JPH08105353A - Heat drive device - Google Patents

Abstract

PURPOSE: To make a heat drive device compact and reduce its manufacturing cost by raising the performance of a heating means. CONSTITUTION: A combustion unit 18, which heats a heater tube 15, through which operating gas runs, of a heat drive device, is composed to have it cover the upper part of a cylinder 9 of a first gas operating device and is provided with a combustion chamber 19 to which an air supply part 34 for supplying combustion air thereto is facing and made in a cylindrical space containing the heater tube 15 therein. The periphery of the combustion chamber 19 is enclosed by a plurality of flat plate shaped hollow air preheaters 36 longitudinally arranged nearly in the tangential direction, combustion air introduced through a part of the shell of the combustion unit 18 is branched into respective air preheaters 36 and supplied to the air supply part 34, and combustion exhaust gas generated in the combustion chamber 19 is exhausted outside therefrom through gaps between respective air preheaters 36 by an exhaust port 57 provided on a part of the shell of the combustion unit 18.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat drive device such as a Stirling engine or a heat drive type heat pump device using a Wilmier cycle, and more particularly to a heating device thereof.

[0002]

2. Description of the Related Art As a heat driving device of this type, for example, a heat driving type heat pump device is also called a Vilmier heat pump device (VMHP), and has been conventionally used, for example, in Japanese Patent Laid-Open No. 61-44254 and Japanese Patent Laid-Open No. 4174. There is one as shown in Japanese Patent Publication. The former is, as shown in FIG. 17, the first and second gas actuating devices 200, 201.
It has. The first gas actuating device 200 includes a high temperature cylinder 205 whose interior filled with a working gas by a reciprocating displacer 202 is divided into a high temperature chamber 203 and a middle greenhouse 204, and a high temperature chamber 203 of the high temperature cylinder 205. And the middle greenhouse 204 are connected to each other through a working gas flow path including a high temperature side heat exchanger 206, a heat accumulator 207, and a middle temperature side heat exchanger 208, which are sequentially connected from the high temperature chamber 203 side to the middle greenhouse 204 side. The high temperature side heat exchanger 206 is provided with a heating means 209.

The second gas actuating device 201 includes a low temperature cylinder 213 whose interior filled with a working gas by a reciprocating displacer 210 is divided into a low temperature chamber 211 and a middle greenhouse 212, and the low temperature cylinder 213. A low temperature side heat exchanger 214, a regenerator 215, and a middle temperature side heat exchanger 216, in which the low temperature chamber 211 and the middle greenhouse 212 of 213 are sequentially connected from the low temperature chamber 211 side to the middle greenhouse 212 side, are formed by a working gas flow path. It is in communication.

First and second gas actuators 200, 201
The inner greenhouses 204 and 212 communicate with each other through a communication portion provided at the end of each gas flow path. High temperature cylinder 2
05 and the low temperature cylinder 213 are connected to each other at a base portion at a substantially right angle, and the crank mechanism portion 21 is connected to the connecting portion.
7, the displacers 202 and 210 on the high temperature side and the low temperature side are configured to reciprocate with a certain phase difference.

The latter is also basically the same in construction as the former, and the crank mechanism portion 217 is formed at the connecting portion between the high temperature cylinder 205 and the low temperature cylinder 213 at right angles to the plane formed by the high temperature cylinder 205 and the low temperature cylinder 213. A crank shaft is provided, and an output shaft of a starter motor that moves the crank mechanism unit 217 is connected to the crank shaft.

Each of the above-described conventional heat-driven heat pump devices has a basic structure utilizing the Brummier cycle, like the Stirling engine belonging to the external combustion engine,
By the external heating method in which the working gas is forcibly heated by the high temperature side heat exchanger 206, the low temperature heat medium is taken out from the low temperature side heat exchanger 214 and the medium temperature heat medium is taken out from the middle temperature side heat exchangers 208 and 216, respectively. The heat medium is used for cooling and the medium temperature medium is used for heating.

As a conventional technique relating to the heating means 209 for heating the working gas in such a heat-driving device, there is, for example, one disclosed in Japanese Patent Application Laid-Open No. 4-90404. That is, as shown in FIG.
8, a heater tube 22 through which a working gas flows is formed in a combustion space 220 formed by an internal heat insulating material 219.
1 is provided. The combustion space 220 is provided with a fuel nozzle 222 for ejecting fuel and a swirling nozzle 223 for supplying combustion air in the vicinity thereof. Fuel nozzle 2
The fuel ejected from 22 and the combustion air ejected from the swirling nozzle 223 are mixed by the burner throat 224 opening toward the combustion space 220.

Internal thermal insulation 2 surrounding the combustion space 220
An exhaust gas flow path and a combustion air flow path, which are separated by a heat exchange wall 225, are formed inside and outside between the outer peripheral surface of 19 and the inner peripheral surface of the outer heat insulating material 218. One end of the exhaust gas flow path is
The combustion space 220 is communicated between the outer peripheral portion of the burner throat 224 and the internal heat insulating material 219, and the other end is connected to the external heat insulating material 2
It communicates with the exhaust port opened to the outside of 18. The combustion air flow path is formed along the inner surface of the outer heat insulating material 218, one end of which communicates with the swirling nozzle 223, and the other end of which is the outer heat insulating material 2.
18 is connected to the air supply port opened outside.

In the heating means 209, the combustion air is preheated by the heat of the combustion exhaust gas through the heat exchange wall 225 while passing through the combustion air flow path, blown out from the swirling nozzle 223, and ejected from the fuel nozzle 222. Mixed with fuel,
It is ignited by the ignition discharge electrode and burns in the combustion space 220. The combustion exhaust gas generated by combustion passes through the exhaust gas flow path and transfers heat to the combustion air and is exhausted to the outside from the exhaust port. Combustion space 2 surrounded by internal heat insulating material 219
20 is maintained at a high temperature, and the heater tube 221 is also kept warm.
The internal heat insulating material 219 also prevents heat transfer from the combustion space 220 to the exhaust gas after heat exchange.

[0010]

In the heating means 209 of the conventional heat-driving device described above, the preheating of the combustion air by the combustion exhaust gas is performed only by the further heat exchanging portion, so that the necessary heat exchange is required. In order to obtain the amount, it is necessary to increase the outer diameter or height of the entire heating means 209, which is a factor that prevents achievement of downsizing of the heat driving device.

The present invention has been made in order to solve the above-mentioned conventional problems. The problem is to achieve a compact thermal drive unit and a reduction in cost by improving the performance of the heating means. That is, it is intended to improve the heat exchange performance regarding the heat exchange between the combustion exhaust gas and the combustion air in the heating means.

[0012]

In order to achieve the above object, the invention according to claim 1 provides a first gas operating device including a displacer, a cylinder, a heater pipe, a heat storage regenerator, a heat exchanger, and the like. A second gas operating device including a sir, a cylinder, a low temperature side heat exchanger, a regenerator, and a heat exchanger,
Regarding the heating means for heating the heater pipe in the thermal drive device including the crank mechanism section that reciprocates the displacers of the first and second gas actuating devices with a certain phase difference, the cylinder of the first gas actuating device In addition to the above structure, the heating means is provided with a fuel nozzle for injecting fuel and an air supply section for supplying combustion air near the fuel nozzle, and a cylindrical space containing a heater tube. As a combustion chamber, the outer periphery of the combustion chamber is surrounded by a plurality of flat plate-shaped hollow air preheaters vertically arranged in a substantially tangential direction from a position close to the outer diameter of the combustion chamber. Combustion air introduced from a part of the outer shell is divided into each air preheater and is supplied to the air supply unit via each air preheater, and combustion exhaust gas generated in the combustion chamber is discharged from the combustion chamber to each air preheater. same Employing means to be exhausted to the outside by the exhaust port provided on a part of the outer shell of the combustion apparatus via the gap.

