JPS63306238A - Thermal prime mover - Google Patents

Abstract

PURPOSE:To prevent occurrence of surging by rotating a male rotor and a female rotor in the opposite direction with each other, compressing air, and feeding a combustor with this compressed air. CONSTITUTION:A blade 2 of a male rotor 1 is locked to a blade supporter 4, rotating this blade solidly together with a rotary hollow body 9 as joining it close to the circumference of a fixed follow body 11. In a female rotor 5, there are provided with an outer circumferential part 6 to contact close to a rotor casing inner circumferential surface and a sinking part 7 where the blade 2 is fitted in from the outer circumferential part 6 as sinking down. The female rotor 5 and the male rotor 1 are rotated in the opposite direction with each other, and air out of a suction passage 14 is compressed, feeding a gas turbine combustor with this compressed air. With this constitution, air is compressed by a displacement type compressor so that any surging can be prevented from occurring.

Description

Detailed Description of the Invention The present invention provides a positive displacement compressor and a velocity expander (turbine) configured such that a male rotor and a female rotor synchronously rotate in opposite directions without contacting each other. This relates to a thermal motor connected to

In general, gas turbines, which are a type of heat engine, have superior features compared to piston engines, such as being smaller, lighter, less vibrating, less polluting, and able to use poor combustion. Because it uses a machine, it is prone to surging and has the fatal disadvantage of having a narrow range of high thermal efficiency.

As a countermeasure to this problem, there have been cases where a screw compressor, which is a type of positive displacement compressor, is adopted for the part corresponding to the compressor of the gas turbine, but this creates a new problem of being extremely expensive, and has not been put into practical use. Not yet.

Furthermore, the gas turbine has a serious drawback of extremely low thermal efficiency in the partial load region.

The present invention is a new gas turbine that inherits the characteristics of a gas turbine that is small, lightweight, low vibration, low pollution, and can use inferior fuel, while also being inexpensive and highly efficient, especially in the partial load range. In one embodiment of the heat engine, the compressors C1 and C2 are positive displacement compressors, the former being the first stage compressor and the latter being the second stage compressor, and the first and second stage compressors are shown in the figure. The two-stage compression type used here may be replaced by a three-stage compression type by adding a third-stage compressor, or alternatively, a two-stage compression type using only one compressor.

It is also possible to connect the compressors C1, C2 and the turbine 21 with a fluid interposed therebetween.

A cross-sectional view taken along the line AA' of the compressor C1 is shown in FIG. 2, and the cross-sectional view of the compressor C2 is exactly the same, with the only difference being the axial length of the rotor.

First, the compressor C1 will be explained.

In FIG. 2, the blade 2 is firmly fixed and supported by the blade support 4, and is closely spaced around the fixed hollow body 9 (0.1~
The rotating hollow body 9 rotates integrally with the fixed hollow body 9 while closely surrounding the rotating hollow body 11, which is provided so as to be fixed with a minute gap of about 0.3 mm.

The female rotor 5 has a female rotor outer circumferential portion 6 that is in close contact with the inner circumferential surface of the rotor casing, and a recessed portion 7 into which the blades 2 fit while recessing from the female rotor outer peripheral portion 6. The rotor consisting of the body 4) and the female rotor 5 are in a non-contact state (0.1 to 0.3 mm) with each other.
They are rotated synchronously in opposite directions by a synchronous gear 15 (while maintaining a very small gap).

The female rotor outer periphery 6 is configured to be in close contact with the rotating hollow body 11, and preferably, the female rotor outer periphery 6 of the rotating hollow body 11 is in close contact with each other as shown in the figure.

Next, if we pay attention to the line L1 of the blade 2 (actually it is a surface, but we are considering a cross section), the line L1 is the line L3 of the female rotor 5.
It is desirable that the line L2 of the blade 2 and the line L4 of the female rotor be created by the tip of the blade 2 (a point or a small roundness), and that the line L2 of the blade 2 and the line L4 of the female rotor be mutually created by the other line. , if it is convenient for manufacturing, etc., the part on the base side of line L2 and the part on the tip side of line L4 are created so that they overlap each other, and the part on the tip side of line L2 and the part on the root side of line L4 are created. Although the capacity of the compressor will be slightly smaller even if a large gap is left between the lines L2 and L
During the very early period of the compression process when the meshing with 4 begins, the gas trapped inside is released to the suction side in an uncompressed state.■) The machine as a compressor can be maintained. .

