JP2008133824A - Stirling system and freezer system using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a Stirling system materializing great simplification and improvement of durability by storing a high temperature expansion mechanism part and a low temperature compression mechanism part, and a drive shaft common for both mechanism parts in a hermetic vessel. <P>SOLUTION: The Stirling system 10 has the high temperature expansion mechanism part 24 and the low temperature compression mechanism part 44, and the drive shaft 14 common for the both mechanism parts for constructing Stirling cycle stored in the hermetic vessel 12. An inside of the hermetic vessel 12 is partitioned to the high temperature expansion mechanism part 24 side and the low temperature compression mechanism part 44 side by a bulkhead 16. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a high-temperature expansion mechanism for configuring a Stirling cycle in a closed container, a Stirling system that houses a low-temperature compression mechanism, and a refrigerator system using the Stirling system.

  Conventionally, a Stirling engine (Stirling cycle) that is an external combustion engine is provided with a displacer piston that reciprocates in a cylinder as an example. The high-pressure working gas sealed in the cylinder is reciprocated between a heating unit heated by a heating source such as a combustion gas and a cooling unit cooled by a cooling heat source used in cooling water. Accordingly, there has been proposed a configuration in which a pressure difference of the working gas is generated in the cylinder, and this pressure difference is extracted as power through a power piston interlocked with the displacer piston at a phase of 90 degrees (Patent Literature). 1).

While such a piston type (reciprocating) type Stirling system is mainstream, simplification of a Stirling system equipped with a rotary type mechanism (rotary type) was studied. As an example of this simplification, the application of the Wankel type mechanism was studied academically.
JP 2006-275018 A

  However, unlike the current mainstream internal combustion engine, the Stirling system has excellent characteristics such as high efficiency, diversity of fuels and heat sources, quietness, and cleanliness of exhaust. The whole mechanism tended to be complicated and heavy due to the transfer of heat, internal heat exchange, and the use of high-pressure working gas. In addition, there is a lot of room for improvement in durability and responsiveness, the cost is expensive, and the market is not competitive. For this reason, simplification of the Stirling system and cost reduction have been desired.

  The drive part of the latter Wankel type mechanism is simplified from the crank mechanism to the rotation mechanism, but the characteristics of the essential fluid operation mechanism such as the operation volume are not compatible, the structure is not integral, Since the system is complicated, it has not been put into practical use.

  The present invention has been made to solve the problems of the related art, and includes a high temperature expansion mechanism section, a low temperature compression mechanism section, and a drive shaft common to both mechanism sections in a sealed container. It is an object of the present invention to provide a Stirling system and a refrigerator system using the same that are simplified and improved in durability.

  That is, the Stirling system of the present invention accommodates a high-temperature expansion mechanism part for constituting a Stirling cycle, a low-temperature compression mechanism part, and a drive shaft common to both mechanism parts in the sealed container, and the inside of the sealed container. Is divided into a high-temperature expansion mechanism part side and a low-temperature compression mechanism part side by a partition wall.

  Further, the Stirling system of the invention of the second aspect is characterized in that, in the above, the control mechanism for controlling the performance characteristics of the Stirling cycle and the generator or the electric motor are directly connected to the drive shaft on the low-temperature compression mechanism section side in the sealed container. It is characterized by that.

  A Stirling system according to a third aspect of the present invention is the Stirling system according to the first or second aspect, wherein the heater, the cooler, and the regenerative heat exchanger for constituting the Stirling cycle are placed in a sealed container or a sealed container. It is characterized by being integrated with the sealed container outside.

  According to a fourth aspect of the present invention, there is provided a Stirling system according to any one of the first to third aspects, wherein the lubricant pressure guide mechanism for lubricating the sliding portion in the sealed container and the outside of the sealed container are discharged. And a return mechanism for separating the lubricant from the working gas and returning it to the sealed container.

  A refrigerator system according to a fifth aspect of the present invention is characterized in that, in any of the first to fourth aspects, the electric motor that drives the drive shaft is provided, and the Stirling cycle functions in the reverse cycle.

  As described above in detail, according to the present invention, the high-temperature expansion mechanism part for constituting the Stirling system, the low-temperature compression mechanism part, and the drive shaft common to both mechanism parts are housed in the sealed container, and the sealed Since the inside of the container is divided into a high-temperature expansion mechanism part side and a low-temperature compression mechanism part side by a partition wall, for example, as in claim 2, a control mechanism that controls performance characteristics of a Stirling cycle, a generator, or an electric motor Can be directly connected to the drive shaft on the low temperature compression mechanism portion side in the hermetic container, the responsiveness of power transmission can be greatly improved. Further, since the high-temperature expansion mechanism and the low-temperature compression mechanism are housed in the sealed container, the control mechanism, the generator, the electric motor, and the like are not directly impacted from the outside, and wind and rain can be avoided. Thereby, since corrosion of those control mechanisms, generators, or electric motors can be reliably prevented by scratches or wind and rain, the durability of the Stirling system can be greatly improved.

