JP2008516147A - Power generation method and system using Stirling engine principle - Google Patents

Abstract

The heat engine surrounding the chamber in the housing has two regions that are maintained at different temperatures. The first region receives thermal energy from an external power source. The second region is connected to the thermal region by two conduits so that fluid filling the chamber (eg, air, water or any other gas or liquid) can circulate between the two regions. The expansion of the fluid in the hot region and the compression of the fluid in the cold region drive the rotation of the housing to provide power output. The fluid may be pressurized to improve efficiency. The cooling fluid provided in the fixed reservoir maintains a suitable operating temperature difference between the hot zone and the cold zone. A heat storage structure including a fluid having a high heat capacity is provided as a heat accumulator.
[Selection] Figure 1

Description

The present invention relates to the application of Stirling engine principles to the design and use of power converters. In particular, the invention relates to the application of the Stirling engine principle for power generation, for example to generate mechanical power.

A Stirling engine is a heat engine that operates by converting the heat energy flowing between regions of different temperatures into useful work. A typical Stirling engine uses thermal energy to drive the coordinated reciprocating motion of a set of pistons. The movement of the piston drives the mechanism or generator. Heat engines that rotate are also known. Many designs of rotating Stirling engines are described in US Pat. Can be found in the prior art including 6,195,992, 3,984,981 and 5,325,671. In the prior art, moving parts for Stirling engine operation are placed in a housing and mechanically coupled to an external part (eg, by a drive shaft) to drive an external mechanism. High efficiency in such an arrangement requires that the housing be closed to be sealed. Failure to seal can lead to engine failure.

The present invention provides a method and rotary engine based on the Stirling engine principle. According to one embodiment of the present invention, the rotary engine housing rotates as a result of fluid flow between two regions of different temperatures within the housing chamber. Therefore, the torque of the rotational movement of the housing can be used to drive a mechanism (eg, a generator) through a drive shaft or gear structure coupled to the outside of the housing. Unlike the prior art, under this arrangement, the rotary engine of the present invention is less susceptible to failure due to leakage in sealing the housing.
According to one embodiment of the present invention, the hot area of the chamber is heated by energy from the heat source and the cooling device maintains the cold area at a lower temperature than the hot area. The cooling fluid can be drawn from a fixed external reservoir of cooling fluid. In one example, the rotational movement of the housing may be used to draw cooling fluid. In this embodiment, the volume of cooling fluid drawn to the rotary engine depends on the angular velocity of the rotational motion that can in turn be determined by the power output of the rotary engine. A self-controlled cooling device can then be achieved. The structure used to reinforce the housing where the external drive shaft (or external gear structure) is to be attached may include a threaded passage. In this embodiment, in the vicinity of the cold region (eg, an insulator layer abutting the cold region, a fluid guide structure, or a region between the cold region and the housing) so as to maintain the cold region within a desired temperature range. Through the expanding passage, the rotating screw passage urges the cooling fluid into the housing.
The turbine of the heat engine of the present invention may be located at any suitable location on the inner surface of the hot or cold region of the housing, but is connected to the housing to provide rotational movement to the housing, and the rotary There is no need to drive the drive shaft or gear structure directly to provide engine output power. The chamber of the rotary engine can be filled with a compressible working fluid (eg air). The fluid guide may be provided within the chamber to direct the flow of compressible working fluid at a flow rate that provides high efficiency in a suitable direction. The fluid guide may also provide structural or mechanical support to the chamber. Thus, the design of the heat engine provides a way to adjust the working fluid temperature within the housing 101 by flowing fluid from a cooling source or heating source through a fluid guide to the hot region, the cold region, or both. This also provides a method for adjusting the power output of the engine without changing the heat source or radiator.
In one embodiment, a one-way valve may be provided between the hot and cold regions to prevent hot working fluid from flowing back to the cold region.
In another embodiment, a metal mesh is provided in the heat region to increase the efficiency of heat transfer from the heat source to the heat region. A heat storage structure may also be provided to minimize the impact of fluctuating heat sources on the rotary engine power output during the engine cycle or to provide a secondary heat source to the heat engine. it can. Certain high heat capacity fluids or heat storage fluids can be used in the heat storage structure. Thermal storage can be used to equalize energy production or power requirements during times of different energy requirements.
In one embodiment, after reaching a predetermined operating condition (eg, a predetermined temperature), the conductive plate is biased by a mounted spring to bring the heat zone into contact.
The present invention is better understood upon consideration of the detailed description below and the accompanying drawings.

