EP1863663A1 - Installation de refroidissement mue par train d'engrenages - Google Patents

Installation de refroidissement mue par train d'engrenages

Info

Publication number
EP1863663A1
EP1863663A1 EP06739355A EP06739355A EP1863663A1 EP 1863663 A1 EP1863663 A1 EP 1863663A1 EP 06739355 A EP06739355 A EP 06739355A EP 06739355 A EP06739355 A EP 06739355A EP 1863663 A1 EP1863663 A1 EP 1863663A1
Authority
EP
European Patent Office
Prior art keywords
compressor
drive assembly
gear drive
air
refrigeration
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06739355A
Other languages
German (de)
English (en)
Inventor
Thomas J. Leck
Donald Bernard Bivens
Fuqin Zhao
Miroslav Rohacek
Paul K. Mathur
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
EIDP Inc
Original Assignee
EI Du Pont de Nemours and Co
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 EI Du Pont de Nemours and Co filed Critical EI Du Pont de Nemours and Co
Publication of EP1863663A1 publication Critical patent/EP1863663A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3222—Cooling devices using compression characterised by the compressor driving arrangements, e.g. clutches, transmissions or multiple drives
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3223—Cooling devices using compression characterised by the arrangement or type of the compressor

Definitions

  • the present invention relates to refrigeration and air- conditioning apparatus.
  • the present invention relates to mobile refrigeration and air-conditioning apparatus utilizing a mini- centrifugal compressor with rotational power provided by a ratioed gear drive assembly.
  • a new approach to this problem of high GWP HFCs for the mobile air-conditioning market involves the use of new, low-pressure, low GWP refrigerants in an innovative type of vapor compression refrigeration or air-conditioning apparatus.
  • Miniature scale centrifugal (mini-centrifugal) compressors would facilitate the use of these new low GWP refrigerants.
  • the power requirements for such a system are not met in existing automobile designs.
  • power is transmitted from the engine to the air-conditioner compressor via a system of belts and pulleys. It is known that it is difficult to achieve the step up in rotational speed from normal engine rotation speeds to the rotational speed required to run a centrifugal compressor via only belts and pulleys without even greater loss of efficiency and reliability.
  • the present invention relates to a means of supplying rotational power to a mini-centrifugal compressor for a refrigeration or air- conditioning apparatus.
  • the present invention relates to a refrigeration or air-conditioning apparatus comprising a compressor driven by a ratioed gear drive assembly coupled to an internal combustion engine.
  • the ratioed gear drive with optional ratioed belt drive provides the energy necessary with the required increase in
  • a mini-centrifugal compressor requires electrical power of about 50 volts.
  • the present invention allows the use of the mini-centrifugal compressor by utilizing a ratioed gear drive from an internal combustion engine crankshaft to provide rotational power to the mini-centrifugal compressor impeller shaft as described above with respect to Fig. 1
  • FIG. 1 is a diagram of one embodiment of a compressor powered by a ratioed gear drive assembly coupled to an internal combustion engine via a ratioed belt drive, as incorporated in a refrigeration or air-conditioning apparatus.
  • FIG. 2 is a diagram of a second embodiment of a compressor 30 coupled to a ratioed gear drive assembly via a coupling device, which is coupled to an internal combustion engine via a ratioed belt drive, as incorporated in a refrigeration or air-conditioning apparatus.
  • Fig. 3 is a diagram of a ratioed gear drive assembly showing two gear sets, which can be used instead of the gear drive assembly used 35 in either Fig. 1 or Fig. 2.
  • a cooling apparatus which could be either a refrigeration or air-conditioning apparatus.
  • a refrigeration apparatus is shown in Fig. 1.
  • Vapor-compression refrigeration and air conditioning systems include an evaporator, a compressor, a condenser, and an expansion device.
  • a vapor- compression cycle re-uses refrigerant in multiple steps producing a cooling effect in one step and a heating effect in a different step.
  • Such a system generally includes an evaporator, a compressor, a condenser and an expansion device as will be described below in detail with respect to Fig. 1. With reference to Fig.
  • gaseous refrigerant from an evaporator (42) flows through a pipeline (63) to a compressor, which may be a centrifugal compressor, and more preferably, a mini-centrifugal compressor, mini-centrifugal compressor where it enters at the suction of a first stage housing, having an impeller (11) therein, and is discharged from the first stage housing to the suction of a second stage housing having a second impeller (12) therein.
