JP3899079B2 - Heat source equipment - Google Patents

Description

  The present invention relates to a heat source device including a Rankine cycle driven by a displacer type Stirling engine.

  Most household heat source devices today are powered by electricity transmitted from power plants. By the way, as shown in FIG. 5, the power generation efficiency in the power plant is usually about 40 to 45%, and when the loss of power transmission is about 10%, the electrical energy that can be used for the heat source device in each home is supplied by the power plant. It is only 30 to 35% of the energy such as oil, and the remaining 65 to 70% is wasted.

  For example, when heating is performed in each home, etc., when this electric energy is directly used as an electric heater, only 30 to 35% of heating heat can be used. On the other hand, when the motor is rotated by this electric energy and the heat pump is driven by this motor, if the operating efficiency (COP) of this heat pump is 3, 60 to 70% of the heat pumped up from the outside air is added, Although 90-105% of the heating heat can be used, in this case as well, 65-70% of the energy such as oil supplied at the power plant is wasted before being transmitted to each household. There is no change.

  For this reason, means for directly using an energy source such as oil in each household can be considered. For example, if oil or the like is burned, almost 100% of heat energy can be used for heating. However, it is not possible to use thermal energy that exceeds the energy of oil or the like. Therefore, conventionally, means for operating an absorption cycle with combustion heat of petroleum or the like, and means for driving an engine with oil or the like and operating a Rankine cycle with this engine have been adopted.

  For example, as shown in the lower part of FIG. 5, when an internal combustion engine is operated using petroleum as a direct fuel and the heat pump is driven by this internal combustion engine, the thermal efficiency η of the internal combustion engine is 0.25, the operating coefficient of the heat pump ( If COP) is 3, the heating heat can generate 150% heating heat, which is 75% exhaust heat of the internal combustion engine, 25% of the generated power of the internal combustion engine, and 50% of the heat generated from the outside air. it can. Further, when the outside air temperature is low, such as in winter, the coefficient of operation (COP) of the heat pump can be easily improved to about 6, for example, by absorbing heat from warmer groundwater. In this case, as indicated by the numbers in parentheses at the bottom of FIG. 5, 225% of the heating heat can be generated. In addition, for the same amount of energy, the price of petroleum fuel is about 1/5 of the price of electricity, and considering the difference in energy cost, further significant cost reduction is possible.

  However, the absorption cycle has a lower operating coefficient than the Rankine cycle. Therefore, the heat energy does not cost, for example, it is used when using exhaust heat or the like, and is not suitable for home use. Further, since lithium, bromine and ammonia are used as the working fluid, there is a possibility that it may become a problem in terms of environmental protection. On the other hand, as described above, the means for driving the Rankine cycle in the internal combustion engine has the following problems.

  That is, the conventional engine uses a reciprocating internal combustion engine, and therefore generally has a large noise and a short life. And since the heat source device for home needs a small driving force, a small engine is used, but this small internal combustion engine is particularly noisy, has low thermal efficiency, is inferior in durability, and starts more than anything else There are drawbacks such as poor performance and stability, and there are many practical problems. Second, it is difficult to seal a reciprocating compressor used in the Rankine cycle. In other words, in order to block refrigerant leakage from the gap between the piston and cylinder of the reciprocating compressor, it is necessary to make this gap as small as possible. On the other hand, if the gap is made too small, the frictional force between the two increases. , Loss increases. Therefore, it is difficult to completely block the leakage of the refrigerant, and the leaked refrigerant such as chlorofluorocarbon and ammonia can adversely affect the environment.

  Therefore, it is clear that the Rankine cycle using a reciprocating internal combustion engine that uses oil as fuel is, in principle, an extremely efficient means as a heat source device for home use. Therefore, no attractive and practical means have been proposed.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a heat source device that has low cost, low noise, excellent environmental resistance, high efficiency, high durability, and reliability.

