JP2010261409A - Heat engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat engine which reduces a heat transport loss. <P>SOLUTION: The heat engine is provided with a liquid supply part 19 and adjusting means 151, 152a, 152b, and 40. The liquid supply part 19 is connected to a heating part 13, and is filled with a working medium in liquid phase condition which is supplied to the heating part 13. The adjusting means 151, 152a, 152b, and 40 adjust the liquid-supply timing which is the timing with which the working medium in liquid phase condition in the liquid supply part 19 is supplied to the heating part 13. The adjusting means 151, 152a, 152b, and 40 are constituted so that they delay the liquid-supply timing later than the timing with which a liquid piston 20 undergoes displacement toward the heating part 13 in the compression stroke. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a heat engine that displaces a working medium in a liquid phase by a change in the volume of steam in the working medium, converts the displacement of the working medium in a liquid phase into mechanical energy, and outputs the mechanical energy.

  Conventionally, this type of heat engine is described in Patent Documents 1 and 2. In the prior art of Patent Documents 1 and 2, the working medium is sealed in a tubular container in a liquid phase state, and a part of the working medium in a liquid phase is heated and vaporized by a heating unit of the container, and the vaporization is performed. The liquid in the liquid phase is displaced as a liquid piston by changing the volume of the vapor in the working medium by cooling the vapor of the working medium in the cooling section of the container and converting it into mechanical energy. And output.

  Furthermore, in the prior art of Patent Document 2, the tubular container is expanded in a disk shape in the heating section. For this reason, when the vapor | steam of a working medium is cooled and liquefied in a cooling part, the working medium of a liquid phase will flow in into the center part of a heating part, and will spread and flow toward the outer peripheral part of a heating part after that. Then, the working medium in the liquid phase is heated in the heating unit and vaporizes again.

  According to the prior art disclosed in Patent Document 2, the liquid-phase working medium collides with the inner wall surface of the heating section when the liquid-phase working medium flows into the heating section. Is stirred and turbulent flow is generated, and the temperature boundary layer near the inner wall surface of the heating unit is destroyed. As a result, the heat exchange efficiency in the heating part can be improved.

JP 2004-84523 A Japanese Patent Laid-Open No. 2007-247592

  As described above, in the conventional techniques of Patent Documents 1 and 2, since the output is taken out when the working medium is vaporized in the heating unit, the working medium is moved to the cooling unit side without vaporizing in the heating unit. In this case, the working medium only transports the amount of heat given from the heating unit to the cooling unit, and the amount of heat given from the heating unit to the working medium does not contribute to the output, resulting in heat loss. Hereinafter, such heat loss is referred to as heat transport loss.

  According to the detailed examination of the present inventors, it has been found that the conventional techniques of Patent Documents 1 and 2 have a factor that increases heat transport loss. This will be described below.

  FIG. 9A is a graph showing the temperature distribution of the heating unit 13 in the heat engine (hereinafter referred to as a study example) studied by the present inventors. This examination example corresponds to the prior art of Patent Document 2 above, and an outline of the vicinity of the heating unit 13 in the examination example is shown in FIG. FIG. 9A shows the temperature distribution in the radial direction (left and right direction in FIG. 9) of the heating unit 13 corresponding to FIG. 9B.

  In this examination example, when the liquid piston 20 flows into the heating unit 13, a liquid-phase working medium (hereinafter simply referred to as “liquid”) is supplied to the heating unit 13. In other words, the liquid supplied to the heating unit 13 and the liquid piston 20 are a continuous body. For this reason, the contact time with the liquid in each part of the heating unit 13 is shortened from the radially inner side (liquid inlet side) of the heating unit 13 toward the radially outer side.

  In other words, the radially inner portion (center portion) of the heating unit 13 is exposed to the liquid and the time for heat exchange with the liquid becomes longer. For this reason, as shown to Fig.9 (a), the temperature of the heating part 13 becomes so low that a radial direction inner side part.

  FIG. 9C is a graph showing the time during which the liquid enters the heating unit 13 (hereinafter referred to as the liquid retention time) as a radial distribution of the heating unit 13 in the study example. FIG. 9D is a graph showing, in the examination example, the ratio of the liquid that heat-transports without boiling (hereinafter referred to as the ratio of the heat-transported liquid) as a radial distribution of the heating unit 13. In addition, the “position of the liquid piston” on the horizontal axis in FIGS. 9C and 9D means each part of the liquid when the liquid reaches the top dead center (when the liquid enters the heating unit 13 at the maximum). It is shown.

