WO2010016842A1 - Système d'alimentation et de réfrigération en cascade - Google Patents

Système d'alimentation et de réfrigération en cascade Download PDF

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Publication number
WO2010016842A1
WO2010016842A1 PCT/US2008/072463 US2008072463W WO2010016842A1 WO 2010016842 A1 WO2010016842 A1 WO 2010016842A1 US 2008072463 W US2008072463 W US 2008072463W WO 2010016842 A1 WO2010016842 A1 WO 2010016842A1
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WO
WIPO (PCT)
Prior art keywords
refrigeration
electric power
power
absorption
refrigeration system
Prior art date
Application number
PCT/US2008/072463
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English (en)
Inventor
H. Ezzat Khalifa
Original Assignee
Syracuse University
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
Application filed by Syracuse University filed Critical Syracuse University
Priority to PCT/US2008/072463 priority Critical patent/WO2010016842A1/fr
Publication of WO2010016842A1 publication Critical patent/WO2010016842A1/fr

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Classifications

    • 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
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • 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
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/02—Sorption machines, plants or systems, operating continuously, e.g. absorption type without inert gas

Definitions

  • the present invention relates generally to combined power and cooling generation systems, and, more particularly, to a combined power and refrigeration cascade system (“PARCS”) that includes an electric power system (PS) that produces both electric power and medium-to-high-grade waste heat that can be used for providing the cooling and power supply needs of data centers and the like.
  • PARCS combined power and refrigeration cascade system
  • PS electric power system
  • On-site power generation systems using combustion engines (for example, gas turbines) or fuel cells allow much higher energy efficiency through the utilization of the prime mover's waste heat.
  • combustion engines for example, gas turbines
  • fuel cells allow much higher energy efficiency through the utilization of the prime mover's waste heat.
  • CHP combined heat and power
  • CCP combined cooling and power
  • CCHP combined cooling, heat and power
  • CHP combined heat and power
  • the basic distinction is the mode of waste heat utilization, which is dictated by the type of load(s) served by the system.
  • An important factor in determining the economic effectiveness of these systems is the matching of their power and thermal output to the time varying power and thermal demands of the load(s).
  • the power and thermal output (heating or cooing) of an on-site system should be fully utilized by the load at all times, which occurs very rarely except when the power and thermal (e.g., cooling) demands are strongly correlated, as they are in computer data centers.
  • CCP and CCHP systems typically use absorption chillers to utilize the waste heat for cooling.
  • the most common type is single-effect or double effect LiBr-H 2 O absorption systems (ABS), modified to operate with the lower temperature waste heat from the power system.
  • a CCP system comprising a 30%-efficient power generation system driving an Rl 34a vapor compression (“VC") water chiller (COP 0 - 6) and a double-effect absorption chiller (COP 3 ⁇ 1.1) can achieve a fuel-based cooling COP higher than 2.4 under typical water-cooled chiller operating conditions (5°C evaporator/°35C condenser).
  • VC vapor compression
  • COP 3 ⁇ 1.1 double-effect absorption chiller
  • LiBr-H 2 O ABS use water as a refrigerant and cannot provide sub zero 0 C refrigeration, making such systems unsuitable for low-temperature refrigeration applications.
  • an on-site power generation system may be grid-independent (see DEFINITIONS section), especially to be grid- independent with good temporal matching, and even more especially to be grid-independent with good temporal matching under a condition of time dependent load(s).
  • the on-site power generation system it would be useful and desirable for the on-site power generation system to be able to provide combined power generation and refrigeration for loads in which the refrigeration loads are strongly correlated with the power needs, as they are in computer data centers.
  • Various embodiments of the present invention may exhibit one or more of the following objects, features and/or advantages:
  • a power and refrigeration cascade system includes an electric power system, a refrigeration system, and an absortion system.
  • the refrigeration system is powered at least in part by the electric power system.
  • the refrigeration system is thermally coupled to a component, wherein the component is the electric power system and/or a load powered by the electric power system.
  • the absorption system is thermally coupled to the refrigeration system and configured to remove heat rejected by the refrigeration system. The thermal coupling between the refrigeration system and the absorption system enables a refrigeration system condensing temperature of less than approximately twenty degrees Celsius.
  • an on-site power generation system includes an electric power system and a refrigeration cascade system.
  • the refrigeration cascade system is thermally coupled to the electric power system.
  • the refrigeration cascade system is configured to temporally match cooling needs of a load coupled to the electric power system based on actual power supplied to the load.
  • a refrigeration cascade system includes a refrigeration system and an absorption system.
  • the refrigeration system is configured: (i) to be powered at least in part by electricity; and (ii) to be thermally coupled to a load powered by electricity.