  In order to solve the above-mentioned problems, a first feature of the heat source device according to the present invention includes a Displacer-type Stirling engine and a Rankine cycle heat pump, and the power piston of the Stirling engine is a reciprocating compression of the heat pump. It is to drive the machine. The cylinder of the reciprocating compressor is formed integrally with the cylinder at one end of the cylinder of the power piston, while the piston of the reciprocating compressor is formed integrally with the power piston at one end of the power piston. Has been.

  The heat pump includes a separator between a condenser and an expansion valve, the working fluid of the Stirling engine is helium gas, and the working fluid of the heat pump is all liquid at the outlet of the condenser. It is cooled to the state. The separator separates the helium gas from the working fluid of the heat pump, and the separated helium gas is recirculated to the Stirling engine, while the separated working fluid of the heat pump is supplied to the expansion valve. Is done.

  A second feature of the heat source device according to the present invention is that the expansion valve described in the feature 1 includes two expansion valves connected in series, and the separator is provided between the two expansion valves. There is to be. The reciprocating compressor can be switched between a suction path and a discharge path of the working fluid by a switching valve, and is located upstream of the two expansion valves in conjunction with the switching of the switching valve. The throttle function of the expansion valve is released.

  Here, the Displacer-type Stirling engine is a known technique, in which a power piston and a displacer arranged concentrically in a cylinder reciprocate each other and heat supplied from the outside. Energy is used to generate mechanical energy in the power piston. Rankine cycle is a well-known technique in which working fluid is compressed into high-temperature and high-pressure gas by a reciprocating compressor, dissipated by a condenser, expanded by an enthalpy with an expansion valve, and evaporated by a vaporizer to absorb heat. To do. If the heat dissipation of the condenser is used, a heat pump is obtained, and if the heat absorption of one vaporizer is used, a refrigerator or a cooling device is obtained. The heat source device means a device that can be used for either a cooling device or a heating device.

  The cylinder of the reciprocating compressor is formed integrally with the cylinder at one end of the cylinder of the power piston, which means that the working fluid in the cylinder does not leak to the outside from the joint between both cylinders. This includes not only the case where both cylinders are made of a single part but also the case where the cylinders are composed of a plurality of parts. In addition, the piston of the reciprocating compressor is integrally formed with the power piston at one end portion of the power piston, which means that both pistons are mechanically connected. This includes not only the case of being made of parts, but also the case of being composed of a plurality of parts, for example, where both are connected by a connecting rod.

  The operating fluid of the heat pump is all cooled to the liquid state at the outlet of the condenser. When the operating fluid of the heat pump is at the outlet of the condenser and enters the expansion valve, the condenser is cooled. This means that the liquid is cooled to the saturated liquid line or the liquid phase on the lower enthalpy side than the saturated liquid line, and the working fluid that can be used in this state is used for the standard Rankine cycle. For example, ammonia, R-134, R-407C, R600A and R-717 are applicable.

  The separator separates the helium gas from the working fluid of the heat pump, and between the piston and cylinder of the reciprocating compressor, the helium gas that is the working fluid of the Stirling engine mixed in the working fluid of the heat pump, It means to recover from the working fluid of this heat pump.

  The fact that the separator is provided between the two expansion valves means that the separator is provided between one outflow side and the other inflow side of the two expansion valves connected in series. When the switching function of the expansion valve located upstream of these two expansion valves is released in conjunction with the switching of the switching valve, the switching valve releases the working fluid suction path and the discharge path of the reciprocating compressor. When the switching operation with the path is performed, in conjunction with the switching operation, the throttle of the expansion valve on the upstream side of the two expansion valves as viewed from the flow direction of the working fluid is opened, and the expansion on the downstream side is performed. It means that only the valve performs the throttling function. Therefore, when using the heat radiation of the condenser, the pressure of the separator becomes the outlet pressure of this condenser. On the other hand, the flow direction of the working fluid is reversed using the switching valve, and the vaporizer is used as a condenser. In this case, the pressure of the separator becomes the outlet pressure of the vaporizer. That is, the pressure of the separator is the pressure after the working fluid is condensed in any case.