That is, if we pay attention to the recessed part 7 of the male rotor and the blade 2 of the male rotor that should fit into the recessed part 7, we can see that the part on the tip side of the advancing side wall forming the recessed part 7 (the tip of line L3 - A line (line L2) of the cross section of the blade side surface on the back side of the blade cross section (line L1) of the same blade 2 created by a point or small roundness) and a line (line L2) of the cross section of the wall surface on the lagging side forming the depression 7. Among the lines L4), one of the lines is constructed such that they mutually create each other by a portion that occupies at least a relatively large portion of the other line.

A sufficient gap is left between the tip of the line L1 and the line L3 (excluding the tip) so that gas can freely enter and exit even when the two are closest.

Line L5 is a circular arc in which the male rotor outer circumferential portion 3 is in close contact.

Now, paying attention to the working chamber 8 sandwiched between the male rotor blades 2 and the male rotor 5, the gas in the working chamber 8 is hermetically compressed by the reduction in the volume of the working chamber 8, and the fixed hollow body 9 When the internal pressure (high pressure) becomes almost equal to the internal pressure (high pressure), the liquid is discharged into the fixed hollow body 9 through the communication port 12 formed in the fixed hollow body 11 and the opening/closing port 10 formed in the fixed hollow body 9. It has become.

That is, the working chamber 8 is configured to communicate with the fixed hollow body 9 through the communication port 12 and the opening/closing port 10 from the intermediate volume state to the minimum volume state of the working chamber 8.

When the blade 2 communicates with the communication port 12, in order to prevent the working chamber 8 from communicating with the working chamber on the lagging side through the communication port 12, the central angle of the communication port 12 should be The central angle of the portion that is in close contact with the periphery of the rotating hollow body 11 may be set as follows.

A PV diagram (pressure-volume diagram) of the working chamber 8 is shown in FIG. 3, and it will be understood that it has a high total adiabatic efficiency.

In the figure, the number of blades 2 of the male rotor and the number of recessed portions 7 of the female rotor are 2 and 2, respectively, but it is clear that other configurations, such as 3 or 2, are also possible.

Although the blade support 4' in FIG. 1 is not directly fixed to the fixed hollow body 9, it has the role of balancing and reinforcing the centrifugal force acting on each blade 2.

Returning to FIG. 1, the thermal motor according to the present invention will be described in more detail (see also FIG. 2 below).

That is, the gas (usually air at atmospheric pressure) sucked into the first stage compressor C1 from the suction passage is compressed here, and after being cooled by the cooler 6 from inside the fixed hollow body 9, it is compressed in the second stage. The air flows into the compressor C2, where it is compressed again and introduced from the fixed hollow body 9 of the second stage compressor C2 into the heating chamber 18 via the heat exchanger 17.

An ignition line 9 and a fuel injection valve 20 face into the heating chamber 18, and when fuel is injected and ignited by the ignition plug 9,
Continuous combustion is maintained within the heating chamber 18.

The gas (usually combustion gas) that has been given thermal energy in the heating chamber 18 is thus introduced into the turbine 21, where it is sufficiently expanded.

22 is a nozzle, and 23 is a turbine blade.

At this time, the gas discharged from the turbine 21 is transferred to the heat exchanger 1
The gas introduced into the heating chamber 18 is heated and then discharged into the atmosphere.

This is to recover waste heat and improve the thermal efficiency of the heat engine.

The purpose of the cooler 16 is to take away the compressor, approximate isothermal compression, and save compression power, and it may be removed if a reduction in structure is required.

In this way, from the power generated by the turbine 21, the compressor C1,
After subtracting the power required to drive C2, the thermal motor will generate power corresponding to the amount of power required to drive C2, which will drive a load such as a generator.

Next, the thermal motor according to the invention is a pure rotating machine,
Since it is a continuous combustion type, it has the characteristics of being small, lightweight, low vibration, and low pollution, and can use poor quality fuel, but since it uses a positive displacement compressor as a compressor, no surging occurs. Compared to speed type compressors, high efficiency can be obtained over the entire motion range, and a high pressure ratio can be generated even in the low speed range, so thermal efficiency is extremely high, and high thermal efficiency is expected even in the partial load range where low speed operation is required. I can do things.

