EP4237759A1 - Machine frigorifique à gaz, procédé de fonctionnement d'une machine frigorifique à gaz et procédé de fabrication d'une machine frigorifique à gaz comprenant un récupérateur autour de la zone d'aspiration - Google Patents

Machine frigorifique à gaz, procédé de fonctionnement d'une machine frigorifique à gaz et procédé de fabrication d'une machine frigorifique à gaz comprenant un récupérateur autour de la zone d'aspiration

Info

Publication number
EP4237759A1
EP4237759A1 EP21799047.2A EP21799047A EP4237759A1 EP 4237759 A1 EP4237759 A1 EP 4237759A1 EP 21799047 A EP21799047 A EP 21799047A EP 4237759 A1 EP4237759 A1 EP 4237759A1
Authority
EP
European Patent Office
Prior art keywords
gas
recuperator
compressor
inlet
outlet
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.)
Pending
Application number
EP21799047.2A
Other languages
German (de)
English (en)
Inventor
Holger Sedlak
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.)
Justairtech GmbH
Original Assignee
Justairtech GmbH
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 Justairtech GmbH filed Critical Justairtech GmbH
Publication of EP4237759A1 publication Critical patent/EP4237759A1/fr
Pending legal-status Critical Current

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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/004—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being air
    • 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
    • F25B11/00—Compression machines, plants or systems, using turbines, e.g. gas turbines
    • F25B11/02—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders
    • F25B11/04—Compression machines, plants or systems, using turbines, e.g. gas turbines as expanders centrifugal type
    • 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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/003—Gas cycle refrigeration machines characterised by construction or composition of the regenerator
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/004—Gas cycle refrigeration machines using a compressor of the rotary type
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/005—Gas cycle refrigeration machines using an expander of the rotary type
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components

Definitions

  • Gas refrigerating machine method for operating a gas refrigerating machine and method for producing a gas refrigerating machine with a recuperator around the intake area
  • the present invention relates to machines for heating and cooling and in particular to cold air refrigerating machines or gas refrigerating machines.
  • Cold air chillers are known and are used, for example, in space travel.
  • a cryocooler is disclosed which is shown schematically in FIG.
  • a compressor C compresses gas circulating in the closed system.
  • the compressed gas is cooled by a heat exchanger, which is schematically labeled "heat sink” and "heat release” respectively.
  • the cooled gas is fed into a recuperator R, which feeds the gas cooled in this way to a turbine E.
  • Cold gas is discharged from the turbine E, which absorbs heat via a heat exchanger or achieves a cooling effect.
  • the gas leaving the heat exchanger providing the refrigeration effect again warmer than the gas entering the same, is also fed into the recuperator R to be reheated.
  • the temperature-entropy diagram of the cycle in FIG. 5 is shown in FIG.
  • Compressor C performs isentropic compression as shown by the transition from transition point 1 to transition point 2.
  • An isobaric heat dissipation takes place through the heat exchanger for heat dissipation, as illustrated by the transition from point 2 to point 3 in FIG.
  • Isobaric heat dissipation also takes place through the recuperator R, as illustrated by the transition between point 3 and point 4.
  • an isentropic expansion takes place in the turbine E, as represented by the transition between point 4 and point 5.
  • the refrigeration effect of the heat exchanger in turn, represents an isobaric heat input, as represented by the transition from point 5 to point 6.
  • the heat released in the heat exchanger is represented in the temperature-entropy diagram as the temperature difference between point 2 and point 3.
  • the temperature reduction achieved by the turbine expansion is corresponding represented by the temperature difference between point 4 and point 5.
  • the temperature difference that can be used for cooling is shown between point 5 and point 6.
  • gas chillers Compared to heat pumps, which are used for cooling and heating, gas chillers have the advantage that energy-intensive circulation of liquid refrigerant can be avoided.
  • gas refrigeration machines do not require continuous evaporation on the one hand and continuous condensation on the other. Only gas circulates in the cycle shown in FIG. 5, without there being any transitions between the different states of aggregation.
  • heat pumps require very low pressures close to vacuum, especially if climate-problematic refrigerants are to be dispensed with, which can lead to considerable expense, especially in terms of equipment, in the production, handling and maintenance during operation. Nevertheless, the use of cold air chillers is limited.
  • the object of the present invention is to create an improved gas refrigerator.
  • One aspect of the present invention is based on the knowledge that the gas refrigerating machine must be constructed in a particularly compact manner in order to prevent losses through lines, in particular in the recuperator or in the connection between the recuperator and the compressor.
  • the recuperator is arranged to extend around a suction area of the compressor, the suction area of the recuperator being delimited by a suction wall.
  • This integrated arrangement between the compressor with the intake area on the one hand and the recuperator on the other hand means that a compact structure can be achieved with optimal flow conditions to allow gas present in the primary side of the recuperator to flow through the recuperator to suck through.
