JPS5929784A - Thermal type compressor and energy converter - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates generally to energy converters and, more particularly, to energy converters that utilize regenerative fluid cycles, and more particularly to fluid delivery or differential pressure or cyclic pressure systems. Stirling type free piston thermo compressor (thermo compressor) feeding the load
ssor).

The latest technology is
No. 90, ie, Japanese Patent Application Laid-Open No. 53-29435, Book 1, ``Thermal Compressor Utilizing a Free Piston Coasting Between Each Repulsion Chamber''. This thermal compressor, similar to the present invention but unlike a typical Stirling cycle engine, is useful for driving common loads and variable loads such as free-piston linear synchronous generators. It has an automatic reciprocating piston that provides stability. Possible loads include heat pumps, water pumps, and any driftwood field #I.

The present invention is similar to that disclosed in Japanese Patent Application Laid-open No. 53/1993, except that a short conduit and a check valve are added in the nipple at the hot end of the cylinder.
It is basically the same as the specification of No. 29435. This check valve is suitably double-acting and suitably spring-loaded and automatically bypasses the heating chamber during the Stirling cycle cold fill so that the piston is directed downwardly toward the nipple and finally As it coasts up the nipple, most or virtually all of the gas or compressible fluid between the nipple and the piston passes through a short vertical conduit and then through a short section of the heating chamber inlet conduit to the cooling cylinder. Hot V of the bypass; an easier (lower resistance) cooler path can be taken towards the M section. A very small amount of gas, 10% or less if desired, then passes through a heating chamber for cooling to the (lower) end of the cylinder bypass, where the resistance is even higher. This is different from the thermal compressor disclosed in Japanese Patent Application Laid-open No. 53-29435 (1986).
In the case of 1-#, part is the selection of an annular rigid area between the nipple and/or ring sidewall. 1) Depending on the thickness, a substantial portion of such gas may be transferred through the heating chamber to the hot part of the norinda bypass. Return to the end. In a Stirling cycle engine, virtually all such gases have to pass through the heating chamber and return. That is, for Stirling cycle cooling, gas flows from the hot (expansion) space i) to the cold (compression) space.

During the regenerative cooling portion of the cycle, unnecessary fluid resistance is effectively reduced by reducing the heat load by heating in the heating chamber and by reducing the temperature difference across the regenerator in the heating chamber. The chamber can be made smaller and generate less heat (fluid resistance), and the heat storage can also be made smaller, reducing heat losses and viscous losses (fluid resistance), i.e., the invention enables conventional devices of this type, e.g. This facilitates the use of thermal compressors or Stirling-type engines, which are smaller in size and have higher efficiency and higher specific power output than free-piston Stirling-cycle engines.

Hereinafter, actual examples of the thermal compressor and energy converter according to the present invention will be explained in detail with reference to the accompanying drawings.

FIG. 1 is a top view of the shaft of a free piston Stirling type thermal compressor according to the present invention. FIG. 1 shows a thermal compressor or thermal compressor in which thermal energy is used to generate periodic pressures that drive a load by periodically heating and cooling a pressure fluid, such as a gas. A driving reciprocating piston device is illustrated. The device has a substantially closed cylinder '1 with a side wall 2 of circular cross-section and end walls or end plates 3, 4 at the upper and lower cylinder ends.

The lower or hot end/wall 4 has a circular cross section and is provided with a nipple 5 or plug which projects upwardly towards the free piston/6. The piston side wall γ forms a loosely sliding seal against the side wall 2 of the cylinder 1, thereby dividing the cylinder 1 into a variable volume hot and cold cylinder end below and above the piston 6. The free piston 6 is a cup dog, with its open end facing towards the nipple 5, allowing the piston 6 to pass almost completely F around the cylindrical outer surface 9 of the leek 11150.

The cylinder 1 has a cylinder 1 which forms a bypass region of the cylinder 1 by connecting the hot and low cylinder ends to each other so that the piston coasts when the free piston 6 or 71 reciprocates along the cylinder axis. A bypass 10 is provided. The cylinder/piece/space 10 is sequentially connected to a cold cylinder end slot 11 which is partitioned to the side of the cold cylinder end, and a cooling system equipped with a fan to cool the working gas by an external cooling device. chamber 13 and a heat storage '515 (for example,
stainless steel wool) and a hot bypass conduit 16 terminating in a hot bypass port 17 in the cylinder side wall 2 at the hot end of the cylinder 1 . FIG. 1 shows a thermal compressor with two ports or conduits symmetrical about the cylinder axis and each offset from the axis. However, it is obvious that one such port or conduit is sufficient. Alternatively, two or more ports or conduits, each off-axis, may be used.