Unlike a screw compressor, the compressor in the heat engine according to the present invention does not have a helical rotor around the shaft, and is therefore easy to manufacture and inexpensive to manufacture.

In addition, each rotor is in close contact with the inner peripheral surface of the rotor casing over a wide area, and the part where the outer peripheral part 6 of the female rotor and the rotating hollow body 11 are in close contact can be made into a wide surface, so that leakage loss can be reduced. is extremely small, and has a higher total adiabatic efficiency than a screw compressor.

This is an important element that makes the thermal efficiency of the thermal engine high.

The object of the invention is thus achieved.

In Fig. 1, compressors C1 and C2 are gas (usually air).
You may also inhale only the

That is, once combustion occurs with the ignition plug 19, the mixture of gas and fuel successively sent by the remaining flame can be combined and combusted within the heating chamber 18 (in this case, the fuel injection valve 20 is not necessary).

It is also possible to apply thermal energy from the outside to the gas introduced into the heating chamber 18 in FIG. 1, and this is shown in FIG. 4.

That is, in FIG. 4, when fuel is injected from the fuel injection valve 20 and combustion (coupled combustion) occurs by the spark plug 19, the gas sent from the compressor (second stage compressor C2) enters the heating chamber. Thermal energy is applied from the outside of the turbine 24, and thus high-temperature, high-pressure gas is introduced into the turbine 21 to generate power, thereby achieving the object of the present invention.

Next, the embodiment shown in FIG. 5 is basically the same as that in FIG. 1, but differs in that two-stage compression is achieved using three rotors and the structure is simplified.

That is, the male rotor 1 meshes with the female rotor 5 in a non-contact manner.
It uses a compressor equipped on both sides of the female rotor 5,
The compressor is a first stage compressor C1 consisting of a female rotor 5 and a male rotor 1 on one side meshing with the female rotor 5.
The second stage compressor C2 consists of a female rotor 5 and a male rotor 1 on the other side that meshes with the female rotor 5.

The compressor and turbine (not shown) are connected to each other.

Therefore, the fixed hollow body 9 compressed by the first stage compressor C1
While introducing the gas from inside to the second stage compressor C2,
The gas from the fixed hollow body 9 compressed by the second-stage compressor C2 is introduced into the heating chamber 18 (see Figure 1) to give thermal energy, and the high-temperature and high-pressure gas is sent to the turbine. It is introduced and expanded.

Note that Figures 1 to 5 apply the open cycle, but if the gas discharged from the turbine 21 is cooled and sucked into the compressor again, a closed cycle can be applied. (However, the heating chamber must be of the type shown in Figure 4).

Furthermore, the present invention uses the power generated by the turbine 21 to drive the compressor.
It is also conceivable that the gas discharged from the turbine 21 be used to drive another turbine connected to the load.

Next, in the above heat engine, since the timing at which communication between the opening/closing port 10 and the communication port 12 starts, that is, the timing at which communication starts between the working chamber 8 and the inside of the fixed hollow body 9, is fixed, the heating chamber 18 (including heating chamber 24 - hereinafter referred to as heating chamber 18
When the pressure inside the heating chamber 18 decreases as the thermal energy given to the gas introduced into the chamber (represented by ) decreases (as the amount of fuel injected from the fuel injection valve 20 decreases), the As is clear from FIG. 6, which shows a P-V diagram, overcompression within the working chamber 8 causes a loss corresponding to the shaded area, and there is a problem that the thermal efficiency in the partial load range becomes slightly negative.

In order to eliminate this drawback, it is sufficient to make the communication start timing between the working chamber 8 and the inside of the fixed hollow body 9 variable.As shown in FIG. The opening/closing opening 10 and the control port 26 formed in the rotating body 25 are freely provided (in the figure, the rotating body 25 is provided in close contact with the inner peripheral surface of the fixed hollow body 9), and by rotating the rotating body 25, the opening/closing opening 10 and the control port 26 formed in the rotating body 25 are rotated. It is better to vary the start time of communication.

That is, when the amount of fuel injected from the fuel injection valve 20 decreases in the partial load region (the thermal energy given to the gas introduced into the heating chamber 18 decreases), the pressure inside the heating chamber 18 decreases. , the rotating body 25 is rotated to the illustrated position to advance the timing at which communication between the opening/closing port 10 and the control port 26 starts (by enlarging the communication port 12, the timing at which communication between the opening/closing port 10 and the control port 26 starts is advanced). (It is designed so that it can be obtained earlier than the one in Figure 2). Control is performed to bring forward the timing at which communication between the working chamber 8 and the interior of the fixed hollow body 9 begins.