  • the compressed refrigerant gas output from the second stage housing flows through a pipeline (61) from the compressor to a condenser (41).
  • a pressure regulating valve (51) in pipeline (61) allows recycle of the refrigerant flow back to the compressor via a pipeline (63) providing the ability to control the pressure of the refrigerant reaching the condenser (41) and if necessary to prevent compressor surge.
  • the compressed refrigerant is condensed in the condenser, thus giving off heat.
  • the liquid refrigerant flows through an expansion device (52) via a pipeline (62) to the evaporator (42), which is located in the passenger compartment. In the evaporator, the liquid refrigerant is vaporized providing cooling and the cycle then repeats.
  • the expansion device (52) may be an expansion valve, a capillary tube or an orifice tube.
  • the compressor of the present invention is driven by a ratioed gear drive assembly coupled to an internal combustion engine.
  • Fig. 1 This is accomplished as shown in Fig. 1 as follows.
  • An engine crankshaft (73) drives a belt (33) via a first pulley (31).
  • Said belt also turns a second pulley (32) that is attached to a ratioed gear drive assembly (80) comprising a clutch (81) and at least 1 gear set (82).
  • This gear drive assembly provides the rotational power to the rotating shaft (71) of the mini-centrifugal compressor.
  • the belt and pulley system may be a ratioed belt drive providing some increase in rotational speed from the engine. Ratioed gear drive assemblies and ratioed belt drives, as described herein, are available commercially.
  • the gear drive and the compressor may share a common rotating shaft.
  • the compressor rotating shaft (71) may be separate from a ratioed gear assembly shaft (72) and the two shafts may be joined by a coupling device (21).
  • This coupling device (21) may be a rotary magnetic coupling device.
  • Magnetic couplings are used to transmit rotational motion without direct contact.
  • Rotary couplings are principally used to eliminate the use of seals in rotating machines. Use of magnetic couplers improves the reliability and safety aspects of such machines because seals are prone to deterioration over time and cause leaks.
  • Rotary magnetic couplers used in the present invention will preferably be of co-axial configuration.
  • the two halves of the coupler are mounted co-axially with each other and nested one within the other.
  • the outer member is connected to the gear assembly shaft and the inner member to the compressor rotating shaft.
  • a cup-shaped stationary member, mounted to the compressor body resides between the driver (gear assembly shaft) and the follower (compressor rotating shaft) and separates the refrigerant fluid from the ambient environment and the gear assembly.
  • Magnetic couplings of this type are available commercially.
  • coupling (21) shown in Fig. 2 may be joined by any other means of mechanical coupling that may be used to join rotating shafts.
  • the refrigeration or air-conditioning system of the present invention includes a compressor.
  • a seal may be required around the compressor rotating shaft in the event a common shaft is used or if there are separate shafts coupled by the optional mechanical coupling (21) of Fig. 2, to prevent refrigerant from leaking out and to prevent air from leaking into the compressor.
  • the present invention may include the use of a compressor shaft seal for sealing the interior of the compressor from ambient air.
  • the refrigerants used with the mini-centrifugal compressor are low-pressure refrigerants
  • the seal may be required to prevent air from leaking into the compressor, in particular, and causing deterioration in cooling performance.
  • the shaft seal may be one of several designs known in the art and of several materials of construction, including, but not limited to steel, ceramic, or carbon against steel.
  • compressors there are various types of compressors that may be used in refrigeration applications. Compressors can be generally classified as reciprocating, rotary, jet, centrifugal, scroll, screw or axial-flow, depending on the mechanical means to compress the fluid, or as positive- displacement (e.g., reciprocating, scroll or screw) or dynamic (e.g., centrifugal or jet), depending on how the mechanical elements act on the fluid to be compressed.
  • the present inventive apparatus preferably utilizes a centrifugal type compressor.
  • a centrifugal compressor uses rotating elements to accelerate the refrigerant radially, and typically includes an impeller and diffuser housed in a casing or housing.