  In particular, since the high-temperature expansion mechanism and the low-temperature compression mechanism are housed in a sealed container, the Stirling system can be greatly simplified and durable. Thereby, since the Stirling system can be made compact, for example, it becomes possible to achieve a significant weight reduction compared to the conventional Stirling system. Therefore, productivity can be greatly improved and costs can be significantly reduced, and the market competitiveness of the Stirling system can be greatly improved as a whole.

  According to the invention of claim 3, in claim 1 or claim 2, the heater, cooler, and regenerative heat exchanger for constituting the Stirling cycle are installed in the sealed container or outside the sealed container. In this case, the Stirling system can be easily transported anywhere and can be easily installed anywhere. Thereby, the transportability and installation property of the Stirling system can be greatly improved, and the versatility of the Stirling system can be greatly improved.

  According to a fourth aspect of the present invention, in any one of the first to third aspects, the lubricant pumping mechanism for lubricating the sliding portion in the sealed container and the operation discharged to the outside of the sealed container. Since the lubricant is separated from the gas and provided with a return mechanism for returning the lubricant into the sealed container, the lubricant can be smoothly supplied to each sliding portion of the Stirling cycle. In addition, since a return mechanism for separating the lubricant from the working gas and returning it to the sealed container is provided, for example, the lubricant is mixed with the working gas and excessively flows into the low-temperature compression mechanism. be able to. As a result, it is possible to smoothly operate the Stirling cycle, and it is possible to reliably prevent a decrease in output and performance deterioration of the Stirling cycle.

  According to a fifth aspect of the present invention, since the electric motor for driving the drive shaft is provided in the first to fourth aspects and the Stirling cycle functions in the reverse cycle, the operation of the low temperature compression mechanism and the high temperature expansion mechanism The refrigerator system can be constructed by utilizing the compression / expansion of the working gas accompanying the operation. In addition, if a natural working medium such as hydrogen or helium is used as the working gas, the working gas can be applied to the refrigerator field having excellent environmental performance. Therefore, both the generator and the refrigerator can be used, and the convenience of the refrigerator system can be greatly improved.

  The main feature of the present invention is to reduce the weight and improve the productivity in order to improve the lack of energy efficiency and lack of market competitiveness. The purpose of improving energy efficiency and improving productivity has been realized with a simple structure in which the high-temperature expansion mechanism and the low-temperature compression mechanism are housed in a sealed container.

  Next, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal side view (schematic diagram) of a Stirling system 10 showing an embodiment of the present invention, and FIG. 2 is a conceptual diagram of the Stirling system 10 showing an embodiment of the present invention. As shown in FIG. 1, the Stirling system 10 of the present invention includes a cylindrical sealed container 12 made of a steel plate, and a drive mechanism section (a high temperature expansion mechanism section 24 and a low temperature compression mechanism section) in the inner space of the sealed container 12. 44) is stored.

  The high temperature expansion mechanism part 24 is disposed on one side (upper side in the figure) of the sealed container 12, and the low temperature compression mechanism part 44 is disposed on the other side (lower side in the figure) of the sealed container 12. Both mechanism parts 24 and 44 are fixed to a common drive shaft 14 provided in the longitudinal direction of the hermetic container 12, and a pressure feeding mechanism 15 is provided on the other side (lower side in the figure) of the drive shaft 14. It has been. The pressure feeding mechanism 15 is configured to supply a lubricating oil 70 (corresponding to the lubricant of the present invention) stored on the other side of the sealed container 12 from a lubricating oil 70 supply passage provided in the sealed container 12 in advance to a first rotor described later. 28 (including the first vane 30), the second rotor 48 (including the second vane 50), or the sliding portion on which the low-temperature compression mechanism 44 slides is lubricated and lubricated. The pumping mechanism 15 pumps the lubricating oil 70 into the first cylinder 26 and the second cylinder 46 by centrifugal force generated by, for example, a spiral groove carved in a spiral shape or a propeller-shaped member rotating. is there. In addition, since the technique of pumping the lubricating oil 70 by the pumping mechanism 15 is a well-known technique from the past, detailed description is omitted.

  A partition wall 16 is provided between the high temperature expansion mechanism unit 24 and the low temperature compression mechanism unit 44, and the sealed container 12 is partitioned by the partition wall 16 into a high temperature expansion mechanism unit 24 side and a low temperature compression mechanism unit 44 side. ing. That is, the high-temperature expansion mechanism 24 is provided on one side (upper side in the drawing) of the partition wall 16 and the low-temperature compression mechanism 44 is provided on the other side (lower side in the drawing). The partition wall 16 is composed of a highly heat insulating heat insulating wall using a porous material, or a high heat insulating heat insulating wall having a vacuum space formed therein, and a high temperature expansion mechanism portion 24 and a low temperature compression mechanism portion. Insulation between the two and 44 is suitably insulated. A control mechanism 18 is provided between the low temperature compression mechanism unit 44 and the partition wall 16 with a predetermined distance from the partition wall 16, and a sealed container is provided between the low temperature compression mechanism unit 44 and the pressure feeding mechanism 15. A generator 20 is provided that is in close contact with the inner surface of the twelve inner surface and at a predetermined distance from the control mechanism 18. There is a predetermined space around the control mechanism 18, and a second space 44A is formed in this space. This control mechanism 18 suitably controls the performance characteristics of the Stirling system 10, and suitably adjusts the phase angle of the compression top dead center of both the high temperature expansion mechanism 24 and the low temperature compression mechanism 44. is there.

