Abstract:
The present invention provides a scroll-type expander that simultaneously performs expansion and re-heating such that efficient expansion is realized and there is no reduction in efficiency caused by pressure loss occurring during the supply of an working fluid to the scroll-type expander, and that minimizes a difference in temperature between a stationary scroll member and a rotating scroll member, as well as a temperature distribution of a scroll wrap. The present invention also relates to a heat exchange system that uses a scroll-type expander to replace pistons in a conventional reciprocating Stirling engine or refrigerator with a pair of scroll-type compressor and expander such that the heat exchange system may be used as a Stirling engine or refrigerator. The present invention also provides a steam engine, in which a steam turbine in the conventional steam engine (Rankine system) is replaced with a scroll-type expander such that the steam cycle has both a re-heating cycle and a regeneration cycle.

Description:
BACKGROUND OF THE INVENTION  
       [0001]     (a) Field of the Invention  
         [0002]     The present invention relates to a scroll-type expander and a scroll-type compressor, and more particularly, to a scroll-type expander and a scroll-type compressor that include a stationary scroll member and a rotating scroll member to continuously perform expansion and compression of an working fluid. The present invention also relates to a scroll-type heat exchange system that includes a scroll-type expander and scroll-type compressor for use as a Stirling engine or refrigerator.  
         [0003]     (b) Description of the Related Art  
         [0004]     Scroll device offers many advantages including high efficiency, low noise, low vibration, small size, and light weight. Scroll devices are widely used as a result of these advantages scroll-type compressor In more detail, with reference to  FIG. 1 , a stationary scroll member  30  of involute form and a rotating scroll member  40  are provided at a 180° phase difference. As a result, a series of crescent-shaped pockets are formed within the scroll-type compressor. Gas flows into the scroll-type compressor through an intake passage located at a circumference of the stationary scroll member  30 , and the crescent-shaped pockets move toward a center of the two scrolls  30  and  40  by the orbiting action of the rotating scroll member  40 . A volume of the pockets is reduced through this operation such that the gas is compressed. The gas is then discharged through a discharge port formed in a center of the stationary scroll member  30 . During each orbit, several crescent-shaped pockets are compressed simultaneously, so operation is continuous.  
         [0005]     In the scroll-type expander, the scroll-type compressor is simply operated in reverse such that a gas is expanded. That is, a high pressure gas is provided to the center of the stationary scroll member  30  such that the orbiting scroll member  40  is displaced to realize expansion of the gas, which is then discharged through the circumferential opening of the stationary scroll member  30 . Motive power is generated by the orbiting motion of the rotating scroll member  40 .  
         [0006]     Compared to other types of compressors, the scroll-type compressor requires less parts, is small and lightweight, and provides other advantages such as high efficiency, low vibration, and low noise. As a result, the scroll-type compressor is widely used as a refrigerant compressor and air compressor. The scroll-type expander, on the other hand, has not experienced widespread use.  
         [0007]     As a conventional expander, U.S. Pat. No. 4,192,152 discloses a scroll apparatus with peripheral drive that can be used as a compressor and an expander, and a heat engine that combines a compressor, a burner, and an expander, and also discloses a Brayton cycle-type cooling cycle that combines a compressor and an expander. Also, EP Patent No. 0846843A1 discloses a heat engine that combines a compressor, a regenerator, a burner, and an expander. In addition, there has also been recently disclosed in the United States a steam cycle (Rankine system) that uses a scroll-type expander in place of a steam engine.  
         [0008]     However, in patents and research related to scroll-type expanders disclosed up to now, high pressure gas or steam is supplied to a center area of the scroll-type expander to generate motive power as in conventional turbines. As a result, efficiency is reduced by pressure loss when supplying the gas or steam such that while compression efficiency reaches up to 90%, expansion efficiency is only about 60˜70%. Further, in the conventional scroll-type expander, a difference in temperatures between the stationary scroll member and the orbiting scroll member develops, and a temperature gradient occurs within the same scroll wrap itself. These factors result in a reduction in efficiency by the generated friction, leakage, and increased vibration.  
         [0009]     A Stirling engine is an external combustion engine that includes a plurality of heat exchangers that heat and cool the enclosed charge gas. Most Stirling engines are external combustion engines of reciprocating piston types.  
         [0010]     Because the Stirling engine is an external combustion engine, it may use various heat sources such as liquid fuel, gas fuel, solid fuel, industrial waste energy, solar energy, and LNG. The Stirling engine provides high efficiency due to a regenerator mounted between a heater and a cooler. Also, because the Stirling engine does not include valves and realizes smooth pressure changes, a low level of noise and vibration are generated compared to the internal combustion engine. Also, since continuous combustion occurs in the Stirling engine, combustion control is easy and the exhaust gas is relatively clean, thereby making the Stirling engine a possible candidate for widespread use in the future.  