  • Centrifugal compressors usually take fluid in at an impeller eye, or central inlet of a circulating impeller, and accelerate it radially outward. Some static pressure rise occurs in the impeller, but most of the pressure rise occurs in the diffuser section of the casing, where velocity is converted to static pressure.
  • Each impeller- diffuser set is a stage of the compressor.
  • Centrifugal compressors are built with from 1 to 12 or more stages, depending on the final pressure desired and the volume of refrigerant to be handled.
  • the present inventive apparatus utilizes a centrifugal compressor with at least one stage (one impeller), preferably 2 stages (2 impellers).
  • the pressure ratio, or compression ratio, of a compressor is the ratio of absolute discharge pressure to the absolute inlet pressure.
  • Pressure delivered by a centrifugal compressor is practically constant over a relatively wide range of capacities.
  • Positive displacement compressors draw vapor into a chamber, and the chamber decreases in volume to compress the vapor. After being compressed, the vapor is forced from the chamber by further decreasing the volume of the chamber to zero or nearly zero.
  • a positive displacement compressor can build up a pressure, which is limited only by the volumetric efficiency and the strength of the parts to withstand the pressure.
  • a centrifugal compressor depends entirely on the centrifugal force of the high-speed impeller to compress the vapor passing through the impeller. There is no positive displacement, but rather what is called dynamic-compression.
  • a multi-stage impeller system may be used in a centrifugal compressor to improve compressor efficiency thus requiring less power in use.
  • the discharge of the first stage impeller goes to the suction intake of a second impeller.
  • Both impellers may operate by use of a single shaft (or axle).
  • Each stage can build up a compression ratio of about 4 to 1 ; that is, the absolute discharge pressure can be four times the absolute suction pressure.
  • the pressure a centrifugal compressor can develop depends on the tip speed of the impeller. Tip speed is the speed of the impeller measured at its tip and is related to the diameter of the impeller and its revolutions per minute. Tip speed and impeller diameter can be estimated by making some fundamental relationships for refrigeration equipment that use centrifugal compressors.
  • the torque an impeller ideally imparts to a gas is defined as
  • T m*(v 2 *r 2 -vi*ri) Equation 1
  • T torque
  • m mass rate of flow, kg/sec
  • T m*v 2 *r 2 Equation 2
  • the power required at the shaft is the product of the torque and the rotative speed
  • the capacity of the centrifugal compressor is determined by the size of the passages through the impeller. This makes the size of the compressor more dependent on the pressure required than the capacity.
  • Large centrifugal compressors typically operate at 3000 to 7000 revolutions per minute (rpm).
  • Small scale centrifugal compressors mini- centrifugals are designed for high speeds, from about 20,000 rpm to about 75,000 rpm, and have small impeller diameter, typically less than about 0.15 meters (about 6 inches).
  • the mini-centrifugal compressors which can be used with the present invention preferably operate at impeller speeds of 30,000 to 50,000 rpm and have impeller diameter of less than 0.10 meters (about 4 inches).
  • Stationary refrigeration or air-conditioning apparatus refers to the equipment used for cooling the air in a building, or cooling perishable goods such as foods, pharmaceutical materials, etc, in a conventional, non-mobile, non-vehicle mounted, system.
  • Such stationary refrigeration or air conditioning systems may be associated with CHP (Combined Heat and Power) systems, wherein a stationary internal combustion engine is used to drive an electrical generator.
  • the waste heat produced by the engine may be recovered and used to perform work, by such means as a Rankine Cycle (steam engine) or Organic Rankine cycle (ORC).
  • a Rankine cycle the heat is used to vaporize a liquid (an organic liquid in the case of an ORC), which in turn drives a turbine.
  • the mechanical energy of the turbine may be used to drive an electricity generator, which runs a refrigeration or air-conditioning system.
  • An alternative embodiment of the present invention involves using a high ratio gear drive from the crankshaft of the stationary engine employed in such a system, with the output shaft from the gears being coupled to a mini-centrifugal compressor.
  • a high ratio gear drive from the crankshaft of the stationary engine employed in such a system with the output shaft from the gears being coupled to a mini-centrifugal compressor.