  In addition, releasing the throttle function of the upstream expansion valve is not limited to the case where the throttle of the expansion valve is completely opened and no pressure drop is caused, but the working fluid is liquid at the outlet of the upstream expansion valve. This includes the case where a pressure drop that can be maintained in the phase state occurs.

  By configuring the invention in this way, the following effects can be obtained. First, by using a Stirling engine, the drive engine of the reciprocating compressor can be made compact, lightweight, highly efficient and low noise, and durability, startability and stability can also be improved. . Secondly, by forming the cylinders of the Stirling engine and the reciprocating compressor constantly, leakage of the working fluid to the outside can be easily prevented, so that excellent environmental performance can be realized.

By integrally forming the piston of the Stirling engine and the reciprocating compressor,
The coupling structure of both can be made extremely small, simple, low cost and highly reliable. In addition, by using helium gas with the lowest specific heat as the working fluid of the Stirling engine, high Stirling engine thermal efficiency can be achieved, and since helium gas is an inert gas, it has excellent fire resistance and environmental performance can do.

  By separating and recovering the helium gas mixed in the working fluid of the heat pump by the separator and returning it to the Stirling engine, the Stirling engine can be continuously operated with the ideal helium gas. Therefore, the high thermal efficiency of the Stirling engine can be maintained. On the other hand, since the remaining working fluid from which the helium gas is separated is supplied to the vaporizer of the heat pump, it is possible to avoid a decrease in heat absorption efficiency in the vaporizer due to the mixing of the helium gas.

  By providing the separator at the outlet of the condenser, the following effects can be obtained. First, in the present invention, the working fluid of the heat pump is cooled to the liquid phase at the outlet of the condenser. Therefore, in the separator, the mixed helium gas can be easily separated as a gas from the working fluid of the heat pump in a liquefied state due to the difference in specific gravity. In the separator, the working fluid of the heat pump is cooled not to the mixed phase of liquid and vapor but to the liquid phase, so the vapor of this working fluid is not mixed into the separated helium gas. Only helium gas is returned to the Stirling engine.

  Next, by providing a separator at the outlet of the condenser and refluxing the separated helium gas to the Stirling engine, the outlet pressure of the condenser and the operating pressure of the Stirling engine can be made substantially the same level. Accordingly, it is possible to select various media used as the working fluid of the standard Rankine cycle, while the operating pressure of the Stirling engine can be set to a pressure that is not too high and that provides good thermal efficiency. That is, when the operating pressure of the Stirling engine is set to a high pressure, the size of the engine can be reduced, but the manufacturing cost increases and there is a problem in safety.

  If the separator is installed downstream of the expansion valve, the working fluid used in the standard Rankine cycle will have a low pressure after the separator has been reduced by the expansion valve. The pressure is too low to obtain good thermal efficiency. Furthermore, since the working fluid changes to an enthalpy change downstream of the expansion valve and is cooled to a mixed phase of vapor and liquid, it is not possible to separate only helium gas by the separator, and a large amount of working fluid vapor is helium. It will be mixed into the gas.

  A separator is provided between two expansion valves connected in series, and the reciprocating compressor can be switched in and out of the working fluid by a switching valve. In conjunction with the switching operation of the switching valve, the two expansion valves By releasing the throttling function of the expansion valve located on the upstream side, the heat source device can be used as a cooling device or a heating device while exhibiting the above-described effects only by switching the switching valve.

  In other words, if the flow direction of the working fluid from the reciprocating compressor is reversed, the working fluid is condensed by the vaporizer and then passed through the upstream expansion valve with the throttle opened, and then the helium gas is separated by the separator. Later, it can be expanded and cooled by an expansion valve on the downstream side, and vaporized by a condenser to absorb heat from the outside. Therefore, if one of the vaporizer or the condenser is installed indoors and the other is installed outdoors, the cooling / heating can be switched very easily only by switching the switching valve.

