JP2013185467A - Heat engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat engine capable of reducing energy loss by suppressing vapor condensation when a vapor is taken into a container.SOLUTION: Vapor streams respectively sucked from a plurality of suction ports 32 flow along an undersurface of a ceiling part 13, and collide with one another in the center of a first straight part 10a of a container 10. The collision of the vapor steams with one another makes vapor streams be mixed together to make a flow direction be changed downwards, and the vapor streams directed downwards are uniformized in a horizontal direction.

Description

  The present invention relates to a heat engine that displaces a liquid piston by expansion of steam, converts the displacement of the liquid piston into mechanical energy, and outputs the mechanical energy.

  As a prior art, there is a heat engine disclosed in Patent Document 1 below. This heat engine is arranged in a tubular container in which a liquid piston made of a liquid-phase working medium is flowably enclosed, an external evaporator that generates vapor of the working medium outside the container, and one end side portion of the container. An intake means for sucking the steam generated by the external evaporator into the container, and the displacement of the liquid piston, which is disposed at the other end portion of the container and caused by the expansion of the steam sucked into the container, And an output unit for converting the data into an output.

JP 2011-208633 A

  However, in the conventional heat engine, when the steam is taken into the container, the liquid piston absorbs heat and part of the steam is condensed. When such a large amount of vapor condensation occurs during intake, there is a problem that the input heat energy increases or the mechanical energy that can be extracted at the output section decreases, resulting in a large energy loss.

  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 suppressing the condensation of steam when the steam is taken into the container and reducing energy loss. To do.

  In order to achieve the above object, in the present invention, an intake means (31) disposed in a portion (11) on one end side of the container (10) and the liquid piston (20) in the container are provided. Velocity equalizing means (30a, 130a, 80) for equalizing the distribution of the velocity component in the container axial direction (XX) of the steam sucked by the means in the orthogonal direction (YY) perpendicular to the container axial direction is provided. It is said.

  According to this, the distribution of the velocity component of the inhaled steam in the container axial direction can be made uniform in the orthogonal direction orthogonal to the axis by the velocity uniformizing means. Therefore, the dynamic pressure due to the vapor acting on the end face of the liquid piston on one end side in the container can be made uniform in the end face, and the disturbance of the liquid level can be suppressed. Thereby, an increase in the contact area between the steam and the liquid piston can be suppressed, and heat transfer from the steam to the liquid piston can be suppressed. In this way, it is possible to suppress the condensation of the steam taken into the container and reduce the energy loss.

  In addition, the code | symbol in the parenthesis attached | subjected to each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

It is a schematic block diagram which shows schematic structure of the heat engine in 1st Embodiment to which this invention is applied. It is a principal part block diagram which shows the structure of the one end part of the container in 1st Embodiment. It is a time chart which shows the relationship between the volume change in a container, the opening-and-closing state change of an intake valve, the opening-and-closing state change of an exhaust valve, and the pressure change in a container. It is a PV diagram which shows the change in the container by the action | operation of a heat engine. It is a principal part block diagram which shows the structure of the one end part of the container in 2nd Embodiment. It is a principal part block diagram which shows the structure of the one end part of the container in 3rd Embodiment. It is a principal part block diagram which shows the structure of the one end part of the container in 4th Embodiment. It is a principal part block diagram which shows the structure of the one end part of the container in 5th Embodiment. It is a principal part block diagram which shows the structure of the one end part of the container in other embodiment.

  A plurality of modes for carrying out the present invention will be described below with reference to the drawings. In each embodiment, parts corresponding to the matters described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. In the case where only a part of the configuration is described in each embodiment, the other parts of the configuration are the same as those described previously. In addition to the combination of parts specifically described in each embodiment, the embodiments may be partially combined as long as the combination is not particularly troublesome.

(First embodiment)
A first embodiment to which the present invention is applied will be described with reference to FIGS.

  As shown in FIG. 1, the heat engine 1 of the present embodiment includes a container 10, a cooler 19, a liquid piston 20, an intake pipe 30, an exhaust pipe 40, an output unit 50, a liquid piston discharge unit 60, and the like. The heat engine 1 is also called a liquid piston steam engine.