Therefore, the gas fully sucked into the working chamber 8 is hermetically compressed by reducing the volume of the working chamber 8, and the almost fixed hollow body 9
Discharge is started when the pressure within the working chamber 8 becomes equal to that of the inside, and the PV diagram of the working chamber 8 can be drawn as shown in Fig. 8, and the shaded area shown in Fig. 6 It is possible to completely eliminate the corresponding loss and improve thermal efficiency in the partial load range.

The rotating body 25 is driven by a drive device such as a diaphragm device or a piston device that operates by sensing the pressure within the heating chamber 18, for example.

The rotating body 25 can also be provided in close contact with the outer peripheral surface of the fixed hollow body 9, and this is shown in FIG.

That is, in FIG. 9, the opening/closing opening 1 is rotated by rotating the rotating body 25 (of course, the rotating body 25 is inside the fixed hollow body 11) provided in close contact with the outer peripheral surface of the fixed hollow body 9.
0 and the control port 26 are changed to eliminate overcompression within the working chamber 8.

A close contact valve 27 is fixed to the rotating body 25 and is adapted to come into close contact with a portion of the blade 2 that is in close contact with the periphery of the rotating hollow body 11.

In the full load range, the opening/closing port 10 and the control port 26 are smaller than in the partial load range.
In this case, as shown in FIG. 10, the rotating body 25 is rotated by a predetermined angle in the counterclockwise direction. Immediately before the communication with the control port 26 is cut off, the close valve 27 prevents the high pressure gas in the fixed hollow body 9 from escaping to the low pressure side via the opening/closing port 10 and the control port 26 (if If there is no valve 27, opening/closing port 1
Immediately before the communication between the opening and closing port 26 is cut off, the high pressure gas in the fixed hollow body 9 escapes to the low pressure side. If the width is large, the close valve 27 is unnecessary).

Next, a method for improving thermal efficiency in the partial load range will be further described.

That is, in the thermal motors described in Figs. 1 to 10,
A method is adopted in which the output is controlled only by varying the amount of combustion injection injected from the fuel injection valve 20, but although this method is simple, the air overload rate becomes large in the partial load range, and the cycle peaks. There is a drawback that the temperature decreases and the thermal efficiency deteriorates significantly.

The output control method that can maintain high thermal efficiency in the partial load range is to change the amount of fuel injection and the flow rate of gas introduced into the heating chamber 18 to keep the maximum cycle temperature high at all times. will be explained with reference to FIG.

That is, FIG. 11 shows a compressor of a heat engine according to the present invention that achieves the above object (therefore, the heat engine according to the invention that achieves the above object replaces the compressors C1 and C2 in FIG. 1 with the compressor shown in FIG. 11). (represented by replacing machine),
A rotary body 25 is rotatably provided in the interior of the rotating hollow body 11 in close contact with each other so as to be rotatable. ) A communication valve 29 is provided in the communication passage 28 leading to the
30 (it may be provided with three communication valves, or conversely, it may be provided with only one).

At this time, the working chamber 8 communicates with the inside of the fixed hollow body 9 from the intermediate volume state to the minimum volume state through the communication port 12, the opening/closing port 10, and the control port 26 formed in the rotating body 25.
By rotating 5, the timing at which communication between the opening/closing port 10 and the control port 26 starts can be changed, thereby changing the timing at which communication between the working chamber 8 and the inside of the fixed hollow body 9 starts.

By opening the communication valve 29, the working chamber 8 changes from the maximum volume state to the predetermined volume state on the suction side of the compressor (inside the suction passage 14).
By opening and closing the communication valve 29, the communication cutoff timing between the working chamber 8 and the suction side of the compressor can be changed (the same applies to the communication valve 30).

Now, when the amount of fuel injected from the fuel injection valve 20 decreases in the partial load region, the communication valve 29 is opened and the rotating body 25 is rotated to the illustrated position to start communication between the opening/closing port 10 and the control port 26. Control is performed to delay the timing of communication between the working chamber 8 and the inside of the fixed hollow body 9.