FIG. 1 shows the cylinder coasting upwardly in the gas/gas area of the cylinder during the first coasting or first power portion of the reciprocating cycle and downwardly from the cold cylinder end for heating and pressure generation. A piston 6 is shown (see arrow) pushing cold gas through the cylinders. The gas is annular 7
Each hot cylinder bypass conduit 16 after being partially heated by an annular regenerator 15 in the cylinder/mass 10
The heat exits in substantially separate streams 11 which flow into the hot cylinder end through each 71 non-dabypass blower 17.The two fluid streams exiting from the hot end mouth 17 of the cylinder by-pass are: The nipple 50 flows perpendicularly through an extremely thin annular region or gap 18 separating the hot cylinder between the cylindrical outer surface 9 and the inner surface of the cylinder wall 2, and then flows into the two heating chambers of the T-shaped heating chamber 4 and the thunder 21. Inlet 2
0.20. The conduit 21 has 20 conduits each day in its common vertical central section or trunk section.
It has two short horizontal ゛1゛-shaped conduit bowl portions 22.22. The central section or axis 11 of the T-shaped inflow conduit #21 urinary trunk section connects to the T-shaped arm section 22 via the population 20.
The inwardly flowing gaseous stream is directed downward into a heating chamber 24 heated by an external heat source 25 . That is, the heating chamber inflow conduit 2
1 passes through the nipple 5 and terminates at the heating chamber inlet 20V on the cylindrical outer surface 9 of the nipple 5 at the hot cylinder end. The inlet 20 is located directly in the conduit of the fluid flow exiting each hot cylinder/minor slot 17 at a distance from each day 11 of a very small dimension, e.g. equal to or less than 1° of the cylinder radius. It's a shame. 1 pair mouth 1γ, 20
The conductive portion in contact with the
As stated in the first floor of No. 3-39435, Ic mutual (
C aligned or coaxial, annular area or gap 18
Minimizing the loss of fluid from the gas streams, virtually all of the gas in these streams is removed from the nipple 5 before exiting the heating chamber during this first power portion of the cycle or the Stirling cycle heating portion. and heat it in a heating chamber.

To facilitate good heating of the gas, the hot cylinder end wall 4 is provided with a cup-shaped projection 26 which projects downwardly towards a heat source 25 which may be any suitable heat source. Around the protrusion 26 is provided a double-walled cup-shaped enclosure or can 27 which is heated by a heat source 25 . The can 27 has a cup-shaped protrusion 2
6 to form a passage for heating the fluid flow flowing through or into the heating chamber 24. For good heat transfer, the cooling chamber as well as the heating chamber 24 are provided with inner/outer fins (not shown). Can 27 extends upwardly around the thermal compressor to create a good cold seal at the cold cylinder end to contain commercial working fluids such as helium for extended periods of time. Two protrusions or nipples 5
and a hot cylinder end plate 4 with a protrusion 26 is connected to a heat source 25
The hottest part of the can 21 is heated only indirectly by the heating chamber 24, and then the gas flow flows upwardly through the heating chamber outflow conduit 29. It flows through an outlet in the upper surface 30 of the tube 5 to the hot cylinder end below the piston 6. The conduit 29 passes behind the T-shaped conduit arm 22.

The free piston/6 coasts upwards until the cold rebound conduit 39 of the cooling/splash chamber 40 therein is blocked by a cold rebound plug 43 which projects downwardly from the cold/cylinder 4Aj plate 3 towards the free piston 6. Next, during the rebound portion of the reciprocating cycle, the piston chamber 40
Compression by the tap 43 of the gas within causes the free piston 6 to rebound and then enter the second coasting part of the cycle, i.e. the second
During the power section of the engine, it begins to move downwards towards the hot end of the cylinder.

During the first power part of the cycle, the pressure increase across the thermal compressor transfers some of the working gas to the fluid driven load (not shown) via the load port 4G of the load conduit 45 in the cold cylinder end wall 3. ) can be sent to This pressure increase, caused by increasing the average temperature of the working gas in the thermal compressor by heating as much gas as possible, is caused by a labyrinth groove in the upper part of the cylindrical outer surface 9 of the nipple 5, just below the upper nipple face 30. 36 makes it easier. Each groove 36 allows a hot cylinder bypass conduit 16
That is, it reduces the amount of gas that rises along the annular gap 18 from the aforementioned gas stream or jet flowing out from the nozzle toward the heating chamber 24.