  The container 10 has a cylindrical shape that forms a cylinder in which a liquid piston 20 made of a working medium (in this example, water) in a liquid state is sealed so as to be flowable. The container 10 has a bent portion 10b positioned at the lowermost portion, and first and second straight portions 10a and 10c disposed on both sides of the bent portion 10b, and has a cylindrical pipe-like pressure formed in a substantially U shape. It is a container.

  The first linear portion 10a extends in the vertical direction (XX direction in the drawing) on the right side in the drawing with respect to the bent portion 10b. The upper part of the first linear part 10 a is an end part 11 corresponding to a part on one end side of the container 10. An intake pipe 30 and an exhaust pipe 40 are connected to the one end portion 11.

  The intake pipe 30 forms an intake path through which the vapor of the working medium supplied from the steam generator 2 which is a steam supply source provided outside the container 10 is sucked into the container 10. The steam generator 2 generates steam by the heat of high-temperature gas such as exhaust gas from an internal combustion engine. The intake pipe 30 is provided with an intake valve 31 that opens and closes an intake path. The intake valve 31 corresponds to the intake means in this embodiment.

  The exhaust pipe 40 forms an exhaust path for discharging the steam that has not been condensed in the container 10 to the outside of the container 10. The exhaust pipe 40 is provided with an exhaust valve 41 that opens and closes an exhaust path. The exhaust valve 41 is an exhaust means in the present embodiment. The intake valve 31 and the exhaust valve 41 can be constituted by, for example, a rotary valve or a poppet valve.

  The cooler 19 is provided below the connection portion of the intake pipe 30 and the exhaust pipe 40 in the first linear portion 10a. For example, cooling water circulates in the cooler 19. Although not shown, a radiator that dissipates heat taken from the steam of the working medium by the cooling water is disposed in the circulation circuit of the cooling water.

  The container 10 is made of stainless steel having relatively excellent heat insulation. It is desirable that the cooling unit 18 that is a part of the container 10 that is in contact with the cooler 19 to condense the working medium is made of a material having excellent thermal conductivity. In this example, the cooling unit 18 is made of copper or aluminum.

  The second linear portion 10c extends in the vertical direction (XX direction in the drawing) on the left side of the bending portion 10b in the drawing. The upper part of the second linear portion 10 c is the other end portion 12 corresponding to the other end portion of the container 10. An output unit 50 is provided at the other end portion 12. The output unit 50 converts the displacement of the liquid piston 20 in the container 10 into mechanical energy and outputs the mechanical energy.

  The output unit 50 includes a solid piston 51 that can reciprocate within the second linear portion 10 c, and a connecting rod 52 that is coupled to the solid piston 51. Connected to the connecting rod 52 is a flywheel 3 as an inertial force generating member that forms part of the power conversion mechanism. A drive target device (not shown) is connected to the rotation shaft of the flywheel 3. The drive target device is, for example, a generator.

  The liquid piston discharge unit 60 that is a liquid piston discharge means discharges a part of the liquid piston 20 from the inside of the container 10, thereby maintaining the amount of the liquid piston 20 in the container 10 at a predetermined amount. Specifically, the liquid piston discharge unit 60 includes a discharge pipe 61 connected to a portion of the container 10 between the cooling unit 18 and the output unit 50, and a relief valve 62 that opens and closes the discharge pipe 61. ing. The relief valve 62 opens when the internal pressure of the container 10 exceeds a predetermined pressure.

  Next, the basic operation in the above configuration will be described with reference to FIG.

  The volume V shown in FIG. 3A is the volume of the container 10 and varies with the displacement of the solid piston 51. The pressure P shown in FIG. 3D is the internal pressure of the container 10. The top dead center shown in FIG. 3 means that the liquid piston 20 is closest to the one end 11 side. The bottom dead center shown in FIG. 3 means that the liquid piston 20 is closest to the other end 12 side.

  When the intake valve 31 is opened in a state immediately after the liquid piston 20 reaches the top dead center, the steam from the steam generator 2 is sucked into the one end portion 11. Hereinafter, the stroke in which the intake valve 31 is opened and the steam is sucked may be referred to as an intake stroke.