Therefore, the gas fully sucked into the working chamber 8 is transferred to the communication path 2.
8, a predetermined amount of gas is returned to the suction side of the compressor, and after the communication between the working chamber 8 and the suction side of the compressor is cut off, the gas in the working chamber 8 is hermetically sealed due to the volume reduction. compressed,
When the pressure in the fixed hollow body 9 becomes almost equal to that in the fixed hollow body 9, the air is discharged into the fixed hollow body 9 through the communication port 12, the opening/closing port 10, and the control port 26. In other words, the PV diagram of the working chamber 8 is As shown in FIG. 12 (solid line), the capacity of the compressor is thus controlled (reduced) and the flow rate of gas introduced into the heating chamber 18 is reduced.

In this case, since the flow rate of the gas introduced into the heating chamber 18 is decreasing, the turbine 21 side (see Fig. 1) also uses the nozzle shut-off method (the nozzle 22 is divided into several sets and installed in each set). This is a method of sequentially opening and closing valves to prevent a decrease in the flow velocity of gas passing through the nozzle 22, which is already in practical use in steam turbines, etc.) or a method of making the nozzle 22 a variable node.
It is desirable to improve the efficiency on the turbine 22 side.

When the fuel injection amount further decreases and shifts to a low load range, the communication valve 30 is also opened to control (reduce) the capacity of the compressor, and the rotating body 25 is further rotated to close the opening/closing port 10. By delaying the start of communication with the control port 26, the P-V of the working chamber 8 is
Control is performed so that the line diagram is drawn as shown at the end of the two points (■■) in Figure 12.

In this way, the capacity of the compressor is controlled (reduced) in accordance with the decrease in the amount of fuel injected from the fuel injection valve 20, and the flow rate of the gas flowing inside the heating chamber 18 can be reduced. The excess rate is always kept reasonable (almost the same as at full load) and the maximum cycle temperature is always kept high (the maximum cycle temperature is approximately the same as at full load - the maximum cycle pressure is also kept at full load). This makes it possible to maintain almost the same value as when under load), and it is possible to significantly improve thermal efficiency in the partial load range.

Needless to say, the communication valves 29 and 30 are fully closed during full load.

If the center angle of the opening of the communication passage 28 that opens into the inner peripheral surface of the rotor casing is the center angle of the male rotor outer peripheral part 3 of the blade 2, then the communication passage 28 is configured as follows.
The opening on the inner peripheral surface of the rotor casing of the blade 2
When passing, the working chambers will not be in communication with each other.

In Fig. 11, the communication cutoff timing between the working chamber 8 and the suction side of the compressor is changed in stages by sequentially opening and closing the communication valves 29 and 30, but in an embodiment in which the timing is changed continuously. An example is shown in FIG.

That is, FIG. 13 shows a thermal motor according to the present invention that achieves the above object, and is a sectional view taken along line B-B' of the first stage compressor C1, and C
-C' line cross-sectional views are shown in FIGS. 14 and 15, respectively (the second-stage compressor C2 is configured similarly to the first-stage compressor), and the inside of the rotating hollow body 11 is separated by the separating wall 37. (
The inside of the fixed hollow body 9 is connected to the suction side (through the high pressure space H which leads to the discharge side), the square 8 formed in the fixed hollow body 9, and the passage 39.
It is divided into a low-pressure space L that communicates with the suction passage 14 (inside the suction passage 14) (see also FIGS. 13, 14, and 15 below).

A rotary body 25 is rotatably provided in the rotating hollow pair 11 on the side of the high pressure space H (for example, provided in close contact with the inner circumferential surface of the fixed hollow body 9), and the high pressure space The timing at which communication starts between the opening/closing port 10 formed in the fixed hollow body 9 on the H side and the control port 26 formed in the rotating body 25, that is, the timing at which communication starts between the working chamber 8 and the inside of the high pressure space H is changed. .

12 is a communication port formed in the rotating hollow pair 11 on the high pressure space H side.

On the other hand, a low-pressure rotating body 32 is rotatably provided in the rotating hollow pair 11 on the low-pressure space L side (in the figure, it is provided in close contact with the outer circumferential surface of the fixed hollow body 9).
From the maximum volume state to the predetermined volume state, the low pressure communication port 31 formed in the rotating hollow pair 11 on the low pressure space L side, the low pressure control port 33 formed on the low pressure rotating body 32, and the fixed hollow body 9 on the low pressure space L side It communicates with the low pressure space L through the low pressure opening/closing port 34 formed in the low pressure opening/closing port 34, and by rotating the low pressure rotating shaft 32, it is possible to determine when to cut off the communication between the low pressure opening/closing port 34 and the low pressure control port 33, that is, to operate the low pressure opening/closing port 34. The timing of communication interruption between the chamber 8 and the low pressure space L is changed.