  • An example could be use of this as part of a commercially available CHP system for homes, which are off the power grid, to generate electricity and recover exhaust heat to heat water or building air, and at the same time, use the ratioed gear driven compressor to provide cooling.
  • the present invention is particularly useful in remote locations where access to electrical power is limited, if available at all.
  • Mobile refrigeration apparatus or mobile air-conditioning apparatus refers to any refrigeration or air-conditioning apparatus incorporated into a mobile transportation unit for the road, rail, sea or air.
  • apparatus which are meant to provide refrigeration or air- conditioning for a system independent of any moving carrier, known as “intermodal" systems, are included in the present invention.
  • intermodal systems include “containers” (combined sea/land transport) as well as “swap bodies” (combined road and rail transport).
  • the present invention is particularly useful for road transport refrigerating or air- conditioning apparatus, such as automobile air-conditioning apparatus or refrigerated road transport equipment.
  • the mini-centrifugal compressors of the present invention are capable of producing refrigeration capacity in the range from about 0.5 tons (1.7 kW) to about 3 tons (10.3 KW). Typically, about 1.2 tons (4.0 kW) to about 2.0 tons (6.8 kW) would be needed to cool an automobile 5 passenger compartment. Greater capacity may be needed for many mobile refrigeration units such as road and rail refrigerated containers.
  • the refrigeration or air-conditioning apparatus of the present invention may additionally employ fin and tube heat exchangers, microchannel heat exchangers and vertical or horizontal single pass tube
  • the evaporator design may be modified. Rather than several microchannel slabs connected in series (with respect to the refrigerant path) a single slab/single pass heat exchanger arrangement may be used. This type of heat exchanger comprises multiple channels through which the refrigerant all flows at the
  • a preferred heat exchanger design for use as the evaporator and/or condenser in the refrigeration or air-conditioning apparatus of the present invention is a single slab/single pass heat exchanger.
  • the engine crank-shaft will generally operate in a range from about 600 revolutions per minute (rpm) to about 6000 rpm.
  • rpm revolutions per minute
  • the ratioed gear drive assembly is needed to provide the increased rotational speed.
  • the gears and the optional ratioed belt drive must be used to provide the increased rotational speed.
  • compressor impeller speed must be maintained at a minimum speed to ensure adequate cooling during all road speeds and engine idle.
  • Certain controls may be needed within the present refrigeration or air-conditioning apparatus to ensure optimum cooling performance.
  • the engine crank-shaft will be rotating at a higher rate, which will increase the compressor impeller speeds as well.
  • the ratioed gear drive must be controlled such that the compressor impeller is not driven to too high a rate of speed. Excessive impeller speeds above the design limits may cause damage to compressor internals, such as distortion of the impeller blades, which may result in generally reduced compressor performance and eventually, shorter compressor lifetime. Further, at engine idle, the gears must maintain the impeller speed at a minimum level for adequate cooling to be accomplished.
  • At least 2 gear sets are used to control the compressor impeller speed in the optimum range for adequate cooling.
  • a gear assembly shaft (74) is shown joining gear set (82a) to gear set (82b).
  • the controls would clutch to a lower ratio gear set to keep the compressor running at a suitable speed for proper air-conditioner performance.
  • the gear drive would clutch to a higher ratio gear set, thus maintaining adequate impeller speeds for proper cooling by the air- conditioner.
  • the speed of the compressor impeller may be controlled by way of a drive belt system, which employs adjustable sheaves on the pulleys in order to increase or decrease the speed of the compressor to accommodate for changes in engine rpm from idle speeds to highway speeds.
  • the adjustable sheave variable speed drive mechanism can be sized to either increase or decrease the speed of the driven pulley.
  • Variable sheave belt drives are available commercially.
  • adjustable speed drives include traction drives, belt and chain drives, gear drives or differentials, hydraulic drives, eddy current drives, and magnetic coupling.
  • Traction drives depend upon friction between a speed adjusting mechanism and specially shaped input and output plates to achieve adjustable speed with relatively high efficiency.
  • Belt and train drives operate with adjustable diameter sheaves or pulleys.