This leakage is minimized by the thinness of the thin-walled piston section 37, which acts as a thin wall of the opposite cup formed by the cup-shaped free piston 6. The thin-walled piston portion 37 is needed later in the cycle to plug the bypass port 17 of the cylinder bypass 10 during the hot rebound cycle portion followed by the second power portion of the cycle.

Returning to the first power portion of the cycle, the pressure increase across the thermal compressor is controlled by a heating chamber bypass conduit 50 leading from a port 51 in the top nipple 30 and downwardly to a port 52 along the cylinder axis. It becomes even easier by blocking it.

Port 52 connects the short vertical low resistance heating chamber bypass conductor 50 to the midpoint or reed connection of T-shaped heating chamber inlet conduit 21 . Due to the upward movement of the piston 6 and the pressure drop in the heating chamber due to the fluid friction exerted on the gas flow,
1 , the pressure is even greater than in the heating chamber bypass conduit 50 and the cylinder space between the conduit 50 and the upwardly moving free piston 6 . This differential flow single pressure across the check valve bulkhead 60 causes the lamella 60 to be applied upwardly against the short heating chamber bypass conduit 500 port 52 during the upward movement of the free piston 6, thereby starting the cycle. During the first coasting portion and also during the initial portion of the cold splash out of the cycle, the opening 52 and conduit 50 are added to facilitate the introduction of the fluid stream into the heating chamber for heating within the cram room. Make it.

During the final part of the cold rebound part of the cycle and during the second inertial part of the cycle, the groaning motion of the piston 6 forces gas from the hot cylinder end upwards through the cylinder bypass and stores heat. The gas is further cooled by a cooling chamber 13 before flowing from the cold end of the /ring bypass through the cold cylinder bypass blower 11 to the cold cylinder end. This cooling process also causes some gas to return from the load via conduit 45 (reversing the gas flow arrows) in response to a drop in gas pressure across the thermal compressor. The downward movement of the piston 6 and opposing fluid friction within the heating chamber 24, including the inlet and outlet, in this case causes the heating chamber inlet conduit to flow into the heating chamber bypass conduit 50 and into the hot space just above the nipple top surface 30. A fluid pressure higher than that in 21 results. The above-mentioned check valve leaflet 60 is installed within the nipple 5 by 1 fft at the four-way intersection of the two horizontal arm portions 22 of the T-shaped heating chamber inlet pipe 210. The vertical common flow axial trunk portion of the T-shaped heating chamber inflow conduit 21 is
It extends downward from the intersection toward the heat source 25. Also short (・
A low resistance heating chamber bypass conduit 50 in the vertical axial direction (along the cylinder axis) extends in two directions from the intersection.

Therefore, the check valve lamina 60 is located above the lamina in the conduit 50.
It receives the higher pressure noted and the lower pressure below the lamina in conduit #21 and responds to this difference @fluid pressure by moving downwardly from port 52 toward the trunk portion of conduit 21. In this way, the lamina 60 opens the heating chamber pipe conduit 50 and heats the cylinder end by directing most of the gas at the end of the cylinder through the conduit 50 and the arm section 22 so that the fluid flows through the hotter cylinder pipe. 17, the higher fluid flow resistance through the heating chamber bypasses the heating path and cools in the cylinder bypass.
50 and check valve lamella 60 together form a pressure driven heating chamber bypass with the advantages described above.

The thin-walled piston part 3γ passes as a sleeve around the upper part of the cylindrical outer surface 9 of the nipple 5, including the labyrinth groove 36, and then passes around the hot cylinder bypass opening 17, thereby forming a cylinder. Start plugging the hot end of the bypass.

