JP4985828B2 - Heat engine - Google Patents

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 evaporation section (evaporation chamber) that evaporates the working fluid, whereas the condensing section that condenses (condensates) the steam has a low pressure. In general, a device such as a pump is used to return the liquid to the evaporation section (for example, Patent Document 1). That is, by driving a device such as a pump using external energy, the working fluid in the condensing unit is pumped and returned to the evaporating unit.

JP-A-8-338207

  In the heat engine that returns the working fluid condensed in the condensing unit to the evaporation chamber by a mechanism such as a pump as in the above prior art, a device such as a pump in addition to external energy (heat energy) that heats and evaporates the working fluid Since external energy for driving the power source is also required, there is a limit to improving the output efficiency.

  The present invention has been made in view of the above points, and an object of the present invention is to provide a heat engine capable of returning hydraulic fluid condensed in a condensing unit to a high-pressure evaporation chamber without using external energy as much as possible. And

In order to achieve the above object, according to the first aspect of the present invention, in the evaporation chamber (156), the working fluid (14) is heated by the heat supplied from the external heat source (3) to generate the vapor of the working fluid (14). 308), and a boiler section (11) in which a liquid reservoir chamber (157a) for storing the hydraulic fluid (14) supplied to the evaporation chambers (156, 308) is formed;
An output section (12) through which steam generated in the evaporation chamber (156, 308) flows, converts the steam energy into mechanical energy, and takes it out;
Condensing unit is recirculated to the condensed steam that has passed through the output unit (12), condensed working fluid (14) a liquid reservoir chamber (157 a) and (13),
Disposed boiler unit (11), a reservoir chamber and (157 a) of the hydraulic fluid (14) operating fluid introduction member for supplying a suction to the evaporation chamber (156,308) to a capillary force (17) liquid Prepared,
Evaporation chamber (156,308) is adapted to a higher pressure than they are separated to the liquid reservoir chamber (157 a) liquid reservoir chamber (157 a),
The hydraulic fluid introduction member (17)
(2σ / r) · cos θ> PH-PL
Boiler unit (11) has a heat transfer member (15 2) abutting on and hydraulic fluid introducing member are thermally connected to an external heat source (3) (17),
Hydraulic fluid introducing member (17) is heat from an external heat source (3) via a heat transfer member (15 2),
The site abuts the hydraulic fluid introducing member (17) of the heat transfer member (15 2), to exhaust the vapor generated from the hydraulic fluid introducing member (17) to the outside of the hydraulic fluid introducing member (17) An exhaust passage (21) is formed for
The heat transfer member (152 ) has an upper surface portion extending in the horizontal direction,
The hydraulic fluid introduction member (17) is formed in a flat plate shape and is superimposed on the upper surface portion of the heat transfer member (152 ) ,
A through hole (172) penetrating the front and back is formed in a portion located inside the evaporation chamber (156) of the hydraulic fluid introduction member (17),
The boiler section (11) forms a liquid storage chamber (157a) on the horizontal direction side of the evaporation chamber (156),
In the portion of the heat transfer member (152) located closer to the liquid reservoir chamber (157a) than the portion overlapping the through hole (172), horizontal heat conduction inside the heat transfer member (152) is suppressed. A heat insulating groove (152a) is formed;
The heat insulating groove (152a) has a shape in which the outer surface located on the external heat source (3) side of the heat transfer member (152) is recessed in a direction away from the external heat source (3),
In the heat transfer member (152), the portion (152b) located on the opposite side of the liquid reservoir chamber (157a) from the heat insulating groove (152a) receives heat from the external heat source (3) ,
Of the hydraulic fluid introduction member (17) , the horizontal end surface (171) located closer to the liquid reservoir chamber (157a) than the heat insulating groove (152a) is filled with the hydraulic fluid (14) in the liquid reservoir chamber (157a). It is characterized in that an inflow port is formed.

Where σ is the surface tension of the hydraulic fluid (14), r is the equivalent circle radius of the void in the hydraulic fluid introduction member (17), and θ is the wetting angle of the hydraulic fluid (14) with respect to the hydraulic fluid introduction member (17). , PH is the pressure in the evaporation chamber (156,308), PL is the pressure of the liquid reservoir chamber (157 a).

According to this, by configuring the hydraulic fluid introduction member (17) so as to satisfy the relationship of the above mathematical formula, the pressure due to the capillary force of the hydraulic fluid introduction member (17) is reduced to the high-pressure evaporation chamber (156, 308). becomes larger than the pressure difference between the low pressure liquid reservoir chamber (157 a) and, actuating the supply of hydraulic fluid to the high pressure of the evaporation chamber (156,308) (14) from the low pressure liquid reservoir chamber (157 a) This can be performed by utilizing the capillary force of the liquid introduction member (17). Therefore, the working fluid (14) condensed in the condensing unit (13) can be returned to the high-pressure evaporation chamber (156, 308) without using external energy as much as possible.

Further, exhaust the site in contact with the hydraulic fluid introducing member (17) of the heat transfer member (15 2), the vapor generated from the hydraulic fluid introducing member (17) to the outside of the hydraulic fluid introducing member (17) Since the exhaust passage (21) for this purpose is formed, it is possible to prevent the steam from staying inside the working fluid introduction member (17) and hindering the suction of the working fluid (14).
Moreover, since the heat receiving area of the hydraulic fluid introduction member (17) can be secured large, the hydraulic fluid (14) sucked by the hydraulic fluid introduction member (17) can be effectively heated.
Further, since the hydraulic fluid introduction member (17) sucks the hydraulic fluid (14) in the horizontal direction, the hydraulic fluid introduction member (17) is affected by gravity when sucking the hydraulic fluid (14). Can be suppressed. For this reason, the hydraulic fluid (14) in the liquid reservoir chamber (157a) can be reliably supplied to the evaporation chamber (156) by the hydraulic fluid introduction member (17).
Further, the upper so can be released quickly to the side, for steam working fluid introducing member of the heat transfer member (15 2) hydraulic fluid introducing member a heated and vaporized steam from the through-hole (172) (17) (17) It can suppress staying in and hindering attraction | suction of a hydraulic fluid (14).
Further, the heat transfer member (152) has a heat insulating groove (152a) formed by recessing the outer surface located on the side of the external heat source (3) in a concave shape in a direction away from the external heat source (3). The horizontal end face (171) located on the liquid reservoir chamber (157a) side of the heat insulating groove (152a) of the flat plate-like hydraulic fluid introduction member (17) superimposed on the upper surface portion of (152), It constitutes the working fluid inlet of the liquid reservoir chamber (157a).
According to this, since the heat conduction to the portion of the heat transfer member (152) located closer to the liquid reservoir chamber (157a) than the heat insulation groove (152a) can be suppressed by the heat insulation groove (152a), horizontal In the plate-shaped working fluid introduction member (17) extending in the direction, heat receiving at a portion on the liquid reservoir chamber (157a) side , that is, an inlet portion of the working fluid is suppressed. For this reason, it can further suppress that vapor | steam stagnates in the hydraulic-fluid introduction member (17), and prevents the suction | inhalation of hydraulic-fluid (14).

  Specifically, as in the invention according to claim 2, in the heat engine according to claim 1, the exhaust passage (21) is configured by a groove (22) formed in the heat transfer member (152). It only has to be.