  • the absorption system thermally coupled to the refrigeration system and configured to remove heat rejected by the refrigeration system.
  • a datacenter power and cooling system includes an electric power system, a server rack, a refrigeration system and an absorption system.
  • the server rack is powered by the electric power system.
  • the refrigeration system is powered at least in part by the electric power system and is thermally coupled to the server rack to remove heat from it.
  • the absorption system is thermally coupled to the refrigeration system and configured to remove heat rejected by the refrigeration system.
  • the thermal coupling between the refrigeration system and the absorption system enables a refrigeration system condensing temperature of less than approximately twenty degrees Celsius.
  • a method of reducing energy consumption by a computer chip powered by a power source includes several steps.
  • the computer chip is thermally coupling to a refrigeration system.
  • the refrigeration system is powered, at least in part, by the power source.
  • the refrigeration system is thermally coupling to an absorption system. The thermal coupling between the refrigeration system and the absorption system enables a refrigeration system condensing temperature and an absorption system evaporating temperature which are within less than approximately ten degrees Celsius of each other.
  • Fig. 1 is a high-level energy flow diagram of a first embodiment of a PARCS according to the present invention.
  • Fig. 2 is a graphical illustration that illustrates a minimum waste heat utilization efficiency in an ABS generator according to an embodiment of the present invention.
  • Fig. 3 is a high level schematic that illustrates potential savings from on-site
  • Fig. 4 is a block diagram that illustrates a PARCS with distributed RS according to an embodiment of the present invention.
  • Fig. 5 is a graph showing the power allocation of the first embodiment PARCS.
  • Fig. 6 is a graph showing the evolution of active and passive power dissipation in
  • Fig. 7 is a graph showing typical CMOS chip thermal characteristics of the first embodiment PARCS.
  • a first embodiment of an on-site combined Power And Refrigeration Cascade System (“PARCS”) 100 includes: fuel supply 101; electric power system ("PS") 102; exhaust to abs system line 103; generator 104; abs component 106; valve 108; condenser 110; valve 112; valve 114; solution HX 116; pump 118; valve 120; absorber 122; valve 124; evaporator 126; chilled water return manifold assembly 128; condensers 130; compressors 131; evaporators 132; server rack assembly 133; and DC power to data center line 134.
  • PS electric power system
  • the PS is preferably a heat-engine-driven electric generator or a fuel cell, that produces both DC electric power and medium-to-high-grade waste heat.
  • the components are interconnected as shown in Figure 4 to make the PARCS system 100.
  • the electric power output of the PS which could be DC, AC or a combination of the two, is split between: (i) DC power to data center line 134 (which supplies an electric load in the form of server rack assembly 133); and (ii) a complementary portion supplied to an electrically-driven refrigeration system (RS) 128, 130, 131, 132, 133.
  • RS electrically-driven refrigeration system
  • the RS hardware may take various forms, now known or to developed in the future, such as, vapor-compression (VC), reversed Brayton (RB), reversed Stirling (RS), thermo-electric (TE), magneto caloric (MC), or other types of refrigeration systems.
  • VC vapor-compression
  • RB reversed Brayton
  • RS reversed Stirling
  • TE thermo-electric
  • MC magneto caloric
  • the heat rejected by the RS is pumped to ambient air by means of an absorption heat pump system (ABS) 104, 106, 108, 110, 112, 114, 116, 118, 120, 122, 124, 126.
  • ABS absorption heat pump system
  • the ABS is activated by the exhaust heat from the power system over line 103.
  • the ABS condenser 110 and absorber 122 could be either water-cooled or air cooled (water-cooled is preferred because of its higher efficiency and compactness).
  • the ABS and the RS subsystems are thermally integrated in a high-efficiency thermo- mechanical (e.g., ABS/VC) or thermo-electric (e.g., ABS/TE) cascade.
  • the RS is depicted as a VC system (VCS).
  • ⁇ is the thermal efficiency of the PS
  • ⁇ is the fraction of its waste heat that is not recoverable (e.g., radiation loss)
  • ⁇ is the waste heat utilization efficiency in the ABS generator
  • ⁇ is the fraction of the PS output needed to drive the RS.
  • the coefficient of performance (COP) of the ABS based on its generator heat input is COP a and that of the RS based on its work input is COP r .
  • the COP of the RS depends on its cold- and warm-side temperatures (the evaporator and condenser saturation temperatures in the VCS).
  • the heat rejection temperature of the RS is dictated by the evaporator temperature of the ABS, which, for LiBr- H 2 O systems, is typically in the 5-10 0 C range.
  • the refrigeration system may be either centralized and integrated with the ABS using a combined condenser/evaporator, or distributed, with one (or more) RS per computer rack.
  • the heat rejected from the distributed RS units is transferred to chilled water distributed from a central waste-heat driven ABS.
  • the RS and the ABS could be coupled in one of at least two ways: (i) in the centralized configuration, an integrated condenser/evaporator heat exchanger of superb effectiveness allows the condensing temperature in the VCS to be only a few degrees higher than the evaporating temperature in the ABS.
  • the VCS evaporator chills a heat transfer fluid (anti-freeze) that is distributed to liquid-cooled rack cabinets; or (ii) in the distributed configuration, the ABS chilled water is delivered via a supply manifold to the VCS condenser in each computer rack, and returned to the ABS evaporator (water chiller) via a return manifold.