Thus the second coasting part 1 of the cycle - the second power part - ends and the hot rebound part of the cycle begins. In this case, the gas trapped below the piston 6 at the hot cylinder end is compressed by the piston 6 and forced into the nipple 5 and into the heating chamber 24, heating the gas with a thermal delay and increasing the thermal effect of the spring. This spring effect directs the piston 6 toward the cold cylinder end when the free piston 6 opens the hot cylinder bypass port 17 at the end of the hot splash portion of the cycle, and causes the piston 6 to close the 017 at the beginning of the hot splash portion. When the velocity and momentum of the piston 6 is higher than the pushing force σ. The above-mentioned "thermal lag" means that the time of generation of the highest instantaneous temperature and pressure of the trapped gas lags the time of generation of the highest instantaneous HJ compression ratio (at the bottom of the piston stroke); (averaged over mutually equal portions of the stroke chosen symmetrically with respect to the point of maximum instantaneous compression ratio) after which a higher average pressure is produced at the piston face than before the generation of the maximum instantaneous compression ratio.

The thermally delayed driving action of the reciprocating walls of a closed chamber is described in US Pat. No. 3,807, published April 60, 1974 by the inventor
The invention is described in various patent specifications of the present inventor, including "Reciprocating Piston Device" in the specification of No. 904. The heating chamber 24 can combine the properties required for Stirling cycle heating of the fluid and actuation with thermal lag of the free piston.

The rebound chamber 40, which is generally warmer than the cold cylinder end circle gas, also produces a driving effect that causes some thermal lag in the free piston. The inventor has constructed a partial heat-driven model showing the loading of the free piston in the top area of the cylinder bypass and the actuation of the free piston to thermally retard it. The model is powered by waste heat energy from a standard 200W incandescent bulb.

In the free piston of FIG. 1, during the first half of the hot rebound portion of the cycle, the downward movement of the piston causes a downward flow of gas in the heated bypass conduit 950 and a downward flow of gas into the non-return square lamella 60. When it hits, the direction is about 90°7
The continued internal action of the debris that must be dislodged exerts a slight downward force on the check valve lamina 60. also occurred during the second half and during the second coasting part of the cycle, but in this case the cylinder bypass port 17 was blocked by the piston part 31 and the axial or trunk part of the heating chamber inlet conduit 21 The gas flow in the Dn heat chamber outlet conduit 1f29 is downwardly parallel to the gas flow in the Dn heat chamber outlet conduit 1f29.The piston also slows down in this case and the temperature of the trapped gas increases, i.e. the force of the gas on the lamina 60 is initially is still downward but hot during the first half of the rebound cycle portion and then reverses.During the upward movement of piston 6 the upward flow of gas in conduit 21 increases, causing lamella 60 to move upward and through the conduit. 500 ports 52. The lamina 60 is held by a pressure difference mJ approximately equal to 1 below the pressure along the path of the fluid flowing from the inlet conduit 21 through the heating chamber 24 and its outlet conduit 29 towards the piston 6.

Thus, the heating chamber bypass conduit 50 is connected to the cylinder bypass port 17 at the hot end of the cylinder bypass at the piston portion 37.
The check valve leaflet 60 is closed by the time it opens. Conduit 50 then remains occluded during at least the first coasting portion of the cycle and also during the initial portion of the first half of the subsequent cold splash portion of the cycle due to the differential pressure described above. ing.

The check valve lamina 60 is guided by a loose fit within its niprun housing. This loose fit allows fluid to flow relatively freely around the lamina 60 as the lamina 60 is urged away from the mouth 52. Optionally, the lamina 60 is attached to the spring arm 6 of a spring 62 mounted within a slightly enlarged L portion 64 of the uniaxial common flow trunk portion of the T-shaped inlet conduit 21 of the heating chamber 24.
It is guided by a part like 1, and also supports or springs. However, the present thermal compressor equipped with an in-nipple IC check valve operates without a mechanical spring. That is, spring 62 is not necessary. The check valve can be thought of as a combination of the check valve lamina 60 and an adjacent or adjacent structure of the nipple which acts as a wall or housing of the check valve. Includes 4 (') conduit openings in the 4-way cross section with 4 hot/
If a cylinder bypass conduit is used instead of two conduits, the check valve lamella 60 may be located within the nick 5 at the center of the six-way U intersection on the cylinder axis. Of course, other combinations of fathers may also be used.

