人员可以理解，这些示例仅用于说明，并不能限制本发明的范围，并且可以在不偏离本发明保护范围的情况下进行其他修改和变化。因此，本发明的范围仅限于附带声明。

Claims (13)

  1. 一种重力热管，其特征在于：所述重力热管的工作流体选自HFO-1234ze(Z)、HFO-1234ze(E)、HFO-1234yf、HFO-1336mzz(Z)、HFO-1336mzz(E)、HFO-1224yd(Z)、HFO-1233zd(E)及其混合物。
  2. 根据权利要求1所述的重力热管，其特征在于：所述工作流体选自HFO-1234ze(Z)、HFO-1234yf、HFO-1233zd(E)、HFO-1336mzz(E)、HFO-1224yd(Z)及其混合物。
  3. 根据权利要求2所述的重力热管，其特征在于：所述工作流体为HFO-1234ze(Z)。
  4. 根据权利要求1所述的重力热管，其特征在于：所述工作流体为混合物时，1234ze(Z)、HFO-1233zd(E)或HFO-1336mzz(E)作为其中一种组分。
  5. 根据权利要求4所述的重力热管，其特征在于：作为工作流体的混合物包括：
    HFO-1234ze(Z)/HFO-1336mzz(E)；HFO-1234ze(Z)/HFO-1336mzz(E)；
    HFO-1234ze(Z)/HCFO-1224yd；HFO-1234ze(Z)/HCFO-1224yd；
    HFO-1234ze(Z)/HCFO-1233zd(E)；HFO-1234ze(Z)/HCFO-1233zd(E)；
    HCFO-1233zd(E)/HCFO-1224yd；HCFO-1233zd(E)/HCFO-1224yd；
    HFO-1336mzz(E)/HCFO-1224yd；和HFO-1336mzz(E)/HCFO-1224yd。
  6. 根据权利要求1所述的重力热管，其特征在于：所述工作流体用于直接替代HFC-245fa，HFC-134a或R410a用于原设计使用HFC-245fa，HFC-134a或R410a作为工作流体的重力热管。
  7. 根据权利要求1所述的重力热管，其特征在于：所述重力热管为平板重力热管。
  8. 根据权利要求1所述的重力热管，其特征在于：所述重力热管用于冷却电子设备、计算机、通信基站、服务器或数据中心。
  9. 一种使用权利要求1所述的重力热管进行冷却的方法。
  10. 根据权利要求9所述的冷却方法，其特征在于：所述工作流体选自HFO-1234ze(Z)、HFO-1234ze(E)、HFO-1336mzz(Z)、HFO-1336mzz(E)、HFO-1224yd(Z)、HFO-1233zd(E)及其混合物。
  11. 根据权利要求9所述的冷却方法，其特征在于：所述工作流体选自HFO-1234ze(Z)、HFO-1234yf、HFO-1233zd(E)、HFO-1224yd(Z)及其混合物。
  12. 根据权利要求9或10所述的冷却方法，其特征在于：所述工作流体为HFO-1234ze(Z)。
  13. 根据权利要求9所述的冷却方法，其特征在于：所述重力热管在0-100℃之间工作。
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