  • the effect of the recuperator is important for the efficiency of the entire gas refrigeration machine, which is why the recuperator is arranged so that it extends at least partially and preferably completely around the intake area. This ensures that a considerable amount of gas is sucked in from the recuperator from all sides over the entire intake area, which extends away from the compressor inlet and is delimited by the recuperator by the intake wall.
  • the recuperator can take up a considerable volume, a compact construction is nevertheless achieved because the compressor is directly integrated with the recuperator.
  • this implementation also ensures that there is enough space for the secondary side in the recuperator, which must be in thermal interaction with the primary side in the recuperator, to accommodate the streams of warm gas flowing on the primary side and the streams of warmer gas flowing on the secondary side To bring gas well in thermal interaction.
  • a cocurrent or countercurrent principle is used in the recuperator in order to achieve particularly good efficiency in this component.
  • the first inlet of the recuperator into the primary side thereof represents a gas or air inlet, so that the gas refrigerator can be operated in an open system.
  • the turbine outlet or the gas outlet is then also directed into a space, for example, into which the cooled air or, generally speaking, the cooled gas is brought.
  • the gas inlet on the one hand and the gas outlet on the other hand can be connected via a line system and a heat exchanger to a system that is to be cooled. Then the gas refrigerator according to the present invention is a closed system.
  • the entire gas refrigerating machine is installed in a housing which is typically rotationally symmetrical, at least in its “inside”, with an upright shape and a greater height than diameter, ie as a slender, upright shape.
  • Both the gas inlet and the gas outlet and the recuperator, the compressor and the turbine and preferably also the heat exchanger are located in this housing.
  • the compressor is preferably arranged above the turbine.
  • the compressor includes a radial wheel and the turbine also includes a turbine wheel, with the compressor wheel and the turbine wheel on a common Axis are arranged, and this axis further comprises a rotor of a drive motor, which interacts with a stator of the drive motor.
  • the rotor is preferably arranged between the compressor wheel and the turbine wheel.
  • the recuperator is arranged in an outer area of the volume of the gas engine and the compressor inlet is arranged in an inner area of the volume of the gas engine, with the intake area also being located in the inner area of the volume.
  • the suction area preferably has an opening area that increases continuously from a first end to the second end, so that the suction wall is designed to be continuous, ie preferably without edges.
  • the end with the smaller opening area is connected to the compressor inlet and the end with the larger opening area is closed, so that the operation of the compressor creates a suction effect in the suction area, which spreads via the primary outlet of the recuperator, which is fluidically coupled to the suction area, via the Recuperator extends through to the primary input of the recuperator, which is either designed directly as a gas inlet or is connected to a gas outlet in the housing.
  • a control chamber of the compressor is arranged in such a way that it guides the compressed gas outwards from the middle of the volume of the gas engine and feeds it there directly into a primary inlet of the heat exchanger.
  • the heated gas flows through the heat exchanger from the outside in and from there enters the secondary inlet or second inlet of the recuperator, which is preferably located inside the volume and extends around the intake area and in particular around the intake wall, but fluidly from the intake area is separated.
  • the gas fed into the secondary inlet flows from the inside to the outside in the secondary side of the recuperator and thus enables a counterflow principle, which is thermally particularly favorable, and then flows from the outside with respect to the recuperator, preferably into the intake area of the turbine, with the gas flowing from the outside to the inside to relax over the turbine wheel in the air outlet, which is preferably formed as a large area at the bottom of the gas refrigerator.
  • the gas inlet is formed in the lateral upper area of the gas refrigeration machine, namely by a large number of perforations which are connected to corresponding gas ducts and which form the gas inlet or the primary inlet into the recuperator.
  • Electronics required for controlling and operating the gas refrigerator are preferably arranged in an area below the turbine intake area, ie next to the air outlet, so that the cooled air can have a cooling effect on electronic elements via the turbine outlet wall.
  • a cold-air chiller is technically less complex and therefore also less error-prone, for example in comparison to a heat pump.
  • higher efficiency can be expected since no work is required to move a significant amount of liquid refrigerant around the circuit.
  • One aspect of the present invention relates to the placement of the recuperator at least partially around the intake area.
  • Another aspect of the present invention relates to the arrangement of the recuperator, the compressor, the heat exchanger, and the turbine in a single housing, z. B. can be cylindrical and z. B. has an elongated shape that has a height that is greater than the diameter
  • a further aspect of the present invention relates to the specific implementation in which the compressor is arranged above the turbine in order to achieve an optimal flow effect of the gas in the gas refrigerator.
  • a further aspect of the present invention relates to the placement of the compressor wheel and the turbine wheel on an axis on which the rotor of the engine is also arranged in order to create an optimal and efficient transmission of power from the turbine to the compressor to save drive energy to be supplied as far as possible.
  • a further aspect of the present invention relates to the implementation of a rotationally symmetrical recuperator with the compressor and the turbine, whose axis of rotation coincides with the axis of the recuperator, whether to achieve efficient flow guidance in the gas refrigerator.