  The generator 20 can also be used as an electric motor (motor), and is a so-called generator that can reversibly use power generation and a motor. The generator 20 generates power and outputs electric power when the Stirling system 10 is operated (when the drive shaft 14 is rotated). Further, when the Stirling system 10 is started, the generator 20 operates as an electric motor by energizing a power source provided in advance, and automatically switches to the generator 20 when sufficient shaft output is generated. It is configured. In the airtight container 12, the high temperature expansion mechanism 24, the low temperature compression mechanism 44, the control mechanism 18, the generator 20 and the lubricating oil 70 are enclosed. Thus, the Stirling system 10 is configured to be simple and have an optimum shape structure, and to obtain practicality and convenience such as performance, volume, weight, pressure tightness and low cost. The control mechanism 18 will be described in detail later.

  Here, the mechanism part which made the rolling piston type an example is described below. The high-temperature expansion mechanism unit 24 includes a first cylinder 26 whose outer peripheral surface is provided in close contact with the inner surface of the sealed container 12, and a first rotor 28 that is rotatably provided inside the first cylinder 26. ing. The high-temperature expansion mechanism section 24 has a predetermined volume space on both the partition wall 16 and the first cylinder 26, and the partition wall 16 and the opposed surface side (upper side in FIG. 1) of the first cylinder 26, and the first space in this space. 24A is formed. The first cylinder 26 is provided with a first vane 30 whose tip always contacts the first rotor 28. The inside of the first cylinder 26 is divided into a high temperature discharge side and a high temperature suction side by the first vane 30. It has been. That is, in the first cylinder 26, the first vane 30 partitions the high temperature side discharge port 34 side of the first vane 30 into the high temperature discharge side and the high temperature side suction port 32 side to the high temperature suction side (FIG. 2).

  The center of the first rotor 28 is fixed to a crankshaft 14A (solid line in FIG. 2) of the drive shaft 14 (dotted line in FIG. 2), and the drive shaft 14 rolls in the first cylinder 26 as the crank rotates. . That is, with the center of the first cylinder 26 as the rotation axis, the first rotor 28 rolls in the first cylinder 26 around the rotation axis. Further, the first cylinder 26 is provided with a second heater 38A (shown in FIG. 2) for supporting isothermal heating of the working gas sucked into the high temperature suction side.

  The low-temperature compression mechanism 44 includes a second cylinder 46 whose outer peripheral surface is provided in close contact with the inner surface of the hermetic container 12, and a second rotor 48 that is rotatably provided inside the second cylinder 46. It is configured. The second cylinder 46 is provided with a second vane 50 whose tip always contacts the second rotor 48, and the second cylinder 46 is partitioned by the second vane 50. That is, in the second cylinder 46, the second vane 50 partitions the low-temperature side discharge port 54 side of the second vane 50 into the low-temperature discharge side and the low-temperature side suction port 52 side into the low-temperature suction side (FIG. 2). The Stirling system 10 is configured by a rotary mechanism (rolling piston type) including a first rotor 28 and a second rotor 48 provided in the high temperature expansion mechanism 24 and the low temperature compression mechanism 44.

  The second rotor 48 is fixed to the crankshaft 14A of the drive shaft 14, and the drive shaft 14 rolls in the second cylinder 46 as the crank rotates. That is, with the center of the second cylinder 46 as the rotation axis, the second rotor 48 rolls in the second cylinder 46 around the rotation axis. Further, the second cylinder 46 is provided with a second cooler 58A (shown in FIG. 2) for supporting isothermal cooling of the working gas sucked from the outside of the second cylinder 46 to the low temperature suction side.

  A hollow connection pipe 36 is connected to the high-temperature side discharge port 34 of the first cylinder 26 constituting the high-temperature expansion mechanism portion 24, and the connection pipe 36 includes the regenerative heat exchanger 60, the return mechanism 62, and the first cooling. 1 is connected to the low-temperature side suction port 52 of the second cylinder 46 constituting the low-temperature compression mechanism 44 via a container 58 (dotted line in FIG. 1). A hollow connection pipe 56 is connected to the low temperature side discharge port 54 of the second cylinder 46. The connection pipe 56 is connected to the high temperature side suction port 32 of the first cylinder 26 constituting the high temperature expansion mechanism unit 24 via the return mechanism 62, the regenerative heat exchanger 60, and the first heater 38. (Figure 1 solid line).