The lamina 60 is a loosely fitted enlarged but very short cylinder section that extends upwardly or downwardly and
2 or at the top of the axial section of the inlet conduit 21, or both of these locations (by forming a recessed valve seat, the fluid flow can be taken out. If both locations are used as described above) The thin piece 60 is A of the double-acting check valve inside the nipple.
g.Use it as a moving part (this applies whether or not the valve seat is inflated). However, due to the thin section 60, T
There is no need to block the lower trunk portion of the shaped inflow conduit 21 (
・0 In fact, in order to keep the groove piece 60 against the trunk part and to keep it in a state of blocking the flow in this trunk part, the thin piece 6
A small protrusion may be provided at the top of the trunk portion of the conduit 21 on the underside of the tube. These protrusions allow a small amount of gas to flow through the heating chamber parallel to the flow through the heating chamber bypass conduit 5Q during the second power portion of the cycle so that the fluid resistance is further reduced. Alternatively, these projections can improve the drive action with thermal lag of the free piston during the subsequent hot rebound circle section. Alternatively, these protrusions facilitate proper closing of the port 52 and conduit 50 by the lamina 60 during the subsequent upward movement of the free piston during the hot rebound cycle portion. The objective is to open and close the heating chamber bypass conduit at appropriate times in the cycle without restricting fluid flow in required or critical portions of the heating chamber inlet conduit within the nipple.

After supplying sufficient heat to the heating chamber 24 by the heat source 25, the compressor is moved below the piston, i.e., in accordance with my U.S. Pat.
It can be easily started by a single pressure pulse or reciprocating pressure applied to any part of the gas volume 7 below the free piston, as described in the respective specifications of the patent application. Alternatively, a suction pulse or reciprocating suction action may be applied above the piston.

As part of a thermally driven free piston displacement linear synchronous generator, the voltage applied to the generator's coils produces this attraction effect. However, if properly designed, such generators can be self-starting. Based on the inventor's calculations and some design considerations, the Stirling lag angle between the phases of the two free pistons of such a synchronous generator becomes a lag of 90° under increasing negative This synchronous generator, if properly designed and properly heated, will provide a relatively constant amplitude and frequency of about 40% under variable loads at a relatively constant amplitude and frequency.
It is thought that it is possible to operate with a heat to air efficiency of 1.5 or more. The energy converter according to the present invention is safe, quiet, clean, inexpensive, and has very low pollution (and can be powered by any fuel or even by solar energy or waste heat).

Considering a Stirling cycle engine of the type, a thermal compressor with a free piston coasting (self-reciprocating) driven with a thermal lag is particularly suited to the pressure-driven heating chamber bypass of the present invention for the following reasons: considered suitable.

First, to remove the heating chamber from its normal position in the Stirling cycle and position this chamber at the hot end of the cylinder for the thermally retarded drive of the free piston, between the regenerator and the heating chamber. A good lunar cycle conduit is needed to easily and quickly transport the fluid between the two so that a good Stirling cycle heating and cooling of the working fluid can be easily achieved. The heat chamber bypass of the present invention also requires such sound guidance to easily and quickly direct fluid from the hot space of the cylinder directly into the regenerator during Stirling cycle cooling.

In other words, heating; heat storage) Iwadobetsu [Flow #16 in Figure 1,
211 serves both purposes simultaneously.

Second, a self-reciprocating piston traps fluid in a heating chamber to drive the piston over a thermal lag and presses 1. Since it is necessary to close the conduit after each cycle to ensure a good temperature, the heater-heat storage 4 conductor passes through the hot V1% of the /su/da and connects this conduit to the hot / cylinder space below the piston. It is best to pass it very close to the gas. This closeness also allows the heating chamber bypass conduit (conduit 50) to be very short in this manner, resulting in very low driftwood flow resistance and very little dead volume added to the hot cylinder end. Advantageous for chamber bypass.

That is, the passage of the heater-regenerator conduit through the hot end of the cylinder also serves two purposes at once.

Sixth, the coasting free piston device, driven with thermal delay, has a nipple at the hot cylinder end and is shaped like a conventional Uziknob through which the heating 4-washer conduit and the heat-chamber outflow conduit pass. 1) y, no. 1, d, 1, to reduce fluid loss from the fluid flow flowing across the gap in the conduit [the gap between b 17 and 20], and to reduce the loss of fluid from the fluid flow flowing across the gap in the conduit, and to reduce the loss of fluid as described above in the hot cylinder end. A special shaped dead space 7 is filled adjacent to each conduit of the book, filling an axially symmetrical dead space through which a simple cup-shaped free piston passes. This same nipple eliminates the need for fittings and leads external to the cylinder and creates less fluid resistance or dead space or additional heat loss.
The non-return valve of the present invention and the short heating chamber bypass conduit form an appropriate housing in the correct place. In these respects, therefore, the double valve also serves multiple purposes at once.