  As described above, in this examination example, the liquid supplied to the heating unit 13 and the liquid piston 20 are a continuous body. For this reason, while the part which reached | attained the radial direction outer side (top dead center side) of the heating part 13 among liquids becomes longer in the heating part 13, the radial inside of the heating part 13 among liquids becomes long. The portion that has reached only the top dead center side has a shorter time in the heating unit 13. Therefore, as shown in FIG. 9C, the liquid retention time becomes shorter toward the radially inner side of the heating unit 13.

  Here, the heat exchange amount between the heating unit 13 and the liquid is expressed by the following mathematical formula.

Q = S · h · ΔT · t
However, Q is a heat exchange amount, S is a heat transfer area, h is a heat transfer coefficient, ΔT is a temperature difference between the heating unit 13 and the liquid, and t is a heating time, that is, a liquid retention time.

  In the examination example, as shown in FIG. 9A, the temperature of the heating unit 13 decreases as it reaches the inner side in the radial direction. Further, as shown in FIG. 9C, the liquid retention time (heating time) t becomes shorter toward the radially inner side of the heating unit 13.

  For this reason, as is clear from the above mathematical formula, the liquid has a smaller heat exchange amount Q toward the radially inner portion of the heating unit 13. As a result, a sufficient amount of heat exchange required for vaporization of the liquid cannot be secured on the inner side in the radial direction of the heating unit 13, so that the heat does not completely boil on the inner side in the radial direction of the heating unit 13 as shown in FIG. The proportion of liquid to be transported increases. In other words, the portion of the liquid that reaches only the inner side in the radial direction of the heating unit 13 increases the proportion of the liquid that is heat transported. As a result, the heat transport loss is increased in the study example.

  For these reasons, the heat transfer loss increases in the prior art of Patent Document 2 described above. Moreover, also in the prior art of the said patent document 1, a heat transport loss will increase for the same reason.

  In short, in the conventional techniques of Patent Documents 1 and 2, since the liquid supplied to the heating unit and the liquid piston displaced in the container are a continuous body, a sufficient amount of heat exchange is required for vaporizing the liquid. As a result, it becomes impossible to ensure the heat transport loss.

  In view of the above points, the present invention aims to reduce heat transport loss.

In order to achieve the above object, the invention according to claim 1 includes a container (11) in which a working medium is encapsulated in a liquid phase so as to be flowable.
The container (11)
A liquid piston displacement portion (12) in which the working medium in a liquid phase is reciprocally displaced as the liquid piston (20);
A heating section (13) that communicates with one end of the liquid piston displacement section (12) and heats the working medium in a liquid phase to generate vapor of the working medium;
A cooling part (14) formed in an intermediate part of the liquid piston displacement part (12) for cooling and condensing the vapor;
An output portion (15) that communicates with the other end of the liquid piston displacement portion (12), converts the displacement of the liquid piston (20) into mechanical energy, and outputs the mechanical energy;
The expansion stroke in which the liquid piston (20) is displaced toward the output section (15) by the steam generated in the heating section (13), and the steam is condensed in the cooling section (14) and the liquid piston (20) is heated in the heating section ( 13) a heat engine that alternately performs a compression stroke displaced toward
A liquid supply unit (19) that communicates with the heating unit (13) and encloses a liquid-phase working medium supplied to the heating unit (13);
Adjusting means (151, 152a, 152b, 40) for adjusting the liquid supply timing, which is the timing at which the liquid-phase working medium in the liquid supply section (19) is supplied to the heating section (13),
The adjusting means (151, 152a, 152b, 40) is configured to delay the liquid supply timing with respect to the timing at which the liquid piston (20) is displaced toward the heating section (13) in the compression stroke. And

  According to this, since the liquid phase working medium is supplied to the heating section (13) by the liquid supply section (19), the liquid phase working medium supplied to the heating section (13) is used as the liquid piston displacement section. It can be discontinuous with respect to the liquid piston (20) displaced in (12). For this reason, a sufficient amount of heat exchange for vaporizing the liquid-phase working medium can be ensured, and heat transport loss can be reduced.

  Here, the liquid supply timing, which is the timing at which the liquid phase working medium in the liquid supply section (19) is supplied to the heating section (13), is the liquid piston (in the liquid piston displacement section (12) in the compression stroke). Since the steam is generated in the heating part (13) from the initial stage of the compression stroke when the timing of 20) is displaced toward the heating part (13), the liquid piston (20) is heated in the heating part (13). ) Will be hindered from displacing.

  In view of this point, in the present invention, since the liquid supply timing is delayed from the timing at which the liquid piston (20) is displaced toward the heating unit (13) in the compression stroke, the liquid supply timing is delayed from the initial stage of the compression stroke. It is possible to avoid the generation of steam in the heating part (13), and as a result, the liquid piston (20) can be favorably displaced toward the heating part (13) in the compression stroke.