  The regenerative heat exchanger 60 has a function of storing heat and precooling when the working gas flows in and passes from the high temperature expansion mechanism section 24 side at a high temperature and preheats it by flowing when it flows from the low temperature compression mechanism section 44 side. I need. The regenerative heat exchanger 60 is, for example, a double pipe or a plate-type sensible heat exchanger so that heat exchange is easy without mixing working gas flows (opposite flows) passing through the inside in opposite directions. It consists of a structure. In this case, the regenerative heat exchanger 60 performs only sensible heat exchange of the working gas and hardly stores heat or releases heat. Such a regenerative heat exchanger 60 does not require a complicated internal packing such as a mesh, and has a relatively small capacity.

  The regenerative heat exchanger 60 and the return mechanism 62 are important elements constituting the present invention, and are provided outside the sealed container 12 in principle. That is, the Stirling system 10 passes through the first cylinder 26, the regenerative heat exchanger 60, the return mechanism 62, the first cooler 58, the second cylinder 46, the return mechanism 62, the regenerative heat exchanger 60, and the first heater 38. The first cylinder 26 is sequentially piped to form an annular working gas circulation circuit (hereinafter referred to as a Stirling cycle). In FIG. 2, the regenerative heat exchanger 60, the return mechanism 62, the first heater 38, the second heater 38A, the first cooler 58, and the second cooler 58A provided outside the sealed container 12 are indicated by dotted lines. It is shown.

  In the Stirling cycle, a predetermined amount of high-pressure working gas such as hydrogen gas, helium gas, or nitrogen gas is sealed as the working gas, and a predetermined amount of silicon-based oil is sealed in the Stirling cycle as the lubricating oil 70. Have been used. Specifications such as the pressure and internal volume of the working gas sealed in the Stirling cycle, the amount of eccentricity of the first rotor 28 and the second rotor 48, the difference in mutual phase angle, the amount of inflow and exhaust heat, the temperature, etc. Is selected and configured.

  The return mechanism 62 separates the lubricating oil 70 contained in the working gas, removes the precipitate, and returns it to the lower part of the sealed container 12. For example, the return mechanism 62 operates by adsorbing the gear pump and the lubricating oil 70. It is composed of a filter having a function of separating lubricating oil 70 that separates from gas. In other words, the return mechanism 62 returns the lubricating oil 70 separated from the working gas by the return mechanism 62 from the connection pipe 63 (one-dot chain line in FIG. 1) to the lower part of the sealed container 12 (lower side in FIG. 1).

  Here, in the conventional reciprocating Stirling cycle, the working gas containing lubricating oil reciprocates between the high temperature high temperature expansion mechanism (high temperature portion) and the low temperature low temperature compression mechanism (low temperature portion). Generally, it is formed by laminating fine mesh-like metals in multiple stages. Thus, the regenerative heat exchanger is configured such that the working gas touches a wide contact area, and a sufficient heat storage and heat dissipation effect can be obtained with the minimum fluid resistance. However, when the lubricating oil changes in quality when heated in the high temperature part and precipitates are generated, the regenerative heat exchanger that passes on the way to the low temperature part may cause clogging. For this reason, lubrication and sealing within the Stirling cycle could not be sufficiently performed using the lubricating oil.

  Therefore, in the present invention, a pressure feeding mechanism 15 that pressure-feeds the lubricating oil 70 stored in the lower part of the sealed container 12 to each sliding portion is provided, and a filter that separates the working gas and the lubricating oil 70 and removes precipitates is provided. The return mechanism 62 is provided. Thus, the precipitate generated in the lubricating oil 70 is removed, and lubrication and sealing in the Stirling cycle can be suitably performed. Then, the stored lubricating oil 70 is pumped again to each sliding portion by the pumping mechanism 15 to cool the sliding portion and prevent wear. When it is desired to suppress the use of the lubricating oil 70 in the high-temperature expansion mechanism section 24 due to inconvenience such as heat resistance, it is separated from the working gas circulating in the Stirling cycle and used only by the low-temperature compression mechanism section 44. It is also possible to improve the return mechanism 62. In addition, about the technique which pumps the lubricating oil 70 with a gear pump, since it is a conventionally well-known technique, detailed description is abbreviate | omitted.

  Next, the operation of the Stirling system 10 will be described. In the high temperature expansion mechanism 24, the working gas is heated by the first heater 38 and becomes high temperature, and the low temperature compression mechanism 44 is cooled by the second cooler 58A and becomes low temperature. For this reason, it is thermodynamically advantageous to stand and use the sealed container 12 so that the high temperature expansion mechanism 24 is positioned above and the low temperature compression mechanism 44 positioned below. I will explain in the state. In addition, the control mechanism 18 and the generator 20 are provided in the same space as the low-temperature compression mechanism unit 44 side in order to prevent the control mechanism 18 and the generator 20 from being heated. Further, as a heating source of the first heater 38 (including the second heater 38A), for example, fossil fuel, biomass fuel, exhaust heat of a micro gas turbine or a fuel cell, factory exhaust heat, solar heat, or the like is used. As a cooling source for the first cooler 58 (including the second cooler 58A), for example, groundwater, river water, pond water, seawater, air (room temperature outside air), or the like is used. That is, the first heater 38 and the second heater 38A are heated by the heating source, and the first cylinder 26 is heated isothermally by the second heater 38A. Further, the first cooler 58 and the second cooler 58A are cooled by the cooling source, and the second cylinder 46 is isothermally cooled by the second cooler 58A.

