JP4363254B2 - Steam engine - Google Patents

Description

  The present invention provides a mechanical output from a drive unit for energy output that is driven by receiving pressure from the fluid as the fluid flows and displaces inside the fluid container due to repeated vaporization and liquefaction of the fluid by the heater and the cooler. The present invention relates to a steam engine that outputs energy.

  Conventionally, as one of steam engines, a fluid is enclosed in a fluid container, and the fluid in the container is heated and vaporized using a heater, and the vaporized fluid is cooled using a cooler. A steam engine configured to output energy to the outside by being liquefied is known (see, for example, Patent Document 1 and Patent Document 2).

In other words, this steam engine is configured to change the pressure in the fluid container by changing the state (vaporization or liquefaction) of the fluid, and to output mechanical energy from the energy output drive unit driven by the pressure change. ing.
JP 58-057014 (FIG. 1) Japanese Patent Application Laid-Open No. 2004-084523 (FIGS. 1 and 3)

  However, in such a steam engine, if the cross-sectional area of the portion of the fluid container where the fluid liquefies is set to an inappropriate size, the output work (output energy) to the outside by the steam engine becomes small. There is a problem.

  For example, if the cross-sectional area of the part corresponding to the cooler (fluid container cooling corresponding part) of the fluid container is formed too small (the inner radial dimension of the fluid container cooling corresponding part is formed too small), the fluid The heat transfer time from the inner wall of the fluid container to the center portion of the fluid is shortened in the container cross-sectional direction. Thereby, since the cooling efficiency with respect to the fluid in the fluid container cooling corresponding part becomes high (good), the fluid in the gaseous state is liquefied within a very short time.

  In this case, since the fluid vaporized in the part corresponding to the heater (fluid container heating corresponding part) in the fluid container moves to the fluid container cooling corresponding part in the fluid container and is instantly liquefied, The volume expansion amount of the steam engine becomes smaller, and the work of expansion in the steam engine becomes smaller. In such a steam engine, the PV diagram (diagram representing the relationship between pressure and volume) has a shape as shown in FIG. 6B, and the area of the PV diagram is reduced. There is a problem that the amount of work (output energy) is reduced.

  Note that the PV diagram shown in FIG. 6A shows a PV diagram as a theoretical value when fluid liquefaction and vaporization are ideally performed, and FIG. 6B and FIG. ) Shows a PV diagram as a theoretical value by a dotted line.

  In addition, when the cross-sectional area of the fluid container cooling corresponding part is formed to be excessively large (the inner radial dimension of the fluid container cooling corresponding part is excessively large), the fluid flows from the inner wall of the fluid container in the cross sectional direction of the fluid container. The heat transfer time to the central part becomes longer. Thereby, since the cooling efficiency with respect to the fluid in a fluid container cooling corresponding | compatible part becomes low (bad), the time until the fluid of a gaseous state liquefies becomes long.

  In this case, even if the fluid vaporized by the fluid container heating corresponding part moves to the fluid container cooling corresponding part, the time until the fluid in the gaseous state is liquefied becomes long. The internal pressure is maintained at a high pressure. As a result, as shown in FIG. 6C, there is a problem that the area of the PV diagram is reduced and the output work (output energy) to the outside is reduced. Furthermore, when the fluid in the gas state concentrates on the fluid container heating corresponding part, the fluid in the liquid state cannot be heated, and the pressure increase due to the vaporization of the fluid does not occur, and the operation of the steam engine may be abnormally stopped.

  On the other hand, in a steam engine in which a heater and a cooler are arranged with a gap therebetween, the cross-sectional area of a portion (fluid container heat-insulating gap) corresponding to the gap between the heater and the cooler in the fluid container is If it is formed small, the distance from the inner wall of the fluid container heat insulation gap to the center portion in the cross section direction of the fluid container is shortened and the heat transfer time is shortened, so the fluid container (specifically, the fluid container heat insulation gap) and The efficiency of heat exchange with the fluid is high (good).

  In the steam engine having such a configuration, when the fluid in the gaseous state moves from the fluid container heating corresponding part to the fluid container cooling corresponding part, the fluid is liquefied in the fluid container heat insulating gap part during the movement, and the fluid caused by the vaporization The volume expansion amount of the steam engine becomes smaller, and the work of expansion in the steam engine becomes smaller. Such a steam engine has a problem that the output work (output energy) to the outside becomes small because the PV diagram becomes as shown in FIG. 6B and the area of the PV diagram becomes small.