  • a further aspect of the present invention relates to the preferred arrangement and design of the heat exchanger in the gas refrigerator in order to achieve a space-saving gas refrigerator with efficient conversion of thermal energy.
  • Another aspect of the present invention relates to the placement of an electronic assembly in a cool area of the gas refrigerator z. B, between the compressor wheel and the turbine wheel or in thermal interaction with the turbine inlet restriction on the path of the gas from the recuperator outlet into the turbine or near the particularly cool turbine outlet.
  • FIG. 1 shows a basic circuit diagram of a gas refrigerator according to an exemplary embodiment of the present invention
  • FIG. 2a shows a sectional illustration of a fully integrated gas refrigerator according to a further exemplary embodiment of the present invention
  • FIG. 2b shows a sectional illustration of a fully integrated gas refrigerator according to a further exemplary embodiment of the present invention with an alternative arrangement of the electronics assembly;
  • FIG. 3 shows a representation of different temperature/pressure/volume flow conditions at different points of the gas refrigerating machine
  • FIG. 4a shows a schematic representation of a section of a preferred recuperator with collection spaces on the secondary side
  • 4b shows a schematic plan view of a preferred recuperator with collection spaces on the secondary side
  • 4c shows a schematic cross-sectional representation of a wedge-shaped heat exchanger with a larger inlet cross section and a smaller outlet cross section; 5 shows a schematic representation of a known cold-air refrigerating machine;
  • FIG. 6 shows a temperature-entropy diagram of the known cold-air refrigerating machine from FIG. 5;
  • FIG. 7a shows a perspective view of a preferred compressor-turbine combination
  • FIG. 7b shows a side view of the preferred compressor-turbine combination from FIG. 7a.
  • the gas refrigerator with a gas inlet 2 for gas to be cooled, ie “warm” gas, and a gas outlet 5 for cooled, ie “cold” gas.
  • the gas is normal air, such as room air in an office, a data center, a factory, etc.
  • the gas refrigerator can be operated as an open cycle by introducing air via the gas inlet 2 at a point in is sucked in from a room and air that has been cooled is discharged into the room at another location in the room.
  • the present invention can also be implemented as a closed system, in which the gas outlet 5 is connected to a primary side of a heat exchanger and the gas inlet 2 is also connected to the primary side of the heat exchanger, but there to the "warm" end, and the secondary side of this Heat exchanger is connected to a heat source.
  • the gas refrigeration machine also includes a recuperator 10 with a first recuperator inlet 11, a first recuperator outlet 12, and a second recuperator inlet
  • the path from the first recuperator input 11 to the first recuperator output 12 represents the primary side of the recuperator, and the path from the second recuperator input 13 to the second recuperator output
  • a compressor 40 with a compressor inlet 41 and a compressor outlet 42 is provided.
  • the compressor inlet 41 is connected to the first recuperator outlet 12 via an intake region 30, which is delimited by the intake wall 31 coupled.
  • a heat exchanger 60 with a heat exchanger inlet 61 and a heat exchanger outlet 62 is provided.
  • the first heat exchanger inlet 61 and the first heat exchanger outlet 62 form the primary side of the heat exchanger 60.
  • the second heat exchanger inlet 63 and the second heat exchanger outlet 64 form the secondary side of the heat exchanger 60.
  • the secondary side is connected to a heat sink 80, which can be arranged, for example, on a roof if the gas refrigerator is used for cooling, or which can be underfloor heating if the gas refrigerator is used for heating, wherein a pump 90 is also provided on the secondary side, which is preferably arranged between the heat sink 80 and the second heat exchanger inlet 63.
  • the first heat exchanger inlet 61 is connected to the compressor outlet 42, and the first heat exchanger outlet 62 is connected to the second recuperator inlet 13, ie the secondary side of the recuperator.
  • a turbine 70 is provided, which has a turbine inlet 71 and a turbine outlet 72 .
  • the turbine inlet 71 is preferably connected to the second outlet 14 of the recuperator 10, ie to the outlet of the secondary side of the recuperator, and the gas outlet 5 is either identical to the turbine outlet 72 or coupled to it.
  • the compressor inlet 41 is connected to the suction area 30, which is delimited and bounded by a suction wall 31 from the recuperator.
  • the intake area 30 extends away from the compressor 40 and the recuperator 10 is configured to extend at least partially around the intake area.
  • the suction area 30 is delimited by the suction wall 31, this suction wall 31 also representing the boundary of the recuperator.
  • the suction wall 31 is provided with openings in order to let gas that is at the second outlet 12 of the recuperator 10 into the suction area 30 .
  • the openings provided in the intake wall thus represent the first recuperator outlet 12.
  • the intake wall is also designed to ensure a fluidic separation between the intake region 30 and both the second recuperator inlet 13 and the second recuperator outlet 14 (and also with respect to the first recuperator inlet 11, the can only be reached by gas via the intended route in the recuperator).