         [0011]     With reference to  FIG. 8 , which shows a basic structure of a conventional Stirling engine  200 , an expansion piston  201  and a compression piston  203  are coupled to a common crankshaft with about 90° phase difference. An expansion space  205  and a compression space  207  are formed and connected to a regenerator  209  that is filled with thermal energy storage material having gas permeability. With this configuration, since it is difficult to realize sufficient heating and cooling of the working gas by a cylinder wall of a small heat transfer area, a cooler  212  and a heater  214  are provided to opposite sides of the regenerator  209  as shown in  FIG. 9 .  
         [0012]     To simplify the mechanical structure and reduce vibration of the reciprocating-I Stirling engine, U.S. Pat. No. 6,109,040 discloses a configuration that uses two rotary Wankel rotors and provides for a phase difference as in the reciprocating Stirling engine such that compression and expansion are alternatingly realized.  
         [0013]     Since two pistons reciprocate in cylinders synchronously but out of phase so that the working gas shuttles cyclically from one space to the other as the volume and pressure vary from maximum to minimum and go through the four processes of the Stirling cycle in order, the working fluid undergoes pressure loss due to the oscillating flow through the regenerator positioned between the compression cylinder and the expansion cylinder such that an increase in rotational speed results in the reduction in torque. In addition, because it is difficult to realize sufficient heating and cooling of the working gas by a cylinder wall of a small heat transfer area, the cooler  212  and the heater  214  are provided to opposite sides of the regenerator  209  as shown in  FIG. 9 , and it is necessary to use a gas having a low molecular weight such as hydrogen or helium as the working gas. However, in the case where a gas of a low molecular weight is used as the working gas, leakage easily occurs such that it is extremely important to use a high performance gas seal.  
         [0014]     With reference to  FIGS. 10 and 11 , an ideal Stirling cycle includes isothermal compression (I-II) while in a low temperature compression section  223 , constant volume heating (II-III) while passing a regenerator  221 , isothermal expansion (III-IV) while in a high temperature expansion section  224 , and constant volume heat rejection (IV-I) while passing the regenerator  221 . However, the actual cycle is more like that shown in  FIG. 12 , which is significantly less efficient than the ideal case. The reasons for such a difference between an ideal Stirling cycle and the actual cycle, and the difficulties in realizing the ideal cycle, will be described as follows.  
         [0015]     First, to realize the isothermal compression (I-II) and isothermal expansion (III-IV) sections of the ideal Stirling cycle, fast heat transfer must occur through the inside surface of the cylinder walls. However, even if a sufficient number of heat transfer pins are mounted outside the cylinder, since the area of the inside surface of the cylinder walls making contact with the working gas is limited, it is difficult for the working gas to be heated or cooled isothermally. This becomes increasingly problematic if the engine is made faster and to larger sizes, in which case the processes inside the cylinder becomes more adiabatic (no heat transfer) than isothermal (infinite heat transfer).  
         [0016]     It is for this reason that the additional heater  214  and cooler  212  are mounted to opposite ends of the regenerator  209  to ensure effective heating and cooling of the working gas. Although the heater  214  and cooler  212  allow for the effective heating and cooling of the working gas to increase the specific power, the provision of such heat exchangers imposes some penalties as follows.  
         [0017]     In particular, the increase in dead volume, which includes the heater  214 , the regenerator  209 , and the cooler  212 , acts to decrease output. Further, it results in anomalies in which the expanded working gas picks up heat from the heater  214  before deposing its heat in the regenerator  209  and in which the compressed gas has to pass through the cooler  212  before going back through regenerator  209  to pick up heat. As a result, the flow resistance is increased and thermal efficiency is reduced. Further, the thermal stress to the structural parts increases such that care must be given in selecting the materials for the parts and other limitations are given to manufacture of the device.  
         [0018]     In the ideal Stirling cycle as shown in  FIG. 10 , since the motions of the pistons  225  and  227  are discontinuous, only compression occurs in the low temperature compression section  223  and only expansion occurs in the high temperature expansion section  224 . However, in an actual reciprocating Stirling engine shown in  FIG. 9 , the compression piston  203  and the expansion piston  201  are linked to move together such that during compression by the compression piston  203  of the low temperature section, compression occurs slightly also by operation of the expansion piston  201  of the high temperature section. Likewise, during expansion by the expansion piston  201  of the high temperature section, expansion occurs slightly also by operation of the compression piston  203  of the low temperature section. This is another main reason why the efficiency of the actual Stirling engine is significantly less than that of the ideal Carnot engine.  
         [0019]     The steam cycle includes four successive changes. These include heating of the working fluid, evaporation, expansion, and condensation. The Rankine cycle is the ideal cyclical sequence of changes of pressure and temperature of the working I fluid, and is used as a standard for rating the performance of steam power plants.  
