JP5370435B2 - Heat engine - Google Patents

Abstract

The heat engine has boiler section (11) in which working fluid (14) is heated by using heat supplied from heat source (2). An output section (12) converts vapor exhausted out of boiler section into mechanical energy. A condenser section (13) condenses vapor used in output section into working fluid. A working fluid introduction element (15) sucks working fluid due to capillary force in the condenser section, to introduce boiler section. A pump (16) is driven by mechanical energy, to introduce working fluid in condenser section into boiler section.

Description

  The present invention relates to a heat engine that heats and evaporates a working fluid, extracts the evaporated steam energy as mechanical energy, and then condenses and returns the steam, and is suitable for use in an exhaust heat recovery apparatus.

  Conventionally, this type of heat engine has a high pressure in the boiler section that evaporates the working fluid, whereas the condensing section that condenses (condensates) the steam has a low pressure. In general, a machine such as a pump is used to return the product to the factory (for example, Patent Document 1). That is, by driving a device such as a pump using external energy, the hydraulic fluid in the condensing unit is pumped and returned to the boiler unit.

  Conventionally, as this type of heat engine, one having a steam engine for converting steam energy into mechanical energy and a mechanical pump linked to the steam engine is also known.

JP-A-8-338207

  As in the former prior art (Patent Document 1), in a heat engine in which the working fluid condensed in the condensing unit is returned to the boiler unit by a machine such as a pump, the working fluid is heated and evaporated to external energy (thermal energy). In addition, since external energy for driving a machine such as a pump is also required, there is a limit in improving output efficiency.

  Therefore, the present inventor has studied a heat engine that sucks the hydraulic fluid condensed in the condensing unit with the capillary force of the wick (working fluid introducing member) and sends it back to the boiler unit. According to this examination example, the working fluid in the condensing unit can be sent back to the boiler unit without using external energy as much as possible, so that the output efficiency can be improved compared to the former prior art (Patent Document 1).

  In this study example, if the boiler pressure is increased in order to improve the output, it is necessary to reduce the capillary equivalent diameter of the wick to prevent the backflow of steam.

  However, in this examination example, if the capillary equivalent diameter of the wick is reduced in order to increase the boiler pressure, the area of the hydraulic fluid supply path is reduced and the hydraulic fluid supply speed is reduced. If the supply speed of the hydraulic fluid decreases, the amount of steam per hour decreases, and there is a problem that it is difficult to improve both the boiler pressure and the amount of steam.

  In the latter prior art, since the mechanical pump does not operate unless the steam engine moves, a starter for starting the steam engine with power from another is required. Therefore, for example, in a use condition where the heat source is unstable and the steam engine stops occasionally, a control system that starts the starter according to the state of the heat source is required if the steam engine is automatically restarted. .

  In view of the above points, an object of the present invention is to provide a heat engine that can achieve both an improvement in boiler pressure and an improvement in the amount of steam and can easily start operation.

In order to achieve the above object, in the invention according to claim 1, a boiler section (11) for heating and evaporating the working fluid (14) with heat supplied from the heat source (2),
An output part (12) for converting steam energy generated in the boiler part (11) into mechanical energy and taking it out;
A condensing unit (13) for condensing the steam used in the output unit (12);
Refluxing means (15, 16) for refluxing the working fluid (14) of the condensing part (13) to the boiler part (11),
The reflux means is
A working fluid introduction member (15) that sucks the working fluid (14) of the condensing unit (13) by capillary force and guides it to the boiler unit (11);
A mechanical pump (16) that is driven by mechanical energy extracted by the output unit (12) and that pumps the hydraulic fluid (14) of the condensing unit (13) to the boiler unit (11). Features.

  According to this, since it has the mechanical pump (16) driven by the mechanical energy taken out by the output part (12), the supply speed of the working fluid (14) by the working fluid introduction member (15) The hydraulic fluid (14) can be supplied to the boiler part (11) without being affected as much as possible. For this reason, it is possible to achieve both an improvement in boiler pressure and an improvement in the amount of steam.

  Further, even when the mechanical pump (16) is stopped, the hydraulic fluid (14) can be supplied to the boiler section (11) by the hydraulic fluid introduction member (15). For this reason, the operation start is easy.

  In the invention according to claim 2, in the heat engine according to claim 1, the ratio between the flow rate of the steam used in the output section (12) and the supply flow rate of the hydraulic fluid (14) by the mechanical pump (16) is It is larger than 1, and it is below the volume expansion coefficient when a hydraulic fluid (14) evaporates, It is characterized by the above-mentioned.

  According to this, the excess and deficiency of the supply amount of the hydraulic fluid (14) to the boiler part (11) can be suppressed, which is preferable.

In the invention according to claim 3, in the heat engine according to claim 1 or 2, the output section (12) has a steam engine (121) for converting steam energy into mechanical energy,
The steam engine (121) is a pendulum engine having a piston (121a) and a cylinder (121b) that swing like a pendulum,
The mechanical pump (16) is a pendulum pump having a piston (16a) and a cylinder (16b) that swing like a pendulum,
The steam engine (121) and the mechanical pump (16) are arranged on the upper side of the boiler part (11), and are characterized by swinging in the horizontal direction.

  According to this, steam can be efficiently supplied from the boiler section (11) to the steam engine (121), and the mechanism for connecting the steam engine (121) and the mechanical pump (16) can be simplified. .

In the heat engine according to any one of claims 1 to 3, for example, as in the invention according to claim 4, the hydraulic fluid introduction member (15) is formed in a cylindrical shape,
In the boiler part (11), a steam generation space (114) in which the hydraulic fluid (14) is heated and evaporated is formed,
The condensing part (13) is formed with a liquid storage space (131) in which the hydraulic fluid (14) is stored,
The steam generation space (114) is formed on either the inner side or the outer side of the hydraulic fluid introduction member (15),
The liquid reservoir space (131) is formed on the side opposite to the side on which the steam generation space (114) is formed, inside and outside the hydraulic fluid introduction member (15),
The mechanical pump (16) may suck the hydraulic fluid (14) from the liquid reservoir space (131) and discharge the hydraulic fluid (14) to the steam generation space (114).

According to a fifth aspect of the present invention, in the heat engine according to any one of the first to third aspects, the boiler section (11), the output section (12), the condensing section (13) and the mechanical pump (16) A case (101) for housing
Inside the case (101) is formed a liquid storage space (131) in which the working fluid (14) condensed in the condensing part (13) is stored,
The mechanical pump (16) is characterized in that at least a portion where the hydraulic fluid (14) flows is disposed in the hydraulic fluid (14) of the liquid storage space (131).

  According to this, since it is not necessary for the mechanical pump (16) to suck up the hydraulic fluid (14), the mechanical pump (16) can be operated well even if the pressure in the case (101) is lowered. For this reason, it becomes possible to deal with a lower temperature heat source.

In invention of Claim 6, in the heat engine of Claim 5, the output part (12) is arrange | positioned above the boiler part (11),
The mechanical pump (16) is arranged above the output part (12),
A partition member (20) for separating the output portion (12) from the hydraulic fluid (14) in the liquid storage space (131) is provided inside the case (101).