  Therefore, the present invention has been made in view of these problems, and the fluid is appropriately displaced by the change in the state of the fluid (vaporization, liquefaction) inside the fluid container, and the output work (output energy) to the outside It is an object of the present invention to provide a steam engine that can prevent a decrease in the temperature.

  The steam engine according to claim 1, which has been made to achieve such an object, includes a fluid container in which fluid can flow so that the fluid sealed in the fluid container is heated and vaporized by a heater. The cooler cools and liquefies the fluid that is heated and vaporized in the vessel. That is, in this steam engine, the energy output drive unit is driven by receiving pressure from the fluid as the fluid flows and displaces due to the repeated vaporization and liquefaction of the fluid by the heater and the cooler, so that the energy output The mechanical energy is output from the driving unit.

The steam engine includes a fluid container cooling corresponding part, which is a part corresponding to a cooler, and a fluid container heating corresponding part, a part corresponding to a heater. This is characterized in that the inner radial dimension of the portion is defined to be the same as the low-pressure heat penetration depth δ1 expressed by the following equation (1).

In the above formula (1), “a1” represents the temperature conductivity of the fluid at low pressure (temperature conductivity at low pressure), and “ω” represents the angular frequency of the fluid flow displacement.
Here, the numerical value range of the low pressure in the low temperature temperature conductivity a1 is a low pressure side range of the pressure range from the upper pressure limit value to the lower pressure limit value of the fluid inside the fluid container, and the size of the range is the pressure. This is a range corresponding to 25% of the difference between the upper limit value and the pressure lower limit value. That is, the low-temperature temperature conductivity a1 is obtained when the pressure range from the pressure lower limit value to the 25% value in the pressure range from the pressure upper limit value to the pressure lower limit value of the fluid inside the fluid container is a low pressure value range. It is the temperature conductivity of the fluid at any pressure value included in this low pressure numerical range.

  In the steam engine configured as described above, the fluid container has an inner radius dimension (a cross-sectional area of the fluid container cooling corresponding part) of the fluid container cooling corresponding part based on the low-pressure heat penetration depth δ1 of the fluid. . In addition, since the heat penetration depth is one of the indexes that represent the ease of heat transfer in the fluid that reciprocates at the angular frequency ω, the fluid container configured as described above is a fluid container cooling unit. The amount of heat exchange with the fluid can be defined within a certain range.

  Thereby, this steam engine can prevent the cooling efficiency with respect to the fluid in the fluid container cooling corresponding part from becoming excessively high (good) or excessively low (bad), and the fluid in the gaseous state can be prevented at an appropriate timing. It can be liquefied.

  Therefore, according to the steam engine of the present invention, the fluid in the gaseous state can be liquefied at an appropriate timing inside the fluid container, so that the fluid can be appropriately displaced and the output work (output energy) to the outside. Can be prevented. In addition, it is possible to avoid an abnormal stop of the operation of the steam engine due to the fact that the timing at which the gaseous fluid is liquefied is too late.

  In the above-described steam engine, as described in claim 2, the low-temperature temperature conductivity a1 is preferably the fluid temperature conductivity at the lower pressure limit value of the fluid inside the fluid container.

  By setting the low-temperature temperature conductivity a1 in this way, the fluid can be cooled most efficiently at the timing when the pressure of the fluid reaches the lower pressure limit, and the gaseous fluid can be liquefied when the volume of the fluid becomes the largest. Therefore, the expansion energy of the fluid can be used without waste.

  Therefore, according to such a steam engine, the expansion energy generated by the vaporization of the fluid can be used without waste, and the fluid can be displaced and flowed appropriately, thereby preventing a decrease in output work (output energy) to the outside. it can.

  Next, in order to achieve the above-mentioned object, the steam engine according to claim 3, wherein a fluid is sealed in a fluid container so that the fluid can flow, and a heater heats the fluid sealed in the fluid container. The fluid which is vaporized and heated by the heater is vaporized, and the cooler cools and liquefies the fluid. In other words, the engine is driven by receiving the pressure from the fluid as the fluid is displaced by repeated vaporization and liquefaction of the fluid by the heater and the cooler. The mechanical energy is output from the driving unit.

  The heater and the cooler are arranged with a gap therebetween, and the fluid container includes a fluid container cooling corresponding part that is a part corresponding to the cooler and a fluid container heating corresponding part that is a part corresponding to the heater. And a fluid container heat insulating gap that is a portion corresponding to the gap between the heater and the cooler.