The present invention provides a heat engine that operates under the Stirling engine principle to convert thermal energy from a heat source into mechanical energy. Mechanical energy can be coupled to drive the mechanism and generator to perform useful work. Examples of suitable heat sources include solar, geothermal, fossil, landfill, regenerated or another fuel.
FIG. 1 illustrates a cross-sectional view of a heat engine 100 that includes a cooling fluid reservoir 107, according to one embodiment of the present invention. As shown in FIG. 1, the heat engine 100 includes a chamber 110 that is enclosed in an enclosure or housing 101. In operation, if a heat source is provided associated with the top surface 101a of the housing 101, a temperature difference exists within the chamber 110 between the "hot zone" 110a and the "cold zone" 110b. The present invention takes advantage of this temperature difference to rotate the housing 101 about the axis indicated by 'Y' in the method described below. The engine housing rotates during operation, and the working fluid space is entered into the chamber without holes or joints between the passages, chamber and rotating power output device so that the engine working fluid can be externally generated by the gear or mechanical Separated from the device. Therefore, no special sealing treatment is required.
The rotational drive shaft 109 of rotational motion may be used to drive the motion of an external mechanical device. As shown in FIG. 1, the drive shaft 109 is essentially perpendicular to the cross-sectional area or plane between the hot area 110a and the cold area 110b. Using another suitable structure, rotational power output can also be achieved (e.g. gear structure; such structure is located anywhere outside the housing 101 or is built on the outer wall of the housing 101). Is possible). According to one embodiment of the present invention, the drive shaft 109 is partially covered by the rotating structure 111 and extends beyond the cooling storage 107. Alternatively, the drive shaft 109 may also be coupled to the top plate 101 a of the housing 101. Thus, the design of the heat engine provides a way to regulate the temperature of the working fluid within the housing 101 by operating the fluid from a cooling source or heat source through a fluid guide to the heat region, the cold region, or both. . This also provides a way to adjust the engine power output without changing the heat source or heatsink.

In the illustrated embodiment of FIG. 1, a cooling mechanism is provided to maintain a temperature difference between the hot zone 110a and the cold zone 110b. This temperature difference drives the rotational movement of the housing 101 and thus provides output power. The cooling mechanism includes a cooling fluid that circulates between the cooling reservoir 107, the cold region 110b, the space 508, and the insulator layer 104 to maintain or increase the 110a temperature difference between the cold region 110b and the hot region. A storage unit 107 is included. A reservoir cover 115 is provided between the housing 101 and the cooling reservoir 107 to prevent cooling fluid outflow and excessive deposition. In this detailed description, the terms “hot” and “cold” are relative. As long as there is a sufficient temperature difference between the heat zone 110a and the cold zone 110b, the heat engine 100 will operate.
The elements contained within the housing 101 are better illustrated with FIGS. 2 and 3 showing the heat engine 100 in an “equal expanded” side view and an “equal expanded” perspective view, respectively. The outer sidewall of the housing 101 is omitted in FIGS. 2 and 3 to allow the internal structure of the heat engine 100 within the chamber 110 shown. As shown in FIGS. 1, 2 and 3, the top plate 101a and the lower plate 101b are the upper outer wall and the bottom outer wall of the housing 101, respectively. In the present embodiment, a heat source (for example, solar energy) is projected onto the top plate 101a. As will be described below, the cooling fluid in the cooling reservoir 107 maintains the region between the insulator layer 104 and the mounting plate 101b at a low temperature. The combined operation of the heat source and cooling fluid creates a hot zone 110a and a cold zone 110b as shown in FIGS. In this example, the cold region 110b is separated from the lower plate 101b by the disk 108 to create a space 508 between the disk 108 and the lower plate 101b where cooling fluid may flow to achieve temperature regulation. (In this description, the upper and lower portions of FIG. 2 are categorized as “top” and “bottom”, respectively, merely for ease of reference to this detailed description. It is not limited by its physical orientation.) In FIGS. 2 and 3, the heat engine 100 is shown in an “exploded” view in the sense that the separation between the elements of the heat engine 100 is exaggerated in the vertical direction for purposes of illustration. Indicated. In one embodiment, the disk 108 is provided adjacent to the lower plate of the housing 101, thereby separating the cold region 110b from the lower plate 101b. Lower plate 101b surrounds disk 108 and creates a space 508 through which cooling fluid may flow to achieve temperature regulation. The disk 108 can be shown as the bottom of the housing 101 and the lower plate 101b can be shown as a surrounding enclosure around the bottom of the housing 101, so that the space 508 is formed.