  According to this, since the boiler part (11), the output part (12), and the mechanical pump (16) are arranged side by side in the vertical direction, the machine without increasing the size of the case (101) in the horizontal direction. A pump (16) can be placed in the hydraulic fluid (14).

  Moreover, since the output part (12) is separated from the hydraulic fluid (14) of the liquid storage space (131) by the partition member (20), the hydraulic fluid (14) is prevented from entering the output part (12). Can be prevented.

  Further, since the space inside the partition wall member (20) is thermally insulated from the outside air by the hydraulic fluid (14) in the liquid storage space (131), the output portion (12) housed inside the partition wall member (20) is provided. High temperature can be maintained. For this reason, it can suppress that the vapor | steam which entered into the output part (12) cools, and a vapor pressure falls, and can improve efficiency by extension.

  In the invention according to claim 7, in the heat engine according to claim 6, the partition member (20) has an exhaust pipe (203) for exhausting the steam used in the output part (12) to the condensing part (13). ) Is formed so as to extend above the liquid level (14a) of the hydraulic fluid (14).

  Thereby, the vapor | steam discharged | emitted from the output part (12) can be discharged | emitted to a condensation part (13), preventing hydraulic fluid (14) permeating into the inside of a partition member (20).

According to an eighth aspect of the present invention, in the heat engine according to the seventh aspect, the power transmission mechanism (123, 125, 16i, 121h) that transmits the power extracted by the output section (12) to the mechanical pump (16). )
The power transmission mechanism is connected to the mechanical pump (from the output section (12) via the internal space of the exhaust pipe (203) and the space (132) above the liquid level (14a) of the hydraulic fluid (14). 16).

  Thereby, the power transmission mechanism can be efficiently arranged by utilizing the internal space of the exhaust pipe (203).

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a longitudinal cross-sectional view which shows the waste heat recovery apparatus in 1st Embodiment. It is a cross-sectional view showing the exhaust heat recovery apparatus in the first embodiment. It is sectional drawing which shows the steam engine of the waste heat recovery apparatus in 1st Embodiment. It is explanatory drawing explaining the manufacturing method of the wick in 1st Embodiment. It is a longitudinal cross-sectional view which shows the waste heat recovery apparatus in 2nd Embodiment. It is a longitudinal cross-sectional view which shows the waste heat recovery apparatus in 3rd Embodiment. It is the top view and sectional drawing which show the steam engine in other embodiment.

(First embodiment)
A first embodiment will be described with reference to FIGS. In this embodiment, a heat engine is applied to an exhaust heat recovery device. FIG. 1 is a longitudinal sectional view showing the overall configuration of the exhaust heat recovery apparatus, and the up and down arrows in FIG. 1 indicate the up and down direction (top and bottom direction) in the installed state of the exhaust heat recovery apparatus.

  The exhaust heat recovery apparatus 10 according to the present embodiment is roughly divided into a boiler unit 11, an output unit 12, and a condensing unit 13. In this example, the generator 1 is attached to the exhaust heat recovery apparatus 10 in order to use the mechanical energy extracted by the exhaust heat recovery apparatus 10 for power generation.

  The boiler unit 11 evaporates by heating the hydraulic fluid 14 (in this example, water) with heat (exhaust heat) supplied from a heat source. The output unit 12 converts steam energy generated in the boiler unit 11 into mechanical energy and outputs the mechanical energy. The condensing unit 13 condenses the steam used in the output unit 12 and condenses it into the working fluid 14.

  In this example, the boiler unit 11, the output unit 12, and the condensing unit 13 are provided inside the case 101. In this example, since water is used as the working fluid 14, the case 101 is preferably formed of stainless steel having excellent water resistance. The case 101 has a cylindrical portion 101a extending in the vertical direction, and lid portions 101b and 101c that close up and down the cylindrical portion 101a.

  The boiler unit 11 has a heat transfer member 111. The heat transfer member 111 is formed of a material (metal material or the like) excellent in thermal conductivity, and is placed on the heating element 2 that forms a heat source.

  The heat transfer member 111 includes plate-like heat transfer portions 111a and 111b arranged to face each other with an interval in the vertical direction, and a rod-like heat transfer portion 111c that connects the center portions of the plate-like heat transfer portions 111a and 111b. ing. In this example, the heating element 2 represents a part that generates heat by exhaust heat, such as a high-temperature exhaust / high-temperature drain duct surface of a factory.

  A wick 15 corresponding to a hydraulic fluid introduction member is disposed on the outer peripheral side of the rod-shaped heat transfer portion 111c. Here, the hydraulic fluid introduction member defines a member that generates a capillary force that sucks the hydraulic fluid 14 (capillary force generation member). For example, a structure in which fibers are knitted, a porous ceramic, It is a porous body such as a sintered metal body and a gasket seal.

  The wick 15 constitutes a reflux means for refluxing the working fluid 14 of the condensing unit 13 to the boiler unit 11. In this example, the wick 15 is formed in a cylindrical shape and arranged to extend in the vertical direction. Inside the wick 15, a rod-shaped heat transfer portion 111c penetrates.

  The wick 15 may be composed of one cylindrical member, or may be composed of a plurality of cylindrical members. In other words, the entire wick 15 may be integrally formed, or the wick 15 may be divided and formed in the axial direction.

  The wick 15 is a fiber assembly (fiber layer laminate) having a plurality of fiber layers laminated to each other, and in this example, is a mixture of aramid fibers, which are thermoplastic resin fibers, and rock wool particles. The wick 15 may be a mixture of aramid fibers and glass wool particles. Here, the mixture of an aramid fiber and rock wool particles, or a mixture of an aramid fiber and glass wool particles can also be used as a heat insulating material.

  The wick 15 is formed by integrally joining a large number of laminated annular plate materials. In FIG. 1, for convenience of illustration, the interface portion between the annular plate materials is indicated by a solid line. Further, the interface between the annular plate-like materials of the wick 15 extends in the radial direction of the wick 15 (a direction orthogonal to the axial direction).

  Although not shown, each fiber layer of the wick 15 extends in parallel with the interface between the annular plate materials. Therefore, each fiber layer of the wick 15 also extends in the radial direction of the wick 15 (a direction orthogonal to the axial direction).

  The rod-shaped heat transfer portion 111 c passes through the center of the lid portion 101 c on the lower side of the case 101. An annular plate-shaped interposition member 112 is disposed between the lid portion 101 c and the lower end surface of the wick 15. An annular plate-shaped interposition member 113 is also disposed between the upper end surface of the wick 15 and the upper plate-shaped heat transfer portion 111b. The annular plate-shaped interposition members 112 and 113 have substantially the same outer diameter and inner diameter as the cylindrical wick 15.

  A steam generation space 114 is formed between the inner peripheral surface of the cylindrical wick 15 and the outer peripheral surface of the rod-shaped heat transfer portion 111c. The steam generation space 114 is a space where the steam of the working fluid 14 is generated.