Further, as in the invention described in claim 3, in the heat engine described in claim 1, the heat transfer member (152 ) includes an exhaust passage forming member (23) that forms the exhaust passage (21), and a remaining portion. Divided into members (152) constituting the part of
The exhaust passage forming member (23) is a net-like member or a plurality of ball-like members sandwiched between the member (152) constituting the remaining portion and the hydraulic fluid introduction member (17),
The exhaust passage (21) may be constituted by a gap formed by a mesh member or a plurality of ball members.

According to a fourth aspect of the present invention, in the heat engine according to any one of the first to third aspects, the boiler section (11) includes the heat transfer member (152) of the hydraulic fluid introduction member (17 ). And a heat transfer plate (19) for transferring heat from the external heat source (3) to the hydraulic fluid introduction member (17).

  Thereby, the hydraulic fluid introduction member (17) is heated from the upper surface side. For this reason, since the hydraulic fluid (14) evaporates from the upper surface of the hydraulic fluid introduction member (17), the release of the vapor of the hydraulic fluid (14) is improved, and the output can be improved.

In the invention according to claim 5 , in the heat engine according to any one of claims 1 to 4 , a boiler part case (30) that houses the boiler part (11);
A reflux part case (31) for accommodating the output part (12) and the condenser part (13);
A steam passage forming portion (32) that forms a steam passage (32a) that connects the evaporation chamber (308) of the boiler portion (11) and the output portion (12);
A circulation passage forming portion (33) that forms a circulation passage (33a) that communicates between the condensation portion (13) and the liquid storage chamber (309a) of the boiler portion (11);
The boiler part case (30) and the reflux part case (31) are arranged so as to be spaced apart from each other and connected via a steam passage forming part (32) and a circulation passage forming part (33).

  According to this, since the output unit (12) and the condensing unit (13) are spaced apart from the boiler unit (11), the boiler unit (11) is connected to the output unit (12) and the condensing unit (13). It is difficult for the heat to be transmitted, and the temperature rise of the output part (12) and the condensing part (13) is suppressed. For this reason, the aggregation / refluxing performance of the steam discharged from the output section (12) is improved.

According to a sixth aspect of the present invention, in the heat engine according to any one of the first to fifth aspects, the through hole (172) communicates with the exhaust passage (21).

  Thus, the vapor heated and evaporated by the heat transfer member (152, 23, 302) can be quickly released from the exhaust passage (21) and the through hole (172) to the upper side of the hydraulic fluid introduction member (17). Therefore, it is possible to further suppress the vapor from staying in the hydraulic fluid introduction member (17) and hindering the suction of the hydraulic fluid (14).

Specifically, as in the invention according to claim 7 , in the heat engine according to any one of claims 1 to 6 , the through hole (172) is a plate of the working fluid introduction member (17). What is necessary is just to be formed in the groove shape extended in a surface direction.

Further, as in the invention according to claim 8 , in the heat engine according to any one of claims 1 to 6, a large number of through holes (172) may be dispersedly formed.

According to a ninth aspect of the present invention, in the heat engine according to any one of the first to eighth aspects, the boiler section (11) operates so that the gap in the hydraulic fluid introduction member (17) is reduced. A load applying means (161) for applying a load to the liquid introduction member (17);
The hydraulic fluid introduction member (17) is characterized in that it is held in the boiler section (11) in a state where a load is applied from the load application means (161).
The hydraulic fluid introduction member (17) that satisfies the relationship of the mathematical expression can be easily configured.

  According to this, since the load applying means (161) reduces the gap in the hydraulic fluid introduction member (17), the circle equivalent radius r of the gap in the hydraulic fluid introduction member (17) can be reduced. The hydraulic fluid introduction member (17) that satisfies the above mathematical relationship can be easily configured.

In the invention according to claim 10 , in the heat engine according to claim 9 , the boiler part (11) has a partition wall (16) separating the evaporation chamber (156) and the liquid reservoir chamber (157a),
The partition wall (16) is disposed in the boiler section (11) so as to apply a load to the hydraulic fluid introduction member (17),
The load applying means (161) is constituted by a partition wall (16).

  According to this, since the partition wall (16) separating the evaporation chamber (156) and the liquid storage chamber (157a) also serves as a load applying means, it is compared with the case where the load applying means is provided separately from the partition wall (16). Thus, the configuration can be simplified.

According to an eleventh aspect of the present invention, in the heat engine according to the tenth aspect , the hydraulic fluid introducing member (17) extends from the load applying means (161) to the evaporation chamber (156) side. And

  Thereby, the hydraulic fluid (14) in the liquid reservoir chamber (157a) can be reliably supplied to the evaporation chamber (156) by the hydraulic fluid introduction member (17).

According to a twelfth aspect of the present invention, in the heat engine according to any one of the first to eleventh aspects, the hydraulic fluid introduction member (17) is made of a material woven with at least resin fibers. Features.

  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 sectional drawing of the waste heat recovery apparatus in the form used as the premise of this invention. It is a perspective view which shows the external appearance of the waste heat recovery apparatus in the form used as the premise of this invention. It is a perspective view which shows the internal structure of the waste heat recovery apparatus in the form used as the premise of this invention. It is sectional drawing which shows the engine of the waste heat recovery apparatus in the form used as the premise of this invention. It is sectional drawing and the top view which show the principal part of the boiler part in 1st Embodiment of this invention. It is a top view which shows the example of a pattern of the groove | channel in 1st Embodiment of this invention. It is sectional drawing which shows the principal part of the boiler part in 2nd Embodiment of this invention. It is the top view and sectional view which show the principal part of the boiler part in 3rd Embodiment of this invention. It is sectional drawing of the waste heat recovery apparatus in 4th Embodiment of this invention. It is the top view and sectional drawing which show the principal part of the boiler part in 5th Embodiment of this invention. It is the top view and sectional drawing which show the principal part of the boiler part in the modification of 5th Embodiment of this invention. It is sectional drawing which shows the principal part of the boiler part in 6th Embodiment of this invention. It is sectional drawing which shows the principal part of the boiler part in 7th Embodiment of this invention.

(Form which is the premise of the present invention)
The form which becomes the premise of this invention is demonstrated based on FIGS. In this embodiment, the heat engine is applied to the exhaust heat recovery device. FIG. 1 is a cross-sectional view showing the overall configuration of the exhaust heat recovery apparatus. FIG. 2 is a perspective view showing an external appearance of the exhaust heat recovery apparatus. FIG. 3 is a perspective view showing the internal structure of the exhaust heat recovery apparatus. 1 to 4, the up and down arrows indicate the up and down direction (vertical direction) in the installed state of the exhaust heat recovery device.

  The exhaust heat recovery apparatus 10 of this embodiment is roughly divided into a boiler unit 11, an output unit 12, and a condensing unit 13. In the example of FIG. 1, the generator 1 is attached to the exhaust heat recovery device 10 in order to use mechanical energy extracted by the exhaust heat recovery device 10 for power generation. In the example of FIG. 2, the fan 2 is rotationally driven by the mechanical energy extracted by the exhaust heat recovery apparatus 10.