  The heat source device shown in FIG. 1 shows a case where it is used as a heater that draws heat Q2 from the outside and supplies heat Q1. That is, the heat source device drives the reciprocating compressor 21 of the Rankine cycle 2 by the power piston 11 of the displacer type Stirling engine 1, and the cylinder 21a of the reciprocating compressor is connected to the cylinder 13 of the power piston. It is integrally formed at the right end as the same part of this cylinder. The piston 21b of the reciprocating compressor 21 is integrally formed at the center of the right end portion of the power piston 11 as the same component of the power piston.

  Here, the configuration of the displacer type Stirling engine 1 will be described with reference to FIG. The displacer-type Stirling engine 1 includes a cylindrical cylinder 13, a power piston 11 and a displacer 14 that are concentrically arranged so as to slide on the inner peripheral surface of the cylinder and reciprocate opposite to each other. I have. A cylindrical projection is formed at the center of the left end surface of the power piston 11, and this projection is closely inserted into a cylindrical hole formed on the opposing surface of the displacer 14 to form a gas spring 14a. Yes.

  The cylinder 13 is accommodated in a container 15, and helium gas used as a working fluid is sealed in the container. The left side of the cylinder 13 is an open end, the left end surface of the displacer 14 and the left end portion of the container 15 form a left sealed space 16, and a combustion chamber 31 is provided outside thereof. The right side of the cylinder 13 is a closed end, and the above-described reciprocating compressor 21 is formed. On the outer periphery of the cylinder 13, a heat receiving heat exchanger 17 is located at a position corresponding to the left end face of the displacer 14, a heat radiation heat exchanger 19 is located at a position corresponding to the right end face, and a heat accumulator 18 is located between them. The AC generator 32 is wound around a position corresponding to the power piston 11.

  A central space 14 b is formed between the left end surface of the power piston 11 and the right end surface of the displacer 14, and this central space passes through the heat radiating heat exchanger 19, the heat accumulator 18, and the heat receiving heat exchanger 17. And communicated with the left sealed space 16. The central space 14 b communicates with the right sealed space 12 at a neutral position of the power piston via a through hole 13 a formed in the power piston 11 and the cylinder 13.

  Next, the operation of the displacer type Stirling engine 1 will be described. When the fuel supplied via the fuel adjustment device 33 burns in the combustion chamber 31, this combustion heat is supplied to the helium gas in the left sealed space 16 via the heat receiving heat exchanger 17. The helium gas in the left sealed space 16 and the central space 14b communicating therewith expands to push the power piston 11 to the right. Further, the gas spring 14 a moves to the right side while being compressed by the difference between the internal pressure and the pressure in the left sealed space 16. When the movement of the power piston 11 in the right direction is completed, the displacer 14 is pushed back to the left by the repulsive force of the compressed gas spring 14a, and the helium gas in the left sealed space 16 is moved into the central space 14b. During this movement, a part of the heat quantity of the helium gas is stored in the heat accumulator 18.

  Next, the helium gas in the central space 14b is radiated to the outside by the heat radiating heat exchanger 19 and contracts to move the power piston 11 in the left direction. Further, the gas spring 14a moves to the left side while expanding by the difference between the internal pressure and the pressure in the left sealed space 16. When the movement of the power piston 11 in the left direction is completed, the displacer 14 is pulled back to the right side by the restoring force of the expanded gas spring 14a, and the helium gas in the central space 14b is moved into the left sealed space 16. During this movement, a part of the amount of heat stored in the heat accumulator 18 is recovered in helium gas, and this heat recovery greatly improves the thermal efficiency.

