JP3022012B2 - Hot gas engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hot gas engine using a VM (Bulmeier) cycle for use in air conditioners, refrigerators and the like.

[0002]

2. Description of the Related Art Generally, an engine that operates between a low-temperature heat source, a medium-temperature heat source and a high-temperature heat source absorbs heat from a low-temperature heat source by heat energy (heat work) obtained from the high-temperature heat source and radiates heat to the medium-temperature heat source. The most basic organization is a VM organization. This VM engine has two high temperature and low temperature displacers (for moving the working gas), and is divided into a high temperature part and a low temperature part by a region where each displacer is involved. In the high-temperature section and the low-temperature section, the displacement of the displacer causes scavenging of the working gas. If a portion corresponding to the volume change due to the scavenging is defined as a working chamber, each section has two working chambers. One of the working chambers is at the same temperature level as the medium temperature heat source and is called a medium temperature room. Similarly, a working room at a temperature level equivalent to a high-temperature heat source is called a high-temperature room, and a working room at a temperature level equivalent to a low-temperature heat source is called a low-temperature room. The geometrically required work of these working chambers depends on their volume changes and the uniform pressure fluctuations in the working space (entire engine). In a low temperature room, expansion work is performed, and in a low temperature side medium temperature room, compression work is performed. In the case of this VM engine, since it is an engine that only generates heat transfer between three heat sources, the two scavenging volumes in the high temperature part and the low temperature part match in terms of operation principle, and the expansion work and the compression work in the high temperature part, In addition, the absolute amounts of expansion work and compression work in the low temperature part are equal to each other.

[0003]

However, in an actual engine, a rod for driving the displacer is mounted, and a change in volume caused by this causes a difference in the scavenging volume in both parts. In addition to the change in the working chamber volume, the scavenging volumes in both portions are equal to each other as described above. The phases of the low-temperature and high-temperature displacers are not limited to 90 °, and the inner diameters of both cylinders need not be the same.

[0004] In view of the above circumstances, the present invention focuses on the scavenging volume of the high-temperature section, and intentionally increases the scavenging volume of the high-temperature chamber compared to the medium-temperature chamber, thereby increasing the axial output to the outside. It is intended to provide an institution.

[0005]

SUMMARY OF THE INVENTION The present invention provides a high-temperature side cylinder and a low-temperature side cylinder filled with a working gas, a high-temperature side displacer for partitioning the high-temperature side cylinder into a high-temperature chamber and a high-temperature medium-temperature chamber. A low-temperature displacer that partitions the low-temperature cylinder into a low-temperature chamber and a low-temperature medium-temperature chamber;
A high-temperature heat source for working gas heating disposed in a gas flow path connecting the high-temperature chamber and the high-temperature medium-temperature chamber with a rotation shaft connected to the high-temperature displacer and the low-temperature displacer via a rod and a link mechanism, respectively. Exchanger, a high-temperature side regenerator and a medium-temperature side heat exchanger, and a low-temperature side heat exchanger, a low-temperature side regenerator and a medium-temperature side heat exchanger disposed in a gas flow path connecting the low-temperature room and the low-temperature side medium-temperature room. In the hot gas engine, an auxiliary cylinder is provided in the high-temperature chamber, and an auxiliary piston that reciprocates in connection with a rod of the high-temperature side displacer is provided in the auxiliary cylinder.

A high-temperature cylinder and a low-temperature cylinder filled with a working gas, a high-temperature displacer for partitioning the high-temperature cylinder into a high-temperature chamber and a high-temperature medium-temperature chamber, and a low-temperature chamber in the low-temperature cylinder And a low-temperature side displacer partitioned into a low-temperature side medium-temperature room, a high-temperature side displacer and a low-temperature side displacer connected to each other via a rod and a link mechanism, and a gas connecting the high-temperature room and the high-temperature side medium-temperature room. A high-temperature heat exchanger for heating working gas, a high-temperature regenerator and a medium-temperature heat exchanger disposed in the flow path; and a low-temperature heat disposed in a gas flow path connecting the low-temperature chamber and the low-temperature medium-temperature chamber. In a hot gas engine comprising an exchanger, a low-temperature side regenerator and a medium-temperature side heat exchanger, the high-temperature side cylinder has a larger diameter cylinder than the high-temperature side medium-temperature chamber portion in the high-temperature chamber portion Attached has the shape, the hot side displacer are those having a stepped shape in which the portion that reciprocates in the large-diameter cylinder and the large-diameter displacer.