Here, the inner radial dimension of the heat insulation gap of the fluid container is “r2”, and the temperature conductivity of the fluid when the steam engine is at the upper limit of the pressure inside the fluid container when the steam engine is operating. the pressure during the thermal diffusivity is when the "a2", defined to represent the variables τ in the following equation (2).

  In addition, the numerical value range of the high pressure in the high temperature temperature conductivity a2 is a pressure corresponding to the pressure upper limit value on the highest pressure side in the pressure range from the fluid pressure upper limit value to the pressure lower limit value inside the fluid container. That is, the high temperature temperature conductivity a2 is the temperature conductivity of the fluid when the pressure is the upper limit value inside the fluid container.

  The steam engine is characterized in that the fluid container is formed such that the heat insulation gap inner radius r2 that is the inner radius of the fluid container heat insulation gap satisfies the following expression (3).

In the above equation (3), “ω” represents the angular frequency of fluid flow displacement.
Here, a curve representing the relationship between the left side (ωτ) in Equation (3) and the rate of heat loss (specifically, the rate of heat loss due to heat conduction from the fluid to the fluid container thermal insulation gap) is shown in FIG. Show. In FIG. 5, a curve is represented on a semilogarithmic coordinate plane having ωτ as a logarithmic axis. And as shown in FIG. 5, it turns out that the ratio of a heat loss falls, so that the value of (omega) tau becomes large.

  Generally, in order to prevent a decrease in output work (output energy) of the steam engine, it is necessary to set the rate of heat loss in the fluid container heat insulation gap to at least 20% or less. According to FIG. 5, the rate of heat loss when the value of ωτ is about 7 is 20%, and the rate of loss when the value of ωτ is 10 is about 16%. Therefore, by setting ωτ to 10 or less, the rate of heat loss can be reliably suppressed to 20% or less.

  From this, since the steam engine provided with the fluid container in which the radial dimension r2 in the heat insulation gap is defined based on the expressions (2) and (3) can reduce the heat loss in the heat insulation gap in the fluid container, It is possible to prevent the fluid from being liquefied in the fluid container heat insulating gap. Thereby, since the fluid in a gaseous state is liquefied in the fluid container cooling corresponding part without being liquefied in the fluid container heat-insulating gap, the volume expansion amount of the fluid inside the fluid container can be sufficiently secured.

  Therefore, according to this steam engine, since the internal pressure of the fluid container is sufficiently increased due to sufficient volume expansion of the fluid, the energy output drive unit can be reliably driven by the internal pressure. It is possible to prevent the work amount (output energy) from decreasing.

  Next, in the steam engine described above (claim 1 or claim 2), as described in claim 4, the heater and the cooler are arranged with a gap therebetween, and the fluid container is a heater. It is good to provide the fluid container heat insulation clearance part which is a part corresponding to the clearance gap between a heat exchanger and a cooler.

  And when the radius dimension in the heat insulation gap part which is an inner radius dimension of the fluid container heat insulation gap part is set to “r2,” the fluid container so that the radius dimension r2 in the heat insulation gap part satisfies the expressions (4) and (5). Should be formed.

  In addition, Formula (4) is the same formula as Formula (2) mentioned above, Formula (5) is the same formula as Formula (3) mentioned above, Each variable used by Formula (4) and Formula (5) Is the same as each variable used in the above-described equations (2) and (3).

  In the fluid container configured in this way, the inner radial dimensions of the fluid container cooling corresponding part and the fluid container heat insulation gap are each defined within a certain range, so the heat exchange amount with the fluid in the fluid container cooling corresponding part In addition to being appropriately set, heat loss in the heat insulation gap of the fluid container can be reduced.

  In the steam engine including such a fluid container, the fluid in the gaseous state can be liquefied at an appropriate timing in the fluid container cooling corresponding part, so that the fluid can be appropriately flow-displaced, By reducing the heat loss, the fluid is sufficiently expanded in volume and the internal pressure of the fluid container is sufficiently increased.

  Therefore, according to this steam engine, in addition to being able to appropriately flow and displace the fluid, the internal pressure of the fluid container can be sufficiently increased to reliably drive the energy output drive unit. It is possible to prevent the output work amount (output energy) from decreasing.

Moreover, about the steam engine provided with the fluid container which has a fluid container heat insulation clearance part, the inside radial dimension of the fluid container heating corresponding | compatible part is good to be the same dimension as the radial dimension in a heat insulation clearance part, as described in Claim 5. .

  In other words, the fluid container configured in this way is formed with no step on the inner wall at the boundary portion between at least the fluid container heating support part and the fluid container heat insulation gap, so the fluid container heating support part and the fluid container heat insulation The fluid moves smoothly between the gaps. As a result, when the fluid is fluidly displaced, it is possible to prevent wasteful consumption of energy at the stepped portion and the like, and energy loss can be reduced.