  The boiler unit 11 heats and evaporates the hydraulic fluid 14 (water in this example) with heat (exhaust heat) supplied from an external heat source, and supplies the vapor of the hydraulic fluid 14 to the output unit 12. The output unit 12 converts the energy of the steam supplied from the boiler unit 11 into mechanical energy and outputs the mechanical energy.

  The condensing unit 13 condenses the vapor that has passed through the output unit 12 to condense it into the working fluid 14, and returns the condensed working fluid 14 to the boiler unit 11. Therefore, the condensing part 13 can also be expressed as a reflux part.

  The boiler unit 11 and the output unit 12 are accommodated in the case 15. In this example, the case 15 is composed of a single container. The case 15 is placed on the heating element 3 that forms an external heat source. In this example, the heating element 3 generates heat due to exhaust heat from the factory.

  The case 15 includes two flat plates 151 and 152 that extend in the horizontal direction, and a cylinder 153 that extends in the vertical direction between the two flat plates 151 and 152. That is, the upper and lower walls of the case 15 are configured by the flat plates 151 and 152, and the side wall of the case 15 is configured by the cylinder 153.

  In this example, since water is used as the working fluid 14, the flat plates 151 and 152 and the cylinder 153 are preferably formed of stainless steel having excellent water resistance. In this example, the flat plates 151 and 152 are formed in a rectangular flat plate shape, and the tube 153 is formed in a cylindrical shape.

  The flat plates 151 and 152 and the tube 153 are fixed so as to ensure liquid tightness and air tightness. In the example of FIG. 1, a seal member 154 is interposed between the flat plates 151 and 152 and the cylinder 153. In the example of FIGS. 2 and 3, a support column 155 that connects the flat plates 151 and 152 is disposed on the outer peripheral side of the tube 153.

  The internal space of the case 15 is separated by a partition wall 16 into a high pressure chamber 156 and a low pressure chamber 157. The partition wall 16 is divided into a cylindrical wall portion 161 disposed on the lower wall portion 152 of the case 15 and a plate-like wall portion 162 covering the cylindrical wall portion 161. In this example, the cylindrical wall part 161 is formed in a cylindrical shape, and the plate-like wall part 162 is formed in a disk shape.

  The high-pressure chamber 156 is a space formed inside the cylindrical wall portion 161 and below the plate-like wall portion 162, and constitutes an evaporation chamber in which the working fluid 14 is heated by the heat of the heating element 3 to evaporate. Therefore, the high pressure chamber 156 becomes high pressure by the vapor of the working fluid 14.

  The low pressure chamber 157 is a space formed on the outer side of the cylindrical wall portion 161 and on the upper side of the plate-like wall portion 162. The steam that has flowed through the output unit 12 and the working fluid 14 that has been condensed in the condensing unit 13 flow into the low-pressure chamber 157. Therefore, the low pressure chamber 157 has a lower pressure than the high pressure chamber 156.

  The partition wall 16 is formed of a heat-insulating material having heat resistance such as a heat-resistant resin so that the vapor in the evaporation chamber (high pressure chamber) 156 is not cooled and condensed.

  An engine 121 that constitutes the output unit 12 is disposed in the low pressure chamber 157. In this example, the engine 121 is fixed to the upper side of the plate-like wall portion 162 of the partition wall 16, and a steam passage 162 a for supplying the vapor of the evaporation chamber 156 to the engine 121 is formed in the plate-like wall portion 162. Yes.

  A space located between the cylinder 153 of the case 15 and the cylindrical wall portion 161 of the partition wall 16 in the low-pressure chamber 157 constitutes a liquid reservoir chamber 157 a that stores the working fluid 14 supplied to the evaporation chamber 156. That is, the liquid reservoir chamber 157 a is disposed on the horizontal direction side of the evaporation chamber 156.

  A wick 17 corresponding to a hydraulic fluid introduction member is sandwiched between the bottom wall portion (lower wall portion) 152 of the case 15 and the cylindrical wall portion 161 of the partition wall 16.

  Here, the hydraulic fluid introduction member is defined as a member that generates a capillary force (capillary force generation member) that sucks the hydraulic fluid 14 in the liquid reservoir chamber 157, for example, porous ceramic or metal sintered material. It is a structure in which a porous body such as a body or a fiber is knitted.

  In this example, the wick 17 is formed of a heat-resistant sheet material. Specifically, the wick 17 is formed of a braided material of stainless wire and aramid fiber (resin fiber). Moreover, in this example, the wick 17 is formed in a flat plate shape, more specifically in a disk shape.

  The wick 17 is overlaid on an upper surface portion extending in the horizontal direction in the planar bottom wall portion 152. The bottom wall portion 152 is thermally connected to the heating element 3 and serves as a heat transfer member that transfers heat from the heating element 3 to the wick 17. As a result, the lower surface portion (planar portion on the bottom wall portion 152 side) 173 of the wick 17 receives heat from the heating element 3 via the bottom wall portion 152.

  The outer peripheral edge portion of the wick 17 is sandwiched between the bottom wall portion 152 of the case 15 and the cylindrical wall portion 161 of the partition wall 16. Thereby, the end surface 171 in the horizontal direction of the wick 17 constitutes an inflow port through which the working fluid 14 in the liquid reservoir chamber 157 flows.

  A central portion of the wick 17 (a portion closer to the center than the cylindrical wall portion 161) is located in the evaporation chamber 156. In other words, the wick 17 extends from the cylindrical wall portion 161 to the evaporation chamber 156 side.

  In this example, the cylindrical wall portion 161 and the wick 17 are fastened together with the bottom wall portion 152 of the case 15 by bolts 18 and fixed. By tightening the bolt 18, the wick 17 is held in the case 15 in a state of being compressed by receiving a load from the cylindrical wall portion 161.

  When the wick 17 is compressed by receiving a load from the cylindrical wall portion 161, the air gap in the wick 17 is reduced as compared with a state where the load is not received (a single state of the wick 17). In other words, the cylindrical wall portion 161 constitutes a load applying means for applying a load to the wick 17 so that the gap in the wick 17 is reduced.

  Here, a pressure difference is generated inside the wick 17 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 17. The pressure ΔP due to the capillary force of the wick 17 is expressed by the following formula 1.

(Equation 1)
ΔP = (2σ / r) · cos θ
However, r is the equivalent circle radius (capillary radius) of the void in the wick 17, 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.

  As described above, the wick 17 receives the load from the cylindrical wall portion 161 and is compressed to reduce the gap in the wick 17. As a result, the equivalent circle radius r of the gap in the wick 17 in Equation 1 is reduced, and the pressure ΔP due to the capillary force of the wick 17 is the pressure difference between the pressure PH of the high pressure chamber 156 and the pressure PL of the low pressure chamber 157 ( PH-PL) (ΔP> PH-PL).

  In other words, the wick 17 is configured to satisfy the relationship of the following formula 2.

(Equation 2)
(2σ / r) · cos θ> PH-PL
A disc-shaped plate 19 is placed at the center of the wick 17. The plate 19 and the wick 17 are fastened to the bottom wall portion 152 of the case 15 by bolts 20 and fixed. This prevents the central portion of the wick 17 from being lifted.

  A predetermined number of through-holes 172 and 191 extending in the vertical direction and penetrating the front and back are formed in portions of the wick 17 and the plate 19 located in the evaporation chamber 156. The through holes 172 and 191 serve as a steam vent for allowing steam generated in the evaporation chamber 156 to escape upward of the wick 17 and the plate 19.