  A steam passage 115 communicating with the steam generation space 114 is formed in the upper plate-shaped heat transfer section 111b. The steam passage 115 is a passage that guides the steam in the steam generation space 114 to the output unit 12.

  A liquid reservoir space 131 is formed between the outer peripheral surface of the cylindrical wick 15 and the inner wall surface of the cylindrical portion 101 a of the case 101. The hydraulic fluid 14 is stored in the liquid storage space 131.

  A pressure difference is generated inside the wick 15 by capillary action. Hereinafter, the pressure difference due to the capillary phenomenon is referred to as a pressure ΔP due to the capillary force of the wick 15. The pressure ΔP due to the capillary force of the wick 15 is expressed by the following formula (1).

ΔP = (2σ / r) · cos θ (1)
However, r is the equivalent circle radius (capillary radius) of the void in the wick 15, σ is the surface tension, and θ is the wetting angle. The circle-equivalent radius is a radius of a circle having the same area as the target cross section.

  When the pressure ΔP due to the capillary force of the wick 15 is generated, the hydraulic fluid 14 in the liquid reservoir space 131 is sucked from the outer peripheral surface of the wick 15.

  The wick 15 is compressed by receiving a load in the axial direction from the interposition members 112 and 113 in a state where the wick 15 is assembled in the case 101. The wick 15 is swollen by the hydraulic fluid 14. Thereby, the air gap in the wick 15 is further reduced.

  By reducing the gap in the wick 15, the circle equivalent radius r of the gap in the wick 15 in Equation 1 is reduced, and the pressure ΔP due to the capillary force of the wick 15 is also increased. In this example, the pressure ΔP due to the capillary force of the wick 15 is made larger than the pressure difference (PH−PL) between the pressure PH in the steam generation space 114 and the pressure PL in the liquid storage space 131 (ΔP> PH-PL).

  In other words, the wick 15 is configured to satisfy the relationship of the following mathematical formula (2).

(2σ / r) · cos θ> PH-PL (2)
In this example, the wick 15 is formed of a heat insulating material having excellent heat insulating properties. Therefore, the wick 15 also functions as a heat insulating material that blocks heat transfer from the rod-shaped heat transfer portion 111c to the working fluid 14 in the liquid storage space 131.

  The hydraulic fluid 14 absorbed from the outer peripheral surface of the wick 15 reaches the steam generation space 114 due to the capillary force of the wick 15, is heated and evaporated by the rod-shaped heat transfer section 111 c, and becomes steam, through the steam generation space 114 and the steam passage 115. It flows to the steam engine 121 of the output unit 12.

  The steam engine 121 of the output unit 12 is a fluid machine that converts the energy of the steam generated in the boiler unit 11 into mechanical energy. In this example, a pendulum engine in which a piston and a cylinder swing like a pendulum is used as the steam engine 121. A steam turbine or the like may be used instead of the steam engine 121.

  The steam engine 121 is disposed on the upper side of the plate-like heat transfer unit 111b. In this example, the steam engine 121 is fixed to the upper surface of the plate-shaped heat transfer section 111b via the plate-shaped base member 102.

  A mechanical pump 16 is also fixed on the upper surface of the plate-like base member 102. The mechanical pump 16 is a fluid machine that converts mechanical energy into the energy of the hydraulic fluid 14, and constitutes a reflux unit that causes the hydraulic fluid 14 of the condensing unit 13 to return to the boiler unit 11.

  In this example, the configuration of the mechanical pump 16 is the same as the configuration of the steam engine 121. That is, as the mechanical pump 16, a pendulum pump in which a piston and a cylinder swing like a pendulum is used. A volume pump or the like may be used as the mechanical pump 16.

  FIG. 2 is a cross-sectional view of the exhaust heat recovery apparatus of FIG. In the example of FIG. 2, three steam engines 121 (three cylinders) are provided and one mechanical pump 16 (one cylinder) is provided, but the number of steam engines 121 and mechanical pumps 16 (number of cylinders). May be changed as appropriate.

  FIG. 3 is a cross-sectional view showing the steam engine 121 of FIG. Since the configuration of the mechanical pump 16 is the same as that in FIG. 3, the reference numerals corresponding to the mechanical pump 16 are given in parentheses in FIG. 3, and detailed drawings of the mechanical pump 16 are omitted.

  The steam engine 121 has a piston 121a and a cylinder 121b. The cylinder 121b is supported by a cylinder base 121c fixed to the base member 102 so as to be swingable about a swing shaft 121d.

  In the base member 102 and the cylinder base 121c, intake passages 102a and 121e communicating with the steam passage 115 of the boiler unit 11 are formed. The intake passages 102a and 121e are passages through which steam sucked into the cylinder 121b flows. An exhaust passage 121f is formed in the cylinder base 121c. The exhaust path 121f is a flow path through which the steam discharged from the cylinder 121b flows. An outlet portion of the intake passage 121e and an inlet portion of the exhaust passage 121f are opened on the upper surface of the cylinder base 121c. The outlet portion of the exhaust path 121 f is open to the internal space of the case 101. In this example, the outlet part of the exhaust passage 121f is opened to the condensing space 132 of the condensing part 13 shown in FIG.

  In this example, the piston 121a and the cylinder 121b are arranged in the horizontal direction, and the swing shaft 121d is arranged in the vertical direction. Therefore, the piston 121a and the cylinder 121b swing in the horizontal direction.

  A port 121g for sucking and exhausting steam is opened on the lower surface of the cylinder 121b. In a state where the cylinder 121b is located on one end side in the swing direction, the port 121g communicates with the intake passages 102a and 121e. In a state where the cylinder 121b is located on the other end side in the swinging direction, the port 121g communicates with the exhaust passage 121f.

  When the cylinder 121b is positioned at one end side in the swinging direction and the port 121g communicates with the intake passages 102a and 121e, the steam in the steam generation space 114 of the boiler unit 11 flows into the steam passage 115, the intake passages 102a and 121e, and the port. It flows into the cylinder 121b through 121g, and the piston 121a is pushed out to move forward.

  The tip of the piston 121a is connected to the wheel gear 121i via a rod 121h. As shown in FIG. 2, the wheel gear 121 i is connected to the center gear 122. An output shaft 123 is fixed at the center of the center gear 122. Accordingly, when the piston 121a is pushed out, the output shaft 123 rotates through the wheel gear 121i and the center gear 122.

  Further, when the piston 121a is pushed out and the wheel gear 121i rotates, the cylinder 121b swings toward the other end side in the swing direction, and the port 121g is closed by the upper surface of the cylinder base 121c.

  When the port 121g is closed, the wheel gear 121i continues to rotate due to the inertial force, and the piston 121a is pushed back by the inertial force of the wheel gear 121i to return. Also at this time, the swing of the cylinder 121b is continued. When the cylinder 121b is positioned on the other end side in the swinging direction and the port 121g communicates with the exhaust path 121f, the vapor in the cylinder 121b is discharged to the internal space of the case 101 (the condensing space 132 of the condensing unit 13). .