  • the VCS evaporator in the rack is used either to chill air that cools the electronic components in the rack, or to cool the electronic components directly.
  • the condensing temperature of the VCS could be maintained herein 15 0 C, compared with the 35°C typical of water-cooled conventional VCS.
  • the COP r of the RS is substantially higher than that of a conventional VCS.
  • the lower RS condensing temperature in the PARCS of an embodiment of the present invention also enables lower temperature refrigeration with less deterioration in capacity and COP r compared with a conventional VCS. This is one of the main advantages of the PARCS of an embodiment of the present invention. This advantage may also obviate the need for 2-stage VC and liquid injection to moderate the compressor discharge temperature in low- temperature refrigeration, where high compression pressure ratios are experienced (Liquid injection degrades refrigeration performance).
  • an important advantage of the PARCS of an embodiment of the present invention is its suitability for computer data centers.
  • the power consumption is dominated by computer needs (DC power), and the refrigeration load is nearly equal to computer power dissipation. Therefore, referring to the notation in Figure 1 :
  • Fig. 2 shows the minimum value of ⁇ that satisfies the constraint implied by Eq. (4) for typical single-effect and double-effect ABS COP a . It can be seen that higher waste heat utilization efficiencies are required in order to satisfy the matching constraint (Eq. 4a) when a higher efficiency PS is employed. These conditions favor power generation systems with a higher-temperature waste heat, such as gas turbines, or molten-carbonate or solid-oxide fuel cells. A high waste heat utilization efficiency could also be achieved with medium-temperature waste heat if it is mostly in latent form (for example, extracted from a condensing PS exhaust effluent).
  • ⁇ and ⁇ depend on the type of the PS selected, and ⁇ and COP 3 depend on the type of the ABS that is compatible with the temperature and quality of the selected PS waste heat.
  • a PS whose waste heat that is at 100°C or lower would be compatible with a single-effect ABS with a typical COP 3 of about 0.6
  • a PS whose waste heat that is available at 125 0 C or higher would be compatible with a double-effect ABS with a typical COP 3 higher than 1.0.
  • the higher the temperature at which the PS waste heat is available the higher the COP a of the ABS and the waste heat utilization efficiency (for a given ABS cycle).
  • another important aspect of the PARCS of an embodiment of the present invention when used with data centers is its ability to generate "native" DC power, possibly at several voltages suitable for powering computer systems.
  • Fig. 4 shows a preferred embodiment of PARCS with distributed RS in further detail.
  • Fig. 4 includes a fuel cell PS, distributed single-stage refrigeration systems (one per rack), and a waste-heat driven water-cooled double-effect LiBr-H 2 O ABS providing chilled water to cool the condensers of the distributed VC RS.
  • the fuel cell is of the medium- or high-temperature type (for example, phosphoric acid for medium-temperature, or molten-carbonate or solid-oxide for high- temperature).
  • Figure 4 shows VC RS, a reversed Stirling, TE or MC RS could also be used.
  • FIG. 5 shows the fraction of the PS output diverted to the VCS ( Figure 1) for cooling a data center over a range of evaporator temperatures from 1O 0 C (typical for air-conditioning), down to -40 0 C (typical for low-temperature refrigeration in supermarkets).
  • the PS is assumed to be a fuel cell with a thermal efficiency of 40% and a waste heat temperature of ⁇ 150°C ( ⁇ 300°F).
  • the ABS is assumed to be a water-cooled double-effect LiBr-H 2 O type operated at a moderate generator temperature ( ⁇ 100°C) to achieve a thermal COP a of 1.05 with heat rejection (absorber and condenser) at 35°C, and an evaporator saturation temperature of 10 0 C.
  • Two lines are shown, one representing matching the data center power demands (Eq. 1) and the other representing matching constrained by the capacity of the waste-heat-driven ABS.
  • the PARCS of an embodiment of the present invention is an excellent "match" over a wide range of cold-side temperature for the type of correlated computing and refrigeration power demands presented by a data center.
  • the PARCS of an embodiment of the present invention allows efficient low temperature refrigeration.
  • the heat dissipation rate of computer systems can depend both on the computing performance (for example, clock rate) and operating temperature:
  • Q t F(PJ 1 ) , Eq. (5)
  • Q d is the computing power consumption at a computing performance level P and internal temperature of the heat dissipating component, Tj. This temperature is related to the coolant temperature, T 0 , the cooling scheme, and the heat dissipation rate, Q d through the familiar heat transfer equation:
  • Re represents the overall thermal resistance from the chip core to the coolant, which depends on both the cooling scheme and the internal thermal resistance of the electronic component (e.g., CPU die).
  • the relationship represented by Eq. (5) can be inferred from the power dissipation characteristics of CMOS chips, which can be divided into active and passive components (the active component depends on the clock frequency; the passive component is present even if the clock is stopped). Passive power dissipation has surpassed active power dissipation in modern high- density, low voltage CMOS CPUs with low threshold voltage (as shown in Fig. 6).
  • the active component is nearly independent of temperature, but the passive component, which is dominated by the dissipative effect of subthreshold leakage currents, is a strong function of temperature.