  • the recuperator extends completely around the intake area 30, as shown, for example, in FIG. 2a. In certain exemplary embodiments, however, it is already sufficient for the recuperator to extend around the suction area by only part of the entire 360° angle range. Thus, an arrangement of the recuperator that extends only 90° around the intake area 30 can be favorable if the gas refrigerator is to be fitted in a corner of a room, for example. Depending on the implementation, other larger or smaller extensions around the intake area are also conceivable for the recuperator. However, an implementation in which the recuperator extends completely, i.e. 360° around the intake area, is particularly efficient.
  • the recuperator has a circular cross-section in plan view.
  • Other cross-sections such as triangular, quadrangular, pentagonal or other polygonal cross-sections in plan view are also conceivable, since these recuperators with such cross-sections in plan view can easily be designed with corresponding gas ducts in order to achieve a highly efficient recuperation effect, preferably from all sides to reach from.
  • the entire gas refrigerating machine is accommodated in a housing, such as is illustrated at 100 in FIG. 2a.
  • the gas inlet 2 is located in an upper region of the housing 100 of FIG. 2a, the housing or the upper housing wall being designed identically to the recuperator wall.
  • the gas inlet 2 thus simultaneously represents the first recuperator inlet, which is represented by the perforations 11 in the housing wall.
  • the recuperator occupies a significant portion of the height of the overall housing 100, such as between 30 and 60% of the height of the housing.
  • the gas refrigerator in the particularly compact structure of Fig. 2a thus has only one air inlet 2, a Air outlet 5, a connection 63, 64 for the secondary side of the heat exchanger 60 and a current-Zsignal connection 101 for the electronics assembly 102.
  • the electronic module 102 is preferably used to supply a drive motor for the compressor 40 with energy or to supply control data to an element of the gas refrigerating machine or to acquire sensor data from an element of the gas refrigerating machine and is arranged in an area of the gas refrigerating machine which is designed or suitable to cool the electronics assembly.
  • the gas refrigerator can be used for cooling. Then the gas inlet is connected to a space to be cooled either directly or to an area to be cooled via a heat exchanger, and the heat exchanger 60 or the secondary side 63, 64 of the heat exchanger is connected to a heat sink 80, such as a fan on the roof of a building or a fan outside an area to be cooled.
  • a heat sink 80 such as a fan on the roof of a building or a fan outside an area to be cooled.
  • the secondary side 63, 64 of the heat exchanger is connected, for example, to underfloor heating (FBH) or to any heating circuit that can also have heating options other than underfloor heating.
  • the gas inlet 2 is in this case connected to a hot gas source if a direct system is used, or to a heat exchanger which is connected to a heat source on its primary side and the gas inlet 2 and the gas outlet 5 form the secondary side.
  • the secondary inlet of this heat exchanger which is not shown in FIG. 1, is the gas inlet 2 and the secondary outlet is the gas outlet 5 of this heat exchanger, which is not shown in FIG.
  • the compressor 40 is arranged upstream of the turbine 70 in the operating direction of the gas refrigerator.
  • This has the advantage that warm air can be sucked in from top to bottom in an area to be cooled and cold air is discharged downwards into an area to be cooled.
  • the physical property is taken into account that cold air tends to collect on the floor or in the lower area of a room and warm air at the top of the room.
  • the compressor includes a compressor wheel
  • the turbine also includes a turbine wheel 70a. Both wheels are preferably arranged on one and the same axle 43 .
  • a rotor 44 of a drive motor is arranged on the axle 43 in order to supply the additional drive force which is still required over and above the drive force achieved by the turbine.
  • the rotor 44 cooperates with the stator of a drive motor, which is not shown in Fig. 2a.
  • the rotor 44 is preferably positioned between the compressor wheel and the turbine wheel 70a.
  • the recuperator is preferably arranged in an outer area of a volume of the gas refrigerator, so that the intake area 30, which is connected to the compressor inlet 41, can be arranged in the inner area of the recuperator. Air is then sucked in from all sides, as is shown in FIG. 2a, in which the air inlet 2 is shown both on the left and on the right in the schematic cross-sectional representation of the figure.
  • the recuperator 10 thus comprises a volume shape having a central region with a central opening forming the suction region 30, the suction wall extending from a first end to a second end, the second end being covered with a cover 32. Therefore, no air or gas flows from above into the intake area, but only from the side through the primary area of the recuperator.
  • the widening from the first end at the compressor inlet 41 to the second end with the cover plate 32 is a continuous widening with an approximately parabola-like or hyperbola-like shape, which is there to ensure optimal flow patterns within the intake area, to ensure as far as possible a laminar flow that forms the lowest flow resistance in the intake area from top to bottom.
  • the somewhat greater flow resistance due to longer gas ducts in the recuperator closer to the compressor inlet 41 is compensated by somewhat shorter gas ducts further away from the compressor inlet 41, so that the flow resistance conditions are almost the same for the entire area from bottom to top along the intake area, so that the flow through the recuperator is equally efficient over its entire volume.