In order to achieve the above object, the invention of claim 2 forms an air passage integrally with each of the air preheaters in the means according to claim 1 in a meandering manner, and the combustion air is provided at one end of this air passage. A means for introducing from the connected air supply pipe and supplying to the air supply unit via the air supply pipe connected to the other end is adopted.

In order to achieve the above-mentioned object, the invention of claim 3 forms upper and lower inner wall surfaces of an air preheater portion which continues to the upper and lower parts of the combustion chamber in the means according to either claim 1 or claim 2. A means for providing a gap over the entire circumference is employed at the intermediate portion in the radial direction of the partition member.

In order to achieve the above object, the invention of claim 4 is the means according to claim 1 or 2, wherein the upper and lower sides of the combustion chamber are located at the inner edge and the outer edge of each air preheater. A means for providing a pressure equalizing cylinder having a large number of holes over the entire direction is adopted.

In order to achieve the above-mentioned object, the invention of claim 5 is such that a first gas operating device including a displacer, a cylinder, a heater tube, a heat storage regenerator, a heat exchanger, etc., a displacer, a cylinder, and a low temperature side. A second gas operating device including a heat exchanger, a regenerator, and a heat exchanger, and these first and second gas operating devices.
The heating means for heating the heater tube in the heat-driving device including the crank mechanism section that reciprocates each displacer of the gas operating device with a certain phase difference is capped on the upper part of the cylinder of the first gas operating device. In addition to the structure, the heating means includes a fuel nozzle for injecting fuel and an air supply section for supplying combustion air near the fuel nozzle, and a combustion chamber as a cylindrical space containing a heater tube. The outer circumference of the combustion chamber is surrounded by a preheating device in which a plurality of plane fan-shaped air preheaters are combined in a cylindrical shape with a gap between each other, and each of the air preheaters is fan-shaped flat plate-shaped hollow body. Is laminated on a plurality of air supply pipes at intervals, and the combustion air introduced from a part of the outer shell of the combustion device is supplied to each hollow body of each air preheater. It is split by a pipe and is supplied from each hollow body through an air supply pipe to an air supply section, and combustion exhaust gas generated in the combustion chamber is discharged from the combustion chamber to the outside of the combustion device through each gap between the hollow bodies of each air preheater. A means for exhausting to the outside through an exhaust port provided in a part of the shell is adopted.

In order to achieve the above object, the invention of claim 6 is in the radial direction of the partition wall member forming the inner wall surface of the air preheater portion which continues to the upper and lower parts of the combustion chamber in the means according to claim 5. Adopt a means to provide a gap over the entire circumference in the middle part.

In order to achieve the above object, the invention of claim 7 provides a radial throttle in each hollow body of each air preheater in the means according to claim 5, and a compound extending in the radial direction inside each hollow body. Means are provided to form the rows of air passages.

In order to achieve the above object, the invention of claim 8 relates to the means according to claim 5, wherein each hollow body of each air preheater is provided with upper and lower corrugated plates provided with corrugated diaphragms. A means for joining and configuring so as to intersect is adopted.

In order to achieve the above-mentioned object, the invention of claim 9 is such that a first gas operating device including a displacer, a cylinder, a heater tube, a heat storage regenerator, a heat exchanger, etc., a displacer, a cylinder, and a low temperature side. A second gas operating device including a heat exchanger, a regenerator, and a heat exchanger, and these first and second gas operating devices.
The heating means for heating the heater tube in the heat-driving device including the crank mechanism section that reciprocates each displacer of the gas operating device with a certain phase difference is capped on the upper part of the cylinder of the first gas operating device. In addition to the structure, the heating means includes a fuel nozzle for injecting fuel and an air supply section for supplying combustion air near the fuel nozzle, and a combustion chamber as a cylindrical space containing a heater tube. Then, the outer periphery of the combustion chamber is surrounded by a preheating device in which a plurality of cylindrical tubular bodies, which are hollow and flat curved bodies curved in an arc shape and arranged in a fence shape with a gap in the radial direction, are stacked with a gap in the radial direction, Combustion air introduced from a part of the outer shell of the combustion device flows in a spiral shape from the outside to the inside of the cylindrical body through each curved body and is supplied to the air supply unit, and the combustion exhaust generated in the combustion chamber is discharged. From the outer side of the outermost cylindrical body of the preheating device to the outside by an exhaust port provided in a part of the outer shell of the combustion device. Adopt a means to exhaust to.

In order to achieve the above object, the invention of claim 10 is in the radial direction of the partition wall member forming the upper and lower inner wall surfaces of the preheating device portion continuing to the upper and lower portions of the combustion chamber in the means according to claim 9. A means for providing a gap over the entire circumference in the middle part of is adopted.

[0022]

According to the invention of claim 1, the combustion air introduced from a part of the outer shell is divided into each air preheater and flows,
Each of the air preheaters is supplied to the air supply unit for combustion. On the other hand, the combustion exhaust gas generated in the combustion chamber flows tangentially outward from the combustion chamber through the gaps between the air preheaters, and is exhausted to the outside from the exhaust port provided in a part of the outer shell of the combustion device. To be done. During this time, the combustion air exchanges heat with the combustion exhaust gas flowing out from the gap between the air preheaters while flowing through the air preheaters, is sufficiently preheated, and is supplied to the air supply unit. The distribution of the combustion air to the air preheaters is made uniform, and the heat exchange portion is composed of many layers, so that the heat exchange performance is good and the outer diameter of the combustion device can be reduced. Also, the flow velocity of the combustion exhaust gas can be set to an arbitrary value depending on the interval between the air preheaters.

According to the invention of claim 2, the contact area with the combustion exhaust gas in each air preheater can be increased in addition to the operation according to claim 1, and the flow velocity of the combustion air can be changed by the air flow path of each air preheater. Can be set to any value.

According to the third aspect of the invention, the temperature difference between the inner peripheral side and the outer peripheral side due to the combustion heat of each partition wall member separated by a gap is reduced along with the operation according to the first aspect or the second aspect. Yes, thermal stress is reduced.

According to the invention of claim 4, in addition to the operation according to claim 1 or claim 2, even if there is only one exhaust port, the combustion exhaust gas in the air preheater portion can be arranged in the circumferential direction and the axial direction. The flow velocity distribution becomes uniform, and the heat transfer area of each air preheater functions effectively.

In the fifth aspect of the present invention, the combustion air introduced from a part of the outer shell is branched from the air supply pipe into each hollow body of each air preheater and flows from each hollow body to the air supply pipe. After that, it is supplied to the air supply unit and used for combustion. On the other hand, the combustion exhaust gas generated in the combustion chamber flows from the combustion chamber in the radial direction through each gap between the hollow bodies of the air preheaters,
The gas is exhausted to the outside from an exhaust port provided in a part of the outer shell of the combustion device. During this time, the combustion air exchanges heat with the combustion exhaust gas flowing out from the gap between the hollow bodies while flowing through the hollow bodies of the air preheaters, and is sufficiently preheated and supplied to the air supply unit. Since each air preheater is a flat fan and is combined in a cylindrical shape with a gap between each other to form a preheating device, prevent thermal deformation due to a temperature difference between the inner peripheral side and the outer peripheral side of the preheating device. In addition, the distribution of the combustion air is equalized, and the heat exchange portion is composed of many layers, so that the heat exchange performance is good and the outer diameter of the combustion device can be reduced. Also, the flow velocity of the combustion exhaust gas can be set to an arbitrary value depending on the distance between the hollow bodies of each air preheater.

According to the invention of claim 6, in addition to the action according to claim 5, the temperature difference between the inner peripheral side and the outer peripheral side due to the combustion heat of each partition member separated by a gap can be reduced, and the thermal stress is reduced. To do.