The hot region 110a and the cold region 110b are insulated from each other by an insulator layer 104, which will be described in detail below. An optimally positioned support structure may be provided throughout the hot zone 110a and the cold zone 110b for mechanical support within the housing 101. For example, such a support structure may include posts, posts, beams and posts. Thermionic and thermocouple devices may be provided within the insulator layer 104 as well. Such a device may be used to provide a power output as discussed in the pending patent application incorporated in the above reference. In this embodiment, the isolation structure 105 is further interposed between the thermal region 110 a and the insulator layer 104. The fluid flows between the hot zone 110a and the cold zone 110b through the central open shaft 113 and the space 121. The space 121 includes all the spaces between the fluid guide structure 106, the separation structure 105, the insulator layer 104, the rotating structure 111, and the outer wall of the housing 101. Isolation structure 105 is any storage structure detailed below. Chamber 110 is filled with a compressible working fluid that may be air, other fluids, or a mixture of fluids to achieve the desired fluid density and mechanical, aerodynamic and thermal properties. The working fluid can be pressurized.
The heat engine 100 collects thermal energy received by a turbine structure that may be located on the surface of the interior wall of the housing 101. For example, such a location may include 110b in the space 121, the hot region 110a, and the cold region. The turbine structure may also be located on the surface of the internal structure between the hot zone 110a and the cold zone 110b. For example, such a location may include within space 121 and within central open axis 113. The turbine structure may be located at any suitable location where torque can be generated for the desired rotational movement of the housing 101. Turbine structures may also be built on the interior walls of the housing 101. These turbine structures are designed to guide the working fluid to control the working fluid speed and pressure to extract the most rapidly increasing power from the expansion and compression of the working fluid and create torque for rotational motion May include one or more collections of fluid guides or blades. In one embodiment, each fluid guide in the turbine structure preferably maintains a predetermined angle relative to the working fluid during rotation of the housing 101. The turbine structure may be any suitable size or material depending on the application of the heat engine 100.
According to one embodiment of the present invention, the heat engine 100 includes a turbine structure referred to herein as a fluid guide structure 106 in the heat zone 110a. FIG. 4 is a top view of the hot region 110a under the top plate 101a. As shown in FIG. 4, the heat engine 100 is numbered from plates 401, a first set of fluid guides 114 numbered 114-1 to 114-m, and 112-1 to 112-n. A fluid guide structure 106 that includes a second set of fluid guides 112 is included. Here, n and m are integers. The plate 401 may be the separation structure 105 or the top plate of the insulator layer 104 depending on the structure of the heat engine 100. The fluid guides 112 and 114 are designed to work in concert or separately and may function as a residual heat transfer surface as a heat source or radiator. The fluid guides 112 and 114 may be any suitable size, curvature, or any material depending on the application of the heat engine 100. In general, the fluid guides 112-1 through 112-n may be attached to any structure between the hot zone 110a and the cold zone 110b (within the space 121 and the central open shaft 113). The fluid guides 112-1 to 112-n may also be attached to an internal wall of the housing 101. In one embodiment, 112-1 through 112-n fluid guides are attached to the housing 101 and are generally positioned around the periphery of the plate 401 in the space 121 as shown in FIG. The fluid guide 112 may also be attached to the plate 401, the fluid guide structure 106, the separation structure 105 or to the insulator layer 104. The fluid guide 112 may have an aerodynamic design. In the aerodynamic design, a pressure difference is created between the two surfaces of the fluid guide as different velocity fluid flows along the surface. In one embodiment, each fluid guide is provided with a rounded profile such that one side of the fluid guide has a greater cross-section than another, thereby providing a torque that provides rotational movement of the housing 101. Create
As described above, the fluid guides 112-1 to 112-n are designed to maintain a predetermined angle in relation to the direction of flow of the working fluid in the immediate vicinity of each fluid guide 112. During operation, heat accumulates in the heat zone 110 a, so that the expanding working fluid in the heat zone 110 a pushes the fluid guide collection 112 to create a torque that rotates the housing 101. The working fluid in the hot region 110 a flows radially outward from the space above the central open shaft 113 and flows to the cold region 110 b through the annular space 121. Alternatively, the fluid guide 112 may be a central open shaft 113 such as, for example, a cooling device passage to the insulator layer 104, the insulator layer 104, the isolation structure 105, the one-way valve 801 and the fluid guide structure 106. May be attached to the structure within the range of