  When the intake valve 31 is opened for a predetermined time and then closed, the high-temperature and high-pressure steam supplied to the one end portion 11 expands and the liquid piston 20 is pushed out to the output portion 50 side. Hereinafter, the displacement direction of the liquid piston 20 may be referred to as an expansion direction. Further, the stroke in which the liquid piston 20 is displaced in the expansion direction may be hereinafter referred to as an expansion stroke. In the expansion stroke, mechanical energy is output from the output unit 50 as the liquid piston 20 is displaced in the expansion direction.

  When the vapor expanded in the one end portion 11 enters the cooling unit 18 and the liquid level of the liquid piston 20 falls to the cooling unit 18, the vapor is cooled and condensed in the cooling unit 18, and the internal pressure is reduced. Hereinafter, a process in which steam is cooled and condensed by the cooling unit 18 may be referred to as a condensation process. When the condensation stroke is performed, the force for pushing the liquid piston 20 toward the output unit 50 disappears, so that the solid piston 51 returns to the top dead center side by the inertial force of the flywheel 3. Hereinafter, the displacement direction of the liquid piston 20 may be referred to as a compression direction. In addition, the stroke in which the liquid piston 20 is displaced in the compression direction may be hereinafter referred to as a compression stroke.

  In the compression stroke, the exhaust valve 41 is opened at a predetermined timing, and steam and non-condensable gas (for example, mixed air) that has not been condensed in the cooling unit 18 are exhausted through the exhaust pipe 40. The exhaust valve 41 is set to open when the internal pressure becomes equal to the atmospheric pressure, for example. The exhaust valve 41 is closed shortly before the liquid piston 20 reaches top dead center. Hereinafter, the process of opening the exhaust valve 41 and exhausting the steam may be referred to as an exhaust process. When there is little steam or non-condensable gas that has not been condensed, the exhaust stroke can be omitted.

  By repeating such an operation, the liquid piston 20 in the container 10 is periodically reciprocated (so-called self-excited vibration), and the drive target device is continuously driven by the output from the output unit 50. Become.

  Here, in the condensation process, the steam supplied from the steam generator 2 condenses in the cooling unit 18, and accordingly, the amount of the liquid piston 20 in the container 10 increases. When the amount of the liquid piston 20 in the container 10 increases, the liquid level position of the liquid piston 20 rises, so that the volume of the vapor in the container 10 decreases accordingly.

  For this reason, the pressure P may increase due to the compression of the steam from when the exhaust valve 41 is closed until the top dead center is reached. When the pressure P becomes equal to or higher than a predetermined pressure, the relief valve 62 is opened, and a part of the liquid piston 20 is discharged through the discharge pipe 61. When a part of the liquid piston 20 is discharged and the pressure P becomes less than a predetermined pressure, the relief valve 62 is closed. In this way, the amount of the liquid piston 20 is maintained below a predetermined amount.

  Note that when the minimum pressure P in the operation cycle is lower than the atmospheric pressure, the relief valve 62 also plays a role of preventing the backflow of fluid in the discharge pipe 61.

  In the heat engine 1, an operation cycle of repeatedly performing an expansion stroke and a compression stroke is established by opening and closing the intake valve 31 and the exhaust valve 41 in synchronization with the phase of the liquid piston 20.

  In a heat engine in which the working medium is heated in the heating unit while being encapsulated in the container to be steamed, a loss occurs in which the working medium that cannot be boiled in the heating unit is transported to the cooling unit. In the heat engine 1 of the present embodiment, the operation is performed by taking in the steam of the working medium from the outside, so that the heat transport loss described above hardly occurs and the thermopower conversion efficiency can be improved. Further, by opening the exhaust valve 41, it is possible to exhaust the steam and the non-condensable gas that have not been condensed in the cooling unit 18, so that the thermal power conversion efficiency can be further improved.

  Next, the principal part of the heat engine 1 of this embodiment is demonstrated with reference also to FIG.

  As shown in FIG. 2, the ceiling portion 13 of the first linear portion 10a has a dome shape. In the intake pipe 30, the introduction pipe part 30 a that is located closer to the container 10 than the intake valve 31 and serves as a connection part to the one end part 11 has a direction toward the center of the first linear part 10 a and the ceiling part 13. Extending in the tangential direction.