According to the invention of claim 7, in addition to the operation according to claim 5, the combustion air flows in the inside of each hollow body of each air preheater through the double-row air passages extending in the radial direction, so that In addition to making the air flow distribution in the body uniform and increasing the heat transfer area, it is possible to induce turbulence in the flow of combustion exhaust gas at the throttle portion.

According to the invention of claim 8, in addition to the operation according to claim 5, the flow distribution of the air flowing in each hollow body is made uniform, the heat transfer area is widened, and both the combustion air and the combustion exhaust gas are formed by the corrugated throttle. Can induce turbulence in the flow of.

In the invention of claim 9, the combustion air introduced from a part of the outer shell of the combustion device flows in a spiral shape from the outer side to the inner side of the cylindrical body through the respective curved bodies to form an air supply portion. The combustion exhaust gas that is supplied to the combustion chamber and flows into the combustion chamber from the combustion chamber to the outer side of the outermost cylindrical body of the preheating device in a spiral shape through the gap between the curved bodies to the outside, and then to the outer shell of the combustion device. The air is exhausted to the outside through an exhaust port provided in the section. During this time, the combustion air exchanges heat with the combustion exhaust gas flowing out from the gap between the inner and outer curved bodies while flowing in each curved body, is sufficiently preheated, and is supplied to the air supply unit. Therefore, the temperature of the curved body becomes lower as it constitutes the outer cylindrical body, and the heat exchange portion is constituted by many layers, so that the heat exchange performance is good and the outer diameter of the combustion device can be reduced. . Further, the flow velocity of the combustion exhaust gas can be set to an arbitrary value depending on the interval between the curved bodies forming the tubular body and the radial interval between the inner and outer tubular bodies.

According to the invention of claim 10, in addition to the action according to claim 9, the temperature difference between the inner peripheral side and the outer peripheral side due to the combustion heat of each partition member separated by a gap can be reduced,
Thermal stress is reduced.

[0032]

An embodiment of the present invention will be described below with reference to the drawings. Example 1. FIG. 1 is a sectional view showing the configuration of a heat-driven heat pump device which is a heat-driven device according to an embodiment of the present invention. First, the overall configuration will be described with reference to FIG. The heat-driven heat pump device shown in FIG. 1 includes first and second gas actuating devices 1, 2, crank mechanism parts 3 and 4 for operating them, and a starter motor 5.
It is mainly configured by and and is mounted on a base 8 elastically suspended by a suspension device 7 provided with a coil spring on a frame 6. First gas actuating device 1 and second
The gas actuating device 2 is provided above the crank mechanism parts 3 and 4 which are juxtaposed on the base 8 in close proximity to each other, and the crank mechanism parts 3 are provided at the central portions between the crank mechanism parts 3 and 4. , A single starter motor 5 is arranged for initial operation.

The first gas operating device 1 is a high temperature side cylinder 9
And a high temperature side displacer 10 that reciprocates in the high temperature side cylinder 9. The high temperature side cylinder 9 is filled with a working gas such as helium gas, and the high temperature side displacer 10 has a high temperature side space 9 on the cylinder head side and a high temperature side medium temperature space 12 on the crank mechanism 3 side in the high temperature side displacer 10. It is divided into The lower end of the high temperature side cylinder 9 is connected to the upper end of a crank case 13 which constitutes the outer shell of the crank mechanism unit 3, and the high temperature side cylinder 9 is connected by a rod seal portion 14 fitted to the upper part of the crank chamber in the crank case 13. The airtightness between the high temperature side intermediate temperature space 12 and the crank chamber is maintained. The high temperature space 11 and the high temperature side medium temperature space 12 of the high temperature side cylinder 9 are connected in sequence from the high temperature space 11 side to the high temperature side medium temperature space 12 side by a heater pipe 15 and a heat storage regenerator 16.
And the high temperature side intermediate temperature part heat exchanger 17 are connected by a gas flow path. A plurality of heater tubes 15 are arranged in parallel in the cylinder head of the high temperature side cylinder 9 in a rectangular shape, and are respectively arranged in the combustion chambers 19 of the combustion device 18 cap-mounted on the upper side of the high temperature side cylinder 9. ing. One end of each of these heater tubes 15 faces the high temperature space 11,
The other end communicates with the heat storage regenerator 16. Heat storage regenerator 16
The high temperature side middle temperature section heat exchanger 17 and the high temperature side middle temperature section heat exchanger 17 are respectively formed in the recess formed in the inner wall surface of the high temperature side cylinder 9 with the heat storage regenerator 16 on the upper side and the high temperature side middle temperature section heat exchanger 17 on the lower side. Are coaxially assembled, and their inner peripheral sides are covered with a liner that forms a sliding surface of the high temperature side cylinder 9 with the high temperature side displacer 10. A spacer for positioning the height position of the heat storage regenerator 16 is incorporated in the inner wall portion of the high temperature side cylinder 9 between the heater tube 15 and the heat storage regenerator 16.

The second gas operating device 2 is also the low temperature side cylinder 2
0 and a low temperature side displacer 21 that reciprocates in the low temperature side cylinder 20. Low temperature side cylinder 20
Is also filled with a working gas such as helium, and the low temperature side displacer 21 divides the low temperature side cylinder 20 into a low temperature space 22 on the cylinder head side and a low temperature side medium temperature space 23 on the crank mechanism section 4 side. . A lower end of the low temperature side cylinder 20 is connected to an upper end of a crank case 24 which constitutes an outer shell of the crank mechanism unit 4, and a low temperature side cylinder 20 is cooled by a rod seal portion 25 fitted to an upper portion of a crank chamber in the crank case 24. Airtightness between the side intermediate temperature space 23 and the crank chamber is maintained. Low temperature space 22 of low temperature side cylinder 20
The low temperature side medium temperature space 23 and the low temperature side medium temperature space 23 are formed by a gas flow path formed by the low temperature side heat exchanger 26, the regenerator 27 and the low temperature side medium temperature part heat exchanger 28, which are connected in sequence from the low temperature space 22 side to the low temperature side medium temperature space 23 side. It is in communication. Low temperature side heat exchanger 26 and regenerator 2
7 and the low temperature side middle temperature section heat exchanger 28 are connected to the low temperature side cylinder 20.
The low temperature side heat exchanger 26 is placed on the upper side, the regenerator 27 is placed in the middle, and the low temperature side medium temperature section heat exchanger 28 is placed on the lower side in the recesses formed in the inner wall surface of the cylinder. The inner peripheral sides thereof are covered with a liner that forms a sliding surface of the low temperature side cylinder 20 with the low temperature side displacer 21.

High temperature side intermediate temperature space 1 of the first gas operating device 1
2 and the low temperature side intermediate temperature space 23 of the second gas operating device 2 form the respective bottom portions of the rod seal portion 1
Each crankcase 1 through the communication holes formed in 4, 4
The external communication pipes 29 are connected to the connection ports provided at 3, 24, and the connection ports are connected to each other.

The high-temperature side displacer 10 and the low-temperature side displacer 21 of the first gas actuating device 1 and the second gas actuating device 2 are predetermined by crank mechanism parts 3 and 4 provided below them. Reciprocating motions are made in the high temperature side cylinder 9 and the low temperature side cylinder 20 respectively with a phase difference (90 ° in this embodiment). As shown in FIG. 1, the crank mechanism parts 3 and 4 have substantially the same structure, and a crankshaft is connected to each end of the rotary shaft of a biaxial starter motor 5 assembled between them. A large-diameter end of a connecting rod 30 that converts the rotational movement of the crankshaft into a reciprocating linear movement in the crankcases 13 and 24 is pivotally attached to each crankshaft. The small-diameter end of each connecting rod 30 is connected by a pin to a crosshead slidably incorporated in a cylinder portion formed on the upper side of the crankcases 13, 24, and one rotation of the crankshaft causes the crosshead to move inside the cylinder portion. Make one reciprocating movement up and down. The upper portion of each crosshead and the lower portions of the high temperature side displacer 10 and the low temperature side displacer 21 are connected to the rod seal portion 1.
4, 25 are connected by connecting rods 31 and 32, respectively, and the high temperature side displacer 10 and the low temperature side displacer 21 are synchronized with the crossheads connected to them, respectively, inside the high temperature side cylinder 9 and the low temperature side. It reciprocates linearly between the top dead center and the bottom dead center in the cylinder 20. Connection rods 31, 32 penetrating the rod seal portions 14, 25
Moves up and down on the sliding surfaces of the rod seal portions 14 and 25 in an airtight state.