Therefore, according to this steam engine, the energy loss at the time of fluid displacement can be reduced, and the output work (output energy) to the outside can be prevented from decreasing.
Furthermore, for a steam engine including a fluid container having a fluid container heat insulation gap, as described in claim 6, the inner radius dimension of the fluid container heating corresponding part, the inner radius dimension of the fluid container cooling corresponding part, and the heat insulation It is preferable that the radial dimension in the gap is the same .

  That is, the fluid container configured in this way is formed in a state where there is no step on the inner wall of this region from the fluid container heating corresponding part to the fluid container cooling corresponding part via the fluid container heat insulation gap. In such a fluid container, since the fluid can smoothly move at least in the region from the fluid container heating support part to the fluid container cooling support part through the fluid container heat-insulating gap part, wasted energy at the stepped part or the like. Consumption can be prevented.

  Therefore, according to this steam engine, the energy loss at the time of fluid displacement can be reduced, and the output work (output energy) to the outside can be prevented from decreasing.

Embodiments to which the present invention is applied will be described below with reference to the drawings.
In the present embodiment, the steam engine according to the present invention is applied to a linear motor that vibrates and displaces the mover 2 in the generator 1, and FIG. 1 includes the steam engine 10 and the generator 1 according to the present embodiment. The schematic block diagram of a power generator is represented.

In addition, the generator 1 which concerns on this embodiment is a linear vibration generator which generate | occur | produces an electromotive force by carrying out the vibration displacement of the needle | mover 2 with which the permanent magnet was embed | buried.
As shown in FIG. 1, the steam engine 10 includes a fluid container 11 in which a working fluid 20 is enclosed so as to flow, a heater 12 that heats the working fluid 20 inside the fluid container 11, and heating by the heater 12. And a cooler 13 for cooling the vaporized vapor.

The heater 12 and the cooler 13 are arranged with a certain gap so as not to be in direct contact with each other.
For example, when the steam engine 10 is installed in a water-cooled internal combustion engine, the heater 12 can be a heater configured to heat the working fluid 20 using the exhaust gas of the internal combustion engine. Reference numeral 13 may be a cooler configured to cool the working fluid 20 using the cooling water of the internal combustion engine.

  The fluid container 11 includes a fluid container heating corresponding part 31 corresponding to the heater 12, a fluid container cooling corresponding part 33 corresponding to the cooler 13, and the heater 12 and the cooler 13. And a fluid container heat-insulating gap 35 which is a part corresponding to the gap.

  The fluid container heating corresponding part 31 and the fluid container cooling corresponding part 33 of the fluid container 11 are formed of a material having excellent thermal conductivity, and the other parts of the fluid container 11 are excellent in heat insulation. Made of different materials. Further, the fluid container 11 is formed of a material having excellent corrosion resistance against the working fluid 20 sealed inside.

  In the present embodiment, the working fluid 20 is water, and the fluid container 11 is configured using copper or aluminum as a material having excellent thermal conductivity and using stainless steel as a material having excellent heat insulation. Yes.

  The fluid container 11 is formed into a substantially U-shaped pipe by bending a pipe made of stainless steel and copper (or aluminum) into a substantially U-shape, for example, and the bent portion 11a is at the lowermost part. The two straight portions 11b and 11c that are positioned and extend from the bent portion 11a are arranged so as to be positioned on the vertical line.

  Of the two straight portions 11b and 11c constituting the fluid container 11, one of the straight portions 11b is the fluid container heating corresponding portion 31 and the fluid container cooling corresponding portion 33, and the fluid container heating corresponding portion 31 is the fluid. It is formed so as to be positioned above the container cooling counterpart 33 and its upper end is closed.

The heater 12 is provided so as to surround the fluid container heating corresponding part 31, and the cooler 13 is provided so as to surround the fluid container cooling corresponding part 33.
On the other hand, a piston 14 that is displaced by receiving pressure from the working fluid 20 is slidably provided at the upper end portion of the other linear portion 11c constituting the fluid container 11.

  The piston 14 is connected to the shaft 2 a of the mover 2 of the generator 1. In the generator 1, a spring 3 that presses and urges the mover 2 toward the piston 14 is provided on the side opposite to the piston 14 across the mover 2.