         [0020]     With reference to  FIG. 13 , a steam engine  300  typically includes a water supply pump  303  (adiabatic compression), a boiler  305  and a re-heater  307  (isobaric heating), turbines  309  and  312  (adiabatic expansion), and a condenser  301  (isobaric heat radiation). A steam turbine is most commonly used by a power output device in the steam engine that is used as an external combustion engine. The steam turbine converts heat energy into kinetic energy such that high speed steam strikes a turbine to obtain a rotational force of the same.  
         [0021]     As a way to improve efficiency in the steam cycle, referring again to  FIG. 13 , the re-heater  307  is used and the steam in the expansion stage is extracted to the outside of the turbine  309  before being saturated, and is made into superheated steam after being heated in the re-heater  307 . The steam is again directed to the turbine  312  to use a re-heating cycle that expands the steam until reaching the output pressure. Thermal efficiency may be improved by increasing the number of re-heating stages. However, if the number of re-heating stages is increased, the fluid needs to be circulated between the boiler  305  and turbines  309  and  312 , both the overall size of the assembly and equipment costs are increased, and operational control becomes complicated. Accordingly, re-heating is typically performed one or two times, which places a limitation on the efficiency of the steam cycle.  
         [0022]     In the reciprocating piston or Wankel rotary device, which are conventional positive displacement expanders used as external combustion engines in place of the steam turbines  309  and  312 , since the area of heat transfer through the cylinder walls decreases compared to volume as capacity is increased, efficiency reduces in proportion to increases in size of the device.  
       SUMMARY OF THE INVENTION  
       [0023]     The present invention provides a scroll-type expander that simultaneously performs expansion and re-heating such that highly efficient expansion that approximates isothermal expansion is realized and such that there is no reduction in efficiency caused by pressure loss occurring during the supply of an working fluid such as gas or steam to a center area of the scroll-type expander, and that minimizes a difference in temperature between a stationary scroll member and a orbiting scroll member, as well as a temperature distribution of a scroll wrap.  
         [0024]     The present invention also relates to a heat exchange system that uses a scroll-type expander to replace pistons in a conventional reciprocating Stirling engine or refrigerator with a pair of scroll-type compressor and expander such that the heat exchange system may be used as a Stirling engine or refrigerator.  
         [0025]     The present invention also provides a steam engine, in which a steam turbine in the conventional steam engine (Rankine system) is replaced with a scroll-type expander such that the steam cycle has both a re-heating cycle and a regeneration cycle.  
         [0026]     In one embodiment, the present invention provides a scroll-type expander including a sealed housing having a heating surface to an outside area, and including at least one of each of an inflow opening and an exhaust opening at both a center area and a circumferential area; stationary scroll members fixed within the housing and extending from the center area of the housing outwardly in a spiral shape; orbiting scroll members meshed with the stationary scroll members within the housing and extending from the center area of the housing outwardly in a spiral shape, the orbiting scroll members orbiting along a predetermined orbiting radius to continuously expand working fluid entering the housing; heating chambers provided to an outer circumference of the housing and which supply heat when working fluid is expanded by the motion of the orbiting scroll members; and drive shafts connected to the orbiting scroll members to drive the scroll members.  
         [0027]     The scroll-type expander may further include a pre-heating pipe connected to the working fluid inflow opening of the center area of the housing and extending into the heating chambers to pass through the heating chambers so that the working fluid entering the heating chambers may absorb heat, and a plurality of heating pins formed to the external heating surface of the housing that is located within the heating chambers.  
         [0028]     A power transmission shaft may be connected to an outside of one of the drive shafts to enable the transmission of power to outside the scroll-type expander.  
         [0029]     The scroll-type expander may further include heat pipes as a heat transfer assembly connected to the heating chambers and able to transmit large amounts of heat by the low temperature difference as a result of latent heat.  
         [0030]     The steam engine includes a scroll-type expander as described above; a heat exchanger through which high temperature working fluid expanded in the scroll-type expander and exhausted from the scroll-type expander passes; a condenser for condensing the working fluid passing through the heat exchanger; a storage tank for storing the working fluid passing through the condenser; and a pump for pressurizing the working fluid passing through the storage tank. The working fluid pressurized in the pump is circulated by again passing through the heat exchanger to receive heat from high temperature heat source.  
         [0031]     With the scroll-type expander of the present invention, heating, expansion, and re-heating take place in the expander itself such that a compact configuration is realized and isothermal expansion that approaches an infinite stages re-heating cycle is realized.  