Next, the operation of the heat-driven heat pump device having the above-mentioned basic structure will be described. When the combustion device 18 starts combustion by the operation of the combustion device 18, the combustion chamber 1
Each heater tube 15 in 9 is normally heated to 400 ° C. to 800 ° C., the high temperature side intermediate temperature part heat exchanger 17 and the low temperature side intermediate temperature part heat exchanger 28 reach 35 ° C. to 80 ° C., respectively, and the starter motor 5 Start by driving. When the starter motor 5 is driven, the high temperature side displacer 10 and the low temperature side displacer 21 move the low temperature side cylinder 20 and the low temperature side cylinder 90 by the crank mechanism parts 3 and 4, respectively.
Starts reciprocating motion with a phase difference of °.

In the first gas operating device 1, the working gas is supplied from the high temperature space 11 by the movement of the high temperature side displacer 10 to the high temperature side medium temperature space through the heater tube 15, the heat storage regenerator 16 and the high temperature side medium temperature part heat exchanger 17. In the second gas operating device 2, the movement of the low temperature side displacer 21 causes the low temperature side heat exchanger 26, the low temperature side heat exchanger 26, the regenerator 27, and the low temperature movement to be repeated. The movement in the order of reaching the low temperature side intermediate temperature space 23 via the side intermediate temperature section heat exchanger 28 and the movement in the reverse order are alternately repeated. During this time,
The volume of the working space of the working gas is constant, and the temperature and pressure of the working gas change. The change in the pressure of the working gas is instantaneously transmitted because the first gas working device 1 and the second gas working device 2 are communicated with each other by the external communication pipe 29, and the pressure becomes uniform in the entire working space.

When the high temperature side displacer 10 of the first gas operating device 1 is at the top dead center, the heat storage regenerator 16 is heated by the passage of the high temperature working gas to store heat. The high temperature space 11 has no volume, and the working gas that has moved to the high temperature side intermediate temperature space 12 is heated by the action of the low temperature side cylinder 20 to generate heat and is radiated by the high temperature side intermediate temperature heat exchanger 17. This state is isothermal compression as a thermal process. At this time, the low temperature side displacer 21 of the second gas actuating device 2 is in the process of moving to the cylinder head side, and the working gas is moving from the low temperature space 22 to the low temperature side intermediate temperature space 23. The regenerator 27 is deprived of heat by the low-temperature gas from the low-temperature space 22, and the amount of stored heat decreases. Regenerator 27
The working gas heated by the heat received from and moving to the low temperature side intermediate temperature space 23 raises the average temperature of the working gas in the low temperature side cylinder 20 and raises the pressure. This state is isothermal heating (change in state of constant volume) as a thermal process.

When the high temperature side displacer 10 of the first gas operating device 1 is in the middle of descending from the top dead center, the working gas moves from the high temperature side intermediate temperature space 12 to the high temperature space 11. The heat storage regenerator 16 is deprived of heat by the working gas from the high temperature side medium temperature space 12, and the heat storage amount thereof is reduced. By the working gas heated by the heat received from the heat storage regenerator 16 and moving to the high temperature space 11, the average temperature of the working gas in the high temperature side cylinder 9 rises and the pressure rises. This state is isochoric heating as a thermal process. At this time, the low temperature side displacer 21 of the second gas operating device 2 becomes the top dead center, and the regenerator 2
7 is cooled and stored by the passage of a low-temperature working gas. The low temperature space 22 has no volume, and the working gas that has moved to the low temperature side intermediate temperature space 23 is heated by the action of the high temperature side cylinder 9 to generate heat, and the low temperature side intermediate temperature heat exchanger 2
8 radiates heat. This state is isothermal compression as a thermal process.

When the high temperature side displacer 10 of the first gas operating device 1 reaches the bottom dead center, the working gas moves from the high temperature side intermediate temperature space 12 to the high temperature space 11. The heat storage regenerator 16 is deprived of heat by the working gas from the high temperature-side medium temperature space 12, and the heat storage amount thereof is almost lost. The volume of the high temperature space 11 is in the maximum state, and the working gas heated by the heat received from the heat storage regenerator 16 and moved to the high temperature space 11 has the low temperature side cylinder 2
Although the pressure decreases and expands and radiates heat due to the action of 0, heat is absorbed from the combustion device 18 through the heater pipe 15, so that the thermal process is isothermal expansion. At this time, the low temperature side displacer 21 of the second gas operating device 2 is in the middle of descending from the top dead center, and the working gas is cooled by the regenerator 27 and moves from the low temperature side medium temperature space 23 to the low temperature space 22. To go. The working gas cooled by the regenerator 27 and moving to the low temperature space 22 lowers the average temperature of the working gas in the low temperature side cylinder 20 and reduces the pressure. This state is isothermal cooling as a thermal process.

When the high temperature side displacer 10 of the first gas operating device 1 is in the middle of moving from the bottom dead center to the cylinder head side, the working gas is moving from the high temperature space 11 to the high temperature side intermediate temperature space 12. The heat storage regenerator 16 increases its heat storage amount by the high temperature working gas from the high temperature space 11. High temperature side medium temperature space 1 cooled by the heat storage regenerator 16
The working gas moving to 2 lowers the average temperature of the working gas in the high temperature side cylinder 9 and reduces the pressure. This state is isothermal cooling as a thermal process. At this time, the second
The low temperature side displacer 21 of the gas operating device 2 of FIG. When the low temperature side displacer 21 reaches the bottom dead center, the working gas is cooled by the regenerator 27 and moves from the low temperature side medium temperature space 23 to the low temperature space 22. The volume of the low temperature space 22 is in the maximum state, and the working gas that has been cooled by the regenerator 27 and moved to the low temperature space 22 receives the action of the high temperature side cylinder 9 to expand its pressure and radiate heat. Since the heat is absorbed by the vessel 26, the thermal process is isothermal expansion.

By repeating the above-described cycle, the heating output is obtained from the high temperature side intermediate temperature part heat exchanger 17 and the low temperature side intermediate temperature part heat exchanger 28, and the cooling output is obtained from the low temperature side heat exchanger 26, respectively. In the above cycle, if the initial operation is caused by the starter motor 5, then independent operation is possible without requiring the power of the starter motor 5.

The feature of this embodiment is that the first gas operating device 1 is used.
In the combustion device 18 as a heating means for heating the working gas, the description will be given below. As shown in FIGS. 2 to 6, the combustion device 18 of this embodiment includes a high temperature side cylinder 9
A cylindrical shape that is cap-shaped on the cylinder head side and injects fuel into which a fuel nozzle 33 and an air supply portion 34 that supplies combustion air are exposed in the vicinity of the fuel nozzle 33, and that includes a heater tube 15. Combustion chamber 19 as space
It has. The outer periphery of the combustion chamber 19 has a large number of air preheaters 3
It is surrounded by 6 and the upper side and the lower side are respectively surrounded by inner wall surfaces of an upper wall portion 37 and a bottom portion 38 configured as heat insulating walls.