  The rotors 28 and 48 that roll in contact with the inner surfaces of the cylinders 26 and 46 are set so that the phase angle difference between the rotors 28 and 48 is about 180 degrees with the vanes 30 and 50 as base points. In this case, the first cylinder 26 and the second cylinder 46 are arranged so that the eccentric directions are in opposite phases so that the vibrations cancel each other and become low vibrations. The phase angle difference of 180 degrees is when the discharge of the working gas from the high-temperature expansion mechanism unit 24 is started and when the suction of the working gas is started by the low-temperature compression mechanism unit 44. The first rotor 28 and the second rotor 48 are connected by the drive shaft 14, and the high temperature side suction port 32, the low temperature side suction port 52, the high temperature side discharge port 34, and the low temperature side discharge port 54 of both cylinders 26, 46 are Each is provided on the same side.

  Then, the working gas flowing into the first cylinder 26 (on the high temperature suction side) is heated by the first heater 38. Since the first cylinder 26 is heated by the second heater 38 </ b> A, the working gas expands while maintaining a substantially constant temperature, and the first cylinder 26 has a predetermined high pressure. With this high-pressure working gas, the first rotor 28 rolls clockwise along the inner surface of the first cylinder 26 (arrow in FIG. 2), sucks the working gas from the connection pipe 56 to the high-temperature suction side, and lubricates the lubricating oil. 70 is pressure-fed by the pressure-feed mechanism 15 to each sliding part, the first cylinder 26 and the second cylinder 46. In this way, the high-temperature expansion mechanism unit 24 obtains a driving force from the heating source and rotationally drives the driving shaft 14.

  By the rolling of the first rotor 28, the working gas in the first cylinder 26 (high temperature discharge side) is discharged from the high temperature side discharge port 34 into the connection pipe 36. The working gas discharged into the connection pipe 36 proceeds in the arrow direction (right arrow in FIG. 2) and flows into the regenerative heat exchanger 60. The working gas flowing into the regenerative heat exchanger 60 is cooled (pre-cooled) by exchanging heat with the working gas cooled in the second cylinder 46. The working gas leaving the regenerative heat exchanger 60 flows into the return mechanism 62 where the working gas and the lubricating oil 70 are separated. The working gas from which the lubricating oil 70 has been separated flows into the first cooler 58 and is cooled, and then flows into the second cylinder 46 (low temperature suction side) from the low temperature side suction port 52. The lubricating oil 70 pumped by the pumping mechanism 15 circulates in the high-temperature expansion mechanism section 24 together with the working gas to perform sufficient lubrication and sealing in the Stirling cycle.

  At this time, the working gas in the second cylinder 46 (low temperature discharge side) is cooled by the second cooler 58A. By this cooling, the working gas is compressed while being substantially isothermal, whereby the volume of the working gas is compressed in the second cylinder 46. The second rotor 48 rolls clockwise along the inner surface of the second cylinder 46 (arrow in FIG. 2), and sucks the working gas from the connection pipe 36 to the low temperature suction side. The working gas in the second cylinder 46 (low temperature discharge side) is discharged from the low temperature side discharge port 54 into the connection pipe 56. The working gas discharged into the connection pipe 56 proceeds in the direction of the arrow (left arrow in FIG. 2), and the working gas and the lubricating oil 70 are separated by the return mechanism 62. The working gas from which the lubricating oil 70 has been separated flows into the regenerative heat exchanger 60 and is heated (preheated) by exchanging heat with the working gas heated in the first cylinder 26.

  The heated working gas is heated by the first heater 38 and then returned from the high temperature side suction port 32 to the inside of the first cylinder 26 (high temperature suction side). In this way, the high temperature expansion mechanism unit 24 obtains a driving force and drives the drive shaft 14 to rotate. Since the entire Stirling system 10 is based on the working gas in the Stirling cycle 10 as a whole, each part such as the regenerative heat exchanger 60, the first heater 38, the first cooler 58 and the like is simply assigned a function. Simplification and continuous operation. The flow of the working gas in the regenerative heat exchanger 60 is not a reciprocating flow, but the high temperature part (high temperature expansion mechanism part 24) and the low temperature part (low temperature compression mechanism part 44) are separated into the connection pipe 36 and the connection pipe 56. And it is comprised so that it may become a unidirectional flow which can mutually heat-exchange.