Therefore, when the fuel injection amount decreases in the partial load region, the low pressure rotating pair 32 is rotated to delay the timing of disconnecting the communication between the low pressure opening/closing port 34 and the low pressure control port 33. is returned to the suction side by a predetermined amount) to control (reduce) the capacity of the compressor, and also rotates the rotating body 25 to delay the start of communication between the opening/closing port 10 and the control port 26, thereby reducing the P of the working chamber 8. - Control is performed so that the V diagram is drawn as shown in Fig. 12, and by rotating the low-pressure rotating body 32, the timing of cutting off communication between the working chamber 8 and the suction side is continuously varied. .

In this way, thermal efficiency in the partial load range can be significantly improved.

Although the communication valve 36 is not particularly essential, the working chamber 8 is connected to the low pressure communication port 31, the hand pressure opening/closing port 34, and the low pressure control port 3.
3, the communication valve 36 is opened so that the working chamber 8 also communicates with the suction passage 14 via the communication valve 35, which serves to expand the communication cross-sectional area. It is something that will be fulfilled.

This produces the effect of reducing the axial length of the low-pressure communication port 31 and increasing the cross-sectional area of the communication port 12.

When the blade 2 passes through the opening of the connecting path 35 that opens on the inner circumferential surface of the rotor casing, the low-pressure rotating body 32 is in a control position such that communication between the low-pressure opening/closing port 34 and the low-pressure control port 33 is already cut off. In this case, the communication valve 36 must be fully closed, so the switching point of the communication valve 36 (the point at which it switches from open to closed and from closed to open) is dependently determined by the control position of the low-pressure rotating body 32. It's going to happen.

In the full load range, the communication valve 36 is fully closed and the low pressure rotating body 32 is rotated to a position where the low pressure communication port 31, low pressure opening/closing port 34, and low pressure control port 33 do not communicate with each other at the same time. Needless to say.

Note that the low-pressure rotating body 32 is connected to the rotating body 2 via a cam or the like, for example.
It is configured to be linked to 5.

In addition, in FIG. 15, if the central angle of the part of the blade 2 that is in close contact with the periphery of the rotating hollow body 11 is the central angle of the low pressure communication port 31, then When communicating, the working chambers do not fall into communication with each other, but as the size of the low pressure communication port 31 is limited by the width of the blade 2, the control range of the low pressure rotating body 32 is also limited. Become.

In order to expand the control range of the low pressure rotating body 32, a new low pressure communication port 31' may be newly provided as shown in FIG.

When the low pressure communication port 31' is completely closed by the low pressure rotating body 32 as shown in the figure, the blade 2 closes the low pressure communication port 31'.
', 31, the working chambers do not come into communication with each other due to the partition wall 40.

Since the present invention is configured as described above, it is small, lightweight, and
It is possible to provide a thermal motor that has low vibration, low pollution, and can use inferior fuel, does not cause surging, is inexpensive, and has high thermal efficiency, especially in a partial load range.

[Brief explanation of the drawing]

Figures 1, 5, 7, 9, 10, 11, and 13 are cross-sectional views of the thermal motor according to the present invention, Figure 2 is a cross-sectional view taken along line A-A' in Figure 1, and Figures 3, 6, 8, and 12. is a PV diagram, Figure 4 is a diagram showing the heating chamber, Figures 14 and 15 are sectional views taken along lines B-B' and C-C' in Figure 13, respectively, and Figure 16 is a low-pressure connection. A diagram showing a plurality of mouths is shown. 1 is the male rotor, 2 is the blade, 3 is the outer circumference of the male rotor, 4
・4' is the blade support, 5 is the female rotor, 6 is the outer periphery of the female rotor, 7 is the recessed part, 8 is the working chamber, 9 is the fixed hollow body, 1
0 is an opening/closing port, 11 is a rotating hollow body, 12 is a communication port, 13 is a missing circular part, 14 is a suction passage, 15 is a synchronous gear, 16 is a cooler, 17 is a heat exchanger, 18 and 24 are heating chambers, 19 is a spark plug, 20 is a fuel injection valve, 21 is a turbine, 22 is a nozzle, 23 is a turbine blade, 25 is a rotating body, 26 is a control port,
27 is a sealing piece, 28 is a communication passage, 29 and 30 are communication valves, 3
1 is a low pressure communication port, 31' is also a low pressure communication port, 32 is a low pressure rotating body, 33 is a low pressure control port, 34 is a low pressure communication port, 35 is a communication path, 36 is a communication valve, 37 is a separation wall, 38 is a hole, 39 is a passage, 40 is a partition, H is a high pressure space, L is a low pressure space, C1.
C2 indicates the first and second stage compressors, respectively.