  • the recuperator 10 is rotationally symmetrical, and an axis of symmetry of the recuperator 10 coincides with an axis of the compressor or an axis of the turbine or an axis of the intake area and/or with an axis of the housing.
  • the recuperator is designed as a counterflow heat exchanger, which is indicated as one aspect in the schematic representation in FIG. 4a.
  • FIG. 4a which represents the “left half” or “right half” of the recuperator of FIG extending between a first collection space 17 on the left in Fig. 4a and between a second collection space 18 on the right in Fig. 4a.
  • the second gas channels 16 are in thermal interaction with the first gas channels 15.
  • the flow direction in the gas channels 16 is in the same direction as the flow in the gas channels 15.
  • the left one is Connection at the bottom left in Fig. 4a is the second recuperator inlet 13 and the right connection is the recuperator outlet 14.
  • recuperator If the recuperator is to be operated in counterflow, which is preferred, with the direction of flow in the flow channels 15 and 16 being opposite to one another, the inlet is left in Fig. 4a is the second recuperator output 14 and the connection on the right in Fig. 4a is the second recuperator input 13.
  • the thermal interaction takes place via the material of the recuperator, which is arranged between the gas channels 15 and 16, i.e. between a gas channel 15 and a corresponding gas channel 16, i.e. the heating of the warm gas drawn in at the expense of the cooling of the gas flowing in the secondary region of the recuperator , which is brought to the turbine for relaxation.
  • the recuperator includes the collection space 17 in order to distribute gas supplied via the left connection 4 from bottom to top in the embodiment shown in FIG. 4a into the various gas channels.
  • gas that has flowed through the channels is collected on the other side through the second collection space 18 and drawn off via the second connection. If, on the other hand, the occupancy is different, ie in real counterflow, the collection space 18 divides the gas into the individual Gas ducts 16 secure and the collection space 17 causes the gas discharged from each duct to be collected for the purpose of suction through the lower port due to the turbine relaxation effect.
  • the housing in which the compact gas refrigerator is arranged is rotationally symmetrical or cylindrical and has a diameter of between 0.5 and 1.5 meters and a height of between 1.0 and 2.5 meters.
  • sizes with a diameter between 70 and 90 and especially 80 centimeters are preferred, and a height between 170 and 190 and preferably 180 cm is preferred in order to provide an already significant cooling for e.g. a computer room, which is preferably implemented as direct air cooling .
  • an expansion from the turbine outlet 72 to the gas outlet 5 is also provided, which also runs in a parabolic or hyperbolic form, so that a favorable adjustment of the flow conditions from the high speed at the turbine outlet 72 to an adapted, reduced one speed at the air outlet 5 is reached, so that no excessive noise is generated by the cooling.
  • the housing has an elongated shape
  • the gas inlet is formed by a plurality of perforations in an upper region of the housing or a wall of the housing with respect to the operating direction of the gas refrigerator.
  • the gas outlet is formed by an opening in a lower area or in the bottom of the housing, with the opening in the bottom of the area corresponding to at least 50% of a cross-sectional area of the housing in the upper area, i.e. in the air inlet, through the largest possible opening of the gas outlet low air velocities are achieved at the gas outlet and thus a pleasant noise behavior and also a pleasant "draft" behavior in the room with only a small occurrence of air movement.
  • the compressor 40 is preferably arranged in order to achieve an air movement in the intake area, in the operating direction of the gas refrigerator, from top to bottom.
  • the compressor 40 then leads to a deflection of the flow from bottom to top, with a duct 45 of the compressor being advantageously used here, which already inherently achieves a 90° deflection at the transition from the compressor wheel to the duct 45 .
  • the next 90 ° are then achieved by the gas that has been compressed, at the outlet of the control chamber from bottom to top via the heat exchanger inlet 61, which is also the Compressor output 42 is fed.
  • the gas then moves from the outside in, towards the heat exchanger outlet 62, which coincides with the inlet 13 of the recuperator.
  • the gas then moves through collection areas, as shown in FIG. 4a, first from the bottom up in the recuperator and then from the top down at the exit of the corresponding gas channels, before finally entering the turbine inlet 71 at the second recuperator outlet 14 .
  • the turbine inlet 71 is again optimal in terms of flow, connected to the second recuperator outlet in the outer area, i.e. outside the heat exchanger, so that as few gas deflections as possible are achieved so that the gas can enter the turbine 70 without suffering significant losses , relaxes in the turbine, drives the turbine accordingly and loses heat through the relaxation process.
  • the turbine outlet is located at the bottom of the housing.
  • This allows the gas chiller to be placed on a cooling inlet area in a "false" floor of a data center. Air ducts extend from this cooling inlet area into the area to be cooled, e.g. B. computer racks.
  • the gas chiller thus represents a compact measure to feed cold air into an existing infrastructure of false floors or air ducts running in the floor, which lead off from the (central) cooling inlet.