  In other words, when the hydraulic fluid 14 in the evaporation chamber 156 evaporates due to heat transfer from the bottom wall portion 152 of the case 15, the hydraulic fluid 14 escapes to the upper side of the wick 17 and the plate 19 through the through holes 172 and 191.

  A heat insulating groove 152a that suppresses heat conduction in the bottom wall 152 is circumferential, more specifically circumferential, at a portion of the bottom wall 152 that is located closer to the liquid reservoir chamber 157a than the through holes 172 and 191. It is formed in a shape.

  Of the bottom wall portion 152, the inner portion 152 b of the heat insulating groove 152 a, that is, the portion located closer to the through holes 172 and 191 than the heat insulating groove 152 a is placed on the heat generating body 3 and is in contact with the heat generating body 3. On the other hand, the outer portion 152 c of the heat insulating groove 152 a in the bottom wall portion 152 is not placed on the heating element 3 and is not in contact with the heating element 3.

  The cylindrical wall portion 161 of the partition wall 16 is disposed on the outer portion 152 c of the heat insulating groove 152 a in the bottom wall portion 152.

  In this example, the engine 121 of the output unit 12 is a pendulum engine in which the piston 122 and the cylinder 123 swing like a pendulum. A steam turbine or the like may be used instead of the engine 121.

  FIG. 4 is a cross-sectional view showing the engine 121. The cylinder 123 is supported so as to be swingable about a swing shaft 125 with respect to a base 124 fixed to the plate-like wall portion 162 of the partition wall 16.

  The base 124 is formed with an intake passage 124a that communicates with the steam passage 162a. The intake path 124 a is a flow path through which the steam sucked into the cylinder 123 flows. The base 124 is formed with an exhaust passage 124 b communicating with the low pressure chamber 157. The exhaust passage 124b is a passage through which steam exhausted from the cylinder 123 flows. An outlet portion of the intake passage 124 a and an inlet portion of the exhaust passage 124 b are open on the upper surface of the base 124.

  In this example, the piston 122 and the cylinder 123 are disposed in the horizontal direction, and the swing shaft 125 is disposed in the vertical direction. Therefore, the piston 122 and the cylinder 123 swing within the horizontal plane.

  On the lower surface of the cylinder 123, a port 123a for sucking and exhausting steam is opened. In a state where the cylinder 123 is located on one end side in the swinging direction, the port 123a communicates with the intake passage 124a. In a state where the cylinder 123 is located on the other end side in the swinging direction, the port 123a communicates with the exhaust passage 124b.

  When the cylinder 123 is positioned on one end side in the swinging direction and the port 123a communicates with the intake passage 124a, the steam in the evaporation chamber 156 flows into the cylinder 123 and the piston 122 is pushed out to move forward.

  The tip of the piston 122 is connected to the wheel gear 127 via the rod 126. As shown in FIG. 1, the wheel gear 127 is connected to the center gear 128. An output shaft 129 is fixed at the center of the center gear 128. Thereby, when the piston 122 is pushed out, the output shaft 129 rotates through the wheel gear 127 and the center gear 128.

  Further, when the piston 122 is pushed out and the wheel gear 127 rotates, the cylinder 123 swings toward the other end side in the swinging direction, and the port 123 a is closed by the upper surface of the base 124.

  When the port 123a is closed, the wheel gear 127 continues to rotate due to the inertial force, and the piston 122 is pushed back by the inertial force of the wheel gear 127 to return. At this time, the swing of the cylinder 123 is continued. When the cylinder 123 is positioned on the other end side in the swing direction and the port 123a communicates with the exhaust passage 124b, the steam in the cylinder 123 is discharged to the low pressure chamber 157.

  In the example of FIGS. 1 and 3, the engine 121 constitutes a multi-cylinder engine provided with a plurality of cylinders 123, but may constitute a single-cylinder engine provided with only one cylinder 123. .

  The output shaft 129 of the output unit 12 and the rotating shaft 1a of the generator 1 are connected by a magnet coupling via the upper wall portion 151 of the case 15. The rotor 1b is rotated by the rotation of the rotating shaft 1a, and power is generated by the coil 1c by the rotation of the rotor 1b. The electric power generated by the coil 1 c is supplied to an arbitrary electric device 4 connected to the generator 1.

  In the example of FIG. 1, the condensing unit 13 is disposed on the upper side of the case 15. On the upper wall portion 151 of the case 15, an outflow path 151 a for allowing the vapor of the low pressure chamber 157 discharged from the output portion 12 to flow out to the condensing portion 13, and the working fluid 14 condensed in the condensing portion 13 to the low pressure chamber 157. A reflux path 151b for refluxing is formed.

  The condensing part 13 is formed of a container having a predetermined shape, and the internal space of the condensing part 13 communicates with the outflow path 151a and the reflux path 151b. The steam that has flowed into the condensing unit 13 through the outflow passage 151 a dissipates heat into the atmosphere and condenses in the condensing unit 13. That is, in the condensing unit 13, the steam is returned to the working fluid 14. The working fluid 14 recovered by the condensing unit 13 is returned to the low pressure chamber 157 through the reflux path 151b and is stored in the liquid storage chamber 157a.

  In the example of FIG. 1, the fan 1d is connected to the rotating shaft 1a of the generator 1 to increase the heat radiation amount of the steam in the condensing unit 13, and the fan 1d is rotated by the rotating shaft 1a. The condensing unit 13 is cooled by the blown air.

  Next, the operation in the above configuration will be described. The heat of the heating element 3 is transmitted to the working fluid 14 in the evaporation chamber 156 via the bottom wall portion 152 of the case 15, and the working fluid 14 evaporates. The steam generated in the evaporation chamber 156 is supplied to the engine 121 through the steam passage 162a.

  The steam supplied to the engine 121 drives the piston 122. Thereby, the energy of the steam is converted into mechanical energy. The output shaft 129 is rotated by driving the piston 122, and the generator 1 generates power. In this way, the exhaust heat energy of the heating element 3 is recovered as electric energy.

  The steam in the engine 121 is discharged to the low pressure chamber 157 through the exhaust passage 124b after driving the piston 122. The steam discharged from the engine 121 to the low pressure chamber 157 flows into the condensing unit 13 through the outflow passage 151 a, is condensed in the condensing unit 13, and is returned to the working fluid 14. The working fluid 14 recovered by the condensing unit 13 returns to the low-pressure chamber 157 through the reflux path 151b and accumulates in the liquid reservoir chamber 157a.

  The working fluid 14 accumulated in the liquid reservoir chamber 157a is sucked into the wick 17 and supplied to the evaporation chamber 156 to evaporate. That is, the wick 17 generates a capillary force that sucks the hydraulic fluid 14 in the liquid reservoir chamber 157a, so that the hydraulic fluid 14 is transferred from the low-pressure reservoir chamber 157a to the high-pressure evaporation chamber 156 by using this capillary force. Supply.

  More specifically, in the boiler section 11 having the pressure partition wall 16, the reflux working fluid 14 in the low-temperature and low-pressure reservoir chamber 157 a is pulled into the high-pressure evaporation chamber 156 by the capillary force of the wick 17 and reaches the end of the wick 17. Drops of the working fluid 14 are continuously evaporated.