  • Gear drives are the most durable, rugged, and efficient of all adjustable-speed drives, but they are capable of providing only a specific number of fixed gear ratios.
  • In a hydraulic drive there are two main methods of hydraulically varying the speed of the driven load when the driving motor is operating at a constant speed, fluid coupling and hydraulic pump and motor.
  • Hydraulic drives offer some additional flexibility in that the orientation of the output and input shafts can be in any of a variety of geometries, thus allowing more design and installation options.
  • hydraulic drives do add elements of complexity in that hydraulic fluid systems are required.
  • the speed of the compressor impeller may be controlled by use of a magnetic adjustable speed drive.
  • This adjustable speed drive may serve as the coupling device (21) as shown in Fig. 2.
  • Such magnetic drives replace the physical connection between drivers and loads with a gap of air. As there is no physical connection, this type of drive eliminates vibration, reduces noise, tolerates misalignment, provides overload protection, extends equipment life and reduces overall maintenance costs.
  • the adjustable speed drives work by transmitting torque from the driver to the load across an air gap.
  • the driving side e.g., gear assembly
  • the driven side e.g., compressor impeller shaft
  • the torque is created by the interaction of rare-earth magnets on one side of the drive with induced magnetic fields on the other side.
  • the magnetic adjustable speed drive may be located between the gear assembly (82) and the compressor rotating shaft (71).
  • the compressor rotating shaft would be separate from a shaft being rotated by the gear assembly.
  • This gear assembly shaft would be the driving side for the adjustable speed drive and the compressor impeller shaft would be the load side.
  • the magnetic adjustable speed drive consists of a magnet rotor assembly, containing rare-earth magnets, attached to the load; a copper conductor rotor assembly attached to the gear driven shaft; and actuation components that control the air gap spacing between the magnet rotors and the conductor rotors. Relative rotation of the copper conductor and magnet rotor assemblies induces a magnetic coupling across the air gap. Varying the air gap spacing between the magnet rotors and the conductor rotors results in controlled output speed. The output speed is adjustable, controllable, and reproducible.
  • a control system may be used that senses the compressor shaft rotational speed and adjusts the engine idle, gear set in operation, or magnetic adjustable speed drive as necessary to maintain desired cooling capacity and optimum operation of the refrigeration or air-conditioning apparatus.
  • the present invention further relates to a process for producing cooling comprising compressing a refrigerant in a mini-centrifugal compressor powered by a ratioed gear drive assembly coupled to an internal combustion engine; condensing said refrigerant; and thereafter evaporating said refrigerant in the vicinity of a body to be cooled.
  • the refrigerants for which this new refrigeration or air- conditioning apparatus are useful are hydrofluorocarbons (HFCs), including saturated and unsaturated compounds, fluoroethers (HFOCs), haloketones, hydrocarbons, chlorocarbons, alcohols, ketones, ethers, esters, N-(difluoromethyl)-N,N-dimethylamine, 1 ,1,1 ,2,2-pentafluoro-2- [(pentafluoroethyl)thio]ethane and combinations thereof.
  • HFCs hydrofluorocarbons
  • HFOCs fluoroethers
  • haloketones hydrocarbons
  • hydrocarbons chlorocarbons
  • alcohols ketones
  • ethers esters
  • the refrigerants useful with the present invention possess boiling points in the range from about 0 °C to about +60 0 C, thus having lower vapor pressures at room temperature than the conventional CFC, HCFC and HFC refrigerants, such as R-12, R-22, or R-134a.
  • the refrigerants also have low or zero ozone depletion potential and low global warming potential.
  • HFOC-347mmzE ⁇ (CH 2 FOCH(CF 3 ) 2 , 1 ,1 ,1 ,3,3,3-hexafluoro-2- (fluoromethoxy)propane), HFOC-365mcE ⁇ (CF 3 CF 2 CH 2 OCH 3 , 1,1,1,2,2- pentafluoro-3-methoxypropane ), HFOC-356mmzE ⁇ (CH 3 OCH(CHs) 2 , 1 ,1 ,1 ,3,3,3-hexafluoro-2- methoxypropane), HFOC-467mmyE ⁇ (CH 3 CH 2 OCF(CF 3 ) 2 , 2-ethoxy-
  • a body to be cooled may be any space, location or object requiring refrigeration or air-conditioning.
  • the body may be the interior of a structure, i.e. residential or commercial, or a storage location for perishables, such as food or pharmaceuticals.
  • perishables such as food or pharmaceuticals.
  • Numerous mobile systems are described earlier in defining mobile refrigeration apparatus and mobile air-conditioning apparatus.
  • the present invention further relates to a method for providing power to a compressor within a refrigeration or air-conditioning apparatus, said method comprising coupling the compressor to a ratioed gear drive assembly driven by an internal combustion engine to power the compressor.