  As shown in FIG. 1, the output shaft 123 of the output unit 12 and the rotating shaft 1 a of the generator 1 are connected by a magnet coupling via a lid 101 b on the upper side of the case 101. Electric power is generated by the generator 1 by the rotation of the rotating shaft 1a. The generated electric power is supplied to an arbitrary electric device (not shown) connected to the generator 1.

  The condensing unit 13 has the liquid storage space 131 and the condensing space 132 described above. The condensing space 132 is a space in which the steam exhausted from the steam engine 121 is condensed and returned to the working fluid 14. In this example, the condensing space 132 is configured as an upper space in the internal space of the case 101.

  The liquid storage space 131 is a space for storing the hydraulic fluid 14 that has been condensed in the condensing space 132, and is formed in the case 101 below the condensing space 132. In order to allow the liquid storage space 131 and the condensing space 132 to communicate with each other, gaps are provided between the tubular portion 101a and the base member 102 of the case 101 and between the tubular portion 101a and the plate-like heat transfer portion 111b. It has been.

  As indicated by reference numerals in parentheses in FIG. 3, the mechanical pump 16 has a piston 16a and a cylinder 16b. The cylinder 16b is supported so as to be swingable about a swing shaft 16d with respect to a cylinder base 16c fixed to the base member 102.

  A liquid absorption path 16e is formed in the cylinder base 16c. The liquid suction path 16e is a flow path through which the working fluid 14 sucked into the cylinder 16b flows. The outlet portion of the liquid absorption path 16e opens on the upper surface of the cylinder base 121c. The inlet of the liquid absorption path 16e communicates with the outlet of the liquid absorption pipe 17 shown in FIG.

  In the example of FIG. 1, the inlet portion of the liquid suction path 16 e communicates with the outlet portion of the liquid suction pipe 17 through the hydraulic fluid passage formed in the base member 102. The inlet of the liquid absorption pipe 17 is disposed in the liquid storage space 131.

  As shown in FIG. 3, a discharge passage 16f is formed in the cylinder base 16c. The liquid discharge path 16f is a flow path through which the hydraulic fluid 14 discharged from the cylinder 16b flows. Although not shown in FIG. 3, the discharge channel 16f penetrates the cylinder base 121c, and the inlet of the discharge channel 16f opens on the upper surface of the cylinder base 121c, and the outlet of the discharge channel 16f. Is in communication with the inlet of the spout pipe 18 shown in FIG.

  In the example of FIG. 1, the outlet portion of the liquid discharge passage 16 f communicates with the inlet portion of the liquid discharge pipe 18 through a hydraulic fluid passage formed in the base member 102.

  The outlet of the spout pipe 18 communicates with the steam generation space 114 of the boiler unit 11. In the example of FIG. 1, the outlet portion of the discharge pipe 18 communicates with the steam generation space 114 via the hydraulic fluid passage formed in the interposed member 112 of the boiler portion 11.

  In this example, the piston 16a and the cylinder 16b are disposed in the horizontal direction, and the swing shaft 16d is disposed in the up-down direction. Therefore, the piston 16a and the cylinder 16b swing in the horizontal direction.

  A port 16g for sucking and discharging the hydraulic fluid 14 is opened on the lower surface of the cylinder 16b. In a state where the cylinder 16b is positioned on one end side in the swinging direction, the port 16g communicates with the liquid absorption path 16e. In a state where the cylinder 16b is positioned on the other end side in the swinging direction, the port 16g communicates with the liquid discharge path 16f.

  The tip of the piston 16a is connected to the wheel gear 16i via a rod 16h. As shown in FIG. 2, the wheel gear 16 i is connected to the center gear 122. Thus, when the steam engine 121 rotates the center gear 122, the wheel gear 16i also rotates, the cylinder 16b swings, and the piston 16a reciprocates.

  In the example of FIG. 2, the rotation of the wheel gear 16 i is decelerated with respect to the rotation of the wheel gear 121 i of the steam engine 121.

  In a state in which the piston 16a is pulled out from the cylinder 16b and moves forward, the cylinder 16b is positioned at one end side in the swinging direction, and the port 16g communicates with the liquid suction path 16e. As a result, the hydraulic fluid 14 in the liquid reservoir space 131 is sucked into the cylinder 16b via the liquid suction pipe 17 and the intake passage 16e.

  In a state where the piston 16a is pushed back to the cylinder 16b side and moves backward, the mechanical pump 16 is disposed on the side of the boiler unit 11 on the other end side in the swinging direction of the cylinder 16b. Positioned and the port 16g communicates with the discharge channel 16f. As a result, the hydraulic fluid 14 in the cylinder 16b is discharged into the steam generation space 114 of the boiler unit 11 through the discharge passage 16f, the discharge pipe 18 and the like.

  Next, an outline of a manufacturing method of the wick 15 will be described with reference to FIG. First, as shown in FIG. 4A, a plate material W1 is prepared.

  The plate-like material W1 is a fiber assembly (fiber layer laminate) having a plurality of fiber layers laminated to each other, and is formed to a predetermined thickness by repeating the paper-making method. In this example, the plate-like material W1 is a mixture of aramid fibers, which are thermoplastic resin fibers, and rock wool particles. In this example, a thin material having a thickness of about 4 mm is used as the plate-like material W1.

  FIG. 4B is an enlarged view of a portion A in FIG. In FIG.4 (b), the interface between fiber layers is shown as the continuous line for convenience of illustration. As shown in FIG. 4B, the plurality of fiber layers constituting the plate material W1 are stacked in the thickness direction of the plate material W1. In other words, the plurality of fiber layers constituting the plate material W1 extend in parallel with the plate surface of the plate material W1.

  Next, as shown in FIG. 4C, the plate material W1 is cut to obtain a large number of ring plate materials W2. At this time, the inner and outer diameters of a large number of annular plate-like materials W2 are made to be the same.

  Next, as shown in FIG. 4D, a large number of annular plate materials W2 are stacked in the thickness direction to obtain a cylindrical array W3. In the cylindrical array W3 obtained in this way, the fiber layer extends in the radial direction (direction orthogonal to the axial direction).

  Next, as shown in FIG. 4 (e), the annular array material W2 of the array body W3 is joined to each other by setting the cylindrical array body W3 on the jigs J1, J2, and J3 and performing hot pressing. A cylindrical wick 15 can be obtained.

  In the wick 15 thus obtained, the fiber layer extends in the radial direction (direction orthogonal to the axial direction). And in the interface part of the fiber layers of the wick 15, the continuity of a space | gap becomes higher than the remaining site | part (site | part which comprises a fiber layer). For this reason, the wick 15 has a structure in which a portion where the continuity of the gap is high extends in the radial direction (direction orthogonal to the axial direction).