[0007]

With the above arrangement, if the high temperature side displacer and the low temperature side displacer interlocking with the rotation of the crank mechanism reciprocate with a predetermined phase difference,
The working gas sealed in the cylinder expands in the high and low temperature chambers, and is compressed in the high and low temperature medium temperature chambers.The gas is compressed in the high and low temperature medium temperature chambers. At times, heat is dissipated, and the heat dissipated is used for heating through a heat exchanger communicating with each medium-temperature room, and is used for cooling by absorbing heat when the low-temperature room expands. In this case, since the high-temperature chamber is provided with the auxiliary cylinder and the auxiliary piston in order to increase the volume change, the amount of pressure drop is reduced when heat is absorbed in the low-temperature chamber, and the amount of heat absorbed is reduced. Correspondingly, the pressure rise decreases,
The amount of heat radiation in the low-temperature medium-temperature room also decreases. Since the amount of heat absorbed in the high-temperature chamber is constant regardless of the increase in the scavenging volume in the high-temperature chamber, the shaft output to the outside increases.

The high temperature side cylinder has a stepped shape in which the diameter of the high temperature chamber is larger than that of the medium temperature chamber at the high temperature side, and the high temperature side displacer is also a corresponding stepped displacer. Each time the displacer reciprocates, the volume change of the high temperature chamber becomes larger than the volume change of the high temperature side medium temperature chamber, and the shaft output increases.

[0009]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the drawings of the embodiments.

FIG. 1 shows an embodiment of a hot gas engine having an auxiliary cylinder and an auxiliary piston below a middle temperature chamber in a high temperature side cylinder, wherein 1 is a high temperature side cylinder, 2 is a low temperature side cylinder. The cylinders are arranged at right angles. A high temperature side displacer 3 serving as a piston is disposed in the high temperature side cylinder 1, and the cylinder is divided into a high temperature side chamber 4 and a high temperature side middle temperature chamber 5.
A low-temperature side displacer 6 is disposed inside the cylinder, and a cylinder is partitioned into a low-temperature chamber 7 and a low-temperature middle-temperature chamber 8. Reference numeral 9 denotes a high-temperature gas passage connecting the high-temperature chamber 4 and the high-temperature medium-temperature chamber 5.
0, a high temperature side regenerator 11 and a high temperature part middle temperature side heat exchanger 12 are sequentially arranged. A low-temperature gas passage 13 connects the low-temperature chamber 7 and the low-temperature medium-temperature chamber 8. The low-temperature gas passage 13 includes a low-temperature heat exchanger 14, a low-temperature regenerator 15, and a low-temperature medium-temperature heat exchanger 16. Is arranged. Further, the high temperature side middle temperature chamber 5 and the low temperature side middle temperature chamber 8 communicate with each other through a communication passage 17.
Reference numeral 18 denotes an auxiliary piston provided in an auxiliary cylinder 19 formed in a crank chamber 32 facing below the high temperature side middle temperature chamber 5. A piston rod of the auxiliary piston 18 is connected to a high temperature side piston rod 25 inserted into the high temperature side displacer 3 in the middle temperature chamber. The auxiliary chamber 20 of the auxiliary cylinder 19 divided by the auxiliary piston 18 and the high temperature chamber 5 of the high temperature side cylinder 4 communicate with a high temperature chamber communication passage 33 penetrating the high temperature side piston rod 25, The scavenging volume of the high temperature chamber 5 is set substantially larger than the scavenging volume of the high temperature side middle temperature chamber 5. Further, the lower end of the auxiliary piston 18 and the end of the low-temperature side piston rod 26 that passes through the low-temperature side middle-temperature chamber 8 provided in the low-temperature side displacer 6 are connected in two directions to a crank mechanism 31 attached to a rotating shaft installed in the crank chamber 32. , And reciprocate.
Reference numeral 22 denotes a high-temperature-side piston seal mounted on the outer periphery of the high-temperature-side displacer 3, 23 denotes a low-temperature-side piston seal mounted on the outer periphery of the low-temperature-side displacer 6, and 24 denotes an auxiliary piston seal mounted on the outer periphery of the auxiliary piston 18. is there. 28 is a high temperature side rod seal, and 29 is a low temperature side rod seal.

That is, in this embodiment, an auxiliary cylinder 19 and an auxiliary piston 18 (also serving as a crosshead guide in FIG. 1) are provided by sharing a piston rod below the middle temperature chamber in the high temperature side cylinder. Yes, auxiliary piston 1
The working chamber (in phase with the high-temperature chamber) formed above the high-temperature chamber 4
And the volume change amount is increased. The inner diameter of the auxiliary cylinder and the outer diameter of the auxiliary piston are set to appropriate values.
And the auxiliary chamber 20 communicate with each other.

