MOTOR, REFRIGERATION MACHINE OR HEAT PUMP

Abstract: When not only integrating the compressor and expander, but also the heat exchanger in one single rotor, a machine working according to the gas turbine process can be simplified. The gas turbine process in such a machine can also be run in reversed mode as a refrigeration machine or heat pump. Lower relative velocities between the working fluid and the components of the machine can be used which should lead to lower frictional losses and a higher efficiency. In order to further reduce the friction the rotor should rotate in a chamber with low pressure or in a medium with lower friction than air. The medium that exchanges heat with the working medium here called the heat carrying fluid is also taken into the rotor.

Description: Motor, refrigeration machine or heat pump A machine according to this invention works as a motor according to the gas turbine cycle (the Joule/Brayton cycle) or as a refrigeration machine or heat pump according to the reversed gas turbine cycle. The invention thus includes a machine that can run either as a motor when the produced shaft power is utilised, a refrigeration machine when the produced cooling power is used or as a heat pump when the heating power is utilised. In both the motor case and the refrigeration/heat pump case a working medium is being compressed, heat is being added or subtracted and thereafter expanded. If heat is being added to the compressed working medium in the heat exchanger the machine according to the invention will become a motor. If heat on the other hand is subtracted the machine according to the invention will become a refrigeration machine or a heat pump. The main components, the compressor, the heat exchanger and the expander are according to the invention joined into one single rotating part, in the future called the rotor. Two media are flowing through the rotor, the working medium that is compressible and the heat carrying fluid. When the machine is used as a motor, hot oil could be used as a heat carrying fluid and for instance air as working medium. Alternatively an exothermal reaction for instance combustion in the working medium itself can be used as a heat carrying fluid. When the machine is used as a refrigeration machine/heat pump air can be used as a working medium and for instance water as a heat carrying fluid. In another form of the machine, when the working medium is not atmospheric air, an additional heat exchanger is needed to another fluid called the cold carrying fluid. In the motor case, the cold carrying fluid is absorbing heat while it in the refrigeration or heat pump case is delivering heat to the working medium. In a third form of the machine as a motor, the mechanical energy output is delivered fully or partly from an external expander. If the machine in this form is run as a heat pump or refrigeration machine the rotor rotation is and the propulsion of the working medium is accomplished fully or partly with an external compressor. The gas turbine cycle is normally accomplished by first comprimating the working medium (normally air) in a separate compressor after which it is heated in a separate combustion chamber and finally is expanded in a separate turbine. In all the three components the velocity relative to the walls, guidevanes and blades are high which results in frictional losses. Heat pumps similar to the invention are shown in the Swedish patents 122418 and 163924. According to the first patent the heat carrying fluid is led outside the rotating heat exchanger whereby the velocity difference between the heat carrying fluid and the heat exchanger surface becomes large and the frictional losses between the heat carrying fluid and the heat exchanging surface become large. In the second patent an attempt to reduce the velocity difference between the rotating heat exchanger and the heat carrying fluid has been made, by introducing a secondary separating wall, so that the velocity difference is divided into two parts. This method will not likely result in an especially large reduction of the frictional losses. A similar idea is also described in GB 1443802A. In this invention the heat exchange is integrated with the compressor, and the expander is placed on a separate shaft so that the expander is not rotating with the same angular velocity as the compressor. FR2699653-A1 describes another similar idea where the compression among other things is accomplished with an axial compressor. In DE2729134-A a machine is described where among other things the heat is transferred by radiation from the heat carrying fluid which runs outside the machine and where the cold carrying fluid runs centrally in the machine. The patent GB21283K) shows an advanced magnetic construction where the heat carrying fluid runs in the surrounding stator body and the cold carrying fluid runs through the shaft. In the patents US-2490064 and US- 2451873 solutions are shown where the heat exchange takes place during the compression phase and not as in our invention at substantially constant pressure. The patents US-2490064 and GB- 1420722 differs from our invention as the heat carrying fluid is not rotating inside the rotor. One goal with the suggested machine is to minimise the losses during compression, heat exchange and expansion by reducing the relative velocity of the working medium to the different parts of the machine compared to the normal process with separate compressor, heat exchanger and expander. That should lead to lower losses and an increased efficiency. Another goal is to let both the working medium and the heat carrying fluid run through channels in the rotor. The relative velocity between the two media can then be regulated to a value required by the heat exchange and no more. In order to reduce the frictional losses of the rotor it must rotate surrounded by low pressure or a special medium resulting in low friction. In the following text the invention is described with reference to the following figures in which: figure 1 schematically shows the path of the working medium and the heat carrying fluid through the rotor, figure 2 shows an example of the path of the working medium and the heat carrying fluid through a real rotor, figur 3 schematically shows the path of the working medium using an external compressor in an open loop and figure 4 shows use of an external compressor in a closed loop. In figure 1 ist is shown how the working medium enters at point 1 , is comprimated as the compressor blades 2 forces the medium to rotate whereby the centrifugal force increases the pressure and temperature. Thereafter the working medium absorbs or delivers heat in the heat exchanger 3. Finally the working medium is expanded in the passage through the expander blades 4 whereby pressure and temperature falls. The working medium leaves the machine through the outlet 5. The heat carrying fluid enters the machine at point 6, is pumped radially with the pump 7 after which the the heat carrying fluid delivers or absorbs heat in the heat exchanger 3. Finally the heat carrying fluid passes the turbine 8 and out through he exit 9. The rotational axis is only indicated with a line in figure 1. In figure 2 the way of the paths of the working medium and the heat carrying fluid are shown in an anticipated version of the machine. The blades of the compressor 2 and of the expander 4 are shown more in detail here. The path of the working fluid through the compressor and expander is limited by through the rotors outer end plates 18 and inner end plates 19. In this anticipated example form the heat exchanger 3 is made as a chamber limited by and inner rotor cylinder 12 and an outer rotor cylinder 14 in which a spiral shaped pipe with outer flanges 13 is placed. The heat carrying fluid enters through the shaft 10 via the inlet 6. is then brought to the heat exchanger through the indicated pump channel 7, runs through the flanged heat exchanger pipe 13 to finally exit through the turbine channel 8 and out through the heat carrying fluid outlet 9 in the shaft 10. It could also be anticipated that the heat exchanger is an integral part of the inner rotor cylinder 12. The outer surface of the inner rotor cylinder 12, is then wholly or partly joined with the shaft 10 utilising radially heat conducting material whereby the heat carrying fluid is led through the shaft and heat is radially conducted. The entrance radius of the working medium at 1 can be made smaller the exit radius at 5. A driving force for the flow of the working medium is then automatically achieved. The inlet radius of the heat carrying fluid 6 can be made smaller then the exit radius in the heat carrier exit at 9. A driving force for the flow of the heat carrying fluid is then automatically achieved. The rotor rotates in a stator chamber 15, that is limited by an outer stator cylinder 16 two stator end plates 11 and two seals 17 to the rotor. The stator chamber 15 is preferably connected to a vacuum pump or filled with a medium resulting in low frictional losses. In figure 3 it is shown how an external compressor 20, in an open process can set the rotor into rotation whereby the radius for the working fluid in the inlet 1 can be made just as large as the radius in the outlet 5. Figure 4 shows in the refrigeration machine/heat pump case how the working medium is driven into the rotor inlet 1 by an external compressor 20. From the rotor outlet 5 the working medium is then led to a heat exchanger 22 which in the refrigeration/heat pump case is heated by a cold carrying fluid. The heat carrying fluid enters through the shaft at 6 and exits at 9 in this case.

