WO2012166338A2 - Système de compresseur hybride et procédés - Google Patents

Système de compresseur hybride et procédés Download PDF

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Publication number
WO2012166338A2
WO2012166338A2 PCT/US2012/037872 US2012037872W WO2012166338A2 WO 2012166338 A2 WO2012166338 A2 WO 2012166338A2 US 2012037872 W US2012037872 W US 2012037872W WO 2012166338 A2 WO2012166338 A2 WO 2012166338A2
Authority
WO
WIPO (PCT)
Prior art keywords
mode
compressor
positive displacement
centrifugal compressor
capacity
Prior art date
Application number
PCT/US2012/037872
Other languages
English (en)
Other versions
WO2012166338A3 (fr
Inventor
Vishnu M. Sishtla
Original Assignee
Carrier Corporation
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 Carrier Corporation filed Critical Carrier Corporation
Priority to CN201280026803.3A priority Critical patent/CN103748425B/zh
Priority to EP12722646.2A priority patent/EP2715254A2/fr
Priority to US13/818,210 priority patent/US20130177393A1/en
Publication of WO2012166338A2 publication Critical patent/WO2012166338A2/fr
Publication of WO2012166338A3 publication Critical patent/WO2012166338A3/fr

Links

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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B31/00—Compressor arrangements
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves

Definitions

  • the disclosure relates to refrigeration. More particularly, the disclosure relates to chiller systems.
  • One aspect of the disclosure involves an apparatus having a centrifugal compressor, a positive displacement compressor, a first heat exchanger, and a second heat exchanger.
  • a plurality of valves are positioned to provide operation in at least two modes. In a first mode, refrigerant is compressed in the positive displacement compressor and the centrifugal compressor at least partially in parallel. In a second mode, refrigerant is compressed in the positive displacement compressor and the centrifugal compressor is offline. In a third mode, refrigerant is compressed in the positive displacement compressor and the centrifugal compressor at least partially in series.
  • the positive displacement compressor may be a screw compressor.
  • FIG. 1 is a schematic view of a chiller system.
  • FIG. 2 is a longitudinal vertical schematic view of a condenser of the system of FIG. 1.
  • FIG. 3 is a longitudinal vertical schematic view of a cooler of the system of FIG. 1.
  • FIG. 4 is a plot of entering condenser water temperature against percent capacity.
  • FIG. 5 is a control flowchart for the system of FIG. 1.
  • centrifugal compressors are typically less effective than positive displacement compressors at providing high head. This renders centrifugal compressors as poor candidates for heat reclaim operation.
  • a hybrid system features a centrifugal compressor and a positive displacement compressor.
  • the exemplary positive displacement compressors are two- or three-rotor screw compressors powered by variable frequency drives.
  • Alternative positive displacement compressors include reciprocating compressors and scroll compressors.
  • FIG. 1 shows a vapor compression system 20 having a compressor subsystem 22.
  • the compressor subsystem 22 includes a first compressor 24 (centrifugal) and a second compressor 26 (positive displacement).
  • both compressors have capacity control features which may be of any well known type (e.g., variable inlet guide vanes for the centrifugal compressor and a slide valve for a screw compressor used as the positive displacement compressor and variable speed drives for both compressors).
  • the compressor subsystem drives refrigerant in a downstream direction 500 along a refrigerant flowpath 30.
  • the flowpath 30 passes, sequentially, through a first heat exchanger 32, an expansion device 34, and a second heat exchanger 36.
  • the first heat exchanger 32 is a heat rejection heat exchanger
  • the second heat exchanger 36 is a heat absorption heat exchanger.
  • An exemplary system 20 is a chiller system wherein the first heat exchanger 32 is a liquid-cooled condenser or gas cooler and the second heat exchanger 36 is the cooler.
  • An exemplary expansion device 34 is an electronic expansion valve (EV) which may be controlled by the chiller's controller 40 (e.g., a computer or microcontroller).
  • An alternative expansion device 34 is a float valve within the condenser 32.
  • the exemplary first heat exchanger has at least one inlet 50 and at least one outlet 52 along the refrigerant flowpath 30.
  • the second heat exchanger 36 has at least one inlet 54 and at least one outlet 56 along the refrigerant flowpath.
  • the compressor 24 has an inlet port 60 and an outlet port 62.
  • the second compressor 26 has an inlet port 64 and an outlet port 66.
  • the compressor subsystem includes one or more valves coupled to the compressors to allow switching of the compressors between two or more compression modes.
  • the exemplary system includes three valves 70, 72, and 74.
  • the compressors are operated at least partially in parallel.
  • the respective suction ports and discharge ports of the compressors are at essentially identical conditions.
  • the exemplary flowpath has two parallel branches 80 and 82 diverging at a junction 84 downstream of the second heat exchanger outlet 56 and re-merging at a location 86 at or upstream of the first heat exchanger inlet 50.
  • the separation and/or rejoinder may be at different locations.
  • a bypass branch or line 90 extends between the branches 80 and 82.
  • the exemplary bypass branch 90 extends between upstream of one of the compressors to downstream of the other.
  • the branch extends from a location 92 downstream of the first compressor to a location 94 upstream of the second compressor.
  • the exemplary valves 70 and 74 are respectively along such branches.
  • the valve 70 is downstream of the first end 92 of the bypass line 90 and the valve 74 is upstream of the end 94.
  • valve 72 In the exemplary at least partially parallel operation, the valve 72 is closed whereas the valves 74 and 70 are open. In a second mode, only the second compressor 26 is in operation. The valves 70 and 72 are closed whereas the valve 74 is open.
  • a third mode is a series mode wherein the compressors are operated in series. In the exemplary series mode, the valves 70 and 74 are closed whereas the valve 72 is open. Refrigerant passes without diversion from the second heat exchanger outlet 56 through the first compressor, the valve 72, and the second compressor before entering the first heat exchanger inlet 50.
  • a fourth possible mode involves having only the first compressor 24 in operation. In this mode, the valves 72 and 74 are closed and the valve 70 is open.