In the invention according to claim 2, in the heat engine according to claim 1, the liquid supply part (19) communicates with the output part (15),
The output unit (15) is configured to displace the liquid-phase working medium in the liquid supply unit (19) toward the heating unit (13) in the compression stroke,
The adjustment means (151, 152a, 152b, 40) adjust the liquid supply timing by adjusting the timing at which the liquid phase working medium in the liquid supply section (19) is displaced toward the heating section (13). It is characterized by that.

According to a third aspect of the present invention, in the heat engine according to the second aspect, the output portion (15) includes a solid piston (151) that is displaced by receiving pressure from the liquid piston (20), and a solid piston (151). A cylinder (152) that slidably supports
When the direction of displacement of the solid piston (151) in the compression stroke is the compression direction,
In the cylinder (152), a liquid piston port (152a) communicating with the liquid piston displacement part (12) and a liquid supply port (152b) communicating with the liquid supply part (19) are opened,
The liquid piston port (152a) is formed on the inner peripheral surface of the cylinder (152) so as to be closed by the solid piston (151) when the solid piston (151) is displaced in the compression direction,
The liquid supply port (152b) is formed in a portion of the cylinder (152) closer to the compression direction than the liquid piston port (152a),
The adjusting means is a solid piston (151), a liquid piston port (152a), and a liquid supply port (152b).

  According to this, since the liquid supply timing can be adjusted without providing a valve mechanism, the configuration of the adjusting means can be simplified.

  According to a fourth aspect of the present invention, in the heat engine according to the third aspect, the solid piston (151) includes a port open / close piston (151a) for opening and closing the liquid piston port (152a), a port open / close piston (151a), It is characterized by being separated into a drive piston (151b) that is displaced synchronously and connected to the drive target device (1).

  Thereby, the freedom degree of design of an output part (15) can be improved. For example, the oil / water separation membrane (31) can be disposed in the cylinder (152).

  According to a fifth aspect of the present invention, in the heat engine according to the fourth aspect, the cylinder (152) is provided with a stopper (30) for regulating a stroke amount of the port opening / closing piston (151a). And

  According to a sixth aspect of the present invention, in the heat engine according to any one of the second to fifth aspects, the liquid supply section (19) includes a pressure on the output section (15) side and a heating section (13) side. A one-way valve (191) is provided that opens when the difference from the pressure becomes equal to or greater than a predetermined pressure.

  Thereby, when the liquid piston (20) in the liquid piston displacement part (12) is displaced toward the heating part (13), the working medium in the liquid phase in the liquid supply part (19) becomes the heating part ( Since the displacement toward 13) can be suppressed, the liquid supply timing can be reliably adjusted.

  According to a seventh aspect of the present invention, in the heat engine according to any one of the second to fifth aspects, the flow path resistance of the liquid supply section (19) is greater than the flow path resistance of the liquid piston displacement section (12). It is also characterized by being larger.

  Thereby, when the liquid piston (20) in the liquid piston displacement part (12) is displaced toward the heating part (13), the working medium in the liquid phase in the liquid supply part (19) becomes the heating part ( Since the displacement toward 13) can be suppressed, the liquid supply timing can be adjusted more reliably.

  In the invention according to claim 8, in the heat engine according to claim 7, the average cross-sectional area of the flow path of the liquid supply part (19) is smaller than the average cross-sectional area of the flow path of the liquid piston displacement part (12). By being set, the flow path resistance of the liquid supply part (19) is larger than the flow path resistance of the liquid piston displacement part (12).

  According to the ninth aspect of the present invention, in the heat engine according to the seventh aspect, the flow supply resistance of the liquid supply section (19) is reduced by providing the liquid supply section (19) with the throttle section (192). It is characterized by being larger than the flow path resistance of the liquid piston displacement part (12).

In the invention according to claim 10, in the heat engine according to claim 1, the liquid supply portion (19) communicates with an intermediate portion of the liquid piston displacement portion (12),
The adjusting means is a valve mechanism (40) that closes the liquid supply section (19) in the initial stage of the compression stroke and opens the liquid supply section (19) in the middle of the compression stroke.

  Thereby, a liquid supply timing can be adjusted reliably.

  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.