  In this example, the jigs J1, J2, and J3 are constituted by a stainless steel ring J1, a stainless steel circular plate J2, and a stainless steel cylinder J3. As processing conditions for the hot press, for example, temperature: 300 ° C., pressure: 50 tons, press time: 20 minutes are preferable. That is, the annular plate materials W2 can be joined to each other by hot pressing at a temperature at which the aramid fibers (thermoplastic resin) of the annular plate materials W2 are softened.

  After the pressing time has elapsed, the gap between the fibers can be reduced by cooling while applying pressure and compressing. Moreover, since the contact | adhesion power of fibers can be raised by cooling with applying pressure and compressing, the intensity | strength of the wick 15 can be raised.

  Next, operation in the above configuration will be described. First, the operation in a steady state will be described. In the boiler unit 11, the heat of the heating element 2 is transmitted to the working fluid 14 in the steam generation space 114 via the heat transfer member 111, and the working fluid 14 is heated and evaporated in the steam generation space 114. The steam generated in the steam generation space 114 is supplied to the steam engine 121 of the output unit 12 through the steam passage 115.

  The steam supplied to the steam engine 121 drives the piston 121a. Thereby, the energy of the steam is converted into mechanical energy. The output shaft 123 is rotated by driving the piston 121 a, and power is generated by the generator 1. In this way, the exhaust heat energy of the heating element 2 is recovered as electric energy.

  The steam in the steam engine 121 is discharged into the condensing space 132 of the condensing unit 13 through the exhaust passage 121f after driving the piston 121a. The steam discharged from the steam engine 121 to the condensing space 132 is condensed in the condensing space 132 and returned to the working fluid 14. The working fluid 14 that has been condensed in the condensing space 132 is stored in the liquid storage space 131.

  When the output shaft 123 is rotated by driving the piston 121 a of the steam engine 121, the piston 16 a of the mechanical pump 16 is driven, and the hydraulic fluid 14 in the liquid storage space 131 is pumped to the steam generation space 114 of the boiler unit 11.

  Then, the hydraulic fluid 14 pumped to the steam generation space 114 by the mechanical pump 16 is heated in the steam generation space 114 and evaporates. The above operation is repeated to operate constantly.

  It should be noted that the ratio of the flow rate (volume flow rate) of the steam used in the output unit 121 and the supply flow rate (volume flow rate) of the working fluid 14 by the mechanical pump 16 (the working flow rate of steam in the output unit 121 / the working fluid by the mechanical pump 16). 14 supply flow rate) is preferably larger than 1 and not more than the volume expansion coefficient when the working fluid 14 is vaporized.

  More specifically, the ratio of the intake flow rate (volume flow rate) of the steam engine 121 and the discharge flow rate (volume flow rate) of the mechanical pump 16 (intake flow rate of the steam engine 121 / discharge flow rate of the mechanical pump 16) is activated. It is preferable that the volume expansion coefficient when the liquid 14 is vaporized is made as equal as possible. This is because an excess or deficiency of the supply amount of the hydraulic fluid 14 to the steam generation space 114 is suppressed and the operation is stabilized.

  The ratio between the intake flow rate of the steam engine 121 and the discharge flow rate of the mechanical pump 16 can be obtained by the total volume ratio × reduction ratio. The total volume ratio is a ratio of the total volume of the steam engine 121 and the total volume of the mechanical pump 16 (total volume of the steam engine 121 / total volume of the mechanical pump 16). The total volume is the cylinder volume added by the number of cylinders. The cylinder volume is a volume formed between the top dead center and the bottom dead center of the piston inside the cylinder.

  The reduction ratio is the ratio of the rotational speed of the wheel gear 121i of the steam engine 121 to the rotational speed of the wheel gear 16i of the mechanical pump 16 (the rotational speed of the wheel gear 121i of the steam engine 121 / the wheel gear 16i of the mechanical pump 16). The number of rotations).

  As described above, in this example, the heating element 2 generates heat due to exhaust heat from the factory. For this reason, if the exhaust heat source is unstable, the evaporation of the working fluid 14 in the steam generation space 114 may become unstable, and the operation may sometimes stop.

  When the operation is stopped, the mechanical pump 16 is also stopped. However, according to the above configuration, the hydraulic fluid 14 is supplied to the steam generation space 114 by the wick 15 even if the mechanical pump 16 is stopped. be able to.

  Specifically, since the capillary force that sucks the hydraulic fluid 14 in the liquid reservoir space 131 is generated in the wick 15, the hydraulic fluid 14 is supplied from the liquid reservoir space 131 to the vapor generation space 114 using this capillary force. To do.

  For this reason, if the heat generation of the heating element 2 is resumed, the evaporation of the working fluid 14 in the steam generation space 114 is also resumed, so that the operation can be automatically resumed. Therefore, a starter for starting the steam engine 121 and a control system for controlling the starter are unnecessary.

  That is, according to the present embodiment, since the mechanical pump 16 is provided, the hydraulic fluid 14 can be supplied to the boiler unit 11 without being affected by the supply speed of the hydraulic fluid 14 by the wick 15 as much as possible. For this reason, even if the capillary equivalent diameter of the wick 15 is reduced to increase the boiler pressure, the amount of steam per hour can be secured. Therefore, both improvement in boiler pressure and improvement in steam volume can be achieved.

  Even when the mechanical pump 16 is stopped, the hydraulic fluid 14 can be supplied to the boiler unit 11 by the wick 15. For this reason, if the heat generating body 2 generates heat sufficiently, it is possible to generate steam without using a starter for starting the steam engine 121. Therefore, the operation can be easily started.

  In this example, the air gap in the wick 15 is made small so that the circle-equivalent radius r of the air gap in the wick 15 is sufficiently small so as to satisfy the above formula 2, so the pressure ΔP due to the capillary force of the wick 15 is The pressure difference (PH−PL) between the pressure PH of the steam generation space 114 and the pressure PL of the liquid storage space 131 becomes larger (ΔP> PH−PL).

  For this reason, the capillary force of the wick 15 overcomes the pressure difference (PH-PL) between the pressure PH of the steam generation space 114 and the pressure PL of the liquid storage space 131, and the working fluid 14 that has accumulated in the low-pressure liquid storage space 131 is removed. Suction can be satisfactorily performed in the high-pressure steam generation space 114.

  In other words, in a state where a pressure difference is generated between the liquid storage space 131 and the steam generation space 114, the wick 15 is used to provide a capillary force that does not lose the pressure difference (PH-PL), thereby reducing the low pressure liquid. The hydraulic fluid 14 can be pulled from the reservoir space 131 to the high-pressure steam generation space 114. Therefore, the hydraulic fluid 14 in the liquid storage space 131 can be returned to the high-pressure steam generation space 114 without using external energy.

  Further, since the gap in the wick 15 is made small, it is possible to prevent the steam generated in the steam generation space 114 from flowing back to the liquid storage space 131 through the wick 15.

  Specifically, the wick 15 is compressed (hot press) in the manufacturing process, and is further compressed by receiving a load from the boiler part case 101 in a state where the wick 15 is assembled to the boiler part 11. Furthermore, the wick 15 is swollen by the hydraulic fluid 14. As a result, the gap of the wick 15 is minimized, so that the steam generated in the steam generation space 114 can be prevented from flowing back to the liquid storage space 131 through the gap of the wick 15. That is, it is possible to ensure the sealing property of the vapor.