  In the steam engine 10 of the present embodiment configured as described above, when the heater 12 and the cooler 13 are operated, first, as shown in FIG. Among them, the liquid (water) in the vicinity of the upper end is heated and vaporized (isothermal expansion), and the vaporized vapor further expands (adiabatic expansion) to push down the liquid level inside the linear portion 11b. For this reason, the liquid portion of the working fluid 20 enclosed in the fluid container 11 is fluidly displaced from the straight portion 11b toward the straight portion 11c, and pushes up the piston 14.

  Further, when the liquid level of the liquid inside the linear portion 11 b of the fluid container 11 falls to the fluid container cooling corresponding portion 33 and the steam enters the fluid container cooling corresponding portion 33, the steam passes through the fluid container cooling corresponding portion 33. Then, since the liquid is cooled and liquefied by the cooler 13, the force to push down the liquid surface in the straight portion 11b disappears (isothermal compression → adiabatic compression), and the liquid surface on the straight portion 11b side rises. As a result, the piston 14 on the generator 1 side once pushed up by the expansion of the steam descends.

  Such an operation is repeatedly executed until the operations of the heater 12 and the cooler 13 are stopped. During this time, the working fluid 20 in the fluid container 11 is periodically displaced (so-called self-excited vibration). That is, the steam engine 10 generates a change in the internal pressure of the fluid container 11 in accordance with a change in state (liquefaction, vaporization) of the working fluid 20, and starts from the piston 14 driven by the working fluid 20 that is fluidly displaced by the pressure change. It is configured to output the dynamic energy to the outside. The energy output from the steam engine 10 is used as energy for moving the mover 2 of the generator 1 up and down.

  The steam engine 10 according to the present embodiment can drive the generator 1 without directly exposing the piston 14 to high-temperature and high-pressure steam. Yes.

The fluid container 11 is configured such that the inner radius r1 of the fluid container cooling corresponding portion 33 is the same as the low-pressure heat penetration depth δ1 expressed by the above-described formula (1).
3 is a cross-sectional view showing a schematic configuration of a portion corresponding to the fluid container cooling corresponding portion 33 in the fluid container 11. In FIG. In the figure, φd represents the inner diameter dimension of the fluid container cooling corresponding portion 33, and r 1 represents the inner radius dimension of the fluid container cooling corresponding portion 33.

  The low-temperature heat penetration depth δ1 is the temperature conductivity of the working fluid 20 at low pressure (low-temperature temperature conductivity a1) [m2 / sec. ], And an angular frequency ω [rad / sec.] Representing the characteristics of the flow displacement of the working fluid 20 inside the fluid container 11 (in other words, the characteristics of the reciprocating motion of the piston 14). ].

  In the present embodiment, the temperature conductivity of the working fluid 20 when the internal pressure of the fluid container 11 becomes the pressure lower limit value is used as the low-temperature temperature conductivity a1. That is, the internal pressure of the fluid container 11 changes with the state change (vaporization and liquefaction) of the working fluid 20, and the pressure fluctuation range (the pressure range from the pressure upper limit value to the pressure lower limit value of the working fluid 20). Of these, the low temperature thermal penetration depth δ1 is defined with the temperature conductivity at the pressure lower limit as the low temperature thermal conductivity a1. The inner radius r1 of the fluid container cooling corresponding portion 33 is defined to be the same as the low-pressure heat penetration depth δ1.

  Since the heat penetration depth is one of the indices representing the ease of heat transfer in the fluid reciprocating at the angular frequency ω, the inner radial dimension r1 of the fluid container cooling corresponding portion 33 is the low pressure heat penetration depth δ1. The fluid containers 11 set to the same size can regulate the amount of heat exchange with the working fluid 20 in the fluid container cooling corresponding portion 33 within a certain range.

  Thereby, the steam engine 10 can prevent that the cooling efficiency with respect to the fluid in the fluid container cooling corresponding part 33 is excessively high (good) or excessively low (bad), and the working fluid 20 in the gas state is appropriately selected. It can be liquefied at the right time.

  In particular, the steam engine 10 sets the temperature conductivity of the working fluid 20 when the internal pressure of the fluid container 11 reaches the lower pressure limit as the low-temperature temperature conductivity a1, and thus the internal pressure of the fluid container 11 In other words, the working fluid 20 can be cooled most efficiently at the timing when the pressure of the working fluid 20 reaches the pressure lower limit value. That is, the steam engine 10 can liquefy the working fluid 20 in a gaseous state when the volume of the working fluid 20 becomes the largest, and thus can utilize the expansion energy of the working fluid 20 without waste.