  • the present invention further relates to a method for controlling impeller speed in a compressor within a refrigeration or air- conditioning apparatus, wherein the compressor is driven by a ratioed gear drive assembly coupled to an internal combustion engine, said method comprising varying the engine idle speed during apparatus operation.
  • the present invention further relates to a method for controlling impeller speed in a compressor within a refrigeration or air-conditioning apparatus, wherein the compressor is powered by a ratioed gear drive assembly coupled to an internal combustion engine, said method comprising providing a ratioed gear drive comprising multiple gear sets and at least one clutch.
  • the present invention further relates to a method for controlling impeller speed in a compressor within a refrigeration or air-conditioning apparatus, wherein the compressor is powered by a ratioed gear drive assembly coupled to an internal combustion engine, said method comprising coupling the compressor to the ratioed gear drive assembly via a magnetic adjustable speed drive.
  • the present invention further relates to a method for controlling cooling capacity for a refrigeration or air-conditioning apparatus, wherein said apparatus includes a compressor powered by a ratioed gear drive assembly coupled to an internal combustion engine, said method comprising varying the engine idle speed during apparatus operation.
  • the present invention further relates to a method for controlling cooling capacity for a refrigeration or air-conditioning apparatus including a compressor powered by a ratioed gear drive assembly coupled to an internal combustion engine, said method comprising providing a ratioed gear drive assembly comprising multiple gear sets and at least one clutch.
  • the present invention further relates to a method for controlling cooling capacity for a refrigeration or air-conditioning apparatus, wherein said apparatus includes a compressor, and wherein the compressor is powered by a ratioed gear drive assembly coupled to an internal combustion engine, said method comprising coupling the compressor to the ratioed gear drive assembly via a magnetic adjustable speed drive.
  • the present invention further relates to a method for controlling compressor surge within refrigeration or air-conditioning apparatus, said apparatus including a compressor driven by a ratioed gear drive assembly coupled to an internal combustion engine, said method comprising maintaining minimum flow of a refrigerant through the compressor by controlling recycle of the refrigerant from the discharge to the suction of the compressor.
  • Compressor surge is a condition that must be voided due to potential damage to the compressor. If the forward flow through the compressor can no longer be maintained due to an increased pressure differential across the compressor, a momentary flow reversal may occur.
  • the recycle valve (51) shown in Fig. 1 allows some portion of the refrigerant flow out of the compressor to be diverted back to the compressor suction thus balancing the pressure across the compressor under the surge point.
  • the present invention further relates to a method for controlling impeller speed in a compressor within a refrigeration or air-conditioning apparatus, wherein the compressor is powered by a ratioed gear drive assembly coupled to an internal combustion engine, said method comprising coupling the compressor to the ratioed gear drive assembly via an adjustable speed mechanical drive.
  • the present invention further relates to a method for controlling cooling capacity for a refrigeration or air-conditioning apparatus, wherein said apparatus includes a compressor, and wherein the compressor is powered by a ratioed gear drive assembly coupled to an internal combustion engine, said method comprising coupling the compressor to the ratioed gear drive assembly via an adjustable speed mechanical drive.
  • the table below shows theoretical tip speed and impeller diameter for a system using PEIK (perfluoroethylisopropylketone) as refrigerant to produce cooling capacity of approximately 1.5 tons at an impeller speed of 40,000 rpm.
  • PEIK perfluoroethylisopropylketone
  • Table 1 shows the enthalpy of the refrigerant gas as it leaves the evaporator, (H Evaporator Out), the enthalpy of the refrigerant gas as in enters condenser (H Condenser In), the change in enthalpy between the evaporator and compressor, (Delta Hi), and the change in enthalpy between the evaporator and compressor multiplied by 0.8 to account for a compressor efficiency of 80%.
  • the table below also shows theoretical tip speed and impeller diameter for a refrigeration apparatus.