         [0032]     The scroll heat exchange system includes a scroll-type compressor including a sealed housing having a heat radiation surface and having at least one of each of the working fluid inflow opening and an exhaust opening at both a center area and a circumferential area, a stationary scroll member fixed within the housing and extending from the center area of the housing outwardly in a spiral shape, and an orbiting scroll member meshed with the stationary scroll member within the housing and extending from the center area of the housing outwardly in a spiral shape, the orbiting scroll members orbiting along a predetermined orbiting radius to continuously compress working fluid entering the housing; a scroll-type expander including a sealed housing having a heating surface and having at least one of each of an working fluid inflow opening and an exhaust opening at both a center area and a circumferential area, a stationary scroll member fixed within the housing and extending from the center area of the housing outwardly in a spiral shape, and an orbiting scroll member meshed with the stationary scroll member within the housing and extending from the center area of the housing outwardly in a spiral shape, the orbiting scroll members orbiting along a predetermined orbiting-radius to continuously expand working fluid entering the housing; a driver connected to each of the orbiting scroll members of the scroll-type compressor and the scroll-type expander to drive the orbiting scroll members; a first connector interconnecting the working fluid exhaust and inflow openings at the outer areas of the scroll-type compressor and the scroll-type expander; a second connector interconnecting the working fluid exhaust and inflow openings at the center areas of the scroll-type compressor and the scroll-type expander; a regenerator through which the first and second connectors pass in a state adjacent to one another to realize heat exchange between the working fluid passing through the first and second connectors; and working fluid compressed in the scroll-type compressor, exhausted through the exhaust opening at the center area of the scroll-type compressor, passed through the regenerator via the second connector, then supplied through the inflow opening at the center area of the scroll-type expander, after which the working fluid undergoes expansion in the scroll-type expander, is exhausted through the exhaust opening at the outer area of the scroll-type expander, passed through the regenerator via the first connector, and supplied through the inflow opening at the outer area of the scroll-type compressor to thereby realize circulation of the working fluid through the heat exchange system.  
         [0033]     The scroll heat exchange system may further include a cooling section formed around an outer circumference of the housing that surrounds the scroll-type compressor such that heat generated when working fluid is compressed is expelled outwardly, and a heating section formed around an outer circumference of the housing that surrounds the scroll-type expander such that heat is supplied during expansion of working fluid.  
         [0034]     The scroll heat exchange system may further include a cooler connected to the working fluid inflow opening provided to the outer area of the scroll-type compressor and acting to cool the working fluid that is supplied to the scroll-type compressor after passing through the regenerator, and a heater connected to the working fluid exhaust opening provided to the center area of the scroll-type expander and acting to heat the working fluid that is supplied to the scroll-type expander after passing through the regenerator.  
         [0035]     The scroll heat exchange system may further include a bypass line communicating an area between a center compression area of a predetermined distance from the center area of the housing and the connector connected to the working fluid exhaust opening of the center area, and a control valve mounted on the bypass line to control the amount of fluid that is bypassed to vary compression amounts.  
         [0036]     The scroll heat exchange system may operate as an engine when a heat of a temperature higher than a temperature of the scroll-type compressor is supplied to the scroll-type expander, and power is output from the drivers connected to the scroll-type expander and the scroll-type compressor. Also, the scroll heat exchange system may operate as a refrigerator when power is input to the drivers connected to the scroll-type expander and the scroll-type compressor, and a heat of a temperature lower than a temperature of the scroll-type compressor is absorbed in the scroll-type expander.  
         [0037]     In the scroll heat exchange system of the present invention, the mechanical structure is simple, and compression and expansion are continuously performed such that there is almost no variation in torque and a flow direction of the operational fluid is unchanged. As a result, flow lines and regenerator structure may be realized such that flow resistance is small.  
         [0038]     In addition, since the heat transfer area making contact with the working fluid in the compressor and expander is extremely large, highly efficient isothermal compression and expansion that approaches the ideal Stirling cycle is possible, and a heater and cooler may be made small or removed altogether such that dead volume is reduced to improve output. Finally, overall manufacturing costs are reduced by minimizing or removing the need for the heater.  
         [0039]     In the scroll heat exchange system of the present invention, since the working fluid flow is in one direction, the working fluid heated in the heater is not re-heated following expansion, and the working fluid cooled in the cooler is not re-cooled following compression such that heat loss, flow resistance, thermal stress, etc. caused by anomalies in the cycle may be reduced.  
         [0040]     In addition, since low temperature compression and high temperature expansion are realized as fully separated processes, high efficiency that approaches an ideal cycle may be obtained. Also, compression ratio control by the bypass line in the compressor is easy such that effective engine control is possible.  
         [0041]     Finally, in the scroll heat exchange system of the present invention, since continuous, steady state driving is possible, there are almost no periodic temperature and pressure variations in the structural elements such that limitations on the selection of materials for and manufacture of the structural elements are significantly reduced, and low noise, low vibration, small size, and light weight may be realized as a result. 
     
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0042]      FIG. 1  is a schematic drawing showing the interaction between a stationary scroll member and a orbiting scroll member, and is used to describe an operation of a scroll-type compressor.  
         [0043]      FIG. 2  is a sectional view of a scroll-type expander according to a preferred embodiment of the present invention.  