Each of the air preheaters 36 is constituted by a rectangular flat plate-shaped hollow body, and is vertically arranged in a substantially tangential direction from a position close to the outer diameter of the combustion chamber 19 to the outside. 19 is surrounded by the inner edge which is one long side (see FIG. 4). As shown in FIGS. 5 and 6, the structure of each air preheater 36 is a main body that can be said to be a box body in which two metal plates are joined and a series of meandering air passages 40 formed by a narrowed portion 39 are integrally formed inside. The two air supply pipes 41 are attached to the. One of the air supply pipes 41 has an air passage 4
It is connected to one end of 0 and extends upward along one surface. The other one of the air supply pipes 41 is connected to the other end of the air passage 40 and extends upward along the other surface.

The upper wall portion 37 has a structure in which a cup-shaped outer shell 42 is lined with a heat insulating wall 43 having an inner center recessed between the outer peripheral surface of the heat insulating wall 43 and the inner peripheral surface of the outer shell 42. A space is formed in the space, and an annular air passage 44 is formed by the space. An air supply port 45 communicating with an annular air passage 44 is provided in a part of the outer shell 42 on the peripheral side. A partition member 46 is lined on the inner surface of the heat insulating wall 43. A burner outer cylinder 47 penetrating the upper wall portion 37 is provided in the center of the upper wall portion 37, and a fuel nozzle 33 is passed through the burner outer cylinder 47, and a spark plug 48 and a frame rod 49 are arranged in parallel to the fuel nozzle 33. It is arranged. Fuel nozzle 33
The fuel injection portion at the tip of is provided with a plurality of injection holes facing the inside of the burner throat 50, which are installed facing the combustion chamber 19, and are arranged in the circumferential direction.

The burner throat 50 is attached to the center of a partition member 52 sandwiched between the mating surfaces of the outer shell 51 of the body of the combustion device 18 and the upper wall 37. The disk-shaped air supply unit 3 is provided in the center between the partition wall member 52 to which the burner throat 50 is attached and the partition wall member 46 provided on the inner surface of the heat insulating wall 43 of the upper wall portion 37.
A gap as 4 is provided. This air supply unit 34
Has an inner side communicating directly above the burner throat 50, and an air swirling nozzle 54 is incorporated in this portion so as to surround the fuel injection portion of the fuel nozzle 33.

The aforementioned air preheater 36 includes a partition wall member 52 to which the above-mentioned burner throat 50 is attached and a partition wall member 55 which forms the upper surface of the bottom portion 38 provided inside the lower portion of the body shell 51. It is mounted in the vertical direction with the short sides abutting against each other. That is, one air supply pipe 41 of each air preheater 36 is directed toward the outside to the partition member 5
The free end side is connected to the outer peripheral side of 2, and the free end side of the other air supply pipe 41 is connected to the inner peripheral side of the partition member 52 toward the inside. The connection ends of each air supply pipe 41 with the partition member 52 are arranged on a circular plane, the outer connection ends communicate with the air passages 44 of the upper wall 37, and the inner connection ends communicate with the air supply unit 34. There is. Each air preheater 36
Between the outside of the body and the inner surface of the body shell 51.
6 is formed, and an exhaust port 57 communicating with the exhaust chamber 56 is provided in a part of the outer shell 51 of the body and is open to the outside.

Both the partition wall member 52 and the partition wall member 55 are provided with a gap 58 over the entire circumference in the intermediate portion between the inner peripheral side and the outer peripheral side thereof. These gaps 58 can reduce the temperature difference between the inner peripheral side and the outer peripheral side due to the combustion heat of each of the partition members 52 and 55 separated by the gap 58, and can reduce the thermal stress. The basic performance of the gap 5
It will be maintained without 8.

The entire combustion device 18 is supported from below by support legs provided on the bottom structural member holding the heat insulating wall on the bottom 38 side surrounding the upper part of the high temperature side cylinder 9.

In the combustion apparatus 18 having the above structure, the combustion air flows as shown by the solid line arrow in FIG. 2 and is supplied from the air swirling nozzle 54 toward the fuel injection section. On the other hand, the fuel is supplied to the fuel nozzle 33, is injected in the radial direction from each injection hole, and is mixed with the combustion air to form a swirling flow of the air-fuel mixture, which is ignited by the discharge of the ignition plug 48 and the combustion chamber 1
Burns within 9. The combustion exhaust gas generated by the combustion flows outward from the combustion chamber 19, reaches the exhaust chamber 56 as indicated by a dashed arrow in FIG. 2, and is exhausted to the outside from the exhaust port 57.

The flow of the combustion air and the combustion exhaust gas relating to the performance of the combustion device 18 will be described in more detail. The combustion air sent from the air supply port 45 spreads to the air passage 44, is branched from the connection port to the air passage 40 in each air preheater 36 through the air supply pipe 41, and flows in a meandering shape.
Each of the air preheaters 36 is supplied to the air supply unit 34 through the air supply pipe 41 and is used for combustion. On the other hand, the combustion exhaust gas generated in the combustion chamber 19 flows outward from the combustion chamber 19 tangentially along the air preheater 36 through the gaps between the air preheaters 36, and reaches the exhaust chamber 56 where it is exhausted. It is exhausted to the outside by the mouth 57.

The combustion air exchanges heat with the combustion exhaust gas flowing out from the gap between the air preheaters 36 while flowing through the air preheaters 36, is sufficiently preheated and is supplied to the air supply unit 34. In this combustion device 18, the distribution of the combustion air to each air preheater 36 is equalized, and the heat exchange portion is formed as many layers arranged in the circumferential direction. Therefore, the heat transfer area of the total air preheater 36 is The air preheater 36 occupies a small area and the heat exchange performance is extremely high. Therefore, the outer diameter of the entire combustion device 18 can be reduced accordingly, and the cost can be reduced. Also, the flow velocity of the combustion exhaust gas can be set to an arbitrary value depending on the interval between the air preheaters 36.

The air preheater 36 itself may be a flat plate-shaped hollow body, but as in this embodiment, two metal plates having the narrowed portions 39 are joined to integrally form a meandering air passage 40. In this case, the structure is simple, the manufacturing is easy, and the heat transfer area can be wide. In addition, the combustion exhaust gas passes through the air passage 4
Since the turbulent flow is generated by the protruding portion of 0, the performance is improved. Further, in the combustion device 18, the partition member 5
2 and the partition member 55, a gap 58 is set over the entire circumference in the intermediate portion between the inner circumference side and the outer circumference side. Therefore, the inner circumference due to the combustion heat of each of the partition members 52, 55 separated by the gap 58. The temperature difference between the outer side and the outer side is reduced, thermal stress can be reduced, and durability is improved. Further, the partition members 52 and 55 on the outer side of the gap 58 can be made of a material having not so high heat resistance, which can reduce the material cost.

Example 2. The second embodiment relates to the air preheater 36 in the combustion device 18 of the first embodiment described above, and the other configurations and functions are the same as those shown in the first embodiment. Therefore, the same parts as those in the first embodiment are designated by the same reference numerals as those in the first embodiment, and the description thereof will be omitted.

The air preheater 36 according to the second embodiment has the structure shown in FIG.
As shown in FIG. 5, a pressure equalizing cylinder 59 having a large number of holes is provided on the entire inner and outer edges of each air preheater 36 in the entire vertical direction of the combustion chamber 19. The other configuration is the same as that of the first embodiment. In this combustion device 18, even if there is only one exhaust port 57, the flow velocity distribution of the combustion exhaust gas in the air preheater 36 is uniform in the circumferential direction and the axial direction, and the heat transfer area of each air preheater 36 is effective as a whole. The heat exchange performance is further improved. In addition,
If the pressure equalizing cylinder 59 is provided on either one of the inner end edge and the outer end edge of each air preheater 36, a corresponding effect is achieved, but in that case, it is more effective to provide it on the inner end edge side. . Since the other functions are the same as those of the first embodiment, the description thereof will be omitted.