  Here, the air gap in the wick 17 is made small so that the circle-equivalent radius r of the air gap in the wick 17 is sufficiently small so as to satisfy the above formula 2, so the pressure ΔP due to the capillary force of the wick 17 is It becomes larger than the pressure difference (PH-PL) between the pressure PH of the high pressure chamber 156 and the pressure PL of the low pressure chamber 157 (ΔP> PH-PL).

  For this reason, the capillary force of the wick 17 overcomes the pressure difference (PH-PL) between the pressure PH of the high-pressure chamber 156 and the pressure PL of the low-pressure chamber 157, and the hydraulic fluid 14 accumulated in the low-pressure reservoir chamber 157a The evaporation chamber 156 can be sucked well.

  In other words, in the state where a pressure difference is generated between the liquid storage chamber 157a and the evaporation chamber 156 by the pressure partition wall 16, by using the wick 17, a capillary force that does not lose the pressure difference (PH-PL) is given. The working fluid 14 can be pulled from the low-pressure liquid reservoir chamber 157 a to the high-pressure evaporation chamber 156. Therefore, the hydraulic fluid 14 in the liquid reservoir chamber 157a can be returned to the high-pressure evaporation chamber 156 without using external energy.

  Further, since the evaporation amount of the working fluid 14 in the evaporation chamber 156 and the movement amount of the working fluid 14 from the liquid storage chamber 157a are the same, the recirculation amount control of the working fluid 14 becomes autonomous. For this reason, since the control mechanism for controlling the recirculation | reflux amount of the hydraulic fluid 14 is unnecessary, size reduction and cost reduction of an apparatus physique can be achieved.

  Further, since the gap in the wick 17 is made small, it is possible to prevent the steam generated in the evaporation chamber 156 from flowing back to the low pressure chamber 157 through the wick 17.

  As described above, in this embodiment, as an example of the wick 17, a braided material of stainless wire and aramid fiber is used. When the wick 17 is in a single state (uncompressed state) and the internal gap is large, the wick 17 is compressed to make the fibers dense, thereby reducing the gap in the wick 17 and the gap in the wick 17. It is preferable that the equivalent circle radius r is sufficiently small.

  In this embodiment, the wick 17 is compressed between the cylindrical wall portion 161 and the bottom wall portion 152 by tightening the cylindrical wall portion 161 of the partition wall 16 with the bolt 18 against the bottom wall portion 152 of the case 15. ing. For this reason, the wick 17 satisfying the relationship of the mathematical formula 2 can be easily configured.

One specific example of such compression of the wick 17 is that the wick 17 having a material thickness of 5 mm, a density of 2.5 m / cm ³ , and a fiber diameter of 8 μm is tightened and compressed to 12%. The equivalent circle radius r can be reduced to 12 μm, and a capillary force that overcomes the pressure of 10 kPa in the evaporation chamber 156 can be generated.

  Further, in this embodiment, since the wick 17 is compressed by applying a load to the wick 17 by the cylindrical wall portion 161 that is a part of the partition wall 16, the load that compresses the wick 17 by applying a load to the wick 17. The configuration can be simplified as compared with the case where the applying means is provided separately from the partition wall 16.

  If the gap in the wick 17 is already sufficiently small even when the wick 17 is in a single state (uncompressed state), a sufficient capillary force can be obtained even if the wick 17 is used without being compressed. An example of such a wick 17 is a porous sintered metal plate.

  In this embodiment, since the wick 17 extends to the evaporation chamber 156 side from the cylindrical wall portion 161, the wick 17 is arranged only between the cylindrical wall portion 161 and the bottom wall portion 152 of the case 15. Compared with the case where it exists, the hydraulic fluid 14 of the liquid storage chamber 157a can be reliably supplied to the evaporation chamber 156.

  Further, in the present embodiment, the horizontal end surface 171 of the wick 17 constitutes an inflow port through which the hydraulic fluid 14 in the liquid reservoir chamber 157a flows, so that the wick 17 sucks the hydraulic fluid 14 in the horizontal direction. It becomes. For this reason, it is possible to suppress the influence of gravity when the wick 17 sucks the working fluid 14. For this reason, the hydraulic fluid 14 in the liquid reservoir chamber 157 a can be reliably supplied to the evaporation chamber 156 by the wick 17.

  In this embodiment, since the wick 17 is formed in a flat plate shape extending in the horizontal direction and disposed on the bottom wall portion 152, the flat portion 173 on the bottom wall portion 152 side of the wick 17 is the bottom wall portion. Heat can be received from the heating element 3 via 152. For this reason, since the heat receiving area of the wick 17 can be ensured large, the working fluid 14 sucked by the wick 17 can be effectively heated.

  Further, in this embodiment, since a through hole 172 extending in the vertical direction is formed in a portion of the wick 17 located in the evaporation chamber 156, vapor evaporated by being heated by the bottom wall portion 152 from the through hole 172. It is possible to quickly escape to the upper side of the wick 17. For this reason, it can suppress that vapor | steam retains in the wick 17, and the inside of the wick 17 is heated and dried and the suction | inhalation of the working fluid 14 is prevented.

  In this embodiment, a circumferential heat insulating groove 152a that suppresses heat conduction in the bottom wall portion 152 is formed in a portion of the bottom wall portion 152 that is located closer to the liquid reservoir chamber 157a than the through-hole 172, and the bottom The inner portion 152b of the circumferential heat insulating groove 152a in the wall portion 152 is in contact with the heating element 3.

  For this reason, heat reception is performed satisfactorily in the vicinity of the through-hole 172 in the wick 17, whereas heat reception is suppressed in a portion of the wick 17 away from the through-hole 172 (portion on the liquid reservoir chamber 157a side).

  As a result, the vapor that is heated and evaporated by the bottom wall portion 152 can be more quickly released from the through hole 172 to the upper side of the wick 17, so that the steam stays in the wick 17 and heats the inside of the wick 17. It can be avoided more that the suction of the hydraulic fluid 14 is prevented by drying.

  Therefore, the flow of the hydraulic fluid 14 in the wick 17 can be prevented from being interrupted, and loss (heat loss) in which the heat of the heating element 3 escapes to the case 15 can be suppressed.

  Incidentally, in this example, the inside of the case 15 is set to atmospheric pressure without reducing pressure, the temperature of the external heat source is set to 230 ° C., and the temperature of the high pressure chamber 156 is set to 102 ° C. and the temperature of the low pressure chamber 157 is set to 97 ° C. during operation. It is trying to become.

  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 15, for example, if alcohol is used for the hydraulic fluid 14 and the inside of the case 15 is evacuated, the temperature of the external heat source can be applied below zero degree Is possible. When the temperature of the external heat source is low, it is not necessary to impart heat resistance to the structure of the wick 17 and the boiler part 11 (case 15 and the like). Therefore, a material having low heat resistance as the material of the wick 17 and the boiler part 11 ( Resin or the like).

(First embodiment)
In the first embodiment, as shown in FIG. 5, the exhaust passage 21 is formed in the bottom wall portion 152 of the case 15 according to the above-described embodiment of the present invention. Specifically, the exhaust passage 21 is configured by a groove 22 formed in a contact portion that contacts the wick 17 in the bottom wall portion 152. The groove 22 is formed so as to overlap with the through hole 172 of the wick 17. Therefore, the through hole 172 of the wick 17 communicates with the exhaust passage 21.