         [0044]      FIG. 3  is a schematic view of a scroll heat exchange system according to a first embodiment of the present invention.  
         [0045]      FIG. 4  is a schematic view of a scroll heat exchange system according to a first embodiment of the present invention with a cooler and a heater attached thereto.  
         [0046]      FIG. 5  is a sectional view of a scroll heat exchange system according to a second embodiment of the present invention.  
         [0047]      FIG. 6  is a schematic view of a scroll heat exchange system according to a third embodiment of the present invention.  
         [0048]      FIG. 7  is a schematic view of a scroll assembly connected to a bypass line according to a preferred embodiment of the present invention.  
         [0049]      FIG. 8  is a schematic view of a conventional reciprocating Stirling engine.  
         [0050]      FIG. 9 a  schematic view of a conventional reciprocal Stirling engine with a heater and a cooler attached thereto.  
         [0051]      FIG. 10  is a schematic view used to describe the sequential processes in an ideal Stirling cycle.  
         [0052]      FIG. 11  is a P-V diagram of an ideal Stirling cycle.  
         [0053]      FIG. 12  is a P-V diagram of an actual Stirling cycle.  
         [0054]      FIG. 13  is a schematic view of a conventional Rankine system that uses a re-heating cycle.  
         [0055]      FIG. 14  is a sectional view of a steam engine including a scroll-type expander according to a preferred embodiment of the present invention. 
     
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS  
       [0056]     Preferred embodiments of the present invention will now be described in detail with reference to the accompanying drawings.  
         [0057]     Referring to  FIG. 2 , a scroll-type expander  10  according to a preferred embodiment of the present invention includes stationary scroll members  13  and orbiting scroll members  15  provided within a housing  12 , and it performs expansion of an working fluid flowing into the scroll-type expander  10  then expels the same from the housing  12 .  
         [0058]     The housing  12  includes a heating surface to an outside; two inflow openings  27  to a center area that act as openings for the working fluid, the inflow openings  27  being provided at upper and lower areas; and an exhaust opening  23  that allows the exhaust of the working fluid to outside the housing  12 .  
         [0059]     The stationary scroll members  13  are fixed to an inner surface of the housing  12  and extend from the center area of the housing  12  outwardly in a spiral shape. A pair of the stationary scroll members  13  are provided in an opposing configuration. A center of the stationary scroll members  13  corresponds to the inflow openings  27  of the housing  12 .  
         [0060]     The orbiting scroll members  15  are meshed with stationary scroll members  13  within the housing  12 , and they also extend from the center area of the housing  12  outwardly in a spiral shape. The orbiting scroll members  15  are orbiting along a predetermined orbiting radius to continuously expand working fluid entering the housing  12 . A pair of the orbiting scroll members  15  is mounted between the pair of the opposing stationary scroll members  13 , with one orbiting scroll member  15  being meshed with one stationary scroll member  13 .  
         [0061]     Heating chambers  17  are provided to an outer circumference of the housing  12 . The heating chambers  17  supply heat to inside the housing  12  when working fluid is expanded by the motion of the orbiting scroll members  15 .  
         [0062]     Heat pipes (not shown) may be provided in the heating chambers  17  so that there is sufficient heat transfer and uniform temperature distribution. The heat pipes are able to transmit large amounts of heat by the low temperature difference as a result of latent heat.  
         [0063]     Pre-heating pipes  25  are connected to the inflow openings  27  and extend into the heating chambers  17 . The pre-heating pipes  25  pass through the heating chambers  17  so that the working fluid entering the heating chambers  17  may absorb heat.  
         [0064]     Further, a plurality of heating pins  19  are formed to an external heating surface of the housing  12  that is located within the heating chambers  17 . The heating pins  19  increase the heat transfer rate to the housing  12 .  
         [0065]     Drive shafts  29  are connected to the orbiting scroll members  15  to drive the same. Two of the drive shafts  29  are connected to both ends of the orbiting scroll members  15 . A power transmission shaft  32  is connected to one of the drive shafts  29  to enable the transmission of power to outside the scroll-type expander  10 . A bearing assembly  34  is mounted where the drive shafts  29  are connected to undergo rotation.  
         [0066]     Further, a seal  36  is provided at each area of connection of the drive shafts  29 . The seal  36  prevents leakage of lubrication oil. Also, an insulating material  38  is formed between the bearing assemblies  34  and the housing  12  to prevent overheating of the bearing assemblies  34 .  
         [0067]     Working fluid supplied through the pre-heating pipes  25  undergoes a primary heating process while passing through the pre-heating pipes  25 , and is supplied to inside the housing  12  through the inflow openings  27 . The working fluid is then slowly expanded while passing between the orbiting scroll members  15  and the stationary scroll members  13 . During this process, the working fluid is re-heated by the effective supply of heat of the wide heating surface of the housing  12  and the scroll wraps such that a highly efficient expansion that approaches isothermal expansion is realized. The working fluid expanded in this manner is exhausted to outside the housing  12  through the exhaust opening  23 .  