For these reasons, the Stirling cycle type thermal compressor or engine uses the pressure and drive heating chamber bypass of the present invention (7) J
5. Practically speaking, no significant advantage can be gained from cycle-synchronized heating chamber bypass.

That is, for the above-mentioned reasons, the combination of the pressure-driven compressor Z15 bypass according to the present invention and the coasting free piston type thermal compressor driven with thermal delay according to the present inventor's Japanese Patent Laid-Open No. 53-29435. It is thought that there is a strong relationship between the two. JP-A-53-29435 itself shows that there is a cooperation between the cup-shaped free piston and the 40fjf built-in nipple and some of the inventor's earlier piston patents. Some of these piston patents include a self-reciprocating free piston driven by a thermally delayed heating chamber, and an lti? T,
There is the use of nozzles or jet effects to convey the compressed fluid in the stream from one conduit across the gap into and through another conduit H leading to the heating chamber.

Due to the precise design of the present thermal compressor (and due to the nature of the load), the thermodynamic cycle substantially departs from the Stirling cycle. However, the thermodynamic efficiency can still be extremely high and By providing the automatic synchronous heating bypass of the invention, for virtually any type of load the heating is significantly higher than without this bypass.For free piston loads, such as when driving a linear synchronous generator or a heat pump, This cycle can be considered a modified Stirling cycle with very high thermal efficiency and variable Starry/lag lag angle between the two piston phases.

This delay angle automatically shifts as the force increases with increasing load values. This &i, RLC circuit (resistance -
This can be determined by analogy with inductance (inductance/capantance).

According to the present invention, if the hot cylinder bypass conduit 16 is made of Japanese cedar as described in JP-A No. 53-29435, the heating chamber inflow conduit 21 is basically shaped like a 1' instead of a 1' shape. becomes a 7-figure shape.

The father said that each cylinder bypass conduit should add its own heating chamber inlet conduit, and one or more elbow-shaped heating chamber inlet conduits each with a heating chamber bypass conductor and a check valve. It turns out. Also, instead of a check valve, a pressure sensitive valve or a suitable valve synchronized with the cycle may be used. Of course, it is possible to carry out variations of the inoculum without deviation.

[Brief explanation of drawings]

FIG. 1 is an axial sectional view of an example of a free piston type Stirling type thermal compressor according to the present invention. 1...Cylinder, 6...Free piston, 10...
/Linda bypass, 15...Regenerator, 1γ.../Linda bypass bypass, 20...Heating chamber inlet, 21...
Heating chamber inflow conduit, 24: heating chamber, 29: heating chamber inlet port, 50: heating chamber bypass, 60: bypass valve.

Claims (1)