Landscapes

  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • General Details Of Gearings (AREA)
  • Gear Transmission (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

La présente invention concerne une installation de refroidissement comprenant un dispositif de réfrigération ou de climatisation. L'invention concerne en particulier un tel dispositif faisant appel à un compresseur mini-centrifuge (11, 12) entraîné en rotation par un train d'engrenages (80) couplé à un moteur thermique.
EP06739355A 2005-03-21 2006-03-21 Installation de refroidissement mue par train d'engrenages Withdrawn EP1863663A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US66392405P 2005-03-21 2005-03-21
US11/378,832 US20060245944A1 (en) 2005-03-21 2006-03-17 Cooling apparatus powered by a ratioed gear drive assembly
PCT/US2006/010531 WO2006102492A1 (fr) 2005-03-21 2006-03-21 Installation de refroidissement mue par train d'engrenages

Publications (1)

Publication Number Publication Date
EP1863663A1 true EP1863663A1 (fr) 2007-12-12

Family

ID=36616993

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06739355A Withdrawn EP1863663A1 (fr) 2005-03-21 2006-03-21 Installation de refroidissement mue par train d'engrenages

Country Status (6)

Country Link
US (1) US20060245944A1 (fr)
EP (1) EP1863663A1 (fr)
JP (1) JP2008537919A (fr)
AR (1) AR052626A1 (fr)
TW (1) TW200638003A (fr)
WO (1) WO2006102492A1 (fr)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2006308717B2 (en) 2005-11-01 2012-07-19 The Chemours Company Fc, Llc. Compositions comprising fluoroolefins and uses thereof
ES2932622T3 (es) * 2007-04-27 2023-01-23 Chemours Co Fc Llc Composiciones azeotrópicas y similares a azeótropos de Z-1,1,1,4,4,4-hexafluoro-2-buteno
CN110643328B (zh) * 2007-06-12 2022-04-01 科慕埃弗西有限公司 E-1,1,1,4,4,4-六氟-2-丁烯的共沸和类共沸组合物
US20090025405A1 (en) * 2007-07-27 2009-01-29 Johnson Controls Technology Company Economized Vapor Compression Circuit
CA2725404A1 (fr) * 2008-06-20 2009-12-23 E.I. Du Pont De Nemours And Company Compositions azeotropiques et de type azeotrope de z-1,1,1,4,4,4-hexafluoro-2-butene
FR2933486B1 (fr) * 2008-07-01 2010-08-20 Valeo Systemes Thermiques Procede d'estimation de la puissance absorbee par un compresseur dans une installation de chauffage, ventilation et/ou climatisation
FR2933485B1 (fr) * 2008-07-01 2016-05-13 Valeo Systemes Thermiques Branche Thermique Habitacle Procede d'estimation de la puissance absorbee par un compresseur dans une installation de chauffage, ventilation et/ou climatisation
US9328949B2 (en) 2009-03-30 2016-05-03 Tmeic Corporation Compressor surge control system and method
KR101685729B1 (ko) 2009-06-03 2016-12-12 이 아이 듀폰 디 네모아 앤드 캄파니 Ｃｉｓ-1,1,1,4,4,4-헥사플루오로-2-부텐을 함유하는 칠러 장치, 및 그 안에서 냉각을 생성하는 방법
CA2773692C (fr) * 2009-09-16 2018-01-02 E. I. Du Pont De Nemours And Company Appareil refrigerant contenant du trans-1,1,1,4,4,4-hexafluoro-2-butene et procedes de production de froid utilises dans celui-ci
WO2011034929A1 (fr) 2009-09-16 2011-03-24 E. I. Du Pont De Nemours And Company Composition associant du cis-1,1,1,4,4,4-hexafluoro-2-butène et du trans-1,2-dichloroéthylène, appareil en contenant et procédés de production de froid utilisés dans ce dernier
IT1397145B1 (it) 2009-11-30 2013-01-04 Nuovo Pignone Spa Sistema evaporatore diretto e metodo per sistemi a ciclo rankine organico.
US20110144216A1 (en) * 2009-12-16 2011-06-16 Honeywell International Inc. Compositions and uses of cis-1,1,1,4,4,4-hexafluoro-2-butene
CN104094508B (zh) 2011-05-13 2017-10-24 开利公司 磁驱动耦合装置
US9362812B2 (en) 2012-09-18 2016-06-07 Honeywell International Inc. Shaft coupling apparatus, rotary fluid damper, and deployable device with magnetic coupling mechanism
JP6088238B2 (ja) * 2012-12-19 2017-03-01 出光興産株式会社 回転式圧縮機用潤滑油組成物
CA2960174C (fr) 2014-09-23 2024-03-12 The Chemours Company Fc, Llc Utilisation de (2e)-1,1,1,4,5,5,5-heptafluoro-4-(trifluoromethyl)pent-2-ene dans des pompes a chaleur a haute temperature
EP3334984A1 (fr) 2015-08-11 2018-06-20 Carrier Corporation Système cvc, à faible prg et à faible capacité
US11220160B2 (en) * 2016-09-09 2022-01-11 Terex Usa, Llc System and method for idle mitigation on a utility truck with an electrically isolated hydraulically controlled aerial work platform
FR3065254B1 (fr) * 2017-04-14 2019-06-14 IFP Energies Nouvelles Ensemble de turbopompe pour un circuit ferme, en particulier de type a cycle de rankine, associe a un moteur a combustion interne, notamment pour vehicule automobile
CN108167170A (zh) * 2017-12-13 2018-06-15 广新海事重工股份有限公司 一种变频控制中央海水冷却系统
CN111520925B (zh) * 2020-05-06 2021-11-16 青岛科技大学 一种压缩机供气系统及压缩机供气控制方法
CN112797685A (zh) * 2021-02-03 2021-05-14 江苏新能动力科技股份有限公司 一种高效制冰系统