Next, the operation will be described. When the crank mechanism 31 rotated by a motor or the like rotates, the high-temperature side displacer 3 and the low-temperature side displacer 6 whose phases are shifted by 90 ° in conjunction therewith are respectively connected to the high-temperature side cylinder. 1 and the low-temperature side cylinder 2 reciprocate.

In the first step of FIG. 2, the operation of the displacers 3 and 6 causes the low-temperature medium-temperature chamber 8 to be filled with the working gas and the movement of the working gas in the high-temperature medium-temperature chamber 5 occurs. Along with this, the working gas pressure in the engine rises, and the working gas from the high temperature side middle temperature chamber 5 whose temperature has risen transfers heat contributing to heating when passing through the high temperature part middle temperature side heat exchanger 12 to the outside. To be released.

In the second step, the high-temperature chamber 4 is filled with the working gas and the movement of the working gas in the low-temperature medium-temperature chamber 8 is caused by the working gas of the two displacers 3 and 6. Along with this, the working gas pressure in the engine further rises, and the working gas from the low temperature middle temperature chamber 8 whose temperature has risen passes heat contributing to heating to the outside when passing through the low temperature medium temperature heat exchanger 16. discharge.

In the third step, the operation of the displacers 3 and 6 causes the low-temperature chamber 7 to be filled with the working gas and the movement of the working gas in the high-temperature chamber 4. Accordingly, the working gas pressure in the engine decreases, and the working gas from the high temperature chamber 4 whose temperature has dropped absorbs heat for driving the engine when passing through the high temperature side heat exchanger 10 from the outside.

Further, in the fourth step, the operation of the displacers 3 and 6 causes the high-temperature middle-temperature chamber 5 to be filled with the working gas and the movement of the working gas in the low-temperature chamber 7. Along with this, the working gas pressure in the engine further decreases, and the working gas from the low-temperature chamber 7 whose temperature has fallen absorbs heat that contributes to cooling from the outside when passing through the low-temperature side heat exchanger 14. Become.

Now, this change in the scavenging volume will be described in more detail with reference to the relationship between the volume V in the working space and the pressure P shown in FIG.
Since the scavenging volume of the high-temperature chamber 4 is larger than the scavenging volume of the high-temperature middle-temperature chamber 5, the amount of pressure drop decreases when heat is absorbed in the low-temperature chamber 7 (the solid line in the stroke 4, and the dotted line is a change of the conventional type). Amount), the endothermic amount QC decreases. Correspondingly,
The amount of pressure rise in the stroke 2 is reduced (solid line), and the amount of heat radiation QMl in the low temperature middle temperature chamber 8 is also reduced. At this time, the high temperature chamber 4
Is constant irrespective of the increase in the scavenging volume in the high-temperature chamber 4, the shaft output to the outside increases.

Another embodiment shown in FIG. 3 has an auxiliary cylinder and an auxiliary piston provided separately from the high and low temperature side cylinders. That is, the auxiliary piston 1 is provided separately from the high temperature side cylinder 1 and the low temperature side cylinder 2 which are arranged at right angles.
An auxiliary cylinder 19 with 8 is installed. The auxiliary chamber 20 of the auxiliary cylinder 19 and the high temperature chamber 4 of the high temperature side cylinder 1 are connected by a high temperature chamber communication path 33 to increase the volume change. In the drawing, reference numeral 24 denotes an auxiliary piston seal mounted on the outer periphery of the auxiliary piston 18, and 27 denotes an auxiliary piston rod. In the case of the present embodiment, the inner diameter of the auxiliary cylinder and the outer diameter of the auxiliary piston are selected to appropriate values similarly to the first embodiment, and the piston phase difference is increased so as to increase the volume change of the high temperature chamber 4. Is set.

In the embodiment shown in FIG. 4, the high-temperature chamber portion of the high-temperature side cylinder 1 and the high-temperature side displacer 3 is made larger than the medium-temperature room portion, and the volume of the high-temperature room is made larger than that of the medium-temperature room. That is, the high temperature side cylinder 1 has a stepped shape in which the high temperature chamber portion has a larger diameter cylinder 1a than the high temperature side medium temperature chamber portion, and the high temperature side displacer 3 also has a portion which reciprocates in the large diameter cylinder. The large-diameter displacer 3a has a stepped shape, and the volume of the high-temperature chamber 4 is
Is larger than the volume. At this time, the piston seal 22a is added to the high temperature chamber, and the space formed between the two piston seals communicates with the crank chamber 32 or is opened to the atmosphere. Further, in the case of the present embodiment, not only the volume change amount of the high temperature chamber 4 can be increased but also the volume change amount of the high temperature chamber 4 can be reduced, and both can expect the same effect. 21 is a crank chamber communication passage.