  That is, the Stirling system 10 generates a driving force by the high-temperature expansion mechanism unit 24 to drive the driving shaft 14, and generates power by the generator 20 fixed to the driving shaft 14. The Stirling system 10 compresses or expands in a state where both the high-temperature expansion mechanism unit 24 and the low-temperature compression mechanism unit 44 are nearly isothermal, and generates an overall output. The heat for driving the Stirling system 10 is supplied to the first heater 38 and the second heater 38A from an external heat source, which is transferred to the working gas and converted into power. Heat is radiated from the second cooler 58A to the outside. As a result, the thermodynamic stage is continuously realized, the Stirling cycle is completed, and the engine operates.

  Here, since the Stirling cycle, which is an external combustion engine, obtains heat from the outside, the response reaction of power transmission is inevitably delayed due to heat conduction. This Stirling cycle can demonstrate its maximum capacity. The ideal phase angle difference is 180 degrees and the phase angle difference does not move at 0 degrees, but the thermodynamic capacity is not necessarily 100% at a phase angle of 180 degrees. . Therefore, the control mechanism 18 is configured so that the phase angle can be adjusted so that the maximum output is obtained from the high temperature expansion mechanism unit 24 and the low temperature compression mechanism unit 44, and the phase angle is adjusted during the operation of the Stirling cycle. Thus, the driving force can be varied.

  That is, the control mechanism 18 controls the performance characteristics by changing the thermodynamic characteristics of the Stirling cycle, so that the rotational position between the first rotor 28 of the high temperature expansion mechanism section 24 and the second rotor 48 of the low temperature compression mechanism section 44 is changed. It has a function of appropriately changing the phase difference. The structure of the control mechanism 18 is such that the phase angle is adjusted by meshing the gear provided on the drive shaft 14 on the high temperature expansion mechanism section 24 side with the gear provided on the opposing low temperature compression mechanism section 44 side. In addition, an electromagnetic clutch or the like that adjusts the phase angle can be used. The rotors 28 and 48 are set so that the phase angle difference between the two vanes 30 and 50 is about 180 degrees with the vane 30 and 50 as described above. However, the control mechanism 18 can freely adjust the phase angle difference. Change to show the maximum capacity of the Stirling cycle.

  In addition, the Stirling cycle reduces the load in a short time (for example, within about 1 minute) and reduces the capacity. Even if the input (heating and cooling) is reduced by half, the effect of the remaining heat and the inertia immediately I can't lose my ability. Therefore, the ability can be reduced by shifting the phase angle difference by a predetermined angle by the control mechanism 18. From this, since the output (power) of the generator 20 can be changed due to the load fluctuation, it is possible to prevent the inconvenience that the power generation amount exceeds when the load is small. Since the technology for engaging the control mechanism 18 between gears and shifting the phase angle of the rotors 28 and 48 using an electromagnetic clutch or the like is a well-known technology, detailed description thereof is omitted.

  In addition, since the working gas flows in only one direction in the Stirling cycle, clogging of the regenerative heat exchanger 60 is less likely to occur, so that a Stirling cycle using the lubricating oil 70 can be safely constructed. Further, by circulating the lubricating oil 70 in the Stirling cycle, the sealing performance and the lubricity can be remarkably improved as compared with the prior art. As a result, the first heater 38, the first cooler 58, and the regenerative heat exchanger 60, which form the basis of the present invention, are integrated with the sealed container 12 in the sealed container 12 or outside the sealed container 12. Can be realized, and significant simplification can be achieved. Therefore, the performance characteristics of the Stirling system 10 can be greatly improved, and at the same time, the manufacturing accuracy, materials, surface treatment, and the like of the high temperature expansion mechanism 24 and the low temperature compression mechanism 44 can be greatly simplified. Can do.

  Further, since the control mechanism 18 and the generator 20 are accommodated on the low-temperature compression mechanism 44 side of the sealed container 12, a mechanism such as taking out the output shaft (drive shaft 14) to the outside of the sealed container 12 becomes unnecessary. Also, leakage of working gas can be prevented. Moreover, there is no concern that it will be damaged by overheating. Moreover, since the generator 20 is provided in the second space 44A, when the generator 20 is used as an electric motor, the amount of heat generated is cooled and overheating can be avoided. As a result, if the control mechanism 18, the generator 20, and the like are provided in close contact with the sealed container 12, the sealed container 12 can be reduced in size, and the transportability and installation properties can be greatly improved.

  In the Stirling cycle, the high temperature expansion mechanism 24 and the low temperature compression mechanism 44 are always heated and cooled, or substantially isothermally expanded and substantially isothermally compressed, between the first cylinder 26 and the second cylinder 46. Because the thermodynamic cycles of approximately equal volume movement coexist in a mutually assisting manner (effect of heat recycling), it is possible to realize an innovative, rational and highly efficient thermal cycle that has not been obtained in the past. . In practice, the basic configuration and system of the Stirling cycle is the same as the present invention even if the process portion of the substantially equal volume movement shifts and changes in the direction of equal pressure movement (referred to as the Ericsson cycle). Since the above-described excellent characteristics can be obtained as it is, the effect of heat recycling can be regarded as equivalent to the Stirling cycle.