         [0068]     When the temperature of the scroll-type expander  10  is lower than the temperature of the supplied operational fluid, the scroll-type expander  10  of the preferred embodiment of the present invention may also be used as a scroll-type expander of a refrigerator that absorbs heat in the scroll-type expander  10  driven by external power.  
         [0069]     With reference to  FIG. 3 , a basic structure of a scroll heat exchange system  100  according to a first preferred embodiment of the present invention includes a scroll-type compressor  112 , a scroll-type expander  132 , and a regenerator  120 . The scroll-type compressor  112  and the scroll-type expander  132  are interconnected through a first connector  121  and a second connector  123 .  
         [0070]     The scroll-type compressor  112  includes a stationary scroll member  114  and a orbiting scroll member  116  provided within a housing  113 , and acts to compress working fluid that enters the scroll-type compressor  112  and exhaust the compressed working fluid through a center area. The housing  113  includes one working fluid inflow opening at an outer area and one working fluid exhaust opening at the center area, and is otherwise sealed from the outside. The stationary scroll member  114  is fixed within the housing  113  and is extended from the center area of the housing  113  outwardly in a spiral shape. The orbiting scroll member  116  is meshed with the stationary scroll member  114  within the housing  113 , and also extends from the center area of the housing  113  outwardly in a spiral shape. The orbiting scroll member  116  is orbiting along a predetermined orbiting radius in the space made with the stationary scroll member  114  to continuously compress working I fluid entering the housing  113 .  
         [0071]     A refrigerating section  118  is formed around an outer circumference of the housing  113  that surrounds the scroll-type compressor  112 . The cooling section  118  allows for heat generated when working fluid is compressed to be expelled outwardly. To realize this, the housing  113  has a heat radiation surface to an outer area thereof.  
         [0072]     The scroll-type expander  132  includes a stationary scroll member  134  and a orbiting scroll member  136  provided within a housing  133 , and acts to expand working fluid that enters the scroll-type expander  132  and exhaust the expanded working fluid. The housing  133  includes one working fluid inflow opening at a center area and one working fluid exhaust opening at an outer area, and is otherwise sealed from the outside. The stationary scroll member  134  is fixed within the housing  133  and is extended from the center area of the housing  133  outwardly in a spiral shape. The orbiting scroll member  136  is meshed with the stationary scroll member  134  within the housing  133  and also extends from the center area of the housing  133  outwardly in a spiral shape. The orbiting scroll member  136  is orbiting along a predetermined orbiting radius in the space made with the stationary scroll member  134  to continuously expand working fluid entering the housing  133 .  
         [0073]     A heating section  138  is formed around an outer circumference of the housing  133  that surrounds the scroll-type expander  132 . The heating section  138  allows heat to be supplied during expansion of working fluid, and to realize this, the housing  133  has a heating surface to an outer area thereof.  
         [0074]     Each of the orbiting scroll members  116  and  136  of the scroll-type compressor  112  and the scroll-type expander  132 , respectively, are connected to a driver (not shown) so that the orbiting scroll members  116  and  136  may be orbiting.  
         [0075]     As described above, the scroll-type compressor  112  and the scroll-type expander  132  are interconnected through the first connector  121  and the second connector  123 . In more detail, the first connector  121  interconnects the working fluid exhaust and inflow openings at the outer areas of the scroll-type compressor  112  and the scroll-type expander  132 , while the second connector  123  interconnects the working fluid exhaust and inflow openings at the center areas of the scroll-type compressor  112  and the scroll-type expander  132 .  
         [0076]     Heat exchange is realized in the regenerator  120  by the first and second connectors  121  and  123  structured in this manner. The first and second connectors  121  and  123  pass through the regenerator  120  in a state adjacent to one another to realize heat exchange between the working fluid passing through the first and second connectors  121  and  123 .  
         [0077]     The working fluid is compressed in the scroll-type compressor  112  then exhausted through the exhaust opening at the center area of the scroll-type compressor  112 , passed through the regenerator  120  via the second connector  123 , then supplied through the inflow opening at the center area of the scroll-type expander  132 . The working fluid then undergoes expansion in the scroll-type expander  132 , is exhausted through the exhaust opening at the outer area of the scroll-type expander  132 , passed through the regenerator  120  via the first connector  121 , then is supplied through the inflow opening at the outer area of the scroll-type compressor  112 . This process is repeated to realize circulation of the working fluid through the heat exchange system  100 .  
         [0078]     With reference to  FIG. 4 , a cooler  125  and a heater  127  may be further included in the scroll heat exchange system  100  according to the first embodiment of the invention.  