  As shown in FIG. 2, a plurality of (two in this example) introduction pipe portions 30a are provided. The intake ports 32 respectively formed at the downstream ends of the plurality of introduction pipe portions 30a open at positions facing each other across the axis of the first linear portion 10a.

  In the first linear portion 10a, a rectifying body 90 corresponding to a rectifying member is disposed at a position above the liquid piston 20. The rectifying body 90 has a flat outer shape, and is formed of a porous body made of a material having a smaller thermal conductivity and specific heat than the material forming the container 10, for example, a porous body such as a resin material or a ceramic material.

  The rectifying body 90 is made of a porous body that has a mesh shape and allows steam to flow only in the up-and-down direction, or a porous body that has a continuous bubble structure and repeats splitting and merging of the steam that flows in the up-and-down direction. The rectifier 90 is disposed over the entire region so as to cross the first linear portion 10a in the lateral direction (horizontal direction). Thereby, the flow of the steam that has entered from the upper surface of the rectifier 90 in the axial direction (XX direction in the drawing) of the first linear portion 10a is horizontal (YY in the drawing) orthogonal to the axial direction of the first linear portion 10a. Direction) is difficult to change greatly. Therefore, the steam passing through the rectifying body 90 is rectified in the axial direction of the first linear portion 10a.

  The rectifier 90 is disposed between the opening position of the intake port 32 and the liquid piston 20 in the first linear portion 10a. The rectifier 90 is preferably disposed at the top dead center position of the liquid piston 20. Specifically, it is preferable that the rectifier 90 be disposed so that the lower surface of the rectifier 90 is at the top dead center position of the liquid piston 20.

  According to the main configuration described above, steam is sucked into the one end portion 11 from the plurality of intake ports 32 in the intake stroke. As indicated by arrows in FIG. 2, the steam sucked from the plurality of air inlets 32 flows along the lower surface of the ceiling part 13 and collides with each other at the center of the first linear part 10a. When the steam collides, the steam flow is mixed and the flow direction is changed downward, and the flow toward the lower side of the steam is made uniform in the horizontal direction. The vapor having a uniform velocity toward the lower side passes through the rectifying body 90 and presses the upper surface of the liquid piston 20 (the interface between the liquid phase portion and the gas phase portion of the working medium).

  In the present embodiment, the introduction pipe portion 30a arranged as shown in FIG. 2 is provided between the suction means of the container and the liquid piston, and the axial direction (XX direction) of the container of the steam sucked by the suction means ) Corresponds to speed uniformizing means for uniformizing the distribution of speed components in the orthogonal direction (YY direction) orthogonal to the axial direction.

  With the arrangement configuration of the introduction pipe portion 30a, the distribution of velocity components in the axial direction of the intake steam container 10 (specifically, in the first linear portion 10a) is made uniform in the orthogonal direction perpendicular to the axis. be able to. Therefore, the dynamic pressure due to the steam acting on the end face of the liquid piston 20 at the one end portion 11 is made uniform in the end face, and the liquid level is greatly disturbed or the steam penetrates the interface (vapor bubbles enter the liquid piston. Can be suppressed.

  Thereby, an increase in the contact area between the steam and the liquid piston 20 can be suppressed, and heat transfer from the steam to the liquid piston 20 can be suppressed. In this way, the condensation of the steam taken into the container 10 can be suppressed, and the energy loss can be reduced.

  In a heat engine that does not include speed uniformizing means as in the present embodiment, if there is a surplus in steam supply capacity in the intake stroke, the steam is excessively increased by the amount condensed by heat transfer from the steam to the liquid piston 20. Will be sucked in, and the loss of input heat will increase. In addition, in the intake stroke, when there is no allowance for steam supply capacity and condensation loss exceeding the supply capacity occurs, the maximum cycle pressure decreases below the steam supply pressure as shown by the broken line in FIG. The output from the output unit is reduced. According to this embodiment, as shown by the solid line in FIG. 4, the maximum pressure of the cycle can be set as the steam supply pressure.