  Therefore, according to the steam engine 10 of the present embodiment, since the working fluid 20 in a gas state can be liquefied at an appropriate timing inside the fluid container 11, the working fluid 20 can be appropriately fluidly displaced, and the piston 14 A decrease in output work (output energy) to the generator 1 due to reciprocating motion can be prevented. In addition, since the timing at which the gaseous working fluid 20 is liquefied is not excessively delayed in the steam engine 10, the self-excited vibration of the working fluid 20 is caused by the fact that the liquefaction timing of the working fluid 20 is significantly delayed. It can be stopped and the engine can be prevented from abnormally stopping.

In addition, the fluid container 11 is configured such that the heat insulation gap inner radius dimension r2 of the fluid container heat insulation gap 35 satisfies the above-described expressions (2) and (3).
FIG. 4 is a cross-sectional view showing a schematic configuration of a portion of the fluid container 11 corresponding to the fluid container heat insulating gap 35 and the fluid container heating corresponding portion 31. In the figure, r2 represents the inner radius dimension of the fluid container heat insulation gap 35 (hereinafter also referred to as the heat insulation gap inner radius dimension).

  Then, as shown in the curve (see FIG. 5) representing the relationship between the left side (ωτ) in equation (3) and the rate of heat loss due to heat conduction from the working fluid 20 to the fluid container thermal insulation gap 35 (see FIG. 5), It can be seen that the ratio of heat loss decreases with increasing.

  Further, according to FIG. 5, since the loss ratio when the value of ωτ is 10 is about 16%, the fluid container adiabatic gap is satisfied so as to satisfy the condition that ωτ is 10 or less as in this embodiment. In the fluid container 11 in which the radius dimension r2 in the heat insulating gap of the portion 35 is defined, the rate of heat loss in the heat insulating gap 35 of the fluid container can be reliably suppressed to 20% or less.

  Since the steam engine 10 including such a fluid container 11 can reliably suppress the heat loss ratio to 20% or less, the heat loss in the fluid container heat-insulating gap 35 can be reduced, and the working fluid 20 in the gas state is fluid. It is possible to prevent liquefaction at the container heat insulating gap 35. As a result, the working fluid 20 in the gaseous state is liquefied by the fluid container cooling corresponding portion 33 without being liquefied by the fluid container heat insulation gap portion 35. For this reason, the steam engine 10 can sufficiently secure the volume expansion amount of the working fluid 20 inside the fluid container 11.

  Therefore, since the steam engine 10 is configured to sufficiently increase the internal pressure of the fluid container 11 when the working fluid 20 is sufficiently expanded in volume, the piston 14 can be reliably driven by the internal pressure. It is possible to prevent the output work amount (output energy) from being reduced.

  Further, as shown in FIG. 4, the fluid container 11 is configured such that the inner radius dimension of the fluid container heating corresponding portion 31 is the same as the inner radius dimension r <b> 2 of the heat insulation gap portion of the fluid container heat insulation gap portion 35. . That is, the fluid container 11 is formed in a state where there is no step on the inner wall at the boundary portion between the fluid container heating corresponding part 31 and the fluid container heat insulating gap part 35, and the fluid container heating corresponding part 31 and the fluid container heat insulating gap part When the working fluid 20 is displaced with respect to the flow 35, the working fluid 20 moves smoothly.

  Thereby, when the working fluid 20 is displaced, the steam engine 10 can prevent wasteful consumption of energy at the stepped portion and the like, and energy loss can be reduced. Therefore, the steam engine 10 generates power by self-excited vibration of the working fluid 20. It can prevent that the work amount (output energy) output with respect to the machine 1 falls.

  Further, as shown in FIG. 1, the fluid container 11 includes an inner radius dimension of the fluid container heating corresponding section 31, an inner radius dimension r <b> 1 of the fluid container cooling corresponding section 33, and an inner radius of the heat insulating clearance section of the fluid container insulating clearance section 35. The dimension r2 is all formed with the same dimension.

  That is, the fluid container 11 is formed in a state where there is no step on the inner wall of this region from the fluid container heating corresponding portion 31 to the fluid container cooling corresponding portion 33 via the fluid container heat insulation gap portion 35. In such a fluid container 11, the working fluid 20 can smoothly move at least in the region from the fluid container heating corresponding part 31 to the fluid container cooling corresponding part 33. The magnitude of the resistance received can be reduced.

  Therefore, in the steam engine 10, the magnitude of the resistance that the working fluid 20 receives from the inner wall of the fluid container 11 when the working fluid 20 flows and displaces in the region from the fluid container heating corresponding portion 31 to the fluid container cooling corresponding portion 33. Therefore, useless energy consumption can be prevented, and energy can be efficiently output to the generator 1.