1 is an overall configuration diagram of a heat engine in a first embodiment of the present invention. It is explanatory drawing explaining the state which has a solid piston in a top dead center in the heat engine of FIG. It is explanatory drawing explaining the state which a solid piston displaces to a compression direction in the heat engine of FIG. It is explanatory drawing explaining the state which has a solid piston in a bottom dead center in the heat engine of FIG. It is explanatory drawing explaining the state which a solid piston displaces in an expansion direction in the heat engine of FIG. It is a whole heat engine block diagram in the modification of a 1st embodiment. It is a whole block diagram of the heat engine in 2nd Embodiment of this invention. It is a whole block diagram of the heat engine in 3rd Embodiment of this invention. It is explanatory drawing of the ratio of the heating part temperature distribution in the prior art, the retention time of a liquid, and the heat transported liquid.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a configuration diagram showing a schematic configuration of a heat engine 10 according to the present invention. The up arrow in FIG. 1 indicates the top and bottom direction, and the down arrow indicates the bottom and top direction.

  The heat engine 10 is also called a liquid piston steam engine, and is used as a drive source for driving the drive target device 1 such as a power generator.

  The heat engine 10 includes a container 11 in which a working medium is sealed so as to be able to flow in a liquid phase state. In this embodiment, water is used as the working medium. Hereinafter, the liquid-phase working medium is simply referred to as a liquid.

  The container 11 includes a liquid piston displacement portion 12 where the liquid is reciprocally displaced, a heating portion 13 communicating with one end of the liquid piston displacement portion 12, a cooling portion 14 formed at an intermediate portion of the liquid piston displacement portion 12, and a liquid It is roughly divided into an output portion 15 communicating with the other end portion of the piston displacement portion 12. Hereinafter, the liquid displaced by the liquid piston displacement portion 12 is referred to as a liquid piston 20.

  In this example, one end side portion of the liquid piston displacement part 12 is branched into a plurality (four in the example of FIG. 1), and a plurality of heating parts 13 and cooling parts 14 (four in the example of FIG. 1) are formed. ing.

  The heating unit 13 heats the liquid to generate a working medium vapor (hereinafter simply referred to as vapor) 21. Thereby, the liquid piston 20 in the liquid piston displacement part 12 is displaced toward the output part 15.

  In this example, a high-temperature gas such as exhaust gas is used as the heat source of the heating unit 13. Specifically, one end of the container 11 is constituted by a heater 16 disposed in the flow of high-temperature gas, and the heating unit 13 is formed inside the heater 16. When the heater 16 is heated with the high temperature gas, the liquid in the heating unit 13 is heated.

  In this example, the heating unit 13 has a disk shape that expands in the horizontal direction, and the liquid piston displacement unit 12 is connected to the center of the heating unit 13.

  Inside the heater 16, a steam reservoir 17 is formed on the upper side of each heating unit 13 to store the steam 21 generated in each heating unit 13 in communication with each heating unit 13.

  The cooling unit 14 cools and condenses the steam 21 generated in the heating unit 13. In this example, a part of the container 11 that forms the cooling unit 14 is inserted into the cooler 18. Cooling water circulates in the cooler 18, and a radiator (not shown) that dissipates heat taken from the steam 21 by the cooling water is arranged in the cooling water circulation circuit.

  The output unit 15 converts the displacement of the liquid piston 20 in the liquid piston displacement unit 12 into mechanical energy and outputs the mechanical energy. The output unit 15 is configured as a so-called reciprocating type, and includes a solid piston 151 that is displaced by receiving pressure from the liquid piston 20 and a cylinder 152 that slidably supports the solid piston 151.

  The solid piston 151 is connected to the drive target device 1. The solid piston 151 is connected to an inertial force generating member (not shown) such as a flywheel.

  When the vapor 21 is generated in the heating unit 13 and the liquid piston 20 in the liquid piston displacement unit 12 is displaced toward the output unit 15, the solid piston 151 is pushed out by the liquid piston 20 and displaced upward in FIG. . The displacement direction of the solid piston 151 at this time is hereinafter referred to as an expansion direction.

  When the vapor 21 generated by the heating unit 13 enters the cooling unit 14 and condenses, the solid piston 151 is displaced downward in FIG. 1 by the inertial force of an inertial force generating member (not shown). The displacement direction of the solid piston 151 at this time is hereinafter referred to as a compression direction.

  A liquid piston port 152 a communicating with the liquid piston displacement portion 12 is opened on the inner peripheral surface of the cylinder 152. The liquid piston port 152a is closed by the solid piston 151 when the solid piston 151 is displaced in the compression direction.

  In this example, since a plurality of liquid piston ports 152a (two in the example of FIG. 1) are formed, the end on the output portion 15 side of the liquid piston displacement portion 12 has the same number as the liquid piston ports 152a. Branch to book.

  A liquid supply port 152b that communicates with one end of the liquid supply unit 19 is opened in a portion of the cylinder 152 that is closer to the compression direction than the liquid piston port 152a. In this example, the liquid supply port 152b is formed on the end surface on the compression direction side of the cylinder 152 (the lower end surface in FIG. 1).