An example of using a fluid guide 112 of a fluid guide structure 106 having a drive shaft to form a turbine is disclosed in a pending patent application incorporated by reference above. Torque created by the rotating fluid guide structure 106 is transmitted through the outer wall of the housing 101 to the rotating structure 111 (and thus the drive shaft 109) so that the housing 101 rotates integrally with the fluid guide structure 106. Although an asymmetric surface area on each fluid guide 112 is not required, in some applications it may provide benefits such as ease of starting with motion in a given direction. The fluid guide 112 may provide a large surface area for heat transfer. Therefore, in order to improve efficiency, the heat engine 100 has a high surface relative to the volume ratio. The fluid guides 112-1 to 112-n can also be used as fluid guides to control the working fluid flow at a suitable angle so as to maximize torque generation.
The fluid guides 114-1 to 114-m guide the working fluid at a suitable angle toward the fluid guide 112 in order to achieve a suitable rotational force. The fluid guides 114-1 to 114-m may be formed as a support structure for providing support between the top plate 101 a and the separation structure 105. Fluid guides 114-1 and 114-m may be used to accommodate the design of fluid guide 112. The fluid guides 114-1 and 114-m may have thermal properties to provide a heat or cooling surface for heat transfer. The fluid guides 114-1 and 114-m may also be used to form a passage for working fluid circulation or to control working fluid pressure. The fluid guides 114-1 and 114-m may be used as access to heat or cooling sources outside the engine compartment. Thus, the heat engine design provides a way to regulate the working fluid temperature within the housing 101 by operating the fluid from a cooling source or heat source through a fluid guide to the heat region, the cold region, or both. This also provides a way to adjust the engine power output without changing the heat source or radiator. The fluid guides 114-1 to 114-m may provide working fluid volume shaping or other fluid properties that vary within the working fluid path to improve working fluid movement. For example, such characteristics can include working fluid velocity, direction and volume. Although not shown in this example, a similar fluid guide structure having a corresponding collection of fluid guides may also be provided in the cold region 110b to form a return path for the working fluid. Alternatively, the fluid guide structure in the cold region 110b may be provided in different structures (eg, different materials performing different functions, differently formed fluid guides) to achieve different design objectives. is there. The fluid guides 114-1 to 114-m may be shaped and used as blades that assist the turbine structure creating torque that rotates the housing 101 in a predetermined direction. The fluid guides 114-1 through 114-m may be located anywhere within the chamber 110 depending on application requirements. The fluid guide structure 106 may be considered as part of the turbine structure.
According to other embodiments, the fluid former may be used within the working fluid path to guide the fluid or control fluid volume. For example, the fluid former may include a cone, a power bell and a funnel. The fluid former can be solid or hollow.
The fluid former may be incorporated on or within the internal wall of the housing 101. The fluid former may be executed at an intermediate space between two specific regions in the working fluid space, or at one or more locations within a specific region of the working fluid path. For example, an example of a working fluid space may include a hot region 110a, a cold region 110b, a central open shaft 113 and a space 121. An example using a solid cone-shaped fluid former is shown in FIGS. Thus, the disk 108 extends toward the central open shaft 113 and has a portion that forms a conical fluid former 200 within the housing 101. The fluid former 200 is also located between the cold zone 110b and the space 507 and is used to guide the working fluid towards the hot zone 110a, possibly helping to maintain the direction of fluid flow motion. is there. The fluid former 200 may change the speed of the working fluid by narrowing a portion of the fluid path. In one example, the fluid former 200 is used to control the working fluid volume entering the central open shaft 113 from the cold region 110b. The smaller the working fluid space between the fluid former 200 and the opening of the central open shaft 113, the faster the working fluid flows. A funnel fluid block in the central open shaft 113 with a smaller end towards the heat zone 110a can increase the internal working fluid velocity. The fluid former 200 may be used where the central working fluid outlet opens the shaft 113 or the working fluid enters the hot region 110a, reducing the working fluid volume, thereby providing acceleration of the working fluid. . The fluid former may be provided in any suitable material, shape or function to achieve different design objectives. The fluid former may have an aerodynamic design.

If there is a significant temperature difference between the hot zone 110a and the cold zone 110b, the circulation of the working fluid (indicated by the flow curve 122 in FIG. 1) is established. In this circulation, the working fluid flows in a circular motion further radially outward in the thermal region 110a, enters the cold region 110b (ie, a downward spiral motion) through the space 121, and circular motion. , Flows radially inward in the cold region 110b and returns to the hot region 110a with the open shaft 113 (ie, in an upward spiral motion). As the hot working fluid moves in a circular motion towards the cold zone 110b, it results in a low pressure or pressure drop in the middle of the cold zone. The cold working fluid is drawn and can rise in the hot region in a circulating motion. The fluid flow in each region is thus similar to the motion of a hurricane or cyclone (ie, “cyclonic-like”) fluid. In the hot region, when the working fluid is heated, the updraft spirals outward toward the end and draws the working fluid strongly from the cold region. At the end, the strong downdraft pulls the working fluid into the cold zone, where it then spirals inward toward the low pressure point, where it is pulled back into the hot zone.
The flow of the working fluid has a spiral motion and a flow having a vortex. The work flow produces a continuous force and transmits the propulsive force on the turbine structure. Since the working fluid circulation is a convective vertical circulation, the swirl motion is almost horizontal. The flow of the working fluid from the cold region 110b to the heat region 110a is a rotating updraft. Similarly, the flow of the working fluid from the heat region 110a to the cold region 110b is a rotating downdraft. The driving force of the working fluid is continuously maintained during the engine cycle. Here, the hot working fluid joins the cold working fluid. The working fluid continuously heats, expands, cools and contracts in each region during each engine cycle. Therefore, a complete engine cycle and a complete working fluid path are provided within the chamber 110. During the engine cycle, the working fluid exerts a force simultaneously on all fluid guides or blades of the turbine structure. Each guide or blade of the turbine structure is simultaneously involved in the work. Therefore, fluid control structures such as nozzles and tubes commonly used in fluid drive systems are not required in the heat engine of the present invention to direct the working fluid to specific parts of the turbine to provide an impact.
As described above, the working fluid has a swirl motion, continuous thrust resulting from the heating and cooling of the working fluid and the rotational motion of the fluid guide or blade. The turbine structure rotates by the movement of the working fluid, and alternately rotates the working fluid.
In this engine design, the expansion and contraction of the working fluid results in a force applied to the turbine structure, which creates torque. In each cycle, the working fluid is an expanding hot working fluid, a vertical rotating downdraft that causes the working fluid to flow from the hot zone 110a to the cold zone 110b, the contraction of the working fluid in the cold zone 110b, and the cold zone 110b. To the heat zone 110a is accelerated by the combined force of the rotational rise causing the working fluid to flow.
Therefore, under this environment, the working fluid circulates more rapidly as the engine runs longer. The working fluid speed at the end of the first cycle becomes the working fluid speed at the beginning of the second cycle and increases throughout the second cycle. The working fluid velocity increases with kinetic energy, which is then converted into mechanical work by a heat engine. The speed of the working fluid increases during both the expansion and contraction phases of the engine cycle. The working fluid derives driving force from the rotation of the fluid guide and blades. The shape of the blade or fluid guide and the meridians help the working fluid rotate. The fluid guide is also used to regulate the temperature of various parts of the engine-i.e. reduce or increase the temperature in the hot zone, or reduce or increase the temperature in the cold zone. Can do.
Working fluid rotation and radial outward flow in the hot zone, downward movement to the cold zone, working fluid rotation and radial inner flow in the cold zone, and upward movement to the hot zone are Extend along the updraft. As the effective cylinder diameter decreases, the speed of rotation or twist increases. The cold working fluid is more effectively carried through the space in the form of a rotating updraft. High fluid velocities occur as a result of angular momentum conservation. The engine design is based on continuous heating and cooling to move the working fluid and use rotating turbine blades to rotate the working fluid (ie, maintain the driving force of the working fluid).
The heat engine of the present invention is reversible in that the cold and hot regions can be created by providing mechanical power. Along with the rotational movement of the housing 101 of the engine 100, the engine may also be moved by wind or water. Thus, the heat engine of the present invention may be used in applications such as solar power, or powered by emissions from nuclear power plants. Mechanical power may also be provided to rotate the engine to create indoor hot and cold areas. The hot zone can then be used to power another engine, and depending on the desired application, the cold zone can be used for cooling. The engine can be measured to accommodate different power requirements and can be used in locations with significant temperature changes.