  In the example of FIG. 5, the groove 21 includes a plurality of concentric circular grooves and a plurality of linear grooves that connect the circular grooves radially.

  According to this, the vapor of the working fluid 14 evaporated from the lower surface of the wick 17 reaches the through hole 172 of the wick 17 through the exhaust passage 21, and the vapor that has reached the through hole 172 of the wick 17 exhausts to the upper side of the wick 17. Is done.

  As described above, by forming the exhaust passage 21 in the bottom wall portion 152 of the case 15, it is possible to easily escape the vapor evaporated from the lower surface of the wick 17 to the upper side of the wick 17. For this reason, the discharge | release of the vapor | steam of the working fluid 14 becomes good and can improve an output by extension.

  Further, the steam is further heated while passing through the exhaust passage 21 to become superheated steam, and the steam pressure increases, so the engine thrust increases. In other words, the output energy increases. However, since the heat transfer area decreases as the number of exhaust passages 21 increases, exhaust performance and heat transfer performance are in a trade-off relationship.

  The pattern of the groove 22 can be variously modified as shown in FIG. For example, as shown in FIG. 6A, the pattern of the groove 22 can be a combination of one circular groove and two or more types of linear grooves that intersect the circular groove radially.

  For example, as shown in FIG. 6B, the pattern of the grooves 22 may be a combination of a plurality of linear grooves so as to be orthogonal to each other. Further, as shown in FIGS. 6C and 6D, the pitch of the linear grooves can be appropriately modified.

(Second Embodiment)
In the first embodiment, the exhaust passage 21 is constituted by the groove 22, but in the second embodiment, as shown in FIG. 7, the exhaust passage 21 is disposed between the bottom wall portion 152 of the case 15 and the wick 17. An exhaust passage 21 is configured by sandwiching an exhaust passage forming member 23 that forms the passage.

  The exhaust passage forming member 23 is formed of a metal or the like having excellent heat conductivity, and is also responsible for heat transfer from the bottom wall portion 152 of the case 15 to the wick 17. In other words, in this embodiment, the heat transfer member responsible for heat transfer from the heating element 3 to the wick 17 is formed by being divided into the member constituting the bottom wall portion 152 and the exhaust passage forming member 23.

FIG. 7 shows an example in which a plurality of ball-shaped members are used as the exhaust passage forming member 23. As the ball-shaped member, for example, a bearing ball having a diameter of φ3 can be used. By using a plurality of ball-shaped members as the exhaust passage forming member 23, a space through which steam can flow is formed between the bottom wall portion 152 of the case 15 and the wick 17, and this space functions as the exhaust passage 21. It will be.

A net-like member may be used as the exhaust passage forming member 23 that forms the exhaust passage . As the mesh member, a woven wire mesh is suitable, and, for example, a linear 0.5 mm stainless mesh can be used.

A woven wire mesh is a wire mesh in which vertical lines and horizontal lines are woven by alternately crossing one by one while maintaining a constant interval. The vertical and horizontal lines of the woven wire mesh are bent in a wave shape. Therefore, by using the woven wire net as the exhaust passage forming member 23, a gap through which steam can flow is formed between the bottom wall portion 152 of the case 15 and the wick 17, and this gap functions as the exhaust passage 21. It becomes.

  Thus, also in this embodiment, the same effect as the second embodiment can be obtained.

(Third embodiment)
In each of the above embodiments, the plate 19 plays the role of preventing the central portion of the wick 17 from being lifted. However, in the third embodiment, the plate 19 is moved from the heating element 3 to the wick 17 as shown in FIG. Also plays a role as a heat transfer plate for heat transfer.

  Therefore, the plate 19 of this embodiment is formed of a material having excellent thermal conductivity. In the example of FIG. 8, the plate 19 is divided into a plurality of sectors, and a gap with a predetermined interval is provided between the sector-shaped divided plates.

  According to this, since the heat conduction path of the heating element 3 → the bottom wall portion 152 of the case 15 → the bolt 20 → the plate 19 → the wick 17 is formed, the wick 17 is heated from the upper surface side. For this reason, since the hydraulic fluid 14 evaporates from the upper surface of the wick 17, the vapor | steam discharge | release of the hydraulic fluid 14 becomes good, and an output can be improved by extension.

(Fourth embodiment)
In each of the above embodiments, the boiler unit 11 and the output unit 12 are accommodated in a common case 15, but in the fourth embodiment, the boiler unit 11 is in the boiler unit case 30 as shown in FIG. 9. The output part 12 and the condensing part 13 are accommodated in the reflux part case 31.

  The boiler part case 30 and the reflux part case 31 are arranged so as to be separated from each other and are connected via a steam passage forming part 32 and a circulation passage forming part 33. The steam passage forming portion 32 forms a steam passage 32 a that connects the boiler portion 11 and the output portion 12. The circulation passage forming unit 33 forms a circulation passage 33 a that allows the condensing unit 13 and the boiler unit 11 to communicate with each other.

  According to this, since the output unit 12 and the condensing unit 13 are arranged separately from the boiler unit 11, the heat of the boiler unit 11 is not easily transmitted to the output unit 12 and the condensing unit 13, and the output unit 12 and the condensing unit 13 Temperature rise is suppressed. For this reason, the aggregation / refluxing performance of the steam discharged from the output unit 12 is improved.

  In the example of FIG. 9, the boiler part case 30 and the reflux part case 31 are configured as follows.

  The boiler case 30 is placed on the heating element 3 that forms an external heat source. The boiler case 30 is composed of two flat plates 301 and 302 extending in the horizontal direction and cylinders 303 and 304 extending in the vertical direction between the two flat plates 151 and 152. That is, the upper and lower walls of the boiler part case 30 are configured by the flat plates 301 and 302, and the side walls of the boiler part case 30 are configured by the cylinders 303 and 304. The cylinder 303 is disposed above the cylinder 304.

  In this example, since water is used as the working fluid 14, the flat plates 301 and 302 and the tubes 303 and 304 are preferably formed of stainless steel having excellent water resistance. Seal members 305, 306, and 307 are interposed between the flat plates 301 and 302 and the cylinders 303 and 304. The seal member 307 interposed between the flat plate 302 and the cylinder 304 is formed in an annular plate shape, and also serves as a spacer for adjusting the vertical position of the cylinder 304.

  The internal space of the boiler case 30 is separated by a partition wall 34 into a high pressure chamber 308 and a low pressure chamber 309. The partition wall 34 is divided into a cylindrical wall part 341 disposed on the lower wall part 302 of the boiler part case 30 and a plate-like wall part 342 that covers the cylindrical wall part 341. In this example, the cylindrical wall portion 341 is formed in a bottomed cylindrical shape, and the plate-like wall portion 342 is formed in a disc shape. The bottom surface portion of the cylindrical wall portion 341 serves as a plate that prevents the wick 17 from being lifted.

  The partition wall 34 is formed of a heat-resistant heat-insulating material such as a heat-resistant resin so that the vapor in the high-pressure chamber (evaporation chamber) 308 is not cooled and condensed.