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1221241B (it) * 1988-03-24 1990-06-21 Vm Motori Spa Perfezionamento nella configurazione degli ingombri dei motori per autotrazione,in particolare nella dispozione di unita' motrici azionanti accessori
US5065590A (en) * 1990-09-14 1991-11-19 Williams International Corporation Refrigeration system with high speed, high frequency compressor motor
US5350039A (en) * 1993-02-25 1994-09-27 Nartron Corporation Low capacity centrifugal refrigeration compressor
US5363674A (en) * 1993-05-04 1994-11-15 Ecoair Corp. Zero superheat refrigeration compression system
DE10037094A1 (de) * 2000-07-27 2002-02-07 Linnig Karl Heinz Kraftübertragungseinheit
US6682430B2 (en) * 2001-03-15 2004-01-27 Magnadrive Corporation Adjustable magnetic coupler
US6577037B2 (en) * 2001-07-03 2003-06-10 Magnadrive Corporation Self-unloading magnetic coupler
JP4066236B2 (ja) * 2002-05-10 2008-03-26 株式会社デンソー 自動車用補機駆動装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2006102492A1 *

Also Published As

Publication number Publication date
TW200638003A (en) 2006-11-01
AR052626A1 (es) 2007-03-21
US20060245944A1 (en) 2006-11-02
WO2006102492A1 (fr) 2006-09-28
JP2008537919A (ja) 2008-10-02

Similar Documents

Publication Publication Date Title
US20060245944A1 (en) Cooling apparatus powered by a ratioed gear drive assembly
US20060242985A1 (en) Refrigeration/air-conditioning apparatus powered by an engine exhaust gas driven turbine
Groll et al. Review of recent advances toward transcritical CO2 cycle technology
US7401475B2 (en) Thermodynamic systems operating with near-isothermal compression and expansion cycles
US3945216A (en) Refrigeration systems
CN103270306A (zh) 可变容量的螺杆式压缩机及其方法
WO2012004987A1 (fr) Système à cycle de réfrigération à établissement de pression à deux étages
EP2668455B1 (fr) Système permettant d'effectuer un cycle de réfrigération par compression de vapeur utilisant de l'eau en tant que fluide frigorigène
EP1046869B1 (fr) Système de réfrigération et d'air conditionné
CN101963161B (zh) 涡轮压缩机及冷冻机
Gużda et al. Compressors in heat pumps
JPH05223090A (ja) ターボ圧縮機
JP2016003645A (ja) スクロール圧縮機および空気調和機
CN1193200C (zh) 一种制冷系统用转子压缩－膨胀机
Shuailing et al. A review of reverse Brayton air cycle refrigerators
JP5272941B2 (ja) ターボ圧縮機及び冷凍機
US20090193843A1 (en) Turbo compressor and refrigerator
Kohsokabe et al. Basic operating characteristics of CO2 refrigeration cycles with expander-compressor unit
CN103512256A (zh) 一种制冷系统及空调
JP6004004B2 (ja) ターボ冷凍機
KR20140123968A (ko) 캐스캐이드식 냉각 시스템
EP1877270A2 (fr) Appareil de refrigeration/climatisation alimente par une turbine entrainee par les gaz d'echappement de moteur
Tasdemirci et al. Experimental performance comparison of R1234yf and R134a automobile air conditioning systems employing a variable capacity compressor
JP3414091B2 (ja) 冷凍装置
CN201093793Y (zh) 一种变频磁悬浮压缩膨胀机组

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20070928

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 20080311

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20080923