Example 3. The third embodiment relates to the air preheating portion in the combustion device 18 shown in the above-described first and second embodiments, and other configurations and functions are the same as those shown in the first and second embodiments. is there. Therefore, the same parts as those in the first and second embodiments are designated by the same reference numerals as those in the first and second embodiments, and the description thereof will be omitted.

In short, the air preheater 60 of the third embodiment has a multi-layered heat exchange portion in the center line direction in the outer peripheral portion of the combustion chamber 19 as shown in FIGS. . That is, the outer periphery of the combustion chamber 19 is surrounded by a preheating device 62 in which a plurality of (six in the illustrated example) plane fan-shaped air preheaters 60 are combined in a cylindrical shape with a gap 61 between the circumferential directions. . 6 air preheaters 6 as shown
Reference numeral 0 denotes a configuration in which fan-shaped flat plate-shaped hollow bodies 63 are laminated axially with respect to each other on two air supply pipes 41 penetrating the outside and the inside as shown in FIG. The lower end of each air supply pipe 41 is closed by a lid,
The upper end is connected to the partition member 52 and is connected to the air passage 44 and the air supply unit 34. Each air supply pipe 41 is provided with a communication hole 64 that communicates with the inside of the hollow body 63 of each layer.

Such an air supply pipe 41 and the hollow body 6
The structure related to 3 generally requires a troublesome work such as welding, but in the case of this embodiment, a through hole for piercing the air supply pipe 41 in the hollow body 63 is opened in advance. Assembling is performed by expanding the relevant part of the air supply pipe 41 from the inner side in a state where the 63 is passed through the air supply pipe 41 in which the communication hole 64 is formed and is held at the specified position. This work is easier and easier than welding.

Each hollow body 63 is composed of a plurality of radial diaphragm portions 3.
9 are formed by joining two metal plates and crimping the ends, and inside each hollow body 63, there are double rows (6 rows in the illustrated example) that extend in the radial direction and are separated by the narrowed portions 39. ) Air passage 40 is formed.

In the combustion device 18, the combustion air sent from the air supply port 45 spreads to the air passage 44,
Each air preheater 60 from the connection port through the air supply pipe 41
Will be distributed to. The combustion air that has flowed from each communication hole 64 of the air supply pipe 41 into the hollow body 63 of each layer spreads to each air passage 40 and is supplied to the air supply unit 34 through the air supply pipe 41 on the outer side and provided for combustion. Sent. on the other hand,
The combustion exhaust gas generated in the combustion chamber 19 flows from the combustion chamber 19 through the gaps between the hollow bodies 63 in the radial direction, reaches the exhaust chamber 56, and is exhausted to the outside by the exhaust port 57.

Combustion air is the hollow body 6 of each air preheater 60.
While exchanging with each other in the inner space 3, heat exchange is performed with the combustion exhaust gas flowing out from the gap between the hollow bodies 63, and the air supply portion 3 is sufficiently preheated.
4 is supplied. In this combustion device 18, each air preheater 6
The distribution of the combustion air to 0 is equalized, and the heat exchange portion is composed of many layers that vertically overlap, so that the heat transfer area of the total air preheater 60 functions effectively. The area occupied by the air preheater 60 in the radial direction is smaller than that in the first embodiment. Of course, the heat exchange performance of the combustion device 18 is extremely high. Therefore, the outer diameter of the entire combustion device 18 can be reduced accordingly, and the cost can be reduced. Also, the flow velocity of the combustion exhaust gas can be set to an arbitrary value depending on the distance between the hollow bodies 63. Further, in this preheating device 62, the air preheaters 60 are combined into a cylindrical shape with a plane fan shape and a gap 61 between them, so that the gap 61 allows the temperature difference between the inner peripheral side and the outer peripheral side of the preheating device 62 to be increased. It is possible to prevent thermal deformation due to.

The hollow body 63 itself may be a flat fan-shaped flat plate-shaped hollow body, but as in this embodiment, two metal plates having the narrowed portion 39 are joined together to form several air passages 40.
In the case of integrally molding, the structure is simpler, the manufacturing is easier, and the heat transfer area can be wider. Further, since the combustion exhaust gas is turbulent due to the protruding portion of the air passage 40, the performance is further improved. The other functions are the same as those of the first and second embodiments, and the description thereof will be omitted.

Example 4. The fourth embodiment relates to the preheating device in the combustion device 18 shown in the above-described third embodiment, and other configurations and functions are the first and third embodiments.
Is the same as that shown in. Therefore, the same parts as those in the first and third embodiments are designated by the same reference numerals as those in the first and third embodiments, and the description thereof will be omitted.

In the air preheater 65 of the combustion device 18 of the fourth embodiment, as shown in FIGS. 11 to 14, the hollow bodies 63 shown in the third embodiment are provided with upper and lower corrugated plates 67 provided with corrugated diaphragms 66.
The wavy diaphragm 66 is joined so that the diaphragm surfaces are in contact with each other so that they intersect at a constant angle.
The air supply pipes 41 are provided so as to penetrate through both ends on the outer peripheral side and the center on the inner peripheral side, respectively.
1 and the upper and lower corrugated plates 6 between the inner peripheral air supply pipe 41
7 corrugated diaphragms 66 face each other and are in contact with each other.
The other configuration is the same as that of the third embodiment.

Also in this combustion device 18, the combustion air and the combustion exhaust gas flow in a path substantially similar to that of the third embodiment, and heat exchange is performed between the two, but especially with respect to the hollow body 63, the air supply pipe 41 on the outer peripheral side is used. Air supply pipe 41 on the inner peripheral side
Since the corrugated diaphragms 66 of the upper and lower corrugated plates 67 facing each other face and intersect each other, the air flow distribution inside is made uniform, and turbulent flow is generated in both the combustion air and the combustion exhaust gas. Can be induced. This and the expansion of the heat transfer area by the corrugated plate 67 significantly improve the heat exchange performance. Therefore, it is possible to realize compactness and cost reduction. The other functions are the same as those of the third embodiment, and the description thereof will be omitted.

Example 5. The fifth embodiment relates to the structure of the air preheating portion in the combustion device 18 shown in the above-described first and second embodiments, and other structures and functions are the same as those shown in the first and second embodiments. Is the same. Therefore, the same parts as those in the first and second embodiments are designated by the same reference numerals, and the description thereof will be omitted.

In short, the combustion device 18 of the fifth embodiment has a preheating device 68 having a multi-layered heat exchange portion in the radial direction on the outer peripheral portion of the combustion chamber 19, as shown in FIGS. 15 and 16. It is a thing. That is, on the outer periphery of the combustion chamber 19, a plurality of layers of a tubular body 71 in which hollow flat curved bodies 69 curved in an arc shape are arranged in a fence shape with a gap 70 in the circumferential direction and a gap 72 in the radial direction are formed. Each curved body 69 of the tubular body 71
It is surrounded by a preheating device 68 which is overlapped with a staggered overlap. Any one curved body 69 of the innermost tubular body 71 is bridged by the communication portion 73 on the end side that wraps with the curved body 69 facing the relevant portion of the outer cylindrical body 71, and the same. The curved body 69 of the tubular body 71 outside the
Is bridged. All the bending bodies 69 are connected in the inside and outside in such a set. The path of the combustion air is spiral for each group, and a large number of the paths of the combustion air are formed as a whole. The air supply pipes 41 are provided one by one, and are attached to the innermost curved body 69 and the outermost curved body 69 of the pair, respectively. Further, in the vicinity of the communication portion 73 of each curved body 69, a partition wall 74 for closing the gap 72 between the curved bodies 69 is provided on either the right or left side.