  When the pressure in the steam generation space 114 increases abnormally, the steam in the steam generation space 114 can be released to the outside of the steam generation space 114 through the wick 15. That is, the wick 15 can serve as a limiter.

  Here, since the boiling point of the hydraulic fluid 14 is determined by the material of the hydraulic fluid 14 and the pressure in the case 101, for example, if alcohol is used for the hydraulic fluid 14 and the inside of the case 101 is evacuated, it can be applied even when the temperature of the heat source is less than zero degrees. It is. When the temperature of the heat source is low, there is no need to impart heat resistance to the structure of the wick 15 or the boiler part 11, so a material having low heat resistance (resin etc.) as the material of the structure of the wick 15 or the boiler part 11. Can be used.

  In this example, since the fiber layer of the wick 15 extends in the radial direction from the outer peripheral surface side to the inner peripheral surface side, it continuously extends between the fiber layers from the inner peripheral surface side to the outer peripheral surface side. A void is formed. For this reason, since the fluidity | distribution of the working fluid 14 from an inner peripheral surface to an outer peripheral surface can be improved, the supply property of the working fluid 14 from the liquid storage space 131 to the steam generation space 114 can be improved.

  Particularly in this example, since the wick 15 is formed in a cylindrical shape whose radial direction is the direction in which the fiber layer extends, the flow path length of the working fluid 14 in the wick 15 can be made as short as possible. For this reason, since the flowability of the working fluid 14 from the outer peripheral surface to the inner peripheral surface can be further improved, the supply property of the working fluid 14 from the liquid storage space 131 to the steam generation space 114 can be further improved.

  Further, since the wick 15 is formed in a cylindrical shape, the hydraulic fluid 14 can be evenly supplied from the liquid reservoir space 131 to each part of the steam generation space 114.

  Further, since the wick 15 is formed of a heat insulating material and is interposed in a heat transfer path from the rod-shaped heat transfer portion 111c of the heat transfer member 111 to the liquid storage space 131, the operation of the liquid storage space 131 from the heating element 2 is performed. Heat transfer to the liquid 14 can be suppressed by the wick 15. For this reason, since the heat insulation of the liquid storage space 131 can be improved, it can suppress that the working fluid 14 of the liquid storage space 131 evaporates and the output efficiency falls.

  Further, since the wick 15 is formed in a cylindrical shape, the steam generation space 114 can be secured widely. For this reason, since heat conductivity can be improved, an output can be improved. Moreover, the heat transfer is improved, so that the temperature of heating can be lowered. The thermal deterioration of the wick 15 can be suppressed by reducing the heating temperature.

  Further, since the steam generation space 114 is formed inside the cylindrical wick 15 extending in the vertical direction, the steam generation space 114 extends in the vertical direction. For this reason, since the steam generated in the steam generation space 114 can be easily escaped to the steam passage 115, the release of the steam of the working fluid 14 is improved, and the output can be improved.

  Moreover, since the steam passage 115 is formed in the plate-like heat transfer portion 111b of the heat transfer member 111, the steam is further heated while passing through the steam passage 115 to become superheated steam, and the steam pressure increases, so the engine thrust increases. . In other words, the output energy increases.

  In this example, since the heat transfer member 111 is adapted to transfer heat from the heating element 2 to the steam engine 121 of the output unit 12, the steam temperature (steam pressure) in the steam engine 121 can be increased. As a result, the output can be improved.

(Second Embodiment)
In the first embodiment, the mechanical pump 16 is disposed above the liquid level of the hydraulic fluid 14, but in the second embodiment, as shown in FIG. Is placed inside.

  Specifically, the mechanical pump 16 is disposed on the upper side of the steam engine 121, and the hydraulic fluid 14 is sealed to the upper side of the mechanical pump 16. Therefore, in this embodiment, the space below the liquid level of the working fluid 14 in the internal space of the case 101 is the liquid storage space 131, and the space above the space is the condensation space 132. Yes.

  In the present embodiment, since the mechanical pump 16 is disposed in the hydraulic fluid 14, the liquid suction pipe 17 of the first embodiment is not provided.

  In order to prevent the working fluid 14 from entering the steam engine 121, the partition member 20 is disposed on the side and upper side of the steam engine 121, and the mechanical pump 16 is disposed on the upper surface of the partition member 20. It is fixed.

  The partition member 20 is fixed to the plate-shaped heat transfer section 111b so as to surround the steam engine 121 from the side and the upper side. Thereby, the steam engine 121 is separated from the hydraulic fluid 14 in the liquid storage space 131.

  In the example of FIG. 5, the partition member 20 is composed of a cylindrical member 201 fixed to the plate-shaped heat transfer section 111 b and a plate-shaped base member 202 fixed to the upper end portion of the cylindrical member 201. The space formed by being surrounded by the plate-shaped heat transfer part 111 b, the cylindrical member 201, and the base member 202 constitutes an engine storage space for storing the steam engine 121.

  A through hole through which the output shaft 123 passes is formed in the base member 202, and an exhaust pipe 203 extending upward from the base member 202 is provided at an outer edge portion of the through hole. The upper end of the exhaust cylinder 203 extends above the liquid level 14 a of the hydraulic fluid 14. As a result, the engine accommodation space inside the partition member 20 communicates with the condensation space 132.

  The output shaft 123 is provided with a center gear 125 that meshes with the wheel gear 16i. Similar to the first embodiment, the wheel gear 16i is connected to the piston 121a via a rod 121h or the like. In the example of FIG. 5, the center gear 125 and the wheel gear 16 i are disposed above the exhaust pipe 203.

  The power extracted by the output unit 12 is transmitted to the mechanical pump 16 via the output shaft 123, the center gear 125, the wheel gear 16i, the rod 121h, and the like. In other words, the output shaft 123, the center gear 125, the wheel gear 16i, and the rod 121h constitute a power transmission mechanism that transmits the power extracted by the output unit 12 to the mechanical pump 16. This power transmission mechanism is designed so that the reduction ratio is appropriately set.

  Note that another gear may be interposed between the center gear 125 and the wheel gear 16i depending on the setting of the reduction ratio and the convenience of the component layout. Further, the power transmission mechanism is not limited to the configuration of this example, and various mechanisms capable of transmitting the power extracted by the output unit 12 to the mechanical pump 16 can be used.

  In the first embodiment, since the mechanical pump 16 is disposed above the liquid level of the hydraulic fluid 14, the mechanical pump 16 needs to suck up the hydraulic fluid 14. Specifically, it is necessary to generate an external pressure and a differential pressure by lowering the pressure in the pump, and to suck up and flow the hydraulic fluid 14 with the differential pressure.

  However, in the configuration of the first embodiment, when the exhaust heat recovery apparatus 10 is made to correspond to a low-temperature heat source, the pressure inside the case 101 is lowered to lower the boiling point. The differential pressure for sucking up the hydraulic fluid 14 is reduced. As a result, the mechanical pump 16 becomes difficult to operate.