  • FIG. 1 shows further exemplary details of the condenser 32 and cooler 36.
  • the exemplary condenser 32 includes an upper condenser tube bundle 120 and a lower subcooler tube bundle 122.
  • FIG. 1 also shows a liquid refrigerant accumulation 124 within the condenser.
  • the tube bundles 120 and 122 are connected to one or more sources of heat transfer fluid to withdraw heat from the refrigerant.
  • the sub-cooler tube bundle 122 is contained within a chamber 126.
  • One or more inlet orifices 128 are along the bottom of the chamber 126.
  • a float valve 130 feeds the outlet 52.
  • a pressure sensor 132 may be located in the headspace of the condenser near the inlet 50.
  • the heat transfer fluid (e.g., water) passes along a water loop 138 (FIG. 2) and is received via an inlet 140 and discharged from an outlet 142. Respective temperature sensors 144 and 146 measure inlet temperature TicoND and outlet temperature T 2COND of the water. An exemplary flow meter 147 along the water loop 138 measures a flow rate F MCOND of the water.
  • the cooler 36 also includes a lower tube bundle 160 and an upper tube bundle 162.
  • FIG. 1 further shows a refrigerant accumulation 164 in the cooler.
  • a heat transfer fluid (e.g., water) passes along a water loop 168 (FIG.
  • FIG. 1 further shows a distributor 180 in the lower portion of the cooler approximately fed by the inlet 54.
  • a pressure sensor 182 is shown in the headspace near the outlet 56.
  • FIG. 4 shows a plot of the entering condenser water temperature T 1COND against capacity.
  • Line 200 represents the American Refrigeration Institute (ARI) load line.
  • ARI American Refrigeration Institute
  • chillers are subject to ARI Standard 550. This standard identifies four reference conditions characterized by a percentage of the chiller's rated load (in tons of cooling) and an associated condenser water inlet/entering temperature. Operation is to achieve a chilled water outlet/leaving temperature of 44F(6.67C). The four conditions are: 100%, 85F (29.44C); 75%, 75F (23.89C), 50%, 65F (18.33C); and 25%, 65F (18.33C also).
  • the water flow rate through the cooler is 2.4 gallons per minute per ton of cooling (gpm/ton) (0.043 liters per second per kilowatt (1/s/kW)) and condenser water flow rate is 3gpm/ton (0.054 1/s/kW).
  • the water temperature rise across the condenser is approximately 8F (4.4C) times the percentage load or 8F at 100% load, 6F (3.3C) at 75% load, 4F (2.2C) at 50% load and 2F (1.1C) at 25% load.
  • the cooler saturation temperature is IF (0.6C) or 2F (1.1C) below the leaving chilled water temperature (e.g., 43F in the ARI test).
  • Line 202 represents a constant temperature of 85F (29.44C).
  • 85F 85F
  • the ambient temperature changes very little from day to night. In such regions, the condenser water temperature remains constant. It' s an industry standard, to consider the entering condenser water temperature constant at 85F between 25% and 100% load.
  • Table I shows lift for the ARI conditions and corresponding tropical conditions. Centigrade temperatures are conversions from the listed Fahrenheit values and thus do not add and present false precision. Other SI parentheticals herein similarly represent conversions from the original US or English values.
  • the at least partially parallel first mode is utilized at high loads and the second mode (positive displacement compressor-only) is used at low loads.
  • the second mode may be used from essentially zero load to an intermediate load value. Between the intermediate load value and the maximum load, the at least partially parallel mode is used.
  • the intermediate load value may, however, be subject to appropriate hysteresis control to avoid excessive cycling when operating near changeover conditions.
  • the second compressor may be operated at increasing speed and/or power.
  • the first compressor may be brought online at full or near full capacity and the second compressor reset to zero or other low capacity value. Thereafter, with increasing load, the speed and/or power of the second compressor may be increased.
  • the positive displacement compressor may address more of the variation than the centrifugal compressor does. More narrowly, the positive displacement compressor may address at least 75% or at least 90% of the load variation.
  • the load variation may represent at least an exemplary 30% of a peak load of the system, more narrowly, at least 40%.
  • the rated capacities of the two compressors are essentially the same (e.g., the same or appropriately differently sized to address any hysteresis issues).
  • the changeover point is, therefore, at essentially half load.
  • the changeover point may be between 45% and 55% or 40% and 60% of the total rated system load.
  • centrifugal compressor By using the centrifugal compressor only at or near its own rated load (or, more broadly, not at a low load) issues of surge may largely be avoided.
  • an exemplary rated maximum capacity of the positive displacement compressor is 50-200% of the rated maximum capacity of the centrifugal compressor, more narrowly, 100 to 150%.
  • the fourth (series) mode may be added and used at high condenser water temperatures such as a water heating or a heat reclaim mode.
  • centrifugal compressor may be used alone when very low lift is needed (e.g., less than 25F (13.9C)).