A heating mesh may be provided in the thermal region 110b above the open shaft 113 to increase the surface area over which the working fluid is heated, thereby improving the heating efficiency of the working fluid. The heat may be concentrated and directed to the heating mesh in the heat zone 101a. This heating mesh can also function as a contact between an external heat source and the heat storage heater 701 of the separation structure 105. In this manner, the relatively hot working fluid in the hot zone 110a expands and flows into the cold zone 110b where it is cooled and compressed. A one-way valve may be provided in the open shaft 113 between the hot zone 110a and the cold zone 110b to prevent back flow of working fluid from the hot zone 110a to the cold zone 110b. FIG. 8, which is a cross-sectional view of the heat engine 100, shows a working fluid circulation path through the fluid guide structure 106. As shown in FIG. 8, a one-way valve 801 is provided in the open shaft 113 between the hot zone 110a and the cold zone 110b to prevent backflow of working fluid from the hot zone 110a to the cold zone 110b.
As can be seen from the foregoing, the fluid guide system of the above-described embodiment may perform multiple tasks. For example, each fluid guide is structurally attached to one or more walls of the fluid guide structure 106, the rotating structure 111, the passage between the rotating structure and the insulator layer 104, the insulator layer 104 and the isolation structure 105. there is a possibility. Each fluid guide in the central open shaft 113 may be structurally adapted to one or more walls of the internal structure. A plurality of meridians, passages or conduits for the flow of working fluid within the housing 101 (or chamber 110) are formed. These passages may be located within any part of the working fluid path for different applications. These passages may be angled with respect to the working fluid to assist in the movement of the working fluid. One advantage of having a fluid guide or blade to define a path for fluid flow between adjacent fluid guides is to reduce turbulence of the working fluid. The structure of the fluid guide affects the mechanical parameters 1 of the heat engine 100 such as, for example, the working fluid pressure and its angular velocity, the direction and angle of the working fluid flow, and the magnitude of the torque causing the rotational motion. Can be used as (1: One example of a mechanical parameter is the angular velocity of rotation.) The design of the fluid guide therefore improves the power output of the heat engine 100. Also, the fluid guide need not be attached to the rotating structure 111, the insulator layer 104, and the separating structure 105. In this example, multiple meridians, passages or conduits for working fluid flow are not formed. The resulting simplified design has a more even heat distribution and a lighter housing.
The rotating structure 111 is located below the open shaft 113 and supports the weight of the housing 101 including various elements of the heat engine 100 housed within the housing 101. The rotating structure 111 rotates on the axle 109 by receiving a combined torque transmitted from all turbine structures or fluid guide structures in the housing 101. As described above, the operating temperature difference between the hot zone 110a and the cold zone 110b may be maintained by the cooling fluid. In the illustrated embodiment of FIGS. 1, 2 and 3, the cooling fluid is provided from a fixed cooling reservoir 107. In this embodiment, the rotating structure 111 facilitates the intake of the cooling fluid. FIG. 5 shows the rotating structure 111 of FIGS. 1 and 2 in more detail. As shown in FIG. 5, a part of the rotating structure 111 is inserted into the cooling storage unit 107 through the central opening of the storage unit cover 115 and surrounds the cylindrical inner wall 502 of the cooling storage unit 107. The outer wall 501 is provided. The columnar inner wall 502 of the cooling storage 107 may extend to the upper wall 504 of the rotating structure 111. The drive shaft 109 may be attached to the upper wall 504 of the rotating structure 111. The rotating structure 111 also serves to reinforce the lower plate 101b of the housing 101 so as to be able to support the load of the housing 101 and its included elements of the heat engine 100. The drive shaft 109 is designed to support the rotating structure 111 and to transmit the rotational movement of the housing 101 to the load being driven. The rotating structure 111 includes a screw passage 505 a that opens the cooling storage unit 107. As the rotating structure 111 rotates, cooling fluid is drawn into the chamber 506 over the screw passage 505a, where the cooling fluid is provided in the helical passages 601 and 602 provided in the bottom portion of the insulator layer 104 (FIG. 3). ) To the space 507 in which the cooling fluid is distributed. Cooling fluid may also overflow into the space 507, where it is directed to a passage in the space 508 located between the housing 101 and the lower plate 101b of the disk 108 at the bottom of the cold region 110b. Both the helical passages in the insulator layer 104 and the passage space 508 under the disk 108 return cooling fluid to the cooling reservoir 107 through the outlet at the cooling fluid intake 510. Support elements such as posts, walls, or beams may be provided in the space 508 to provide support and flow fluid flow in a desired manner. The cooling fluid intake 510 may include an enclosed conduit for flowing cooling fluid through the reservoir cover 115. As the housing 101 rotates, the cooling fluid circulates to maintain the temperature of the cold region 110b without an external pump.
According to the illustrated embodiment of FIG. 5, the structure of the cooling device is therefore for dissipating heat from the rotating structure 111, the cooling reservoir 107, the reservoir cover 115, the cooling fluid intake 510 and the cooling reservoir 107. Including a radiator (not shown). The cooling storage unit 107, the storage unit cover 115, and the cooling fluid intake unit 510 are fixed and can be supported by an external structure (not shown). Where contact occurs between the housing 101 and the wall of the cooling reservoir 107, a bearing may be provided. For example, the bearing is between the lower plate 101 b of the housing 101 and the side wall of the cooling fluid intake 510, between the cylindrical outer wall 501 and the cylindrical wall 511 of the storage cover 115, the upper wall 504 of the rotating structure 111 and the cooling storage. It may be provided between the columnar inner walls 502 of the part 107 and between the columnar inner wall 502 of the cooling storage unit 107 and the wall of the recess 503 of the rotating structure 111. The bearing may also be used mechanically to support the weight of the heat engine 100 and provide stability during rotation. The bearing and reservoir cover 115 prevents cooling fluid from flowing out. Of course, external structures other than the cooling reservoir 107 may be provided to mechanically support the housing 101. In this embodiment of the invention, the cooling fluid intake 510 may be surrounded by a bearing. Alternative structures for the cooling fluid intake 510 are possible.