In the present embodiment, the piston 14 corresponds to the energy output drive unit described in the claims.
The embodiment to which the present invention is applied has been described above, but the present invention is not limited to the above-described embodiment, and various modes can be adopted within the technical scope of the present invention.

  For example, the numerical value range of the low pressure in the low-temperature temperature conductivity a1 is not limited to the lower pressure limit value in the internal pressure range of the fluid container 11, and at least the gaseous working fluid 20 is appropriately timed inside the fluid container 11. As long as the inner diameter dimension of the fluid container cooling corresponding portion 33 is defined so that it can be liquefied by the above-mentioned numerical value range. That is, when the pressure range from the pressure lower limit value to the 25% value in the pressure range from the upper pressure limit value to the lower pressure limit value of the fluid inside the fluid container is a low pressure numerical value range, the low-temperature temperature conductivity a1 is What is necessary is just to set the temperature conductivity of the fluid in any pressure value included in this low-pressure numerical range.

  In this way, the low-temperature temperature conductivity a1 is set, the low-pressure heat penetration depth δ1 is determined using the above-described equation (1), and the low-pressure heat penetration depth δ1 is the same or substantially the same size. In addition, the fluid container 11 in which the inner radius r1 of the fluid container cooling corresponding portion 33 is defined can regulate the heat exchange amount with the working fluid 20 in the fluid container cooling corresponding portion 33 within a certain range.

  Since the steam engine 10 including such a fluid container 11 can liquefy at least the working fluid 20 in a gaseous state at an appropriate timing, the working fluid 20 can be appropriately flow-displaced, and output work to the generator 1 can be changed. A decrease in (output energy) can be prevented.

  Next, in the above-described embodiment, the steam engine in which the radius dimension in the heat insulation gap is set so that the value of ωτ is 10 or more has been described, but in order to further reduce the heat loss ratio in the heat insulation gap in the fluid container It is preferable to set the radius dimension in the heat insulating gap so that the value of ωτ is further increased.

  For example, judging based on the curve shown in FIG. 5, in order to make the heat loss ratio in the heat insulation gap of the fluid container 10% or less, the value of the radius dimension r2 in the heat insulation gap so that the value of ωτ is 20 or more. In order to set the heat loss ratio in the heat insulation gap portion of the fluid container to 5% or less, the value of the radial dimension r2 in the heat insulation gap portion may be set so that the value of ωτ is 30 or more. Furthermore, in order to reduce the heat loss ratio in the heat insulation gap portion of the fluid container to 2% or less in order to reduce heat loss, the value of the radial dimension r2 in the heat insulation gap portion is set so that the value of ωτ becomes 100 or more. Is desirable.

  Next, the fluid container 11 is not limited to the case where the inner radius dimension of the fluid container heating corresponding portion 31 is the same as the inner radius dimension r2 of the heat insulating gap portion 35 of the fluid container heat insulating gap portion 35. That's fine. That is, if the dimensions are substantially the same, there is almost no step on the inner wall of the fluid container 11, which is large with respect to the movement of the working fluid 20 between the fluid container heating corresponding portion 31 and the fluid container heat insulation gap portion 35. This is because it is not a resistance, and wasteful energy consumption can be reduced.

  Further, the fluid container 11 is not limited to the case where the inner radius dimension of the fluid container cooling corresponding portion 33 is the same dimension as the radius dimension r2 in the heat insulation gap portion of the fluid container heat insulation gap portion 35. Good. That is, if the dimensions are substantially the same, there is almost no step on the inner wall of the fluid container 11, which is large with respect to the movement of the working fluid 20 between the fluid container cooling support portion 33 and the fluid container heat insulation gap portion 35. This is because it is not a resistance, and wasteful energy consumption can be reduced.

  In addition, the heater is not limited to a configuration that takes in a heat source material (exhaust gas, etc.) from the outside. For example, a heater (electric heater, etc.) that generates heat when energized or combustion of fuel such as gas generates heat. You may comprise using the heater to do.