  As described above, in the Stirling cycle of the present invention, the high-temperature expansion mechanism 24, the low-temperature compression mechanism 44, and the drive shaft 14 common to both mechanisms are housed in the sealed container 12. Further, since the sealed container 12 is partitioned by the partition wall 16 into the high temperature expansion mechanism section 24 side and the low temperature compression mechanism section 44 side, the control mechanism 18 that controls the performance characteristics of the Stirling cycle and the generator 20 (becomes an electric motor). Can be directly connected to the drive shaft 14 on the low-temperature compression mechanism portion 44 side in the sealed container 12, the responsiveness of power transmission can be greatly improved. In addition, since the high-temperature expansion mechanism 24 and the low-temperature compression mechanism 44 are housed in the sealed container 12, the control mechanism 18, the generator 20 (electric motor), and the like are not directly impacted from the outside. Can also be avoided. As a result, corrosion of the control mechanism 18 and the generator 20 (electric motor) due to scratches and wind and rain can be reliably prevented, and the durability of the Stirling cycle can be greatly improved. However, in the Stirling cycle of this method, the control mechanism 18 changes the phase difference between the rotors 28 and 48 of the high-temperature expansion mechanism 24 and the low-temperature compression mechanism 44 so that both mechanism parts are the simplest and most responsive. It is possible to realize a Stirling cycle state in which the volume changes of each other are optimal. However, when this control is not required, the control mechanism 18 is unnecessary.

  As a result, the high efficiency, the diversity of fuels and heat sources, the quietness, the cleanliness of exhaust, etc., which are the features of the Stirling engine, can be achieved with the drive mechanism (high temperature expansion mechanism 24 and low temperature compression mechanism 44). It can be put into practical use with a simple structure which is a hermetically sealed type. Further, since the sealed container 12 is formed in a cylindrical shape, pressure resistance, reliability, and compactness can be dramatically improved, and convenience and energy saving that cannot be obtained by existing engines such as conventional internal combustion engines. And can be used in all energy equipment application fields that require environmental harmony.

  In particular, since the high-temperature expansion mechanism 24 and the low-temperature compression mechanism 44 are housed in the sealed container 12, if both the mechanisms 24 and 44 are configured to have the same outer diameter, the drive shaft 14 is extremely centered. It can be done easily. As a result, the Stirling system 10 can be easily assembled, so that the cost of the Stirling system 10 can be significantly reduced. Further, since the drive mechanism is housed in the sealed container 12, the Stirling system 10 can be greatly simplified and durable. In addition, since the Stirling cycle can be made compact, it is possible to achieve a significant weight reduction compared to the conventional Stirling cycle. As a result, productivity can be greatly improved and costs can be reduced, so that the market competitiveness of the Stirling system 10 can be greatly improved as a whole.

  In addition, the heaters (first heater 38, second heater 38A), coolers (first cooler 58, second cooler 58A), and regenerative heat exchanger 60 for configuring the Stirling cycle are sealed. The Stirling system 10 can be easily transported anywhere and can be easily installed anywhere because it is integrated with the sealed container 12 inside or outside the sealed container 12. . Thereby, the transportability, installation property, etc. of the Stirling system 10 can be significantly improved, and the versatility of the Stirling system 10 can be greatly improved.

  Further, the pressure feeding mechanism 15 for lubricating oil 70 for lubricating the sliding portion in the sealed container 12 and the return for separating the lubricating oil 70 from the working gas discharged to the outside of the sealed container 12 and returning it to the sealed container 12. Since the mechanism 62 is provided, the lubricating oil 70 can be smoothly supplied to each sliding portion of the Stirling cycle. Further, since the lubricating oil 70 is separated from the working gas and returned to the sealed container 12, the lubricating oil 70 is mixed with the working gas and flows into the low-temperature compression mechanism 44. Inconvenience can be prevented. As a result, it is possible to smoothly operate the Stirling cycle, and it is possible to reliably prevent a decrease in output and performance deterioration of the Stirling cycle.

  In addition, an electric motor 20 for driving the drive shaft 14 is provided, and the Stirling cycle is operated in a reverse cycle (that is, the drive shaft 14 in FIG. 2 is rotated counterclockwise and the working gas flow direction is also reversed). A refrigerator system can be constructed using the compression / expansion of the working gas accompanying the operation of the mechanism 44 and the high-temperature expansion mechanism 24. In this case, the first heater 38 and the second heater 38A act as an endothermic cooling unit, and can cool the object by absorbing heat from the outside. The first cooler 58 and the second cooler 58A It acts as a heating part and dissipates heat to the outside. Practically, it can be used for heat pump air conditioning, medium / low temperature chillers and ultra-low temperature refrigerators. Further, if a natural working medium such as hydrogen or helium is used as the working gas, the working gas can be applied to the refrigerator field having excellent environmental performance. Thereby, it becomes possible to use both the generator 20 and a refrigerator, and the convenience of a Stirling cycle can be improved significantly.