  A vapor passage 32 a communicates with the evaporation chamber 308. The steam passage forming portion 32 that forms the steam passage 32 a passes through the upper wall portion 301 of the boiler case 30 and is connected to the plate-like wall portion 342 of the partition wall 34. A sensor 35 for measuring the vapor pressure is arranged in the vapor passage forming part 32.

  A circulation passage 33a communicates with the low pressure chamber 309. The circulation passage forming portion 33 that forms the circulation passage 33 a is connected to the upper wall portion 301 of the boiler portion case 30.

  A space located between the tubes 303 and 304 of the boiler case 30 and the cylindrical wall portion 341 of the partition wall 34 in the low pressure chamber 309 constitutes a liquid reservoir chamber 309 a for storing the working fluid 14 supplied to the evaporation chamber 308. is doing. That is, the liquid reservoir chamber 309 a is disposed on the horizontal direction side of the evaporation chamber 308.

  The wick 17 is sandwiched between the bottom wall portion (lower wall portion) 302 of the boiler case 30 and the cylindrical wall portion 341 of the partition wall 34. The wick 17 is held in the boiler case 30 in a state where the wick 17 is compressed by receiving a load from the cylindrical wall portion 301.

  Since the bottom wall 302 of the boiler case 30 is thermally connected to the heating element 3, the wick 17 receives heat from the heating element 3 through the bottom wall 302 of the boiler case 30. Therefore, the bottom wall 302 of the boiler case 30 serves as a heat transfer member.

  The reflux part case 31 is disposed above the boiler part case 30. The output unit 12 is attached to the center of the lower surface of the reflux unit case 31. A circulation passage forming portion 33 that forms a circulation passage 33 a is connected to the outer peripheral side portion of the lower surface of the reflux portion case 31. The condensing unit 13 is configured by a space around the output unit 12 in the internal space of the boiler unit case 30.

  A sensor 36 for measuring the rotational speed of the fan 1d is fixed to the boiler case 30.

  According to the above configuration, the heat of the heating element 3 is transmitted to the hydraulic fluid 14 in the evaporation chamber 308 via the bottom wall portion 302 of the boiler unit case 30, and the hydraulic fluid 14 evaporates. The steam generated in the evaporation chamber 308 is supplied to the output unit 12 through the steam passage 32a. Thereby, the energy of the steam is converted into mechanical energy.

  Vapor discharged from the output unit 12 dissipates heat into the atmosphere at the condensing unit 13 and condenses, and the working fluid 14 condensed at the condensing unit 13 returns to the low-pressure chamber 309 through the circulation passage 33a and accumulates in the liquid storage chamber 309a. . The working fluid 14 accumulated in the liquid reservoir chamber 309a is sucked into the wick 17 and supplied to the evaporation chamber 308 to evaporate.

  Thus, also in this embodiment, the working fluid 14 in the liquid reservoir chamber 309a can be returned to the high-pressure evaporation chamber 308 without using external energy.

  Although illustration is omitted, also in the present embodiment, the exhaust passage 21 similar to that in the first and second embodiments can be formed in the bottom wall portion 302 of the boiler case 30. As a result, the vapor evaporated from the lower surface of the wick 17 can be easily escaped to the upper side of the wick 17, and the output can be improved.

(Fifth embodiment)
The fifth embodiment shows a specific configuration example of the through hole 172 of the wick 17 in each of the above embodiments.

  In the example of FIG. 10, the through-hole 172 that passes through the front and back of the wick 17 is formed in a groove shape extending in the plate surface direction of the wick 17. More specifically, the through hole 172 is formed in a cross groove shape extending radially from the center of the wick 17 in four directions.

  In the modification of FIG. 11, a large number of through holes 172 are dispersed. More specifically, the through-hole 172 is composed of a large number of circular holes, and the large number of circular holes are distributed on the plate surface of the wick 17.

  According to this, since steam is generated from the edge (interface) of the through-hole 172, the amount of steam can be improved, and the output can be improved. In particular, in the example of FIGS. 10 and 11, the entire length of the edge (interface) of the through hole 172 can be increased. For this reason, the amount of steam can be further improved, and as a result, the output can be further improved.

  In addition, in the example of FIG. 10, FIG. 11, the plate 19 is comprised with the net plate. Thereby, even if the through-hole 172 is formed over a wide range, the wick 17 can be prevented from being lifted without hindering the release of vapor from the edge (interface) of the through-hole 172.

(Sixth embodiment)
In each of the above embodiments, the wick 17 is composed of a single flat plate wick. In the sixth embodiment, as shown in FIG. 12, the wick 17 includes a plurality of flat plate wicks (flat plate operation). (Liquid introduction member) 40 and 41 are laminated. In this example, each of the flat wicks 40 and 41 is formed of a braided material of a stainless wire and an aramid fiber (resin fiber). Each of the flat plate-like wicks 40 and 41 may be formed of RAB (a mixture of aramid fibers and rock wool particles).

  In the present embodiment, the flat wicks 40 and 41 have the same outer diameter and are laminated such that the outer peripheral edge is aligned with the outer peripheral surface of the cylindrical wall 161 of the partition wall 16.

  According to this, the hydraulic fluid 14 in the liquid storage chamber 157 a is sucked into the flat plate wicks 40 and 41 and flows to the center side of the flat plate wicks 40 and 41. In the central part of the flat wick 40 adjacent to the bottom wall 152 of the case 15 among the flat wicks 40 and 41, the hydraulic fluid 14 is heated from the bottom wall 152 and evaporates.

  Then, the hydraulic fluid 14 is not only supplied to the central portion of the flat plate wick 40 from the radial outside of the flat plate wick 40 in the horizontal direction but also operates vertically from the central portion of the other flat plate wick 41. Liquid 14 is supplied. For this reason, the supply property of the hydraulic fluid 14 is improved, and as a result, the output can be improved.

(Seventh embodiment)
In the sixth embodiment, the outer peripheral edge portions of the flat plate wicks 40 and 41 are aligned with the outer peripheral surface of the cylindrical wall portion 161 of the partition wall 16, but in the seventh embodiment, as shown in FIG. Of the flat wicks 40, 41, 42, the outer peripheral side portion 40 a of the flat wick 40 adjacent to the bottom wall portion 152 of the case 15 is expanded to the inner peripheral surface of the tube 153.

  According to this, the outer peripheral side portion 40a of the flat plate wick 40 is overlapped with the portion of the bottom wall 152 facing the liquid reservoir chamber 157a to insulate the liquid reservoir chamber 157a. It can suppress that the working fluid 14 evaporates. For this reason, the working fluid 14 in the liquid reservoir chamber 157a can be reliably supplied to the evaporation chamber 156, and thus the output can be improved.

  If the exhaust passage 21 is provided in the present embodiment as in the first and second embodiments, the same effect as in the first and second embodiments can be obtained.

(Other embodiments)
In the first to third embodiments, the condensing unit 13 is disposed on the upper side of the case 15. However, the present invention is not limited thereto, and for example, the condensing unit 13 is disposed on the side of the case 15. May be. The specific configuration of the outflow path 151a for allowing the vapor of the low-pressure chamber 157 to flow out to the condensing unit 13 and the recirculation path 151b for returning the working fluid 14 condensed in the condensing unit 13 to the low-pressure chamber 157 is as follows. The number can be changed as appropriate according to the arrangement position of 13.