         [0079]     The cooler  125  is connected to the operational fluid inflow opening provided to the outer area of the scroll-type compressor  112 , and acts to cool the working fluid that is supplied to the scroll-type compressor  112  after passing through the regenerator  120 . The heater  127  is connected to the working fluid exhaust opening provided to the center area of the scroll-type expander  132 , and acts to heat the working fluid that is supplied to the scroll-type expander  132  after passing through the regenerator  120 .  
         [0080]     When a temperature of the scroll-type expander  132  is higher than a temperature of the scroll-type compressor  112 , the scroll heat exchange system  100  operates as an engine such that heat is received in the scroll-type expander  132  and heat is rejected from the scroll-type compressor  112  in the manner of a Stirling engine. Further, heat is transferred from the working fluid of after expansion to the working fluid of after compression, and power is output through a driver.  
         [0081]     On the other hand, if the temperature of the scroll-type expander  132  is lower than the temperature of the scroll-type compressor  112 , the scroll heat exchange system  100  operates as a refrigerator such that external power is received through the driver and heat is received from the scroll-type expander  132  and heat is output from the scroll-type compressor in the manner of a Stirling refrigerator. Also, heat is transferd from the working fluid of after compression to the working fluid of after expansion.  
         [0082]      FIG. 5  is a sectional view of a scroll heat exchange system according to a second embodiment of the present invention.  
         [0083]     With reference to the drawing, a scroll heat exchange system  140  according to a second preferred embodiment of the present invention is basically the same in structure to the scroll heat exchange system  100  according to the first preferred embodiment of the present invention. However, a pair of stationary scroll members  143  and a pair of orbiting scroll members  145  are provided in a housing  142  of a scroll-type compressor  141 , and a pair of stationary scroll members  153  and a pair of orbiting scroll members  155  are provided in a housing  152  of the scroll-type expander  151  such that an upsetting moment is not generated.  
         [0084]     A plurality of cooling pins  149  are formed to an external surface of the housing  142  of the scroll-type compressor  141 , and a plurality of heating pins  159  are formed to an external surface of the housing  152  of the scroll-type expander  151  such that cooling and heating are better performed.  
         [0085]     The orbiting scroll members  145  and  155  of the scroll-type compressor  141  and the scroll-type expander  151 , respectively, are each connected to two drive shafts  165  to drive the same. A first drive shaft section  165   a  connected to the orbiting scroll members  145  of the scroll-type compressor  141  and a second drive shaft section  165   b  connected to the orbiting scroll members  155  of the scroll-type expander  151  are 180° out of phase. Such a configuration is used to minimize unbalancing caused by rotational force.  
         [0086]     The two drive shafts  165  are connected by a belt or chain to rotate in unison. Also, the drive shafts  165  transmit power to the outside through a power transmission shaft  167  that extends outwardly from the scroll heat exchange system  140 . A bearing assembly  169  is mounted where the drive shafts  165  are connected to undergo rotation.  
         [0087]     In the heat exchange system  140  according to the second preferred embodiment of the present invention, working fluid is additionally cooled by passing through the regenerator  160  and cooling chambers  147 . Further, the working fluid flows into the scroll-type compressor  141  through the first connector  161  to be compressed by the motion of the orbiting scroll members  145 . During compression, the working fluid is further cooled by the cooling pins  149  formed on the housing  142  in the area of the same corresponding to where the cooling chambers  147  are formed.  
         [0088]     The working fluid compressed in this manner passes through the regenerator  160  through the second connector  162  to realize heat exchange with the high temperature working fluid passing through the first connector  161 , thereby being heated. Next, this working fluid passes through heating chambers  157  to be further heated, then is supplied to inside the scroll-type expander  151  to be expanded while acting against the orbiting scroll members  155 . During expansion, the working fluid is further heated by the heating pins  159  formed on the housing  152  in the area of the same corresponding to where the heating chambers  157  are formed.  
         [0089]     The working fluid expanded in this manner again passes through the regenerator  160  via the first connector  161  to realize heat exchange with the low temperature working fluid passing through the second connector  162 , thereby being cooled. Next, this working fluid is supplied to inside the scroll-type compressor  141  to complete the cycle.  
         [0090]     The upper and lower cooling chambers  147  of the scroll-type compressor  141  are interconnected, and the upper and lower heating chambers  157  of the scroll-type expander  151  are interconnected. Further, the working fluids exhausted through upper and lower center areas of the scroll-type compressor  141  are combined for supply to the regenerator  160 , and the working fluids supplied to the scroll-type expander  151  from the regenerator  160  are also combined.  
         [0091]      FIG. 6  is a schematic view of a scroll heat exchange system according to a third embodiment of the present invention.  