Also in the combustion device 18 of the fifth embodiment,
Except for the preheating device 68, combustion air and combustion exhaust gas flow through the same route as in the first embodiment. In the preheating device 68, the combustion air flows through the set of curved bodies 69 extending from the inside to the outside in a spiral shape from the outside toward the inside, and is supplied to the air supply unit 34. The combustion exhaust gas flows from the gaps 70 between the curved bodies 69 of the innermost tubular body 71 to the gaps 7 of the inner and outer tubular bodies 71.
2 in the circumferential direction, and from the gap 70 between the curved bodies 69 of the second-stage tubular body 71 to the gap 72 formed by the tubular body 71 on the outer side thereof, in a stepwise spiral manner between the groups. It reaches the exhaust chamber 56. Although the combustion air and the combustion exhaust gas are heat-exchanged in the curved body 69, the heat exchange performance is high because the contact area and the path are long.

In the preheating device 68 according to the fifth embodiment, the temperature becomes lower toward the outer cylindrical body 71, and the cylindrical bodies 71 are structurally separated from each other. Therefore, the curved body 69 is made of a material suitable for the temperature level. Curved body 6 made of expensive heat-resistant material
By reducing 9, the cost can be reduced. Further, the flow velocity of the combustion exhaust gas can be set by the gap 70 between the curved bodies 69. The other functions are the same as those of the first embodiment, and the description thereof will be omitted.

By forming the diaphragm portion 39 shown in the first embodiment or the like on the curved body 69, the function of the diaphragm portion 39 can be added similarly to the first embodiment or the like.

[0072]

As is apparent from the above description of the embodiment, according to the invention of claim 1, the distribution of the combustion air to the air preheaters is made uniform, and the heat exchange portion has many layers. As a result, the heat exchange performance is good, the outer diameter of the combustion device can be made small, and the heat drive device can be made compact and the cost can be reduced. Also, the flow velocity of the combustion exhaust gas can be set to an arbitrary value depending on the interval between the air preheaters.

According to the invention of claim 2, in addition to the effect of claim 1, the contact area with the combustion exhaust gas in each air preheater can be increased, and the flow velocity of the combustion air is set to the air flow of each air preheater. Since it can be set to an arbitrary value depending on the road, the heat exchange performance is further improved.

According to the invention of claim 3, in addition to the effect according to claim 1 or claim 2, the temperature difference between the inner peripheral side and the outer peripheral side due to the combustion heat of each partition member separated by a gap is Since it can be made smaller and thermal stress is reduced, durability is increased.

According to the invention of claim 4, in addition to the effect according to claim 1 or claim 2, even if there is only one exhaust port, in the circumferential direction and axial direction of the combustion exhaust gas of the air preheater part. Since the flow velocity distribution of the air is made uniform and the heat transfer area of each air preheater effectively functions, the heat exchange performance is further improved.

According to the invention of claim 5, thermal deformation due to the temperature difference between the inner peripheral side and the outer peripheral side of the preheating device can be prevented, and the distribution of the combustion air can be equalized.
Since the heat exchange portion is composed of many layers, the heat exchange performance is good, the outer diameter of the combustion device can be made small, and the heat drive device can be made compact and the cost can be reduced.

According to the invention of claim 6, in addition to the effect of claim 5, the temperature difference between the inner peripheral side and the outer peripheral side due to the combustion heat of each partition member separated by a gap can be reduced, and the thermal stress can be reduced. The durability is increased.

According to the invention of claim 7, in addition to the effect according to claim 5, the combustion air flows in the inside of each hollow body of each air preheater in the double-row air passages extending in the radial direction. Since the air flow distribution in the hollow body is made uniform and the heat transfer area is widened, and turbulence can be induced in the flow of the combustion exhaust gas at the throttle portion, the heat exchange performance is further improved.

According to the invention of claim 8, in addition to the effect according to claim 5, the flow distribution of the air flowing through each hollow body is made uniform, the heat transfer area is widened, and the wavy throttle restricts the combustion air and the combustion exhaust gas. Since turbulence can be induced in both flows, the heat exchange performance is further improved.

According to the ninth aspect of the present invention, the curved body has a lower temperature as it constitutes the outer cylindrical body and can be made of a material according to the temperature level, so that the cost can be reduced and the heat exchange can be performed. Since the part is composed of many layers, the heat exchange performance is good and the outer diameter of the combustion device can be reduced.
Further, the flow velocity of the combustion exhaust gas can be set to an arbitrary value depending on the interval between the curved bodies forming the tubular body and the radial interval between the inner and outer tubular bodies.

According to the invention of claim 10, in addition to the effect of claim 9, the temperature difference between the inner peripheral side and the outer peripheral side due to the combustion heat of each partition member separated by a gap can be reduced, and the thermal stress is reduced. Therefore, the durability is increased.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a heat-driven heat pump device as a heat-driven device showing an embodiment of the present invention.

FIG. 2 is a sectional view of a combustion device in the heat-driven heat pump device according to the first embodiment of the present invention.

FIG. 3 is a front view of the air preheater according to the first embodiment of the present invention.

FIG. 4 is a plan view of the air preheater according to the first embodiment of the present invention.

FIG. 5 is a plan view showing a single air preheater according to the first embodiment of the present invention.

FIG. 6 is a front view showing a single air preheater according to the first embodiment of the present invention.

FIG. 7 is a sectional view of a combustion apparatus according to a second embodiment of the present invention.

FIG. 8 is a sectional view of a combustion apparatus according to a third embodiment of the present invention.

FIG. 9 is a plan view showing a preheating device according to a third embodiment of the present invention.

FIG. 10 is a sectional view showing an air preheater according to a third embodiment of the present invention.

FIG. 11 is a front view including a cross section showing a preheating device according to a fourth embodiment of the present invention.

FIG. 12 is a plan view showing a preheating device according to a fourth embodiment of the present invention.

FIG. 13 is a plan view showing a hollow body of an air preheater according to a fourth embodiment of the present invention.

FIG. 14 is a sectional view showing a hollow body of an air preheater according to a fourth embodiment of the present invention.

FIG. 15 is a sectional view of a combustion apparatus according to a fifth embodiment of the present invention.

FIG. 16 is an enlarged partial plan view of the preheating device according to the fifth embodiment of the present invention.

FIG. 17 is a configuration diagram showing a configuration of a conventional heat-driven heat pump device.

FIG. 18 is a cross-sectional view of a combustion device of another conventional heat driving device.

[Explanation of symbols]

 1 1st gas operation device 2 2nd gas operation device 3 Crank mechanism part 4 Crank mechanism part 5 Starter motor 9 High temperature side cylinder 10 High temperature side displacer 11 High temperature space 12 High temperature side medium temperature space 15 Heater pipe 16 Heat storage regenerator 17 High temperature side middle temperature part heat exchanger 18 Combustion device 19 Combustion chamber 20 Low temperature side cylinder 21 Low temperature side displacer 22 Low temperature space 23 Low temperature side medium temperature space 26 Low temperature side heat exchanger 27 Regenerator 28 Low temperature side middle temperature part heat exchanger 29 External communication Pipe 33 Fuel nozzle 34 Air supply part 36 Air preheater 37 Upper wall part 38 Bottom part 39 Throttling part 40 Air passage 41 Air supply pipe 42 Outer shell 44 Air passage 45 Air supply port 46 Partition member 51 Body shell 52 Partition wall member 54 Air swirling nozzle 55 Partition member 57 Exhaust port 58 Gap 59 Pressure equalizing cylinder 60 Air pre-load Vessel 61 gap 62 preheater 63 the hollow body 65 the air preheater 66 wavy stop 67 wave plate 68 preheater 69 flexure 70 gap 71 cylindrical body 72 gap

 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor Yoshio Adachi 1-3 Komaba-cho, Nakatsugawa-shi, Gifu Mitsubishi Electric Corporation Nakatsugawa Works (72) Inventor Mitsuo Fukuda 1-3-3 Komaba-cho, Nakatsugawa-shi, Gifu Mitsubishi Electric Nakatsugawa Mfg. Co., Ltd. (72) Inventor Hirotaka Hayashi 1-3 Komabacho, Nakatsugawa, Gifu Prefecture Mitsubishi Electric Co., Ltd. Nakatsugawa Mfg. Co., Ltd. (72) Keiichiro Utsunomiya 1-3, Komabacho, Nakatsugawa City, Gifu Mitsubishi Electric Corporation Company Nakatsugawa Works (72) Inventor Masaaki Haba 1-3 Komaba-cho, Nakatsugawa-shi, Gifu Mitsubishi Electric Corporation Nakatsugawa Works