  • active power can depend on clock frequency, f, and voltage, V:
  • Eq. 11 the actual relationship (Eq. 11) can be much more complex than the one derived above, but the relative trends can be examined by using the simple model represented by Eq. (10), in which the clock frequency is used as a surrogate for the performance, P.
  • Fig. 7 illustrates the relationship implied by Eq. (10) in normalized form. Charts of this qualitative nature can be produced for a chip, an entire motherboard, a server, or a rack, for other performance metrics, and cooling schemes (Re).
  • the iso-performance lines in Fig. 7 are only mildly curved and may be treated as straight lines in simplified parametric analysis. Therefore, whether operating at a lower temperature would lead to a reduction in heat dissipation for a given computing performance level and cooling scheme will depend on the parameter:
  • Fig. 8 presents energy savings trends of the PARCS of an embodiment of the present invention relative to a conventional grid-supplied system operating with a 1O 0 C saturated evaporator temperature and 35 0 C saturated condenser temperature, designated here as CS- 10/35 0 C.
  • the savings displayed in Fig. 9 does not include the potential savings from the use of on-site DC power supply in PARCS of an embodiment of the present invention.
  • the PARCS of an embodiment of the present invention provides primary energy savings in excess of 33% compared with the CS-10/35 0 C baseline, even if operated at the same 10/35 0 C conditions as CS- 10/35 0 C. This is due to the higher thermal efficiency of the fuel cell power plant, and because of the utilization of the fuel cell's waste heat in the ABS to lower the VCS condensing temperature.
  • Fig. 9 displays the variation of the total power requirements (for data processing and refrigeration), normalized with respect to the data processing (IT) power demands of a conventional grid-connected system cooled by a 10 0 C evaporator.
  • the power rating of the refrigeration equipment and the total power demand of the data center are considerably more favorable with PARCS of an embodiment of the present invention compared with a conventional VCS at any low-side temperature.
  • Fig. 10 compares the power demands of PARCS of an embodiment of the present invention relative to a conventional system, taking into account the advantage of on-site DC power generation.
  • the grid-connected power supply system shown in Fig. 3 has an overall efficiency of 48% when operated at conventional data center temperature.
  • the power conversion efficiency is raised to 75% as a result of the elimination the various AC/DC conversion steps.
  • the PARCS power conversion hardware is assumed to be maintained at the same temperature as in a conventional data center.
  • a ⁇ 0.75%/°C.
  • the use of PARCS of an embodiment of the present invention can result in substantial reductions in primary energy consumption and power ratings of power- and cooling-intensive applications such as data centers, and the like.
  • multiple PARCS with appropriate spares are used, reliable grid- independent operation can be achieved.
  • fuel cells are used in PARCS of an embodiment of the present invention, DC power can be supplied directly to the load at multiple voltages, eliminating the multiple energy-dissipating AC/DC electric power conversion and conditioning steps in a grid-connected power supply system.
  • the primary energy savings potential of the DC power generation and the RS/ABS cooling cascade afforded by a fuel-cell based PARCS could exceed 60%, even with low-temperature refrigeration.
  • the benefits of the latter for data centers include higher reliability, improved performance, enhanced ability to handle the ever increasing heat fluxes produced by modem computer systems, for newer denser low voltage CMOS chips, and reduction in leakage power dissipation.
  • the PARCS of an embodiment of the present invention is ideally suited to data centers, where the electric and refrigeration loads are steady and strongly correlated.
  • the matching parameter, ⁇ can be increased or decreased by changing the VCS condenser/ ABS evaporator temperature. By raising this temperature, it is possible to lower the maximum generator temperature and maximum solution concentration in the PARCS' ABS than for a conventional ABS unassisted by the cascade effect of the PARCS. This also results in a higher COP 3 for the PARCS' ABS.
  • PARCSs can be constructed from commercially-available phosphoric acid fuel cells, double effect LiBr-H 2 O absorption chillers, and conventional vapor compression refrigeration systems, it can also be configured to operate with other thermo-mechanical power generation systems such as gas turbines (micro-turbines) and gas engines, or with advanced high-temperature fuel cells (molten carbonate and solid oxide). It can also be configured with other RS such as Stirling, thermoelectric or magneto-caloric systems, and with other types of waste heat-activated heat pumps besides LiBr-H 2 O ABS (e.g., adsorption).
  • thermo-mechanical power generation systems such as gas turbines (micro-turbines) and gas engines, or with advanced high-temperature fuel cells (molten carbonate and solid oxide).
  • RS such as Stirling, thermoelectric or magneto-caloric systems, and with other types of waste heat-activated heat pumps besides LiBr-H 2 O ABS (e.g., adsorption).
  • steps in method steps or process claims need only be performed in the same time order as the order the steps are recited in the claim only to the extent that impossibility or extreme feasibility problems dictate that the recited step order (or portion of the recited step order) be used.
  • This broad interpretation with respect to step order is to be used regardless of whether the alternative time ordering(s) of the claimed steps is particularly mentioned or discussed in this document.