  In view of this point, in the present embodiment, since the mechanical pump 16 is submerged in the hydraulic fluid 14, it is not necessary for the mechanical pump 16 to suck up the hydraulic fluid 14. Therefore, since the mechanical pump 16 can operate even when the pressure in the case 101 is lowered, it is possible to cope with a lower temperature heat source.

  As can be seen from the above description, the entire mechanical pump 16 does not have to be submerged in the hydraulic fluid 14, and a portion of the mechanical pump 16 in which the hydraulic fluid 14 flows sinks in the hydraulic fluid 14. It only has to be.

  Moreover, since the boiler part 11, the output part 12, and the mechanical pump 16 are arrange | positioned along with the up-down direction, the mechanical pump 16 is made into hydraulic fluid 14 without enlarging the physique in the horizontal direction of the waste heat recovery apparatus 10. Can sink inside.

  Further, since the partition member 20 (cylindrical member 201 and base member 202) forming the engine housing space is also submerged in the working fluid 14, the engine housing space is insulated from the outside air, and the steam engine 121 is heated at a high temperature. Is maintained. For this reason, it can suppress that the vapor | steam which entered into the steam engine 121 cools, and a vapor pressure falls, and can improve efficiency by extension.

  Here, the partition member 20 (base member 202) is formed with an exhaust tube 203 extending upward from the liquid level of the hydraulic fluid 14, so that the hydraulic fluid 14 is prevented from entering the engine storage space. Steam discharged from the steam engine 121 can be discharged to the condensation space 132.

  Further, a power transmission mechanism (the output shaft 123, the center gear 125, the wheel gear 16i, and the rod 121h is connected to the internal space of the exhaust pipe 203 from the steam engine 121 to transmit the power extracted by the output unit 12 to the mechanical pump 16. Since the mechanical pump 16 is configured to reach the mechanical pump 16 via the space 132 above the liquid level 14a of the hydraulic fluid 14, the power transmission mechanism is efficiently used by utilizing the internal space of the exhaust pipe 203. Can be arranged.

(Third embodiment)
In the second embodiment, the mechanical pump 16 is disposed above the output unit 12. However, in the third embodiment, as shown in FIG. 6, the mechanical pump 16 is disposed on the side of the boiler unit 11. It is arranged.

  Specifically, the piston 16 a and the cylinder 16 b of the mechanical pump 16 are arranged in a liquid storage space 131 between the outer peripheral surface of the wick 15 and the inner wall surface of the cylindrical portion 101 a of the case 101. The piston 16a and the cylinder 16b are arranged such that their axial directions (reciprocating directions) are directed in the vertical direction. A liquid discharge pipe 18 is connected to the cylinder 16b.

  The piston 16 a is connected to the output shaft 123 through a pair of bevel gears 211 and 212 and the crank mechanism 22. The output shaft 123, the pair of bevel gears 211 and 212, and the crank mechanism 22 constitute a power transmission mechanism that transmits the power extracted by the output unit 12 to the mechanical pump 16.

  The pair of bevel gears 211 and 212 converts the rotation of the output shaft 123 in the horizontal direction into rotation in the vertical direction and transmits the rotation to the crank mechanism 22. The crank mechanism 22 linearly transmits the rotational motion transmitted from the output shaft 123. It is converted into motion and transmitted to the piston 16a.

  In other words, the pair of bevel gears 211 and 212 constitutes a motion conversion mechanism 21 that converts the direction of rotational motion by 90 °, and the crank mechanism 22 constitutes a motion conversion mechanism that converts rotational motion into linear motion. Yes.

  In the example of FIG. 6, the pair of bevel gears 211 and 212 are disposed on the upper side of the steam engine 121, and the crank mechanism 22 is configured in an L shape so as to bypass the steam engine 121.

  Note that another gear may be interposed between the output shaft 123 and the bevel gear 211 depending on the setting of the reduction ratio, the convenience of component layout, and the like. Further, the power transmission mechanism is not limited to the configuration of this example, and various mechanisms capable of converting the rotational power of the output shaft 123 into a linear motion and transmitting it to the piston 16a can be used.

  The liquid level of the hydraulic fluid 14 is located above the wick 15 and below the output unit 12. Therefore, in the present embodiment, the partition member 20 of the second embodiment is not provided.

  Also in this embodiment, since the mechanical pump 16 is submerged in the working fluid 14 as in the second embodiment, it is possible to cope with a lower temperature heat source.

  Moreover, in this embodiment, since the mechanical pump 16 is arrange | positioned to the side of the boiler part 11, the physique in the up-down direction of the exhaust heat recovery apparatus 10 can be reduced compared with the said 2nd Embodiment.

(Other embodiments)
In each of the above embodiments, the steam engine 121 and the mechanical pump 16 are connected by the center gear 122. However, the steam engine 121 and the mechanical pump 16 are connected using a timing belt, a cam, or the like. May be.

  In each of the above embodiments, the mechanical pump 16 is provided inside the case 101, but the mechanical pump 16 may be provided outside the case 101.

  In each of the above embodiments, one set of the wick 15, the steam generation space 114, and the liquid storage space 131 is provided in the case 101. However, a plurality of sets of the wick 15, the steam generation space 114, and the liquid storage space 131 are provided. It may be done.

  In each of the above embodiments, the cylindrical wick 15 is arranged so as to extend in the vertical direction. However, the present invention is not limited to this. For example, the cylindrical wick 15 is arranged so as to extend in the horizontal direction. It may be.

  In each of the above embodiments, the steam generation space 114 is formed inside the cylindrical wick 15, and the liquid storage space 131 is formed outside the cylindrical wick 15 (opposite side of the steam generation space 114). On the contrary, the steam generation space 114 may be formed outside the cylindrical wick 15, and the liquid storage space 131 may be formed inside the cylindrical wick 15.

  Moreover, in each said embodiment, although the fiber layer of the wick 15 is extended in the radial direction of the wick 15, it is not limited to this, For example, the fiber layer of the wick 15 is extended in the axial direction of the wick 15. Also good.

  Further, in each of the above embodiments, the wick 15 is formed in a cylindrical shape, and the working fluid in the liquid storage space 131 is sucked from the outer peripheral surface of the wick 15. However, the present invention is not limited to this. For example, the wick 15 may be formed in a flat plate shape, and the hydraulic fluid in the liquid reservoir space 131 may be sucked from the side end surface of the wick 15.

  In each of the above embodiments, the condensation space 132 is formed inside the case 101, but the condensation space 132 may be formed outside the case 101. That is, a container for forming the condensation space 132 may be provided outside the case 101.

  Further, in each of the above embodiments, a pendulum engine is used as the steam engine 121, but the rotary engine 20 shown in FIG. 7 can be used as the steam engine. The rotary engine 20 is described in Japanese Patent Application No. 2010-267126 previously filed by the present applicant, and its configuration and operation will be briefly described below.