Insulator layer 104 may be filled with a thermally insulating material. Some of the cooling devices are structurally adapted to the insulator layer 104. FIG. 6 is a top view showing helical passages 601 and 602 for cooling fluid in the portion of insulator layer 104 that abuts cold region 110b, according to one embodiment of the present invention. (Although only two passages are shown in FIG. 6, a practical implementation may have additional passages according to the desired coolant circulation rate as will be described later). FIG. 6 shows that the openings 601a and 602a enter the passages 601 and 602 and return to the cooling fluid intake 510 through the passages in the fluid guide structure 106 or through the support structure of the cold region 110b. Each of the cooling fluids passing through the conduit is shown. To achieve effective cooling in the cold region 110b, the passage for the cooling fluid is between the disk 108 and the fluid guide structure, a dedicated conduit, a passage along or incorporated into the support structure, or a cooling passage. It may be provided in a combination of structures in region 110b. In general, from the screw passage 501, cooling fluid may flow radially toward the distal end and pass to the cooling fluid intake 510. Many alternative ways of distributing the cooling fluid throughout the cold region 110b are possible. According to one embodiment, the support structure may be provided throughout the insulator layer 104 for mechanical support to the insulator layer 104.
The cooling fluid is preferably a fluid having a specific heat capacity that is much greater than the specific heat capacity of the working fluid. In order to maintain the cold zone 110b at a suitable temperature, the heat of the working fluid flowing into the cold zone 110b must be dissipated by the cooling fluid and the housing 101. The efficiency of heat dissipation within the housing 101 is determined, for example, by the fluid guide and blade capabilities of the fluid guide structure 106 in the cold region 110b to heat away from the working fluid in contact with the housing 101. The heat of the working fluid that exceeds the heat dissipated by the housing 101 is dissipated by the cooling fluid. The angular velocity at which the cylindrical enclosure rotates determines the pressure at which the cooling fluid is drawn into the threaded passage 505a of the rotating structure 111 and thus determines the volume of cooling fluid that flows into the cold region 110b. At higher energy inputs, the cylindrical enclosure rotates at a higher angular velocity, thereby drawing a larger volume of cooling fluid per unit time and thus maintaining the heat engine 100 within the desired operating temperature range. Therefore, a larger cooling effect occurs. The length and distribution of the passage ambient cold region 110b depends on the volume of cooling fluid required per unit time and the ability of the cooling reservoir 107 to transfer the heat of the cooling fluid to the surrounding environment. When the passage is long, or when the volume of cooling fluid flowing through the passage per unit time is low, the temperature difference between the cooling fluid in the cooling reservoir 107 and the returning cooling fluid becomes larger. Conversely, when the length of the passage is short or when the volume of cooling fluid flowing through the passage per unit time is high, the temperature difference between the cooling fluid in the cooling reservoir 107 and the returning cooling fluid is smaller. . Smaller temperature differences are preferred. Conventional radiators may be provided on the outer wall of the cooling store 107 to dissipate excess heat.
An optional heat storage heater 701 may be provided in the separation structure 105. Such a regenerative heater minimizes power output fluctuations even though the amount of heat provided by the heat source may fluctuate during the engine cycle. The heat storage heater 701 may be used to cope with changes in power demand. That is, the heat storage heater 701 may replenish energy production that is insufficient during periods of high demand and may store power when production exceeds demand. The regenerative heater 701 can also act as another heat source to retain heat and heat on the working fluid after the primary heat source is no longer available or no longer provides sufficient thermal energy. it can. The heat storage heater 701 may be connected to a main heat source in order to increase the heating volume or heating efficiency of the heat region. The heat storage medium for the heat storage heater 701 may be a phase change material or a material that converts stored energy to a higher temperature by a separation or recombination reaction. Materials that convert stored energy to lower temperatures by separation or recombination reactions may be used in the insulator layer 104 or in the cold region 110b for cooling purposes. In one embodiment, the phase change material is used to increase the thermal energy density of the regenerative heater 701 and improve power performance at a constant temperature.