  • the arrangement of the turbine outlet at the bottom of the gas chiller is also advantageous in that condensed moisture falls away from the device due to gravity and can be easily collected and drained off without the engine having to be protected from the moisture at great expense.
  • FIG. 4b shows a schematic plan view of a preferred recuperator 10 with collection spaces on the secondary side.
  • the top view of Fig. 2a or 2b is schematic.
  • the gas refrigerator is completely closed at the top by a closed cover.
  • Fig. 4b shows the situation when the cover is transparent.
  • the intake area 30 is shown, which is delimited by the intake wall 31 .
  • the boundary 18a for the inner collection space 18 and the boundary 17a for the outer collection space 17 extend around the suction area 30.
  • the glass flow is from the outside to the inside, as shown by the arrows 50, namely from the first recuperator inlet 11 to the first recuperator outlet 12. Then the gas in the intake area 30 flows down as indicated by the arrow ends 51 in region 30 is shown.
  • the gas is then compressed and flows through the heat exchanger 60 to flow into the second recuperator inlet 13 . From there it flows from bottom to top as indicated by the arrowheads in collection space 18. The gas then flows back out through the recuperator into the collection space 17 and down there, as shown by the ends of the arrows 53 . From the collection room
  • the flow directions can also be implemented differently, depending on the implementation, as long as the lines 15 on the one hand and 16 on the other hand are separated from one another in the recuperator 10 so that essentially no short-circuiting of the gas flows takes place.
  • the collection spaces 17, 18 are separated from the lines 15.
  • the collection spaces 17 , 18 are assigned to the lines 16 which connect the second recuperator input 3 to the second recuperator output 14 .
  • the implementation can also be such that the collection spaces are assigned to the first recuperator inlet and the first recuperator outlet and the second inlet and the second recuperator outlet are gas-insulated from the collection spaces.
  • the heat exchanger 60 has a disc-shaped volume and the heat exchanger inlet is on the outside of the disc-shaped volume and the heat exchanger outlet is on the inside of the disc-shaped volume. Furthermore, the heat exchanger inlet is preferably arranged at the bottom of the heat exchanger and the heat exchanger outlet is arranged at the top of the disc-shaped volume. In other exemplary embodiments, it is preferred to form the heat exchanger in a wedge-shaped cross section, with a cross section of the heat exchanger inlet 61 being greater than a cross section of the
  • heat exchanger outlet 62 This results in a preferably rotationally symmetrical heat exchanger which is to a certain extent ring-shaped as in Fig. 2a, but whose outer boundary of the ring cross-section in Fig. 2b is larger than the inner boundary, with the heat exchanger also not being horizontal as in Fig. 2b, for example 2a must be arranged, but can be arranged obliquely from bottom to top.
  • FIG. 4c shows a section of a side of this implementation in relation to the recuperator 10 and the compressor 40 and the turbine 70 of FIG. 2a or 2b. Only a schematic representation of one side of the cross-section is shown, with the larger inlet 61 and smaller outlet 62 being seen in the cross-section, and the flow of gas from the outlet 62 into the collection area 18, through the recuperator 10 into the collection area 17 and from there past the heat exchanger 60 into the turbine inlet is also illustrated.
  • a liquid preferably flows, such as a water/glycol mixture, which carries the waste heat to the heat sink 80.
  • the medium cooled in the heat sink 80 which can be designed, for example, as a liquid-to-air heat exchanger with a fan on a roof, is fed back into the inlet 63 of the secondary side of the heat exchanger 60 by the pump 90, as is also shown in FIG is. Therefore, preferably spiral-shaped liquid lines are located in the heat exchanger 40 in the area through which the gas flows, in order to remove and dissipate heat from the gas as efficiently as possible.
  • the suction region extends a distance greater than 10 cm, and preferably greater than 60 cm, from the compressor inlet.
  • the gas ducts are arranged in such a way that they are distributed substantially evenly over the volume on all sides and can therefore guide as much air as possible into the intake area as efficiently as possible with little resistance.
  • FIG. 3 shows a diagram representing the various ratios of velocity c, temperature T, volume V and pressure p.
  • the heat output Q and the electrical output P are each shown in kW.
  • the suction in the suction area increases the speed from a speed of 5 m/s to about 109 m/s, which is accompanied by a subtle temperature reduction from 38°C to 32°C and a small pressure reduction. Due to the compressor effect, however, the air is then brought to a temperature of 56° C.
  • This air provides cooling compared to the 25°C inlet air temperature, which can be increased or decreased as required by turning the compressor faster or slower.
  • the conditions are also shown on the outlet side, i.e. with regard to the heat exchanger. Liquid with a temperature of 55° C. is extracted, with the liquid mixture, ie the glycol/water mixture, being reduced by the fan in the heat sink 80 to 37.9° C., for example, and fed back accordingly into the secondary inlet 63 of the heat exchanger will.