  In addition, the arrangement configuration of the introduction pipe portion 30a in the present embodiment corresponds to a collision unit that causes the steam sucked by the suction unit to collide with a collision object. By changing the flow direction by colliding the sucked steam into the one end portion 11, the distribution of the velocity component of the sucked steam in the axial direction of the first linear portion 10a can be easily made in the orthogonal direction perpendicular to the axis. It can be made uniform.

  For the steam sucked from one introduction pipe portion 30a, the steam sucked from the other introduction pipe portion 30b corresponds to the collision object. By simply arranging a plurality of introduction pipe portions 30a so that the steam collides with each other, the steam sucked into the one end portion 11 can be collided to easily change the flow direction.

  Further, a rectifying body 90 is disposed between the intake port 32 and the liquid piston 20. According to this, the flow of the velocity component in the axial direction of the first linear portion 10a is made uniform in the horizontal direction orthogonal to the axis, and the flow velocity in the axial direction is made uniform by the rectifier 90. It is pressed against the end face of the liquid piston 20 while maintaining. Therefore, the dynamic pressure due to the steam acting on the end surface of the liquid piston 20 at the one end portion 11 can be reliably made uniform in the end surface.

  The rectifying body 90 is made of a material having a lower thermal conductivity than the metal material constituting the container 10. Therefore, it is difficult for the container 10 to absorb heat from the steam passing through the rectifying body 90, and condensation of the steam can be suppressed. The rectifier 90 is made of a material having a specific heat smaller than that of the metal material constituting the container 10 and is flat and relatively thin. Therefore, the rectifier 90 has a relatively small heat capacity. Thereby, it is difficult for the rectifier 90 to absorb heat from the steam passing through the rectifier 90, and the condensation of the steam can be reliably suppressed.

(Second Embodiment)
Next, a second embodiment will be described based on FIG.

  The second embodiment differs from the first embodiment in the arrangement configuration of the introduction pipe portion 30a. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in FIG. 5, in the present embodiment, a large number of introduction pipe portions 30 a are extended toward the center of the curved surface inside the ceiling portion 13. In the present embodiment, the introduction pipe portion 30a arranged as shown in FIG. 5 corresponds to the speed uniformizing means and the collision means. Vapors sucked from a large number of intake ports 32 collide with each other at the central portion of the one end portion 11, and the distribution of velocity components in the axial direction of the first linear portion 10a can be made uniform in the orthogonal direction perpendicular to the axis. . Thereby, the effect similar to 1st Embodiment can be acquired.

(Third embodiment)
Next, a third embodiment will be described with reference to FIG.

  The third embodiment differs from the first and second embodiments described above in the arrangement configuration of the introduction pipe portion 30a and in the object to which the inhaled steam collides. In addition, about the part similar to 1st, 2nd embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in FIG. 6, in the present embodiment, a plurality of (two in this example) introduction pipe portions 30 a are extended in the vertical direction on the side of the ceiling portion 13. An exhaust gas pipe 70 is disposed below the inlet 32 at the lower end of the introduction pipe portion 30a. The exhaust gas pipe 70 is integrally joined to the container 10. The upper surface portion of the exhaust gas pipe 70 is an opposing wall surface portion 14 that faces the air inlet 32 among the wall surface portions constituting the container 10.

  In the exhaust gas pipe 70, for example, high-temperature exhaust gas from an internal combustion engine circulates so that the opposing wall surface portion 14 can be heated. The exhaust gas pipe 70 corresponds to a heating means for heating the opposing wall surface portion 14.

  According to the main configuration described above, steam is sucked into the one end portion 11 from the plurality of intake ports 32 in the intake stroke. As indicated by arrows in FIG. 6, the steam sucked from the plurality of air inlets 32 once collides with the opposing wall surface part 14 to change the direction of flow, and flows along the lower surface of the ceiling part 13, and then the one end part 11. Flows downward in the interior.

  When the steam once collides with the opposing wall surface portion 14 and changes the direction of the flow, the velocity component toward the lower side of the steam is greatly reduced. Thereby, the flow toward the lower side of the steam is made uniform in the horizontal direction.