  The liquid supply unit 19 serves to supply the liquid to the heating unit 13. Specifically, the liquid supply unit 19 is configured by a tubular member in which a liquid is sealed so that the liquid can flow, and a part of the liquid sealed in the liquid supply unit 19 is supplied to the heating unit 13.

  The other end portion of the liquid supply unit 19 (the portion opposite to the liquid supply port 152 b) branches into a plurality of the same number as the plurality of heating units 13 and communicates with the non-center portion of each heating unit 13. .

  The liquid supply unit 19 is provided with a one-way valve 191 that opens when the difference between the pressure on the cylinder 152 side and the pressure on the heating unit 13 side exceeds a predetermined pressure.

  In this example, since the working medium 12 is water, the container 11 and the liquid supply unit 19 are basically made of stainless steel, but the heater 16 is made of copper having excellent thermal conductivity. . Moreover, you may form the cooling part 14 which contacts the cooler 18 among the containers 11 with copper or aluminum excellent in thermal conductivity.

  Next, the operation in the above configuration will be described with reference to FIGS. In FIG. 2 to FIG. 5, only one heating unit 13 is illustrated for easy understanding.

  FIG. 2 → FIG. 3 → FIG. 4 show a compression process in which the vapor 21 generated in the heating unit 13 is condensed in the cooling unit 14 and the liquid piston 20 in the liquid piston displacement unit 12 is displaced toward the heating unit 13. Yes. 4 → FIG. 5 → FIG. 2 shows an expansion stroke in which the vapor 21 is generated in the heating unit 13 and the liquid piston 20 in the liquid piston displacement unit 12 is displaced toward the output unit 15.

  2 shows a state in which the solid piston 151 has come to the uppermost end (top dead center), and FIG. 4 shows a state in which the solid piston 151 has come to the lowermost end (bottom dead center).

  In the state of FIG. 2, the liquid piston 20 in the liquid piston displacement portion 12 is pushed out to the solid piston 151 side by the high-temperature / high-pressure steam 21 generated in the heating portion 13, thereby pushing the solid piston 151 to the top dead center. ing.

  At this time, since the liquid level 20a of the liquid piston 20 is lowered to the cooling unit 14 and the vapor 21 enters the cooling unit 14, the vapor 21 is cooled and condensed in the cooling unit 14.

  As a result, the force that pushes the liquid piston 20 toward the solid piston 151 disappears, so that the solid piston 151 is lowered toward the compression direction by the inertial force of an inertial force generating member (not shown).

  When the solid piston 151 is lowered in the compression direction, the liquid in the cylinder 152 is pushed out to the liquid piston displacement portion 12 through the liquid piston port 152a as indicated by an arrow A1 in FIG. Thereby, the liquid piston 20 in the liquid piston displacement part 12 is displaced to the heating part 13 side.

  At this time, since the pressure in the cylinder 152 hardly increases, the one-way valve 191 is closed. For this reason, the liquid in the cylinder 152 does not flow into the liquid supply unit 19.

  The flow of the liquid in the cylinder 152 indicated by the arrow A1 in FIG. 2 into the liquid piston displacement portion 12 is performed until the solid piston 151 is lowered to a position where the liquid piston port 152a is closed as shown in FIG. That is, when the solid piston 151 closes the liquid piston port 152 a, the liquid in the cylinder 152 is not pushed out to the liquid piston displacement portion 12.

  Incidentally, the broken-line hatched area Va in the cylinder 152 in FIG. 2 is the liquid that is removed from the cylinder 152 when the solid piston 151 is displaced from the top dead center shown in FIG. 2 to the closed position of the liquid piston port 152a shown in FIG. The volume of is shown.

  When the liquid of volume Va flows from the cylinder 152 into the liquid piston displacement part 12, the liquid surface 20a of the liquid piston 20 in the liquid piston displacement part 12 reaches just below the heating part 13 as shown in FIG.

  When the solid piston 151 further descends from the closed position of the liquid piston port 152a shown in FIG. 3 toward the compression direction, the pressure in the cylinder 152 rises, so that the one-way valve 191 opens as shown in FIG. As in A2, the liquid in the cylinder 152 is pushed out to the liquid supply unit 19 through the liquid supply port 152b.

  Incidentally, the broken-line hatched area Vb in the cylinder 152 in FIG. 2 is the liquid that is removed from the cylinder 152 when the solid piston 151 is displaced from the closed position of the liquid piston port 152a shown in FIG. 3 to the bottom dead center shown in FIG. The volume of is shown.