Claims: (1) a cylinder, a free piston dividing the cylinder at mutually opposing piston ends into a hot cylinder end and a cold cylinder end of variable volume; and a regenerator for said hot cylinder; A cylinder bypass which connects an end and a cold cylinder end to each other to form a bypass area of the cylinder for the piston in the VA which reciprocates along the piston or cylinder line 1IqII, and a cylinder bypass which forms a bypass area of the cylinder for the piston, and a heating chamber connected to the cylinder bypass via a heating chamber inlet conduit originating from a heating chamber inlet located at the hot cylinder end adjacent to the hot cylinder bypass at the hot end thereof; The heating chamber is connected to the end of the hot cylinder via the heating chamber outflow conductor at °C. A variable volume space of the hot cylinder end adjacent to the hot end of the piston is connected to the chamber inlet conduit, and reciprocated by the heating chamber bypass valve as the piston moves towards the cold cylinder end within the cylinder bypass region. A thermal compressor characterized in that the heating chamber bypass is closed during at least a substantial portion of the first power portion of the cycle. (2) The heating chamber bypass is arranged at the hot cylinder end. The thermal compressor according to claim (1). (3) The thermal compressor according to claim (1), wherein the heating chamber bypass valve is provided with a pressure sensitive valve disposed at the end of the hot cylinder. (4) The thermal compressor according to claim (3), in which the valve is provided with a thin piece having a valve stem. (5) A hot end plate is provided at the end of the heating cylinder, and this Claims: The hot end plate is formed with a projection extending from the end plate towards the hot end of the free piston, the heating chamber bypass and at least part of the heating chamber inlet conduit being disposed within the projection. Thermal compressor according to claim (1). (6) Thermal compressor according to claim (5), which uses a heating chamber bypass valve that senses periodic fluid flow in the projecting body as the heating chamber bypass valve. type compressor. (7U iJO thermal chamber bypass valve uses a valve with a flow-limiting moving piece, and this moving piece is placed approximately at the junction between the heating chamber inlet conduit and the heating chamber bypass conduit of the heating chamber bypass. (8) The valve and the joint are arranged such that the periodic movement of the moving part occurs primarily in the heating chamber inlet conduit adjacent to the joint. A thermal compressor according to claim (7), which is formed as follows. (9) Claim (7) states that the movable part of the valve is a thin piece that periodically moves across approximately the midpoint of the heating chamber inflow conduit at the joining part with the heating chamber bypass conduit. thermal compressor. (10) A thermal compressor according to claim (9), wherein the thin piece is connected to a valve rod that can guide and correct the movement of the thin piece. (Group) The heating chamber inflow guide is placed within the protrusion and connected to at least two inflow arms starting from the heating chamber inlet on the protrusion surface adjacent to the hot end of the cylinder bypass at the rear end within this protrusion. a common trunk is provided in the heating chamber bypass and connected at said intersection to said common trunk and at least two inlet arms of a heating chamber inlet conduit, said slit being connected at the hot end of the cylinder. The thermal compressor according to claim 5, wherein the heating chamber bypass conduit is located at the hot end of the cylinder adjacent to the hot end of the piston. A heating chamber bypass conduit is formed on the surface of the protrusion proximate to the variable volume space and communicates with this space. Claim 11 terminating in a heating chamber outlet conduit outlet communicating with this space, the heating chamber bypass bypassing the heating chamber, the trunk and at least a portion of the heating chamber outlet conduit.
Thermal compressor described in ). 03) The thermal compressor according to claim 1, wherein the heating chamber bypass valve is provided with a flow restriction piece that moves periodically at the intersection during operation of the thermal compressor. The 0-force heating chamber bypass valve has a thermal pressure type according to claim (11), which is provided with an inner surface of a protruding body at the intersection part.
rm) a. (15) The thermal compressor according to claim 11, wherein the heating chamber bypass valve is provided with a thin piece disposed at an intersecting portion. θ6f A thermal compressor according to claim 151, in which a valve stem connected to a spring is provided in a flake. The thermal compressor according to claim (15), which is made such that the ends thereof periodically intersect across approximately the midpoint of the intersecting parts in the protrusion. (18) Heating chamber bypass A type 19 compressor according to claim (5), in which the main body of the valve is formed by a protruding body.Claim (1), in which the cross section of the u9 heating chamber inflow conduit is approximately "1"-shaped. (20) Provide a hot recessed piston surface on the piston at the hot end, and place a heating chamber bypass at the hot cylinder end.
The hot concave piston surface has a partitioned displacement volume which completely surrounds the heating chamber bypass during the hot rebound portion of the reciprocating cycle and the hot end of the cylinder bypass from the wall of the piston surface. A thermal compressor according to claim (1), wherein the compressor is closed. c21) A claim in which the heating chamber and the heating chamber bypass are constructed in such a way that the heating chamber bypass valve begins to block the heating chamber bypass before the end of the hot rebound portion of the reciprocating cycle immediately preceding the first power portion of the reciprocating cycle. The thermal compressor according to the range (1). (a) a cylinder, a piston that divides the cylinder into first and second cylinder ends at mutually opposing piston ends, and a first cylinder at the first and second cylinder ends including a heat accumulator; and a cylinder bypass that communicates with the second cylinder bypass via a 7m section, and a cylinder bypass that communicates with the first cylinder end via a first port disposed at the first cylinder end and the seventeenth ring bypass end. A first heat exchanger communicated with the part through a conductor penetrating a part of the end of the first cylinder, and a part that maintains the reciprocation of the piston in the cylinder. In an energy converter that utilizes a 6-positive Stirling cycle, a valve is provided in the first heat exchanger bypass to connect the fourth cylinder to the second cylinder at the end of the first cylinder near the piston, and this valve an energy converter, wherein the first heat exchanger bypass is occluded during a portion of the reciprocating cycle. -Claim No. 2 uses a pressure-sensitive valve as a valve (an energy converter as described in the second claim). The energy converter according to claim 1. (c) The energy converter according to claim 5, which includes a spring that acts on the valve stem.