FIG. 7 shows a cross-sectional view of the heat storage heater 701 according to one embodiment of the present invention. As shown in FIG. 7, the regenerative heater 701 includes a cavity that is filled with a fluid of high specific heat capacity or thermal accumulation density, and a metal plate 702 that is supported by springs 703a and 703b. The fluid in the regenerative heater 701 can be pressurized and preferably remains liquid over the entire range of operating temperatures of the heat engine 100. (Although only two springs are shown in FIG. 7, many springs may be used to support the metal plate 702.) A metal support structure (not shown) is used for the heat storage heater 701. May be provided throughout the regenerative heater 701 to support the top and bottom walls of the heat sink and to perform heating from the heat zone 110a. Initially, the fluid in the heat storage heater 701 is cold and the metal plate 702 is not in contact with the bottom portion of the heat zone 110a. When the heat engine 100 operates, the temperature of the fluid in the heat storage heater 701 increases. As a result, the springs 703a and 703b allow the metal plate 702 to contact the floor of the hot zone 110a with a larger surface area for heat transfer between the fluid of the thermal zone 110a and the regenerative heater 701. Inflate. According to one embodiment of the present invention, a solid state material or a mixture of different types of materials can be used in the regenerative heater 701. A heated mesh may also be used to facilitate heat transfer. The fluid guide may be used to provide an external heat source passage to increase heat transfer to the heat zone 110a and the heat storage heater 701. In such a design, a set of heat pipes or heated fluid may be guided with a fluid guide. The working fluid of the heat pipe may enter the first fluid guide from the external housing 101, pass through the heat storage heater 701, and return to the external housing through a passage in the second fluid guide in the heat region 110a. Accordingly, the thermal region 110a may be surrounded by a heating element to provide thermal efficiency.
The heat source may contact the housing 101 in the central or annular region depending on the desired application. If the location of the heat zone 110a and the cold zone 110b are reversed, the structure of the cooling device and the heat source may form different operating structures. This may provide an advantage in circulating the working fluid and maintaining a greater temperature difference between the hot and cold regions.
The above detailed description is provided to illustrate specific embodiments of the present invention and is not intended to be limiting. Many modifications and variations within the scope of the present invention are possible. The invention is described in the following claims.

FIG. 4 shows a cross-sectional view of a heat engine 100 having a cooling storage 107 according to one embodiment of the present invention. 1 shows a heat engine 100 having a cooling storage 107 in an exploded side view of an equal volume. 1 shows a heat engine 100 in an “enlarged” perspective view. It is a top view of the heat | fever area | region 110a under the top plate 101a. The rotating structure 111 of FIGS. 1 and 2 is shown in more detail. It is a top view which shows the helical channel | paths 601 and 602 in the part of the insulator layer 104 which contact | abuts the cold area | region 110b. 1 illustrates a cross section of a heat storage heater 701 according to one embodiment of the present invention. 2 is a cross-sectional view showing a working fluid circulation path inside the housing 101. FIG. To facilitate cross-referencing in the figures and to simplify the following detailed description, like elements in the figures are assigned like reference numerals.