  When the liquid of volume Vb flows from the cylinder 152 into the liquid supply unit 19, the liquid in the liquid supply unit 19 is pushed out toward the heating unit 13 and supplied to the heating unit 13 as indicated by an arrow A3 in FIG.

  The volume Vb of the liquid flowing from the cylinder 152 into the liquid supply section 19 is set to be considerably smaller than the volume Va of the liquid flowing from the cylinder 152 into the liquid piston displacement section 12 (Va >> Vb). In this example, the ratio (Va: Vb) between the volume Va and the volume Vb is set to about 50: 1.

  The liquid supplied from the liquid supply unit 19 to the heating unit 13 as shown by an arrow A 3 in FIG. 4 is heated and vaporized by the heating unit 13, whereby high-temperature and high-pressure steam 21 is accumulated in the heating unit 13. The

  In parallel with this, the solid piston 151 rises from the bottom dead center shown in FIG. 4 to the position shown in FIG. 5, that is, the position where the liquid piston port 152a is opened, by the inertial force of an inertial force generating member (not shown).

  For this reason, the high-temperature / high-pressure steam 21 accumulated in the heating unit 13 pushes the liquid piston 20 in the liquid piston displacement unit 12 toward the solid piston 151, thereby entering the cylinder 152 as indicated by an arrow A 4 in FIG. 5. The liquid piston 20 flows in. For this reason, the liquid piston 20 pushes up the solid piston 151 toward the expansion direction. At this time, since the one-way valve 191 is closed, the steam 21 in the heating unit 13 hardly flows into the liquid supply unit 19.

  When the solid piston 151 reaches top dead center, the state shown in FIG. 2 is obtained again. In this way, the operation of FIG. 2 → FIG. 3 → FIG. 4 → FIG. 5 → FIG. 2 is repeated, whereby the expansion stroke and the compression stroke are alternately performed. Periodically displaced (so-called self-excited vibration) causes the solid piston 151 of the output unit 15 to reciprocate.

  According to this embodiment, since the liquid supply unit 19 supplies the liquid to the heating unit 13, the liquid supplied to the heating unit 13 is discontinuous with respect to the liquid piston 20 that is displaced within the liquid piston displacement unit 12. can do. For this reason, a sufficient amount of heat exchange necessary for vaporization of the liquid can be ensured, so that heat transport loss can be reduced.

  Here, the liquid supply timing which is the timing at which the liquid in the liquid supply unit 19 is supplied to the heating unit 13 is the timing at which the liquid piston 20 in the liquid piston displacement unit 12 is displaced toward the heating unit 13 in the compression stroke. At the same time, since steam is generated in the heating unit 13 from the initial stage of the compression stroke, the liquid piston 20 is prevented from being displaced toward the heating unit 13.

  In view of this point, in the present embodiment, the liquid supply timing is delayed from the timing at which the liquid piston 20 is displaced toward the heating unit 13 in the compression stroke.

  Specifically, the liquid piston port 152a and the liquid supply port 152b are formed in the cylinder 152, and the liquid piston port 152a is configured to be opened and closed by the solid piston 151, whereby the liquid supply timing is set in the compression stroke. Is delayed from the timing of displacement toward the heating unit 13.

  In other words, the solid piston 151, the liquid piston port 152a, and the liquid supply port 152b constitute an adjusting unit that adjusts the liquid supply timing.

  For this reason, since it is possible to avoid generation of steam in the heating unit 13 from the initial stage of the compression stroke, the liquid piston 20 can be favorably displaced toward the heating unit 13 in the compression stroke.

  Furthermore, in this embodiment, since the one-way valve 191 is provided in the liquid supply part 19, it can suppress that the liquid in the cylinder 152 flows into the liquid supply part 19 when the liquid piston port 152a is open. For this reason, liquid supply timing can be adjusted reliably.

  As a modification of the present embodiment, the one-way valve 191 may be eliminated, and instead, the flow path resistance of the liquid supply unit 19 may be made larger than the flow path resistance of the container 11. According to this, by making the flow path resistance of the liquid supply part 19 larger than the flow path resistance of the container 11, the liquid in the cylinder 152 flows into the liquid supply part 19 when the liquid piston port 152 a is open. Therefore, the same effect as the one-way valve 191 can be obtained.

  Here, when a configuration example of the flow path structure in which the flow path resistance of the liquid supply unit 19 is larger than the flow path resistance of the liquid piston displacement unit 12 is given, By setting it smaller than the average cross-sectional area of the flow path of the displacement part 12, the flow path resistance of the liquid supply part 19 can be made larger than the flow path resistance of the container 11.