  Moreover, in each said embodiment, although the boiler part 11 is accommodated in the single case, it divides | segments and accommodates the boiler part 11 in several cases, and connects several cases with piping suitably. It may be. For example, the liquid storage chamber 157a of the boiler unit 11 may be housed in a separate case, and the liquid storage chamber 157a and the evaporation chamber 156 may be connected by piping. In this case, the wick 17 can be disposed in a pipe connecting the liquid reservoir chamber 157a and the evaporation chamber 156.

3 Heating element (external heat source)
DESCRIPTION OF SYMBOLS 11 Boiler part 12 Output part 13 Condensing part 14 Hydraulic fluid 15 Case 16 Partition 17 Wick (member for hydraulic fluid introduction)
19 Plate (heat transfer plate)
21 Exhaust passage 23 Exhaust passage forming member 152 Bottom wall (heat transfer member)
152a Heat insulation groove 156 Evaporation chamber 157a Reservoir chamber 161 Cylindrical wall (load applying means)
172 Through hole

Claims (12)

The working fluid (14) is heated by the heat supplied from the external heat source (3) to generate the vapor of the working fluid (14), and is supplied to the evaporation chamber (156, 308). A boiler part (11) in which a liquid reservoir chamber (157a) for storing the hydraulic fluid (14 ) is formed;
An output section (12) through which the steam generated in the evaporation chamber (156, 308) flows and converts the energy of the steam to mechanical energy and takes it out;
Condensing unit is recirculated to condense the steam which has passed through the output unit (12), condensed the hydraulic fluid (14) to said fluid reservoir chamber (157 a) and (13),
Wherein arranged in the boiler section (11), said fluid reservoir chamber (157 a) the working fluid (14) a hydraulic fluid introducing member supplied to the evaporation chamber (156,308) and sucked by the capillary force of ( 17)
The evaporation chamber (156,308) is adapted to a higher pressure than the fluid reservoir chamber (157 a) the solution has been separated with respect to the reservoir chamber (157 a),
The hydraulic fluid introduction member (17)
(2σ / r) · cos θ> PH-PL
The boiler unit (11), the having an external heat source (3) and thermally connected to and in contact with the heat transfer member to the hydraulic fluid introducing member (17) (15 2),
Said hydraulic fluid introducing member (17) is heat from said external heat source (3) via the heat transfer member (15 2),
The heat transfer member to the abutting portion to the hydraulic fluid introducing member (17) of (15 2), said hydraulic fluid introducing member (17) the hydraulic fluid introducing member said steam generated from (17) An exhaust passage (21) for exhausting to the outside of the
The heat transfer member (152 ) has an upper surface portion extending in the horizontal direction,
The hydraulic fluid introduction member (17) is formed in a flat plate shape and is superimposed on the upper surface portion of the heat transfer member (152 ) ,
A through hole (172) penetrating the front and back is formed in a portion located inside the evaporation chamber (156) of the hydraulic fluid introduction member (17),
The boiler section (11) forms the liquid reservoir chamber (157a) on the horizontal side of the evaporation chamber (156),
A portion of the heat transfer member (152) located closer to the liquid reservoir chamber (157a) than a portion overlapping with the through hole (172) has a horizontal heat inside the heat transfer member (152). A heat insulating groove (152a) for suppressing conduction is formed,
The heat insulating groove (152a) has a shape in which an outer surface located on the external heat source (3) side of the heat transfer member (152) is recessed in a direction away from the external heat source (3),
In the heat transfer member (152), a portion (152b) located on the opposite side of the liquid reservoir chamber (157a) from the heat insulation groove (152a) receives heat from the external heat source (3) ,
The horizontal end surface (171) of the hydraulic fluid introduction member (17) located on the liquid reservoir chamber (157a) side of the heat insulating groove (152a ) is the operation of the liquid reservoir chamber (157a). A heat engine characterized in that it constitutes an inlet into which liquid (14) flows.
However, (sigma) is the surface tension of the said hydraulic fluid (14), r is the circle | round | yen equivalent radius of the space | gap in the said hydraulic fluid introduction member (17), (theta) is the said hydraulic fluid (14) with respect to the said hydraulic fluid introduction member (17). wetting angle), PH pressure of the evaporation chamber (156,308), PL is the pressure of the fluid reservoir chamber (157 a).   The heat engine according to claim 1, wherein the exhaust passage (21) includes a groove (22) formed in the heat transfer member (152). The heat transfer member (15 2), the exhaust passage forming member for forming an exhaust passage (21) (23), is formed by dividing into a member constituting a portion of the residual (152),
The exhaust passage forming member (23) is a net member or a plurality of ball members sandwiched between a member (152) constituting the remaining portion and the hydraulic fluid introduction member (17),
The heat engine according to claim 1, wherein the exhaust passage (21) is configured by a gap formed by the mesh member or the plurality of ball members. The boiler section (11) is overlapped on the surface of the hydraulic fluid introduction member (17) opposite to the heat transfer member (152 ), and heat from the external heat source (3) is introduced into the hydraulic fluid. The heat engine according to any one of claims 1 to 3, further comprising a heat transfer plate (19) for transmitting to the structural member (17). A boiler case (30) for housing the boiler part (11);
A reflux part case (31) for accommodating the output part (12) and the condensing part (13);
A steam passage forming portion (32) that forms a steam passage (32a) that connects the evaporation chamber (308) of the boiler portion (11) and the output portion (12);
A circulation passage forming portion (33) that forms a circulation passage (33a) communicating the condensing portion (13) and the liquid storage chamber (309a) of the boiler portion (11);
The boiler part case (30) and the reflux part case (31) are arranged so as to be separated from each other and connected via a steam passage forming part (32) and a circulation passage forming part (33). The heat engine according to any one of claims 1 to 4 . The heat engine according to any one of claims 1 to 5, wherein the through hole (172) communicates with the exhaust passage (21). The heat engine according to any one of claims 1 to 6, wherein the through hole (172) is formed in a groove shape extending in a plate surface direction of the hydraulic fluid introduction member (17). . The heat engine according to any one of claims 1 to 6, wherein a plurality of the through holes (172) are formed in a dispersed manner. The boiler section (11) has load applying means (161) for applying a load to the hydraulic fluid introduction member (17) so that a gap in the hydraulic fluid introduction member (17) is reduced.
The said hydraulic fluid introduction member (17) is hold | maintained in the said boiler part (11) in the state to which the said load was provided from the said load provision means (161), The Claim 1 thru | or 8 characterized by the above-mentioned. The heat engine as described in any one. The boiler part (11) has a partition wall (16) separating the evaporation chamber (156) and the liquid storage chamber (157a),
The partition wall (16) is disposed in the boiler part (11) so as to apply the load to the hydraulic fluid introduction member (17),
The heat engine according to claim 9 , wherein the load applying means (161) comprises the partition wall (16). The heat engine according to claim 10 , wherein the hydraulic fluid introduction member (17) extends to the evaporation chamber (156) side with respect to the load applying means (161). The heat engine according to any one of claims 1 to 11 , wherein the hydraulic fluid introduction member (17) is made of a material woven with at least resin fibers.

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