  • the gas refrigeration machine is operated in such a way that the suction is achieved through the suction area 30 that specifically protrudes into the recuperator.
  • the individual elements are designed and arranged in such a way that the special preferred arrangement of the suction area in the volume of the recuperator is achieved.
  • recuperator can also be implemented with other heat exchanger technologies, e.g. with a heat exchanger that does not work in counterflow and in which the gas channels are not parallel to each other or perpendicular to the housing direction or are arranged in a horizontal operating direction.
  • the compressor and the turbine do not necessarily have to be arranged on one and the same axis, but other measures can be taken in order to use the energy released by the turbine to drive the compressor.
  • the heat exchanger does not necessarily have to be arranged in the housing between the recuperator and the turbine or between the recuperator and the compressor.
  • the heat exchanger could also be externally connected, although an internal arrangement is preferred for compact construction.
  • compressor and turbine need not necessarily be implemented as radial impellers, although this is preferred, since favorable power matching can be achieved by stepless speed control of the compressor via the electronics assembly 102 of FIG. 2a.
  • the compressor as shown in FIG. 2a, can be in the form of a turbo compressor with a radial impeller and with a duct or duct 45, which achieves a 180° deflection of the gas flow.
  • other gas conduction measures can also be achieved by shaping the guide space differently, for example, or by shaping the radial impeller differently, in order to still achieve a particularly efficient design that leads to good efficiency.
  • FIG. 7a shows a perspective view of a preferred compressor-turbine combination
  • FIG. 7b shows a side view of the preferred compressor-turbine combination from FIG. 7a.
  • the combination is preferably embodied as a monolithic unit or in one piece from the same material. It includes an upper or first bearing area 40b to which the compressor wheel 40a is attached.
  • the compressor wheel 40a goes in a first intermediate region 43a, also shown as axis 43.
  • This axis area 43a in turn merges into the rotor 44, which in turn merges into a further intermediate area 43b.
  • This is followed by the turbine wheel 70a, which can be suspended via a lower bearing section 70b.
  • the bearing area hangers are attached to the wall of the intake area 30 of FIG. 2a or 2b for the first bearing area 40b and the bearing area 70b for the turbine wheel 70a is attached to a hanger in the turbine outlet 72 .
  • Rolling or ball bearings are preferably used as bearings
  • the combination is dimensioned such that the diameter of the compressor wheel 40a is larger than the diameter of the rotor 44, and that the diameter of the rotor 44 (preferably without yoke 44a and magnets 44b) is equal to or larger than the diameter of the turbine wheel 70a.
  • This makes it easier to assemble, because the gas refrigerator with the combination in FIG. 7a or 7b can preferably be assembled from bottom to top with respect to FIG. 2a or 2b. It is also possible to slide a return ring 44a over the turbine wheel 70a and to attach it to the rotor 44 at its periphery.
  • Assembly preferably takes place from the bottom up, using the element with the turbine outlet 71 as a base onto which the inner boundary of the recuperator outlet 14 is placed.
  • the combination of turbine wheel 70a and compressor wheel is then placed on this and inserted into the bearing holder for the lower bearing section 70b.
  • the intake area 30 together with the guide chamber 45 and the heat exchanger 60 and the recuperator 10 arranged above it can be easily assembled by placing the upper bearing bracket on the protruding bearing section 40b.
  • FIG. 2b shows a sectional view of a fully integrated gas refrigerator according to a further exemplary embodiment of the present invention with an alternative arrangement of the electronics assembly 102 with respect to FIG. 2a. While the electronics assembly is mounted in the cool area next to the turbine outlet in FIG. 2a, in FIG. 2b it is in the so-called "machine room" between the base of the compressor wheel 40a of FIG. 7b and the base of the turbine wheel 70a.
  • the arrangement of the assembly 102 on the upper limit 71a of the turbine inlet 71 is advantageous because this area is well cooled due to the gas coming from the heat exchanger, which in the scenario in FIG. 3 is only 27 or 16 ° Celsius. Heat lost from the engine or waste heat from the electronics or sensors in the assembly is therefore easily dissipated via the turbine 70 .
  • the electronics assembly 102 for the electrical supply of the gas refrigerator with energy and/or control signals preferably has an opening in the center and is disk-shaped and extends around a stator of a drive motor for the compressor 40 or is designed to be integrated with the stator, and is also shown by way of example in FIG an area between a base of a compressor wheel 40a of the compressor 40 and a base of a turbine wheel 70a of the turbine.
  • annular assembly is shown in cross-section in FIG. 2b
  • the assembly may be formed in any way so long as it is housed in the machine room and thermally interacts with the boundary 71a of the inlet 71 of the turbine 70, e.g. B. is mounted on the boundary 71a. It is also preferred to route the supply line for energy 101a and data 101b for the motor through the lateral boundary 14a of the recuperator output 14 and through the housing 100 at the appropriate point, as is the case, for example, in FIG. B. shown in Fig. 2b.