  For example, when the channel cross-sectional shapes of the liquid supply unit 19 and the liquid piston displacement unit 12 are circular, the average channel diameter of the channel of the liquid supply unit 19 is greater than the average channel diameter of the channel of the liquid piston displacement unit 12. Can be set smaller.

  FIG. 6 shows another configuration example of the channel structure. That is, the flow path resistance of the liquid supply unit 19 may be made larger than the flow path resistance of the liquid piston displacement unit 12 by providing the liquid supply unit 19 with a throttle 192 such as an orifice.

(Second Embodiment)
In the second embodiment, as shown in FIG. 7, the solid piston 151 is separated into a port opening / closing piston 151a and a drive piston 151b.

  The port opening / closing piston 151a serves to open and close the liquid piston port 152a. The drive piston 151b is connected to the drive target device 1 and is displaced in synchronization with the port opening / closing piston 151a.

  The cylinder 152 is provided with a stopper 30 that regulates the stroke amount of the port opening / closing piston 151a. In the example of FIG. 7, the stopper 30 regulates the top dead center of the port opening / closing piston 151a.

  In the cylinder 152, the diaphragm 31 is disposed between the port opening / closing piston 151a and the drive piston 151b. In the cylinder 152, oil 32 that lubricates the drive piston 151 b is sealed on the drive piston 151 b side of the diaphragm 31. That is, the diaphragm 31 serves as an oil / water separation membrane that separates the liquid and the oil 32 in the cylinder 152.

  Thus, by separating the solid piston 151 into the port opening / closing piston 151a and the drive piston 151b, the degree of freedom in designing the output unit 15 can be improved.

  Incidentally, in this embodiment, like the modified example of the first embodiment, the one-way valve 191 is eliminated, and instead, the flow resistance of the liquid supply unit 19 is made larger than the flow resistance of the container 11. Yes.

(Third embodiment)
In the second embodiment, the adjusting means for adjusting the liquid supply timing is configured by the solid piston 151, the liquid piston port 152a, and the liquid supply port 152b. However, in the third embodiment, as shown in FIG. The adjusting means for adjusting the liquid supply timing includes a valve mechanism 40 that opens and closes the liquid piston displacement section 12 and the liquid supply section 19 at a predetermined timing.

  Specifically, an end of the liquid supply unit 19 opposite to the heating unit 13 is connected to an intermediate part of the liquid piston displacement unit 12, and a valve mechanism is connected to a connection part between the liquid piston displacement unit 12 and the liquid supply unit 19. 40 is arranged. Moreover, the liquid piston port 152a is formed in the end surface (lower end surface of FIG. 4) of the cylinder 152, and the liquid supply port 152b is abolished.

  As the valve mechanism 40, for example, two electromagnetic valves can be used. Further, as the valve mechanism 40, a three-way electromagnetic valve may be used.

  The output unit 15 is provided with a sensor 41 that detects the position of the drive piston 151b. A detection signal of the sensor 41 is input to the control device 42. The control device 42 controls the valve mechanism 40 according to the position of the drive piston 151b detected by the sensor 41.

  Specifically, the opening / closing timing of the liquid piston displacement portion 12 is made the same as the opening / closing timing of the liquid piston port 152a in the second embodiment, and the opening / closing timing of the liquid supply portion 19 is set to the liquid piston port 152a in the second embodiment. The timing may be the same as the opening / closing timing.

  Thereby, the displacement timing of the liquid piston 20 in the liquid piston displacement part 12 and the displacement timing of the liquid in the liquid supply part 19 in a compression stroke can be made the same as the said 2nd Embodiment.

  According to this embodiment, the liquid supply unit 19 can be closed at the initial stage of the compression stroke, and the liquid supply unit 19 can be opened in the middle of the compression stroke, so that the liquid supply timing can be adjusted with certainty.

  The valve mechanism 40 does not necessarily need to open and close both the liquid piston displacement part 12 and the liquid supply part 19, and may open and close only the liquid supply part 19. In this case, it is preferable that the flow path resistance of the liquid supply unit 19 is relatively small so that the liquid easily flows into the liquid supply unit 19 when the valve mechanism 40 opens the liquid supply unit 19. .

(Other embodiments)
In addition, said each embodiment is only what showed an example of the planar shape of the internal space of the heating part 11a, It is not limited to this, The planar shape of the internal space of the heating part 11a can be variously changed. .

  In each of the above embodiments, the output unit 15 is configured as a so-called reciprocating type, but the output unit 15 is configured to displace the liquid in the liquid supply unit 19 toward the heating unit 13 in the compression stroke. For example, the output unit 15 may be configured as a so-called rotary type.