         [0092]     With reference to the drawing, in a heat exchange system according to a third embodiment of the present invention, a center scroll-type compressor  172  is provided to a middle area of the system. Also, a first scroll-type expander  174  of a higher temperature than the center scroll-type compressor  172  is connected to one side of the same, and a second scroll-type expander  176  of a lower temperature than the scroll-type compressor  172  is connected to another side of the same. The heat exchange system structured in this manner may be used as a Stirling refrigerator driven by Stirling engine.  
         [0093]     That is, the combination of the high temperature first scroll-type expander  174  and the scroll-type compressor  172  operates as a Stirling engine, and the combination of the low temperature second scroll-type expander  176  and the scroll-type compressor  172  operates as a Stirling refrigerator.  
         [0094]     Such a structure is made possible by the joint use of the first scroll-type expander  174  and the second scroll-type expander  176  both having inflow and exhaust openings for working fluid of the scroll-type compressor  172 . Accordingly, working fluid is compressed in the scroll-type compressor  172  then exhausted through an exhaust opening of a center area. Part of the working fluid passes through a second connector  182  then through a first regenerator  185 , after which the working fluid flows into a center area inflow opening of the first scroll-type expander  174  to be expanded therein. The working fluid is then exhausted through an exhaust opening of an outer circumference, passed through a first connector  181  and through the first regenerator  185 , and flowed into an inflow opening of an outer circumference of the scroll-type compressor  172  to thereby realize circulation through the system. The other part of the working fluid passes through a fourth connector  184  and through a second regenerator  186  to flow into an inflow opening of a center area of the second scroll-type expander  176  to be expanded therein. The working fluid is then exhausted through an exhaust opening of an outer circumference, passed through a third connector  183  and through a second regenerator  186 , and flowed into an inflow opening of an outer circumference of the scroll-type compressor  172  to thereby realize circulation through the system.  
         [0095]     By jointly using the scroll-type compressor for the Stirling engine and Stirling refrigerator, a compact structure is realized for the Stirling refrigerator driven by Stirling engine. Also, since a power remaining after refrigerator driving may be used to generate electric power using a generator, a system that realizes both air conditioning and electric power generation may be realized.  
         [0096]      FIG. 7  is a schematic view of a scroll assembly connected to a bypass line according to a preferred embodiment of the present invention.  
         [0097]     In the conventional control method for a reciprocating Stirling apparatus, although there are internal working gas pressure changes, dead volume control, and compression ratio changes as a result of stroke control, the entire apparatus is complicated and high in cost. With reference to  FIG. 7 , in a control method for a Stirling cycle apparatus using a scroll apparatus, compression capacity is controlled by controlling a bypass line  193  at a center compression area of a stationary scroll member  191  of a scroll-type compressor. As a result, compression amounts are easily controlled. Engine control is therefore quickly and effectively realized.  
         [0098]     The center compression area is positioned a predetermined distance from a center area of the scroll-type compressor. Further, the bypass line  193  is formed communicating a connector connected to the center area of the scroll-type compressor and the center compression area. A control valve  195  is provided on the bypass line  193  to control the amount of fluid that is bypassed.  
         [0099]      FIG. 14  is a sectional view of a steam engine including a scroll-type expander according to a preferred embodiment of the present invention.  
         [0100]     With reference to the drawing, in addition to a scroll-type expander  410 , the steam engine includes a heat exchanger  440 , a condenser  441 , a storage tank  443 , and a pump  445 .  
         [0101]     An exhaust opening  423  of the scroll-type expander  410  is connected to the heat exchanger  440  such that high temperature working fluid expanded in and exhausted from the scroll-type expander  410  passes through the heat exchanger  440 . The heat exchanger  440  is also connected to the condenser  441 .  
         [0102]     Working fluid passed through the heat exchanger  440  flows into the condenser  441  to be condensed therein. The condenser  441  is connected also to the storage tank  443  such that the working fluid passed through the condenser  441  is temporarily stored in the storage tank  443 . The storage tank  443  is connected to a pump  445  and acts as a gas-water separator to increase a compression efficiency of the pump  445  and to replenish the working fluid.  
         [0103]     The pump  445  acts to pressurize the working fluid supplied from the storage tank  443 . The pump  445  is also connected to the heat exchanger  440 .  
         [0104]     The working fluid pressurized in the pump  445  is heated by receiving heat from the high temperature working fluid exhausted from the scroll-type expander  410  while passing through the heat exchanger  440 . The working fluid heated in this manner is supplied to the scroll-type expander  410  through a pre-heat pipe  425 .  
         [0105]     The steam engine having the scroll-type expander structured as in the above operates identically to the steam turbine Rankine system that uses a regeneration cycle and an infinite stages re-heating cycle.  
         [0106]     Although preferred embodiments of the present invention have been described in detail hereinabove, it should be clearly understood that many variations and/or modifications of the basic inventive concepts herein taught which may appear to those skilled in the present art will still fall within the spirit and scope of the present invention, as defined in the appended claims.