It is a schematic block diagram showing schematic structure of a power generator provided with a steam engine and a generator. It is explanatory drawing showing the operation principle of a steam engine. It is sectional drawing showing schematic structure of the part corresponded to the fluid container cooling corresponding | compatible part among fluid containers. It is sectional drawing showing schematic structure of the part corresponded to a fluid container heat insulation clearance gap part and a fluid container heating corresponding | compatible part among fluid containers. It is explanatory drawing which shows the curve showing the relationship between the variable (omega) tau and the rate of heat loss (ratio of the heat loss by the heat conduction from the fluid to the fluid container heat insulation clearance). (A) is a PV diagram as a theoretical value when fluid liquefaction and vaporization are ideally performed, and (b) is a PV diagram when the cross-sectional area of the fluid container cooling counterpart is formed small. It is a diagram and (c) is a PV diagram when the cross-sectional area of the fluid container cooling corresponding part is formed large.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Generator, 2 ... Movable element, 10 ... Steam engine, 11 ... Fluid container, 11a ... Bending part, 11b ... Linear part, 11c ... Linear part, 12 ... Heater, 13 ... Cooler, 14 ... Piston, 20 ... working fluid, 31 ... fluid container heating support part, 33 ... fluid container cooling support part, 35 ... fluid container heat insulation gap part.

Claims (6)

A fluid container in which fluid can be flowed, and
A heater that heats and vaporizes the fluid enclosed in the fluid container;
A cooler that cools and liquefies the fluid heated and vaporized by the heater;
An energy output drive unit that reciprocates under pressure from the fluid as the fluid flows and displaces due to repeated vaporization and liquefaction of the fluid by the heater and the cooler; and
A steam engine that outputs mechanical energy from the energy output drive unit,
The fluid container includes a fluid container cooling corresponding part which is a part corresponding to the cooler, and a fluid container heating corresponding part which is a part corresponding to the heater.
The inner radial dimension of the fluid container cooling corresponding part is as follows when the low-temperature temperature conductivity, which is the temperature conductivity of the fluid at low pressure, is “a1”, and the angular frequency of the fluid flow displacement is “ω”: Formula (1)

It is specified to be the same size as the heat penetration depth δ1 at low pressure represented by
The low-temperature temperature conductivity a1 is the pressure value in any one of the pressure ranges from the pressure lower limit value to the 25% value in the pressure range from the pressure upper limit value to the pressure lower limit value of the fluid inside the fluid container. The temperature conductivity of the fluid,
A steam engine characterized by. The low-temperature temperature conductivity a1 is the temperature conductivity of the fluid at the pressure lower limit value of the fluid inside the fluid container,
The steam engine according to claim 1. A fluid container in which fluid can be flowed, and
A heater that heats and vaporizes the fluid enclosed in the fluid container;
A cooler that cools and liquefies the fluid heated and vaporized by the heater;
An energy output drive unit that reciprocates under pressure from the fluid as the fluid flows and displaces due to repeated vaporization and liquefaction of the fluid by the heater and the cooler; and
A steam engine that outputs mechanical energy from the energy output drive unit,
The heater and the cooler are arranged with a gap between them,
The fluid container includes a fluid container cooling corresponding part that is a part corresponding to the cooler, a fluid container heating corresponding part that is a part corresponding to the heater, and a gap between the heater and the cooler. A fluid container insulation gap that is a corresponding part, and
The inner radial dimension of the heat insulation gap of the fluid container is “r2”, which is the temperature conductivity of the fluid when the steam engine is at the upper limit of the pressure inside the fluid container when the steam engine is operating. When the temperature conductivity at high pressure is “a2” and the variable τ is defined as in the following equation (2),

The radius r2 in the heat insulating gap of the fluid container is expressed by the following equation (3) when the angular frequency of the fluid flow displacement is “ω”.

Be satisfied,
A steam engine characterized by. The heater and the cooler are arranged with a gap between them,
The fluid container includes a fluid container heat insulation gap that is a portion corresponding to a gap between the heater and the cooler;
The inner radial dimension of the heat insulation gap of the fluid container is “r2”, which is the temperature conductivity of the fluid when the steam engine is at the upper limit of the pressure inside the fluid container when the steam engine is operating. When the temperature conductivity at high pressure is “a2” and the variable τ is defined as in the following equation (4),

The radius r2 in the heat insulating gap of the fluid container is expressed by the following equation (5) when the angular frequency of the fluid flow displacement is “ω”.

Be satisfied,
The steam engine according to claim 1 or 2, characterized in that. The inner radius dimension of the fluid container heating corresponding part is the same dimension as the inner radial dimension of the heat insulating gap,
The steam engine according to claim 3 or 4, characterized by the above-mentioned. The inner radius dimension of the fluid container heating corresponding portion, the inner radius dimension of the fluid container cooling corresponding portion, and the radius dimension in the heat insulating gap portion are all the same dimension ,
The steam engine according to any one of claims 3 to 5, wherein

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