  The rotary engine 20 includes a piston forming member 21, a rotor 22, a cam block 23, a cam follower 24, a supply / exhaust block 25, and the like.

  The piston forming member 21 has a piston 211 that reciprocates and a bracket 212 to which the cam follower 24 is assembled.

  The rotor 22 has a cylinder hole 221 in which the piston 211 reciprocally slides, and a supply / discharge passage 222 for supplying / discharging fluid to / from the cylinder hole 221. The rotor 22 has a rotation axis A 1 orthogonal to the axis A 2 of the cylinder hole 221. Rotating as the center.

  The cam block 23 is disposed on the outer peripheral side of the rotor 22. In this example, the cam block 23 is formed in a cylindrical shape having a substantially triangular (non-circular) cam 231. The cam 231 is a groove cam having an inner peripheral cam surface 231a and an outer peripheral cam surface 231b. It has become. In addition, the cam 231 may be comprised only by the inner peripheral cam surface 231a.

  The cam follower 24 reciprocates integrally with the piston 211 and slides on the cam 231.

  The supply / exhaust block 25 is formed with a supply path 251 through which the fluid supplied to the cylinder hole 221 flows and a discharge path 252 through which the fluid discharged from the cylinder hole 221 flows. The supply path 251 and the discharge path 252 are formed so as to alternately communicate with the supply / discharge path 222 of the rotor 22 as the rotor 22 rotates.

  When high-temperature and high-pressure steam is supplied to the supply path 251 in a state where the supply / discharge path 222 of the rotor 22 communicates with the supply path 251 of the supply / exhaust block 25, the steam in the supply path 251 passes through the supply / discharge path 222. 22 flows into the cylinder hole 221.

  Then, since the piston 211 is pushed out to the outer side of the rotor 22 by the pressure of the steam flowing into the cylinder hole 221, the cam follower 24 assembled to the piston 211 presses the cam 231 of the cam block 23. At this time, a rotational driving force for rotating the rotor 22 is generated depending on the shape of the cam 231 (first stroke).

  When the rotor 22 rotates by a predetermined angle by this rotational driving force, the supply / discharge path 222 of the rotor 22 is disconnected from the supply path 251 of the supply / exhaust block 25 and instead communicates with the discharge path 252 of the supply / exhaust block 25. At this time, due to the shape of the cam 231, the cam follower 24 is pressed from the cam 231 and the piston 211 is pushed back inward of the rotor 22. Thereby, the vapor | steam of the cylinder hole 221 is discharged | emitted through the supply discharge path 222 and the discharge path 252 (2nd process).

  When the rotor 22 further rotates by a predetermined angle, the supply / discharge path 222 of the rotor 22 is disconnected from the discharge path 252 of the supply / exhaust block 25, and instead communicates with the supply path 251 of the supply / exhaust block 25. The operation (first stroke and second stroke) is repeated.

  Thus, since the rotor 22 continuously rotates when high-temperature and high-pressure steam is supplied, the rotary engine 20 can convert the steam energy into mechanical energy and output it. Therefore, it is possible to use the rotary engine 20 as a steam engine.

2 Heating element (heat source)
DESCRIPTION OF SYMBOLS 11 Boiler part 12 Output part 13 Condensing part 14 Hydraulic fluid 15 Wick (Mechanical fluid introduction member)
16 Mechanical pump 114 Steam generation space 131 Liquid reservoir space

Claims (8)

A boiler section (11) for heating and evaporating the hydraulic fluid (14) with heat supplied from the heat source (2);
An output unit (12) for converting and extracting the energy of the steam generated in the boiler unit (11) into mechanical energy;
A condensing unit (13) for condensing the vapor used in the output unit (12);
Recirculation means (15, 16) for recirculating the hydraulic fluid (14) of the condensing unit (13) to the boiler unit (11);
The reflux means includes
A working fluid introduction member (15) that sucks the working fluid (14) of the condensing unit (13) by capillary force and guides it to the boiler unit (11);
A mechanical pump (16) that is driven by mechanical energy extracted by the output unit (12) and that pumps the hydraulic fluid (14) of the condensing unit (13) to the boiler unit (11). A heat engine characterized by   When the ratio of the flow rate of the steam used in the output unit (12) and the supply flow rate of the hydraulic fluid (14) by the mechanical pump (16) is greater than 1 and the hydraulic fluid (14) is vaporized The heat engine according to claim 1, wherein the heat expansion coefficient is equal to or less than the volume expansion coefficient. The output unit (12) includes a steam engine (121) that converts steam energy into mechanical energy,
The steam engine (121) is a pendulum engine having a piston (121a) and a cylinder (121b) that swing like a pendulum,
The mechanical pump (16) is a pendulum pump having a piston (16a) and a cylinder (16b) that swing like a pendulum,
The said steam engine (121) and the said mechanical pump (16) are arrange | positioned above the said boiler part (11), and are rock | fluctuated horizontally, The horizontal direction is characterized by the above-mentioned. The heat engine described in. The hydraulic fluid introduction member (15) is formed in a cylindrical shape,
In the boiler part (11), a steam generation space (114) in which the hydraulic fluid (14) is heated and evaporated is formed,
In the condensing part (13), a liquid storage space (131) in which the hydraulic fluid (14) is stored is formed,
The steam generation space (114) is formed on either the inside or the outside of the hydraulic fluid introduction member (15),
The liquid reservoir space (131) is formed on the side opposite to the side on which the steam generation space (114) is formed, inside and outside the hydraulic fluid introduction member (15),
The mechanical pump (16) sucks the hydraulic fluid (14) from the liquid storage space (131) and discharges the hydraulic fluid (14) to the vapor generation space (114). Item 4. The heat engine according to any one of Items 1 to 3. A case (101) for housing the boiler section (11), the output section (12), the condensing section (13) and the mechanical pump (16);
Inside the case (101) is formed a liquid storage space (131) in which the hydraulic fluid (14) condensed in the condensing part (13) is stored,
The mechanical pump (16) is characterized in that at least a portion where the hydraulic fluid (14) flows is arranged in the hydraulic fluid (14) of the liquid reservoir space (131). 4. The heat engine according to any one of 3. The output part (12) is arranged above the boiler part (11),
The mechanical pump (16) is disposed above the output part (12),
A partition member (20) for separating the output portion (12) from the working fluid (14) in the liquid storage space (131) is provided inside the case (101). The heat engine according to claim 5.   In the partition member (20), an exhaust pipe (203) for exhausting the steam used in the output part (12) to the condensing part (13) is provided on the liquid surface (14a) of the hydraulic fluid (14). The heat engine according to claim 6, wherein the heat engine is formed to extend upward. A power transmission mechanism (123, 125, 16i, 121h) for transmitting the power extracted by the output unit (12) to the mechanical pump (16);
The power transmission mechanism passes from the output section (12) through the internal space of the exhaust pipe (203) and the space (132) above the liquid level (14a) of the hydraulic fluid (14). The heat engine according to claim 7, wherein the heat engine is configured to reach the mechanical pump (16).

Images