  • a control process 300 starts by measuring or otherwise determining 302 the saturation temperatures of the condenser (T COND ) and the cooler (T COOL )- T COND and T COOL may respectively be determined by measuring the pressures via the pressure sensors 132 and 182 and then calculating the saturation temperatures (either via a lookup table or programmed function).
  • the lift is calculated 304 as T COND minus T COOL - If the lift is greater than a given threshold (e.g., 50F (28C)) the system may be operated 306 in the fourth (series) mode. In the series mode, the capacity of the centrifugal compressor is controlled by compressor speed and by inlet guide vane orientation.
  • centrifugal compressor speed is incrementally increased and its guide vanes are incrementally closed until the centrifugal compressor comes out of surge.
  • a similar logic is applied for the screw compressor (i.e., first speed followed by slide valve). Reducing the speed always results in reduced power consumption or increased efficiency.
  • Measurements 308 are made of the flow rate F M COO L and the temperatures TicooL and T 2 COO L - Capacity may also be calculated 310.
  • low capacity e.g. less than a first value such as 50% of a maximum
  • operation is then refined based upon the head.
  • the compressors may be run 320 in the first mode at equal loads. This may involve controlling capacity via the speed when variable speed drive is present and by the centrifugal compressor inlet guide vanes and the screw compressor slide valve for fixed speed case. Head is proportional to the temperature lift. In the example, low head corresponds to temperature lift less than 35F (19C) and high head between 35F and 50F (19C and 28C).
  • the system is operated 322 in the second mode (screw
  • Capacity is controlled via speed when variable speed drive is present and by slide valve for fixed speed case.
  • operation may also be in the first mode.
  • Balance between the compressors may be refined based upon the head.
  • the system is run in the parallel mode with the screw compressor operating at a fixed capacity and the centrifugal compressor operating at variable capacity to provide the required overall capacity.
  • the screw compressor may be operated at 50% of its maximum capacity and the centrifugal compressor being operated at between 50 and 100% of its maximum capacity (thereby combining to provide the exemplary 50-75% of maximum system capacity operation).
  • Such an operation is chosen so as to avoid surge of the centrifugal compressor.
  • the system may be run 332 in the first mode with the centrifugal compressor at essentially fixed capacity and the screw compressor providing capacity control.
  • the exemplary set points of the constant capacity compressor may differ relative to the condition 330.
  • the centrifugal compressor may be run at a relatively high capacity. In the foregoing example, this may be at 80% at its maximum capacity thereby providing 40% of total system capacity.
  • the screw compressor may be run between 20 and 70% of its maximum capacity (thereby providing 10-35% of maximum system capacity and combining with the centrifugal compressor to provide the 50-75% of maximum system capacity).
  • Such operating condition may be selected because the centrifugal compressor is susceptible to surge at low loads and high head.
  • operation may also be in the first mode, with compressors running 340 at equal loads.
  • compressors running 340 at equal loads.
  • each may be run at between 75 and 100% of its own maximum capacity to satisfy the required capacity.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention porte sur un dispositif (20) comprenant un compresseur centrifuge (24), un compresseur à déplacement positif (26), un premier échangeur de chaleur (32) et un second échangeur de chaleur (36). Une pluralité de soupapes (70, 72, 74) sont positionnées pour assurer un fonctionnement dans au moins deux modes. Dans un premier mode, un fluide frigorigène est comprimé dans le compresseur à déplacement positif et dans le compresseur centrifuge au moins partiellement en parallèle. Dans un deuxième mode, le fluide frigorigène est comprimé dans le compresseur à déplacement positif et le compresseur centrifuge est hors circuit. Dans un troisième mode, le fluide frigorigène est comprimé dans le compresseur à déplacement positif et dans le compresseur centrifuge qui sont au moins partiellement en série.
PCT/US2012/037872 2011-05-31 2012-05-15 Système de compresseur hybride et procédés WO2012166338A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201280026803.3A CN103748425B (zh) 2011-05-31 2012-05-15 混合压缩机系统和方法
EP12722646.2A EP2715254A2 (fr) 2011-05-31 2012-05-15 Système de compresseur hybride et procédés
US13/818,210 US20130177393A1 (en) 2011-05-31 2012-05-15 Hybrid Compressor System and Methods

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201161491515P 2011-05-31 2011-05-31
US61/491,515 2011-05-31

Publications (2)

Publication Number Publication Date
WO2012166338A2 true WO2012166338A2 (fr) 2012-12-06
WO2012166338A3 WO2012166338A3 (fr) 2013-01-24

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US (1) US20130177393A1 (fr)
EP (1) EP2715254A2 (fr)
CN (1) CN103748425B (fr)
WO (1) WO2012166338A2 (fr)

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Also Published As

Publication number Publication date
US20130177393A1 (en) 2013-07-11
CN103748425A (zh) 2014-04-23
CN103748425B (zh) 2017-10-17
EP2715254A2 (fr) 2014-04-09
WO2012166338A3 (fr) 2013-01-24

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