DESCRIPTION OF SYMBOLS 11 Container 12 Liquid piston displacement part 13 Heating part 14 Cooling part 15 Output part 19 Liquid supply part 20 Liquid piston 151 Solid piston (adjustment means)
152a Liquid piston port (adjustment means)
152b Liquid supply port (adjustment means)

Claims (10)

A container (11) in which a working medium is encapsulated so as to be flowable in a liquid phase;
The container (11)
A liquid piston displacement section (12) in which the working medium in a liquid phase is reciprocally displaced as a liquid piston (20);
A heating section (13) that communicates with one end of the liquid piston displacement section (12) and heats the working medium in a liquid phase to generate vapor of the working medium;
A cooling part (14) formed in an intermediate part of the liquid piston displacement part (12) for cooling and condensing the vapor;
An output section (15) that communicates with the other end of the liquid piston displacement section (12), converts the displacement of the liquid piston (20) into mechanical energy, and outputs the mechanical energy;
An expansion stroke in which the liquid piston (20) is displaced toward the output section (15) by the steam generated in the heating section (13), and the steam is condensed in the cooling section (14) to form the liquid piston. (20) is a heat engine that alternately performs a compression stroke that is displaced toward the heating section (13),
A liquid supply unit (19) in communication with the heating unit (13) and encapsulating the working medium in a liquid phase supplied to the heating unit (13);
Adjusting means (151, 152a, 152b, 40) for adjusting the liquid supply timing, which is the timing at which the liquid phase working medium in the liquid supply section (19) is supplied to the heating section (13). ,
The adjusting means (151, 152a, 152b, 40) is configured to delay the liquid supply timing from the timing at which the liquid piston (20) is displaced toward the heating unit (13) in the compression stroke. A heat engine characterized by The liquid supply part (19) communicates with the output part (15),
The output section (15) is configured to displace the working medium in a liquid phase in the liquid supply section (19) toward the heating section (13) in the compression stroke,
The adjusting means (151, 152a, 152b, 40) adjusts the timing at which the working medium in the liquid phase in the liquid supply section (19) is displaced toward the heating section (13). The heat engine according to claim 1, wherein supply timing is adjusted. The output unit (15) includes a solid piston (151) that is displaced by receiving pressure from the liquid piston (20), and a cylinder (152) that slidably supports the solid piston (151).
When the direction of displacement of the solid piston (151) in the compression stroke is the compression direction,
The cylinder (152) has a liquid piston port (152a) communicating with the liquid piston displacement part (12) and a liquid supply port (152b) communicating with the liquid supply part (19).
The liquid piston port (152a) is formed on an inner peripheral surface of the cylinder (152) so as to be closed by the solid piston (151) when the solid piston (151) is displaced in the compression direction.
The liquid supply port (152b) is formed in a portion of the cylinder (152) closer to the compression direction than the liquid piston port (152a),
The heat engine according to claim 2, wherein the adjusting means is the solid piston (151), the liquid piston port (152a), and the liquid supply port (152b).   The solid piston (151) is displaced in synchronization with the port opening / closing piston (151a) for opening / closing the liquid piston port (152a) and the port opening / closing piston (151a), and is connected to the drive target device (1). The heat engine according to claim 3, wherein the heat engine is separated into a drive piston (151 b).   The heat engine according to claim 4, wherein the cylinder (152) is provided with a stopper (30) for regulating a stroke amount of the port opening / closing piston (151a).   The liquid supply section (19) is provided with a one-way valve (191) that opens when the difference between the pressure on the output section (15) side and the pressure on the heating section (13) side exceeds a predetermined pressure. The heat engine according to any one of claims 2 to 5, wherein the heat engine is provided.   The heat according to any one of claims 2 to 5, wherein the flow path resistance of the liquid supply section (19) is larger than the flow path resistance of the liquid piston displacement section (12). organ.   Since the average cross-sectional area of the flow path of the liquid supply section (19) is set smaller than the average cross-sectional area of the flow path of the liquid piston displacement section (12), the flow path of the liquid supply section (19) The heat engine according to claim 7, wherein the resistance is larger than the flow path resistance of the liquid piston displacement part (12).   By providing the throttle part (192) in the liquid supply part (19), the flow path resistance of the liquid supply part (19) becomes larger than the flow path resistance of the liquid piston displacement part (12). The heat engine according to claim 7, wherein: The liquid supply part (19) communicates with an intermediate part of the liquid piston displacement part (12),
The adjusting means is a valve mechanism (40) that closes the liquid supply section (19) in an initial stage of the compression stroke and opens the liquid supply section (19) in the middle of the compression stroke. Item 2. The heat engine according to Item 1.

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