Abstract

La présente invention porte d'une manière générale sur des systèmes combinés de génération d'alimentation et de refroidissement, et, plus particulièrement, sur un système combiné d'alimentation et de réfrigération en cascade (« PARCS ») qui comprend un système d'alimentation électrique (PS) qui produit à la fois de l'énergie électrique et de la chaleur résiduelle de qualité intermédiaire à élevée qui peut être utilisée pour répondre aux besoins de refroidissement et d'alimentation électrique de centres de données et analogues.
PCT/US2008/072463 2008-08-07 2008-08-07 Système d'alimentation et de réfrigération en cascade WO2010016842A1 (fr)

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PCT/US2008/072463 WO2010016842A1 (fr) 2008-08-07 2008-08-07 Système d'alimentation et de réfrigération en cascade

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Cited By (2)

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CN103997875A (zh) * 2013-02-15 2014-08-20 Abb研究有限公司 冷却设备
DE102021203527A1 (de) 2021-04-09 2022-10-13 Robert Bosch Gesellschaft mit beschränkter Haftung Kombinationsvorrichtung und Kombinationssystem

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US20020021557A1 (en) * 1998-08-11 2002-02-21 Fujitsu Limited, Liquid-cooled electronic apparatus
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CN103997875A (zh) * 2013-02-15 2014-08-20 Abb研究有限公司 冷却设备
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DE102021203527A1 (de) 2021-04-09 2022-10-13 Robert Bosch Gesellschaft mit beschränkter Haftung Kombinationsvorrichtung und Kombinationssystem

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