Claims (27)

During operation of the heat engine, the first region and the second region have a temperature difference and are immersed in a working fluid that circulates between the first region and the second region. And a housing including a chamber having a second region; and a first portion of the turbine is located in the chamber, and the motion of the working fluid over the plurality of surfaces rotationally moves the turbine. And a heat engine comprising a turbine having a plurality of surfaces in the fluid path of the chamber. The heat engine according to claim 1, wherein the first portion of the turbine is located between the first region and the second region. The heat engine of claim 1, wherein the first portion of the turbine is structurally adapted to the chamber and drives the housing to move. The heat engine according to claim 1, wherein the first portion of the turbine forms a plurality of passages defined by a structure attached to the housing for circulating the working fluid. The heat engine of claim 1, wherein the turbine comprises a second set of blades providing access to a heat source or cooling source outside the chamber. The heat engine according to claim 1, further comprising a cooling device including a rotating portion having a screw passage that causes the rotating motion of the turbine to draw cooling fluid to the engine in the rotating structure. The heat engine of claim 1, comprising a heat storage structure within the chamber that provides a second thermal energy source to the working fluid during operation of the engine. A method for providing a heat engine, wherein during operation of the heat engine, the first region and the second region have a temperature difference, and the first region and the second region Providing a housing including a chamber having a first region and a second region immersed in a working fluid circulated between; and a first portion of the turbine is located in the chamber and is over the plurality of surfaces A method of providing a heat engine, wherein the movement of the working fluid is driven to rotate the turbine and has a plurality of surfaces in the fluid path of the chamber. 9. The method of claim 8, wherein the provision of the first portion of the turbine is located between the first region and the second region. 9. The method of claim 8, wherein the provision of the first portion of the turbine is structurally adapted to the chamber and drives the housing to move. 9. The method of claim 8, wherein the provision of the first portion of the turbine forms a plurality of passages defined by structures attached to the housing for circulating the working fluid. 9. The method of claim 8, wherein the turbine provision comprises a second set of blades providing access to a heat or cooling source outside the chamber. 9. The method of claim 8, further comprising a cooling device wherein the rotational motion of the turbine includes a rotating portion having a threaded passage that causes the rotating structure to draw cooling fluid to the engine. 9. The method of claim 8, comprising providing a heat storage structure that provides heat to the working fluid in the chamber during operation of the engine. A housing having a first region and a second region that include a chamber containing a working fluid and that is maintained with a temperature difference; a first thermal structure within the chamber that transfers heat; and A heat engine comprising a second thermal structure adapted to maintain the temperature difference. 16. The heat engine according to claim 15, wherein the first thermal structure performs heat transfer between the first thermal storage structure and an external heat source through a conduction path. The heat engine according to claim 15, wherein the first thermal structure is a heat storage device. A method for providing a heat engine, comprising: providing a housing that includes a chamber containing a working fluid and having a first region and a second region that are maintained with a temperature difference; Providing a first thermal structure within the chamber; a method comprising providing a second thermal structure adapted to maintain said temperature difference. 19. A heat engine according to claim 18, wherein the provision of the first thermal structure performs heat transfer between the first thermal storage structure and an external heat source through a conduction path. A housing enclosing a chamber having a first region and a second region having a temperature difference immersed in a working fluid circulating undisturbed between the first region and the second region; Is located in the chamber for flowing the working fluid in a cyclone-like path, the region having a surface in contact with the working fluid and attached to the portion of the housing exposed to the chamber A heat engine consisting of multiple structures. 21. A heat engine according to claim 20, wherein the draft increases the speed of the working fluid from the first region to the second region. 21. A heat engine according to claim 20, wherein the driving force of the working fluid returning to the first region in one cycle increases the driving force of the working fluid in the next cycle. A method for providing a heat engine, the first region and the second region having a temperature difference immersed in a working fluid circulating uninterrupted between the first region and the second region Providing a housing that encloses the chamber; and some of the structures are located in the chamber to cause the working fluid to flow in a cyclone-like path, the region having a surface in contact with the working fluid. And providing a plurality of structures attached to the portion of the housing exposed to the chamber. 24. The method of claim 23, wherein a draft is provided to increase the speed of the working fluid from the first region to the second region. 24. The method of claim 23, wherein providing the driving force of the working fluid back to the first region in one cycle increases the driving force of the working fluid in the next cycle. A rotary heat engine having a fluid-based heat exchanger, wherein the fluid reservoir; and the structure is such that the rotational motion of the rotary engine determines the velocity of the fluid flow from the fluid reservoir. A heat engine structurally adapted to the housing of the rotary engine and comprising a screw passage for fluid flow. A method for providing a rotary heat engine having a fluid-based heat exchanger, wherein a fluid reservoir is provided; and the structure is such that the rotational motion of the rotary engine causes fluid flow from the fluid reservoir. A method comprising: providing a structure that is structurally adapted to the housing of the rotary engine to determine the speed of and includes a threaded passage for fluid flow.

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