  As described above, the Displacer type Stirling engine 1 receives heat energy from the outside, releases part of this heat energy, and converts the remaining heat energy into reciprocating kinetic energy of the power piston 11. The reciprocating motion between the power piston 11 and the displacer 14 described above is described by disassembling each motion. In practice, the resonance of the gas spring 14a is used to reciprocate the power piston and the displacer 14. The presser is reciprocated opposite to each other.

  Further, the AC generator 32 supports the reciprocating motion as a linear motor during the period from the start to the stabilization of the reciprocating motion, and after the stabilization, the AC generator 32 supplies necessary electricity and charges the battery. I do. The through hole 13a formed in the power piston 11 and the cylinder 13 causes the pressure difference between the central space 14b and the right end surface space of the power piston to be excessively large or small due to leakage from the outer peripheral sliding surface of the power piston 11. As a result, the spring constant of the gas spring 14a changes and the smooth operation cannot be maintained. Therefore, at the neutral position of the power piston, the central space and the suction pressure of the reciprocating compressor 21 as described later are made the same. The right-side sealed space 12 is communicated to prevent the pressure difference from becoming too large or too small.

  Next, the configuration of the Rankine cycle 2 will be described. The Rankine cycle 2 switches the reciprocating compressor 21 integrally formed at the right end portion of the Stirling engine 1 described above, the discharge path 22 and the suction path 23 of the working fluid communicating with the reciprocating compressor, and the discharge path and the suction path. And a switching valve 24. The discharge path 22 of the switching valve 24 is in communication with the condenser 25, the first expansion valve 26, and the separator 27 in this order. The separator 27 is formed of a simple sealed container, and is a path through which the liquefied working fluid accumulated at the bottom of the container and the gaseous helium gas accumulated at the top of the container flow out to the outside through the respective paths. have.

  The liquefied working fluid accumulated at the bottom of the container of the separator 27 returns to the suction path 23 of the reciprocating compressor 21 via the second expansion valve 28 and the vaporizer 29. The first expansion valve 26 located on the upstream side is released from the throttling function in conjunction with the switching operation of the switching valve 24. On the other hand, the vaporized helium gas accumulated in the upper part of the container of the separator 27 is introduced into the right-side sealed space 12 of the Stirling engine 1. In addition, the working fluid of Rankine cycle 2 uses R-407C as an example of the refrigerant | coolant used for a standard Rankine cycle.

  Next, the operation of Rankine cycle 2 will be described. The power piston 11 of the Displacer type Stirling engine 1 moves rightward, and the reciprocating compressor 21 integrally formed with the power piston 11 compresses the working fluid R-407C to form high-temperature and high-pressure steam, thereby discharging the discharge path. It flows into the condenser 25 via 22 and the switching valve 24. Next, the vapor of R-407C is condensed by releasing heat quantity Q1 to the outside air in the condenser 25, and is cooled to a liquid phase where all R-407C becomes liquid.

  Next, the liquefied R-407C is introduced into the separator 27 and collected at the bottom of the container constituting the separator. By the way, the gap between the inner peripheral surface of the cylinder 21a and the outer peripheral surface of the piston 21b of the reciprocating compressor 21 of the present invention is difficult to completely seal. It has a structure that allows internal leakage. Therefore, helium gas leaked through this gap is mixed into R-407C, which is the working fluid of Rankine cycle 2. The mixed helium gas is not liquefied in the condenser 25 and the first expansion valve 26 and is introduced into the separator 27 in a state of being mixed in the liquefied R-407C.

  Therefore, in the container constituting the separator 27, liquefied R-407C accumulates at the bottom due to the difference in specific gravity, and helium gas is separated at the top. As a result, the liquefied R-407C and the helium gas mixed therein are separated almost completely by the separator 27.

  Next, the liquefied R-407C accumulated at the bottom of the separator 27 flows from the lower part of the separator into the second expansion valve 28 where the throttling function is not released, where it is isenthalpy-expanded, It is introduced into the vaporizer 29. The vaporizer 29 absorbs heat Q2 from the outside and evaporates. The evaporated R-407C is sucked into the reciprocating compressor 21 via the switching valve 24 and the suction path 23. On the other hand, the helium gas separated in the upper part of the separator 27 is refluxed from the upper part of the separator 27 to the right sealed space 12 of the displacer type Stirling engine 1.