  In the present embodiment, the introduction pipe portion 30a and the opposing wall surface portion 14 arranged as shown in FIG. 6 are provided between the intake means of the container and the liquid piston, and the container of the steam sucked by the intake means This corresponds to speed uniformizing means for uniformizing the velocity component distribution in the axial direction (XX direction) in the orthogonal direction (YY direction) orthogonal to the axial direction.

  With the arrangement configuration of the introduction pipe portion 30a and the opposed wall surface portion 14, the distribution of the velocity component in the axial direction of the first linear portion 10a of the inhaled steam can be made uniform in the orthogonal direction perpendicular to the axis. Thereby, the effect similar to 1st, 2nd embodiment can be acquired.

  In addition, the arrangement configuration of the introduction pipe portion 30a and the opposing wall surface portion 14 in the present embodiment corresponds to a collision unit that causes the steam sucked by the suction unit to collide with a collision object. By changing the flow direction by colliding the sucked steam into the one end portion 11, the distribution of the velocity component of the sucked steam in the axial direction of the first linear portion 10a can be easily made in the orthogonal direction perpendicular to the axis. It can be made uniform.

  And for the vapor | steam inhaled from the introductory pipe part 30a, the opposing wall surface part 14 is equivalent to a to-be-collised object. The flow direction can be easily changed by causing the steam sucked into the one end portion 11 to collide only by disposing the opposing wall surface portion 14 so that the steam sucked from the suction port 32 collides.

  Further, the exhaust gas pipe 70 that heats the opposing wall surface portion 14 is provided, and by keeping the opposing wall surface portion 14 at a relatively high temperature, it is possible to prevent the vapor from condensing when colliding with the opposing wall surface portion 14.

  In addition, although the introduction piping 30a was provided with two or more, it is not limited to this, One may be sufficient.

(Fourth embodiment)
Next, a fourth embodiment will be described with reference to FIG. FIG. 7 shows the internal configuration of the one end 11 of the container 10 in a transparent state.

  4th Embodiment differs in the arrangement configuration of an introductory pipe part compared with the above-mentioned 1st-3rd embodiment. In addition, about the part similar to the 1st-3rd embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in FIG. 7, in the present embodiment, a plurality of (two in this example) introduction pipe portions 130 a are extended in the tangential direction in the axial orthogonal cross section of the side wall surface portion of the one end portion 11.

  According to the main configuration described above, steam is sucked into the one end portion 11 from the plurality of intake ports 32 in the intake stroke. As indicated by arrows in FIG. 7, the steam sucked from the plurality of air inlets 32 flows along the side wall surface portion of the one end portion 11 and forms a swirl flow inside the one end portion 11. Then, the swirl flow of the steam gradually moves downward.

  As the steam forms a swirl flow around the axis of the first linear portion 10a, the downward speed component of the moving speed of the steam is extremely small, and the horizontal speed component is extremely large. Therefore, the velocity component in the axial direction of the first linear portion 10a of the steam becomes relatively small, and accordingly, the velocity component in the axial direction of the steam is made uniform in the horizontal direction.

  In the present embodiment, the introduction pipe portion 130a arranged as shown in FIG. 7 is provided between the intake means of the container and the liquid piston, and the axial direction (XX direction) of the container of the steam sucked by the intake means ) Corresponds to speed uniformizing means for uniformizing the distribution of speed components in the orthogonal direction (YY direction) orthogonal to the axial direction.

  With the arrangement configuration of the introduction pipe portion 130a, the distribution of velocity components in the axial direction of the first linear portion 10a of the inhaled steam can be made uniform in the orthogonal direction perpendicular to the axis. Therefore, the same effect as in the first to third embodiments can be obtained.

  Further, the arrangement configuration of the introduction pipe portion 130a in the present embodiment is such that the steam flow in which the velocity component in the orthogonal direction perpendicular to the container axial direction of the steam sucked by the intake means is larger than the velocity component in the container axial direction. It corresponds to the vapor flow forming means for forming By forming a steam flow such that the velocity component in the orthogonal direction perpendicular to the axial direction of the first linear portion 10a of the steam is larger than the velocity component in the axial direction of the first linear portion 10a, the velocity component in the axial direction is formed. Can be suppressed. Thereby, the distribution of the velocity component in the axial direction of the first linear portion 10a of the inhaled steam can be easily made uniform in the orthogonal direction orthogonal to the axis.