FIG. 5 shows the engine performance obtained by a simple calculation on the assumption that the working gas temperature in each part is constant during the cycle and the volume of each working chamber changes sinusoidally. As is clear from FIG. 5, the shaft output increases by making the volume change amount of the high temperature chamber larger than that of the medium temperature chamber.

In the figure, QC is the amount of heat absorbed in the low-temperature chamber, QM
1: Heat dissipation of low-temperature middle-temperature room QH: Heat absorption of high-temperature room, QMh: Heat dissipation of high-temperature, medium-temperature room VH: Scavenging volume of high-temperature room, ΔV: Incremental volume W: Shaft output to outside

[0022]

As described above, the present invention focuses on the scavenging volume in the high-temperature section and intentionally increases the scavenging volume in the high-temperature chamber compared to the medium-temperature chamber, thereby increasing the shaft output to the outside. It is possible to provide a hot gas engine.

[Brief description of the drawings]

FIG. 1 is a schematic diagram of a hot gas engine showing an embodiment of the present invention.

FIG. 2 is a basic cycle diagram of the heat gas engine.

FIG. 3 is a schematic diagram of a hot gas engine according to a second embodiment.

FIG. 4 is a schematic view of a hot gas engine according to a third embodiment.

FIG. 5 is an engine performance diagram of the effect of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 High temperature side cylinder 2 Low temperature side cylinder 3 High temperature side displacer 4 High temperature room 5 High temperature middle temperature room 6 Low temperature side displacer 7 Low temperature room 8 Low temperature side medium temperature room 9 High temperature side gas flow path 10 High temperature side heat exchanger 11 High temperature side regenerator 12 High-temperature part middle-temperature side heat exchanger side 13 Low-temperature side gas flow path 14 Low-temperature side heat exchanger 15 Low-temperature side regenerator 16 Low-temperature part medium-temperature side heat exchanger 17 Communication path 18 Auxiliary piston 19 Auxiliary cylinder 20 Auxiliary chamber 21 Crank chamber communication path 31 Crank mechanism 32 Crank chamber 33 Low temperature chamber communication passage

Continuation of the front page (58) Field surveyed (Int.Cl. ⁷ , DB name) F02G 1/043 F02G 1/053 F25B 9/14 510

Claims (2)

(57) [Claims] 1. A high-temperature side cylinder and a low-temperature side cylinder filled with a working gas, a high-temperature side displacer for partitioning the high-temperature side cylinder into a high-temperature chamber and a high-temperature medium-temperature chamber, and a low-temperature chamber in the low-temperature side cylinder. And a low-temperature side displacer partitioned into a low-temperature side medium-temperature room, a high-temperature side displacer and a low-temperature side displacer connected to each other via a rod and a link mechanism, and a gas connecting the high-temperature room and the high-temperature side medium-temperature room. A high-temperature heat exchanger for heating the working gas, a high-temperature regenerator and a medium-temperature heat exchanger disposed in the flow path, and a low-temperature heat disposed in a gas flow path connecting the low-temperature chamber and the low-temperature medium-temperature chamber. In a hot gas engine comprising an exchanger, a low temperature side regenerator and a medium temperature side heat exchanger, an auxiliary cylinder is provided in the high temperature chamber, and a rod of the high temperature side displacer is provided in the auxiliary cylinder. A hot gas engine having an auxiliary piston that reciprocates in a linked manner. 2. A high-temperature side cylinder and a low-temperature side cylinder filled with a working gas; a high-temperature side displacer for dividing the inside of the high-temperature side cylinder into a high-temperature chamber and a high-temperature medium-temperature chamber; And a low-temperature side displacer partitioned into a low-temperature side medium-temperature room, a high-temperature side displacer and a low-temperature side displacer connected to each other via a rod and a link mechanism, and a gas connecting the high-temperature room and the high-temperature side medium-temperature room. A high-temperature heat exchanger for heating working gas, a high-temperature regenerator and a medium-temperature heat exchanger disposed in the flow path; and a low-temperature heat disposed in a gas flow path connecting the low-temperature chamber and the low-temperature medium-temperature chamber. In a hot gas engine comprising an exchanger, a low-temperature side regenerator and a medium-temperature side heat exchanger, the high-temperature side cylinder has a step in which the high-temperature chamber portion has a larger diameter cylinder than the high-temperature side medium-temperature chamber portion. A hot gas displacer having a stepped shape, wherein the high temperature side displacer has a large diameter displacer in a portion reciprocating in the large diameter cylinder.