  As described above, Rankine cycle 2 efficiently pumps up heat quantity Q2 from the outside by evaporation of liquefied R-407C in vaporizer 29, and uses heat quantity Q1 obtained by adding this heat quantity and power of reciprocating compressor 21 as heating heat. From the condenser 25. On the other hand, since the helium gas leaked and mixed in the reciprocating compressor 21 is separated and recovered from R-407C liquefied by the separator 27, the displacer-type Stirling engine 1 is driven by the helium gas not mixed with R-407C. Continuous operation is possible.

  Now, FIG. 2 has shown the case where a heat-source apparatus is utilized as a cooling device. That is, the heat source device shown in FIG. 2 reverses the Rankine cycle 2 shown in FIG. 1 with the switching valve 24 to reverse the flow of the working fluid, and in conjunction with this switching valve switching operation, the throttle function of the second expansion valve 28 Is released, while the throttle function of the first expansion valve 26 is restored. In this case, the condenser 25 and the vaporizer 29, and the first expansion valve 26 and the second expansion valve 28 exhibit functions opposite to each other, and the working fluid is vaporized by the condenser 25. The heat quantity Q2 is absorbed from the outside and cooled. Then, the heat quantity Q1 obtained by adding the compression work of the reciprocating compressor 21 to the absorbed heat quantity Q2 is radiated from the vaporizer 29. Therefore, if one of the condenser 25 and the vaporizer 29 is installed indoors and the other is installed outdoors, the heating device and the cooling device can be switched and used only by switching the switching valve 24. can do.

  In FIG. 3, an example of the cycle process of Rankine cycle 2 is shown. Points 1h to 4h in FIG. 3 are an example used as the heating device shown in FIG. 1, and the outlet pressure (point 3h) of the condenser 25 is set to 1.2 to 1.6 MPa. That is, R-407C, which is a working fluid, is compressed into superheated steam by the reciprocating compressor 21 (point 2h), and then the heat quantity Q1 is dissipated to the outside by the condenser 25, and is cooled to the liquid phase at the same pressure (point 3h). Then, the first expansion valve 26 released from the throttling function passes through, and isenthalpy-expanded by the second expansion valve 28 (point 4h), and the heat quantity Q2 is absorbed from the outside by the vaporizer 29 (point 1h). In addition, at the point 3h on the outlet side of the first expansion valve 26, the mixed helium gas is separated by the separator 27.

  By the way, as described above, the sealing pressure of helium gas, which is the working fluid of the Stirling engine 1 of the displacer type, is substantially the same as the outlet pressure of the condenser 25 of the Rankine cycle 2. Therefore, in the above-described example, the sealing pressure of the helium gas is approximately 1.2 to 1.6 MPa, and the manufacturing cost of the displacer type Stirling engine 1 is reduced, and the pressure can be operated safely and efficiently. ing.

  Finally, the upper diagram in FIG. 4 shows an example of a heat bill when the heat source device is used as a heating device as shown in FIG. Here, the combustion efficiency η of the combustor 31 is 0.8, and the thermal efficiency η of the Stirling engine 1 is 0.3. Further, the heat absorption Q2 in the vaporizer 29 is pumped from the outside air of -5 [deg.] C., and the heat dissipation Q1 is performed at 35 [deg.] C. from the condenser 25. Under such conditions, the operating coefficient (COP) of Rankine cycle 2 can achieve 4.7. Under such conditions, when the heat pump operates as a standard Rankine cycle, that is, as the operation steps 1h, 2h, 3h, 4h, and 1h shown in FIG. 3, the amount of heat that can be supplied as heating is discharged from the combustor 31. Heat 0.2, exhaust heat from Stirling engine 1, 0.8 X (1.0-0.3) = 0.56, heat dissipation from Rankine cycle 2, 0.24 X 4.7 = 1. 13 is added to obtain 1.89. The amount of heat Q2 pumped up from the outside air is 1.13−0.24 = 0.89. Accordingly, it is possible to obtain 189%, that is, about twice the heating heat with respect to 1.0 of the consumed fuel energy.