Claims (10)

[Claims] 1. A high-temperature space and a medium-temperature space of a cylinder whose interior filled with a working gas is divided into a high-temperature space and a medium-temperature space by a reciprocating displacer, in order from the high-temperature space side to the medium-temperature space side. A first gas actuating device having a heating device for heating the heater pipe in the cylinder, which is connected to each other through a gas flow path including a heater pipe, a heat storage regenerator, and a heat exchanger, which are connected to each other, and a reciprocating displacer. The low temperature space and the medium temperature space of the cylinder whose interior filled with the working gas is divided into a low temperature space and a medium temperature space by
A second gas actuating device which is in communication with a low temperature side heat exchanger, a regenerator and a heat exchanger, which are connected in sequence from the low temperature space side to the medium temperature space side, and the first and second gases. A thermal drive device comprising: each gas flow path of the operating device; a communication part that communicates with each other on the side of the intermediate temperature space; and a crank mechanism part that reciprocates each of the displacers with a certain phase difference. The heating device is capped on the upper part of the cylinder of the first gas operating device, and faces a fuel nozzle for injecting fuel and an air supply unit for supplying combustion air in the vicinity of the fuel nozzle, and the heater is also provided. It is equipped with a combustion chamber as a cylindrical space that encloses a tube, and the outer periphery of the combustion chamber is a plurality of flat plate-like hollow air preheated vertically arranged in a substantially tangential direction from a position close to the outer diameter of the combustion chamber. Surrounded by vessels, above Combustion air introduced from a part of the outer shell of the firing device is split into each of the air preheaters, supplied to the air supply unit via each air preheater, and combustion exhaust gas generated in the combustion chamber is A thermal drive device characterized in that the heat is exhausted to the outside from a combustion chamber through each gap between the air preheaters and an exhaust port provided in a part of an outer shell of the combustion device. 2. The thermal drive device according to claim 1, wherein:
An air passage is integrally formed in a meandering shape in each of the air preheaters. Combustion air is introduced from an air supply pipe connected to one end of this air passage, and an air supply unit is introduced through the air supply pipe connected to the other end. A thermal drive device characterized in that it is configured to supply to the. 3. The heat drive device according to claim 1, further comprising: a partition wall member that forms upper and lower inner wall surfaces of an air preheater portion that continues to an upper portion and a lower portion of the combustion chamber. A thermal drive device characterized in that a gap is provided over the entire circumference in an intermediate portion in the radial direction. 4. The thermal drive device according to claim 1, wherein at least one of an inner end edge and an outer end edge of each air preheater extends over the entire vertical direction of the combustion chamber. A heat-driving device comprising a pressure equalizing cylinder having a large number of holes throughout. 5. The high temperature space and the medium temperature space of a cylinder, whose interior filled with a working gas by a reciprocating displacer, is divided into a high temperature space and a medium temperature space, from the high temperature space side to the medium temperature space side. A first gas actuating device having a heating device for heating the heater pipe in the cylinder, which is connected to each other through a gas flow path including a heater pipe, a heat storage regenerator, and a heat exchanger, which are connected to each other, and a reciprocating displacer. The low temperature space and the medium temperature space of the cylinder whose interior filled with the working gas is divided into a low temperature space and a medium temperature space by
A second gas actuating device which is in communication with a low temperature side heat exchanger, a regenerator and a heat exchanger, which are connected in sequence from the low temperature space side to the medium temperature space side, and the first and second gases. A thermal drive device comprising: each gas flow path of the operating device; a communication part that communicates with each other on the side of the intermediate temperature space; and a crank mechanism part that reciprocates each of the displacers with a certain phase difference. The heating device is capped on the upper part of the cylinder of the first gas operating device, and faces a fuel nozzle for injecting fuel and an air supply unit for supplying combustion air in the vicinity of the fuel nozzle, and the heater is also provided. A combustion chamber is provided as a cylindrical space that encloses a tube, and the outer periphery of the combustion chamber is surrounded by a preheating device in which a plurality of plane fan-shaped air preheaters are combined in a cylindrical shape with a gap between each other. Preheat each air Is a structure in which a fan-shaped flat plate-shaped hollow body is laminated on a plurality of air supply pipes with a space between each other, and combustion air introduced from a part of the outer shell of the combustion device The air supply pipe divides each hollow body of the preheater and supplies the exhaust gas generated in the combustion chamber from each hollow body to the air supply unit through the air supply pipe. A heat-driving device, characterized in that exhaust is provided to the outside through an exhaust port provided in a part of the outer shell of the combustion device through each gap between the hollow bodies of the preheater. 6. The thermal drive device according to claim 5, wherein:
A thermal drive device characterized in that a gap is provided over the entire circumference in a radial intermediate portion of a partition wall member that forms upper and lower inner wall surfaces of an air preheater portion continuing to an upper portion and a lower portion of a combustion chamber. 7. The thermal drive device according to claim 5, wherein:
A thermal drive device characterized in that a radial throttle is provided in each hollow body of each air preheater, and a plurality of rows of air passages extending in the radial direction are formed inside each hollow body. 8. The thermal drive device according to claim 5, wherein:
A heat-driving device, wherein each hollow body of each air preheater has a structure in which upper and lower corrugated plates provided with corrugated diaphragms are joined so that these corrugated diaphragms intersect. 9. A high temperature space and a medium temperature space of a cylinder, the interior of which is filled with a working gas by a reciprocating displacer and divided into a high temperature space and a medium temperature space, from the high temperature space side to the medium temperature space side in order. A first gas actuating device having a heating device for heating the heater pipe in the cylinder, which is connected to each other through a gas flow path including a heater pipe, a heat storage regenerator, and a heat exchanger, which are connected to each other, and a reciprocating displacer. The low temperature space and the medium temperature space of the cylinder whose interior filled with the working gas is divided into a low temperature space and a medium temperature space by
A second gas actuating device which is in communication with a low temperature side heat exchanger, a regenerator and a heat exchanger, which are connected in sequence from the low temperature space side to the medium temperature space side, and the first and second gases. A heat-driving device comprising: each gas flow path of the operating device; a communication part that communicates with each other on the side of the intermediate temperature space; and a crank mechanism part that reciprocates the displacers with a certain phase difference. The heating device is capped on the upper part of the cylinder of the first gas operating device, and faces the fuel nozzle for injecting fuel and an air supply unit for supplying combustion air in the vicinity of the fuel nozzle, and the heater is also provided. It is equipped with a combustion chamber as a cylindrical space that encloses the pipe. Multiple layers with a gap in Surrounded by a preheater that overlaps the curved bodies of the inner and outer cylindrical bodies with a staggered overlap, the combustion air introduced from a part of the outer shell of the combustion device is introduced from the outer side to the inner side of the cylindrical body. Toward the air supply part by flowing in a spiral shape through each of the curved bodies, and the combustion exhaust gas generated in the combustion chamber is swirled outward from the combustion chamber through a gap between the curved bodies. A heat-driving device, characterized in that it is exhausted from the outside of the outermost cylindrical body of the preheating device to the outside through an exhaust port provided in a part of the outer shell of the combustion device. 10. The heat-driving device according to claim 9, wherein a radial intermediate portion of a partition member forming upper and lower inner wall surfaces of a preheating device portion continuing to the inner wall surfaces of the upper and lower portions of the combustion chamber. A thermal drive device characterized in that a gap is provided over the entire circumference.