Claims: Claims 1. Rotor that can be used as motor, refrigeration machine or heat pump characterised by that both a working medium and a heat carrying fluid is led through the rotor, whereby the working medium is led mainly outwards during compression of the working medium, then the working medium is led mainly axially during heat exchange with a heat carrying fluid and finally the working medium is led mainly radially inwards through the rotor undergoing expansion. 2. Machine according to 1 characterised by that the working medium and that the heat carrying fluid are running mainly in counter current during the heat exchange between them. 3. Machine according to 1 and 2 characterised by that the pressure required to force the working medium through the machine wholly or partly is achieved by letting the outer radius at the inlet of the working medium be smaller than the outer radius at the outlet of the working medium. 4. Machine according to 1 , 2 and 3 characterised by that the pressure required to force the heat carrying fluid through the machine wholly or partly is achieved by letting the outer radius at the inlet of the heat carrying fluid be smaller than the outer radius at the outlet of the heat carrying fluid. 5. Machine according to 1, 2, 3 and 4 characterised by that the pressure required to force the working medium through the machine wholly or partly is achieved by adjusting the inlet and outlet angels to the rotor. 6. Machine according to 1, 2, 3, 4 and 5 characterised by that a stator chamber is placed outside the rotor cylinder which either is put under low pressure or is filled with a medium giving lower frictional losses than air. 7. Machine according to 1, 2, 3, 4, 5 and 6 characterised by that both the propulsion of the working medium and the rotation of the rotor wholly of partly is achieved by an external compressor. 8. Machine according to 1, 2, 3, 4, 5 and 6 characterised by that the loop of the working medium is closed within the machine. 9. Machine according to 1, 2, 3, 4, 5, 6, 7 and 8 characterised by that the working medium is exchanging heat with a cold carrying fluid in an external heat exchanger.9999

Inventors: GRANRYD ERIC, NOWACKI JAN-ERIK, GRANRYD, ERIC, NOWACKI, JAN-ERIK
Applicants: GRANRYD ERIC, NOWACKI JAN ERIK, GRANRYD, ERIC, NOWACKI, JAN-ERIK
Application year: 1998
Main classification: F25B3
IPC codes: F02C3, F25B3, F28D11