  The lower diagram in FIG. 4 shows an example of the heat bill when the heat source device is used as a cooling device as shown in FIG. In this case, assuming that heat is radiated to the outside air of 35 ° C. and cold air of 15 ° C. is supplied, the standard Rankine cycle 2 can achieve a COP of 5.0. Therefore, the amount of heat Q2 that can be absorbed by the condenser 25 operating as a vaporizer is 0.24 X 5.0 = 1.20. Note that the heat release amount Q1 to the outside air is 1.20 + 0.24 = 1.44. The exhaust heat from the combustor 31 and the Stirling engine 1, 0.2 + 0.56 = 0.76, can also be used as a heat source for the water heater.

  Therefore, the heat source device according to the present invention can be used as a heater in winter and as a cooler in summer regardless of the season, and the fuel cost can be greatly reduced.

  It is also effective to improve the efficiency of the Rankine cycle 2 by exchanging the heat of the working fluid between the outlet of the condenser 25 and the inlet of the reciprocating compressor 21. Also, as shown by the broken lines in FIGS. 1 and 2, the flow rate of the supplied fuel and the degree of throttling between the first expansion valve 26 and the second expansion valve 28 according to the required load of the Rankine cycle 2, It is also effective to optimize the operating efficiency of the entire heat source device by controlling the flow rate so that the liquefied working fluid that has flowed in is vaporized 100% at the outlet of the vaporizer 29 or the condenser 25 without excess or deficiency. is there.

  The heat source device according to the present invention is small, light and low in noise and high in efficiency, and can improve durability, startability, stability and environmental resistance. Since it can be used as a cooling machine regardless of the season, it can be widely used in ordinary homes and other offices.

It is a whole block diagram in the case of using a heat source device as a heating device. It is a whole block diagram in the case of using a heat source device as a cooling device. It is the diagram which illustrated the relation between the Rankine cycle pressure and enthalpy. It is explanatory drawing which illustrated the heat bill of the heat source device. It is explanatory drawing which illustrated the heat bill of the heating apparatus by a prior art example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Stirling engine 11 Power piston 12 Right side sealed space 13 Cylinder 14 Displacer 15 Container 16 Left side sealed space 2 Rankine cycle 21 Reciprocating compressor 21a Cylinder 21b Piston 24 Switching valve 25 Condenser 26 1st expansion valve 27 Separator 28 2nd Expansion valve 29 carburetor 31 combustion chamber

Claims (2)

It has a Displacer type Stirling engine and a Rankine cycle heat pump,
The power piston of the Stirling engine drives the reciprocating compressor of the heat pump,
The cylinder of the reciprocating compressor is formed integrally with the cylinder at one end of the cylinder of the power piston,
The piston of the reciprocating compressor is formed integrally with the power piston at one end of the power piston,
The heat pump includes a separator between the condenser and the expansion valve,
The working fluid of the Stirling engine is helium gas,
The working fluid of the heat pump is all cooled to a liquid state at the outlet of the condenser,
The separator separates the helium gas from the working fluid of the heat pump;
The separated helium gas is refluxed to the Stirling engine,
The separated heat pump operating fluid is supplied to the expansion valve. In Claim 1, the said expansion valve consists of two expansion valves connected in series,
The separator is provided between the two expansion valves,
The reciprocating compressor is capable of switching between a suction path and a discharge path of the working fluid by a switching valve,
The heat source device, wherein the throttling function of the expansion valve located upstream of the two expansion valves is released in conjunction with the switching of the switching valve.

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