  • aspects have been described in the context of a device, it is understood that these aspects also represent a description of the corresponding method, so that a block or a component of a device is also to be understood as a corresponding method step or as a feature of a method step. Similarly, aspects described in connection with or as a method step also constitute a description of a corresponding block or detail or feature of a corresponding device.
  • Some or all of the method steps may be performed by hardware apparatus (or using a hardware Apparatus), such as a microprocessor, a programmable computer, or an electronic circuit. In some embodiments, some or more of the essential process steps can be performed by such an apparatus.

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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)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne une machine frigorifique à gaz présentant les caractéristiques suivantes : une entrée (2) pour le gaz à refroidir ; un récupérateur (10) ; un compresseur (40) équipé d'une entrée de compresseur (41), ladite entrée de compresseur (41) étant accouplée à une première sortie de récupérateur (12) ; un échangeur de chaleur (60) ; une turbine (70) ; et une sortie de gaz (5), l'entrée de compresseur (41) étant reliée à une zone d'aspiration (30) qui est délimitée par une paroi d'aspiration (31) et s'étend à l'opposé du compresseur (40) ; le récupérateur (10) s'étendant au moins partiellement autour de la zone d'aspiration (30) et étant délimité par la paroi d'aspiration (31) ; et la paroi d'aspiration (31) étant conçue de telle sorte que le gaz puisse être aspiré, à partir du récupérateur (10) dans l'entrée de compresseur (41), par l'intermédiaire de la paroi d'aspiration (31), par le biais de la zone d'aspiration (30).
EP21799047.2A 2020-10-28 2021-10-26 Machine frigorifique à gaz, procédé de fonctionnement d'une machine frigorifique à gaz et procédé de fabrication d'une machine frigorifique à gaz comprenant un récupérateur autour de la zone d'aspiration Pending EP4237759A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020213544.4A DE102020213544B4 (de) 2020-10-28 2020-10-28 Gaskältemaschine, Verfahren zum Betreiben einer Gaskältemaschine und Verfahren zum Herstellen einer Gaskältemaschine mit einem Rekuperator um den Ansaugbereich
PCT/EP2021/079709 WO2022090246A1 (fr) 2020-10-28 2021-10-26 Machine frigorifique à gaz, procédé de fonctionnement d'une machine frigorifique à gaz et procédé de fabrication d'une machine frigorifique à gaz comprenant un récupérateur autour de la zone d'aspiration

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EP4237759A1 true EP4237759A1 (fr) 2023-09-06

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DE102021201532A1 (de) 2021-02-17 2022-08-18 JustAirTech GmbH Wärmetauscher, verfahren zum betreiben eines wärmetauschers, verfahren zum herstellen eines wärmetauschers, gaskältemaschine mit einem wärmetauscher als rekuperator, vorrichtung zum behandeln von gas und raumlufttechnisches gerät
DE102021201530A1 (de) 2021-02-17 2022-08-18 JustAirTech GmbH Vorrichtung und verfahren zum behandeln von gas und rlt-gerät

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3544445A1 (de) 1985-12-16 1987-06-25 Bosch Siemens Hausgeraete Kuehl- und gefriergeraet
US5497615A (en) 1994-03-21 1996-03-12 Noe; James C. Gas turbine generator set
GB9409754D0 (en) 1994-05-16 1994-07-06 Air Prod & Chem Refrigeration system
US6381969B1 (en) 1999-12-17 2002-05-07 Honeywell International Inc. ECS with 2-stage water separation
US6301923B1 (en) 2000-05-01 2001-10-16 Praxair Technology, Inc. Method for generating a cold gas
US6634176B2 (en) 2000-11-02 2003-10-21 Capstone Turbine Corporation Turbine with exhaust vortex disrupter and annular recuperator
US20060059936A1 (en) 2004-09-17 2006-03-23 Radke Robert E Systems and methods for providing cooling in compressed air storage power supply systems
US7621150B2 (en) 2007-01-05 2009-11-24 Delphi Technologies, Inc. Internal heat exchanger integrated with gas cooler
US9395122B2 (en) 2011-02-28 2016-07-19 Pratt & Whitney Canada Corp. Diffusing gas turbine engine recuperator
JP5934482B2 (ja) 2011-08-26 2016-06-15 株式会社前川製作所 閉鎖型ガス循環式冷凍装置及びその運転方法
US9464638B2 (en) 2012-05-01 2016-10-11 California Institute Of Technology Reverse brayton cycle with bladeless turbo compressor for automotive environmental cooling
US10294826B2 (en) 2015-08-12 2019-05-21 Colorado State University Research Foundation Ultra efficient turbo-compression cooling
ITUA20161513A1 (it) * 2016-03-09 2017-09-09 Nuovo Pignone Tecnologie Srl Motocompressore - espantore integrato

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DE102020213544A1 (de) 2022-04-28
DE102020213544B4 (de) 2024-06-06

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