  Further, the introduction pipe portion 130a takes in the steam from the tangential direction of the side wall surface portion, which is one of the directions having a twisted positional relationship with respect to the axial direction of the first linear portion 10a, into the inside of the one end portion 11. It corresponds to the route part. The steam sucked through the introduction pipe 130a forms a swirling flow around the axis of the first linear portion 10a, so that the velocity of the steam in the orthogonal direction perpendicular to the axial direction of the first linear portion 10a can be easily obtained. The component can be greater than the velocity component of the steam in the axial direction.

  In addition, although the introduction piping 130a was extended in the tangential direction of the side wall surface part of the one end part 11, it is not limited to this. The introduction pipe only needs to be extended in a direction having a twisted positional relationship with respect to the axial direction of the first linear portion 10 a (also the axial direction of the one end portion 11). A swirling flow can be formed.

(Fifth embodiment)
Next, a fifth embodiment will be described with reference to FIG. FIG. 8 shows the internal configuration of the one end 11 of the container 10 in a transparent state.

  The fifth embodiment is different from the fourth embodiment described above in the means for forming the swirling flow. In addition, about the part similar to 1st-4th embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in FIG. 8, in this embodiment, the introduction pipe part 30a is extended in the horizontal direction toward the center of the 1st linear part 10a. A guide plate 80 corresponding to a guide member is disposed between the intake port 32 and the liquid piston 20 in the one end portion 11. The guide plate 80 is made of a thin plate material having a spiral shape, for example, and guides the steam flowing from the upper side to the lower side in the one end portion 11 in a spiral shape.

  The guide plate 80 is formed of a material having a smaller thermal conductivity and specific heat than the material forming the container 10, such as a resin material or a ceramic material. The guide plate 80 is not limited to a spiral shape, and any guide plate may be used as long as it guides the flow of steam in a spiral shape. For example, the guide plate may be constituted by a plurality of blade members formed by dividing the guide plate into a plurality in the circumferential direction.

  According to the main configuration described above, steam is sucked into the one end portion 11 from the intake port 32 in the intake stroke. As indicated by arrows in FIG. 8, the steam sucked from the suction port 32 flows spirally along both surfaces of the guide plate 80, and forms a swirl flow in the one end portion 11.

  In the present embodiment, the guide plate 80 corresponds to the speed uniformizing means, and the speed component in the orthogonal direction perpendicular to the container axial direction of the steam sucked by the suction means is larger than the speed component in the container axial direction. It corresponds to a steam flow forming means for forming a steam flow. With this guide plate 80, the distribution of velocity components in the axial direction of the first linear portion 10a of the inhaled steam can be made uniform in the orthogonal direction orthogonal to the axis. Therefore, the same effect as in the fourth embodiment can be obtained.

  Further, the guide plate 80 is formed of a material having a lower thermal conductivity than the metal material constituting the container 10. Therefore, it is difficult for the container 10 to absorb heat from the steam flowing along the guide plate 80 and the condensation of the steam can be suppressed. The guide plate 80 is made of a material having a specific heat smaller than that of the metal material constituting the container 10 and is thin and relatively small in volume. Therefore, the guide plate 80 has a relatively small heat capacity. Thereby, it is difficult for the guide plate 80 to absorb heat from the steam flowing along the guide plate 80, and the condensation of the steam can be reliably suppressed.

(Other embodiments)
The preferred embodiments of the present invention have been described above, but the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.

  In each of the above-described embodiments, the rectifier 90 is disposed between the opening position of the intake port 32 and the liquid piston 20 in the one end portion 11 of the container 10, but the rectifier 90 may not be provided. For example, as shown in FIG. 9, a heat engine in which the rectifier is eliminated from the configuration of the first embodiment may be used. In addition, illustration of the exhaust piping 40 is abbreviate | omitted in FIG. 2, FIG.