  In addition, it can be expected that it can be put to practical use with performance and cost that far exceed the conventional reciprocating Stirling cycle. Further, since the eccentric directions of the first cylinder 26 and the second cylinder 46 are arranged in opposite phases and mutually cancel vibrations, the noise level can be greatly reduced. In both cases of the output from the generator 20 and the refrigeration system, the thermodynamically deviates slightly from the ideal Stirling cycle in the practical cycle, but the principle based on the heat regeneration cycle is observed. Is the gist of the present invention. In addition, the structure of the Stirling cycle is similar to that already known as a “sealed two-cylinder rotary compressor” for compressors for refrigeration and air conditioning, and the productivity and low cost based on its simplicity are low. Sex can be expected as well.

  In the embodiment, the hermetic container 12 constituting the Stirling cycle is installed vertically (the high temperature expansion mechanism 24 is on the upper side and the low temperature compression mechanism 44 is on the lower side). (The state in which the high-temperature expansion mechanism 24 and the low-temperature compression mechanism 44 are installed substantially horizontally) is acceptable. In this case, the structure that can sufficiently supply the lubricating oil 70 to each drive mechanism when the sealed container 12 is in a substantially horizontal state, that is, the pumping mechanism 15 so that the lubricating container 70 can be pumped up and pumped when the sealed container 12 is horizontal. It is necessary to change to the structure which opens the lower end of the inside of the lubricating oil 70. Thereby, the freedom degree of the attitude | position of the airtight container 12 can be ensured, and the whole Stirling system 10 can be put together compactly.

  Further, after the working gas flowing into the first cylinder 26 from the high-temperature side suction port 32 of the high-temperature expansion mechanism section 24 has passed through the first heater 38, the working gas is further passed through the first space 24 </ b> A to bring the first cylinder 26 to the outside. After being heated, it may be allowed to flow into the first cylinder 26 from the high temperature side suction port 32.

  Similarly, after the working gas that has flowed into the second cylinder 46 from the low temperature side suction port 52 of the low temperature compression mechanism 44 passes through the first cooler 58, the working gas is further passed through the second space 44 </ b> A to move the second cylinder 46. After heating from the outer surface, it may be allowed to flow into the second cylinder 46 from the low temperature side suction port 52. Further, a rotating disk or the like for giving a flywheel effect is added to the control mechanism 18 as necessary.

  Further, the rotary mechanism of the Stirling system 10 has been described as a rolling piston type. However, the Stirling system 10 is not limited to the rolling piston type, and the present invention can be realized by using a scroll type rotary mechanism including a fixed scroll and an orbiting scroll. The invention is effective. In addition to the rotating mechanism (rolling piston type) that meets the purpose of the Stirling system 10, “swing rotor type”, “multi-vane type”, and “Wankel type” are also applicable in principle. It is done. Even if the Stirling system 10 is constituted by these, the present invention is effective.

  Moreover, although the shape, dimension, etc. of the Stirling system 10 were described in the Example, the Stirling system 10 may be changed without departing from the gist thereof. Of course, the present invention is not limited to the above-described embodiments, and the present invention is effective even when various other modifications are made without departing from the spirit of the present invention.

1 is a longitudinal side view (partially schematic view) of a Stirling system showing an embodiment of the present invention. It is a conceptual diagram of the Stirling system which shows one Example of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Stirling system 12 Sealed container 14 Drive shaft 15 Pumping mechanism 16 Bulkhead 18 Control mechanism 20 Generator (electric motor)
24 High temperature expansion mechanism part 26 1st cylinder 28 1st rotor 30 1st vane 38 1st heater 44 Low temperature compression mechanism part 46 2nd cylinder 48 2nd rotor 50 2nd vane 58 1st cooler 60 Regenerative heat exchanger 62 Return mechanism 70 Lubricating oil

Claims (5)

  A high-temperature expansion mechanism for configuring a Stirling cycle, a low-temperature compression mechanism, and a drive shaft common to both mechanisms are housed in a sealed container, and the inside of the sealed container is separated by a partition wall, and the high-temperature expansion mechanism A Stirling system, which is partitioned into a side and a side of the low-temperature compression mechanism.   The control mechanism for controlling the performance characteristics of the Stirling cycle and a generator or an electric motor are directly connected to the drive shaft on the low-temperature compression mechanism section side in the sealed container. Stirling system.   The heater, the cooler, and the regenerative heat exchanger for configuring the Stirling cycle are integrated with the sealed container in the sealed container or outside the sealed container. Item 3. A Stirling system according to Item 2.   A lubricant pressure feeding mechanism for lubricating the sliding portion in the sealed container, and a return mechanism for separating the lubricant from the working gas discharged to the outside of the sealed container and returning it to the sealed container. The Stirling system according to any one of claims 1 to 3, wherein the Stirling system is provided.   The refrigerator system using the Stirling apparatus according to claim 1, further comprising an electric motor that drives the drive shaft, wherein the Stirling cycle functions in a reverse cycle.

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