  In each of the above embodiments, the container 10 has a substantially U shape. However, the present invention is not limited to this. For example, the entire container may be L-shaped or straight. It is preferable that a region in which the end surface on the one end portion 11 side of the liquid piston 20 reciprocates, that is, a portion corresponding to the first linear portion 10a in each of the above embodiments extends in the vertical direction. Further, the first linear portion 10a is not limited to the one in which the axial direction completely coincides with the vertical direction. For example, the axial direction of the first linear portion 10a may be slightly inclined from the vertical direction. Absent.

  Further, in the fourth and fifth embodiments, by forming a spiral flow of steam in the one end portion 11, the velocity component in the axial direction of the first linear portion 10a of the steam is made higher than the velocity component in the orthogonal direction. Although it was made small, it is not limited to this. By forming a flow other than the spiral flow, the velocity component in the axial direction may be made smaller than the velocity component in the orthogonal direction in the first linear portion 10a of the steam.

1 heat engine 10 container 11 one end (part on one end side of container)
12 Other end (part on the other end of the container)
20 Liquid Pistons 30a, 130a Introduction Piping Portion 50 Output Portion 80 Guide Plate

Claims (11)

A container (10) that forms a cylinder in which a liquid piston (20) made of a working medium in a liquid phase is enclosed in a reciprocating manner;
An intake means (31) disposed at one end portion (11) of the container, and sucking the vapor of the working medium generated outside the container into the container;
An output unit (50) disposed in the other end portion (12) of the container and converting the displacement of the liquid piston caused by the expansion of the vapor sucked into the container into mechanical energy and outputting the mechanical energy. )When,
A distribution of velocity components in the axial direction (XX) of the vapor of the vapor, which is provided between the intake means and the liquid piston of the container and is sucked by the intake means, is orthogonal to the axial direction ( YY), a heat equalizing means (30a, 130a, 80) for equalizing. The speed uniformizing means has a collision means (30a) for causing the steam sucked by the suction means to collide with a colliding object (14),
The steam is made to collide with the colliding object and the direction of the intake air flow of the steam by the intake means is changed to make the distribution of the velocity component of the steam in the axial direction uniform in the orthogonal direction. The heat engine according to claim 1. The collision means includes a plurality of air inlets (32),
The heat engine according to claim 2, wherein the collision object is the steam sucked from each of the plurality of air intake ports, and the steam sucked from the other air intake ports. The collision means includes an air inlet (32),
3. The heat engine according to claim 2, wherein the colliding object is an opposing wall surface portion (14) facing the intake port among wall surface portions constituting the container.   The heat engine according to claim 4, wherein the speed uniformizing means includes a heating means (70) for heating the opposing wall surface portion. The speed uniformizing means is a steam flow forming means (130a, 130a, 130b) for forming the steam flow such that a speed component in the orthogonal direction of the steam sucked by the suction means is larger than a speed component in the axial direction. 80)
The velocity component in the axial direction of the steam is suppressed by the steam flow forming means, and the distribution of the velocity component in the axial direction of the steam is made uniform in the orthogonal direction. Heat engine. The steam flow forming means has an intake passage part (130a) for sucking the steam into the container from a direction in a twisted positional relationship with respect to the axial direction,
The steam sucked through the suction passage portion forms a swirling flow around the axis of the container, thereby making the velocity component in the orthogonal direction of the steam larger than the velocity component in the axis direction. The heat engine according to claim 6. The steam flow forming means has a guide member (80) disposed inside the container and guiding the steam flow in a spiral shape,
7. The steam component according to claim 6, wherein the steam forms a swirling flow around the axis of the container by the guide member, whereby the velocity component in the orthogonal direction of the steam is larger than the velocity component in the axis direction. The listed heat engine.   The heat exchanger according to claim 8, wherein the guide member is formed of a material having lower thermal conductivity and specific heat than a material forming the container.   The rectifying member (90) provided between the speed equalizing means and the liquid piston and rectifying the flow of the vapor in the axial direction is provided. Heat engine described in one.   11. The heat exchanger according to claim 10, wherein the rectifying member is made of a porous body made of a material having a smaller thermal conductivity and specific heat than a material forming the container.

Images