Claims (4)

[Claims] (1) A male rotor equipped with blades that rotate integrally with the rotary hollow body while closely surrounding the fixed hollow body that is fixed to the outside of the rotary hollow body, and a male rotor that is provided with blades that rotate integrally with the rotary hollow body, and closely attached to the inner circumferential surface of the rotor casing. and a female rotor having a recessed part into which the blades of the male rotor fit while recessed from the outer peripheral part of the female rotor rotate in opposite directions synchronously in a non-contact state, and The compressor is configured such that the outer circumference of the rotor is in close contact with the fixed hollow body. Either the line of the cross section of the blade side surface on the back side of the blade side surface of the same blade created by the part on the tip side of the wall surface, or the line of the cross section of the wall surface on the lagging side forming the same depression. One line is constructed so that it mutually creates at least a relatively large portion of the other line, and furthermore, focusing on the working chamber sandwiched between the blades of the male rotor and the female rotor, The working chamber communicates with the rotating hollow body from the volume state to the minimum volume state through the communication port formed in the fixed hollow body and the opening/closing port formed in the rotating hollow body, and is configured as described above. a compressor connected to a turbine, gas from a rotating hollow body compressed in a working chamber of the compressor is introduced into a heating chamber, and further gas given thermal energy in the heating chamber is introduced into the turbine. A thermal motor that is characterized by being made to expand. (2) A male rotor provided with blades that rotates integrally with the rotating hollow body while closely surrounding the fixed hollow body that is fixed to the outside of the rotating hollow body, and a male rotor that is closely attached to the inner peripheral surface of the rotor casing. and a female rotor having a recessed part into which the blades of the male rotor fit while recessed from the outer peripheral part of the female rotor rotate in opposite directions synchronously in a non-contact state, and The compressor is configured such that the outer circumference of the rotor is brought into close contact with the fixed hollow body, and a rotating body is rotatably provided inside the fixed hollow body, and the rotating body should fit into the same depression as the female rotor. Focusing on the blade of the male rotor, form the same depression with the line of the cross section of the blade side surface on the back side of the blade side surface of the same blade, which is created by the part on the tip side of the advancing side wall that forms the same depression. Within the line of the cross section of the wall on the lagging side,
It is constructed such that one of the lines is mutually generated by at least a relatively large portion of the other line, and further, focusing on the working chamber sandwiched between the blades of the male rotor and the female rotor, the working chamber The operating chamber is connected to the rotating hollow body from the intermediate volume state to the minimum volume state through the communication port formed in the fixed hollow body, the opening/closing port formed in the rotating hollow body, and the control port formed in the rotating body. The compressor configured as described above is connected to the turbine so as to communicate with the body, and the gas from the rotating hollow body compressed in the working chamber of the compressor is introduced into the heating chamber, and further the heat is generated in the heating chamber. In the thermal motor, in which energized gas is introduced into the turbine and expanded, the timing at which communication between the opening/closing port and the control port starts can be varied by rotating the rotating body. A thermal engine characterized by (3) A male rotor provided with blades that rotates integrally with the rotary hollow body while closely surrounding the fixed hollow body provided so as to be fixed to the outside of the rotary hollow body, and a male rotor that is provided with blades that rotate integrally with the rotary hollow body and close to the inner circumferential surface of the rotor casing. and a female rotor having a recessed part into which the blades of the male rotor fit while recessed from the outer peripheral part of the female rotor rotate in opposite directions synchronously in a non-contact state, and The compressor is configured such that the outer circumference of the rotor is brought into close contact with the fixed hollow body, and a rotating body is rotatably provided inside the fixed hollow body, and the rotating body should fit into the same depression as the female rotor. Focusing on the blade of the male rotor, form the same depression with the line of the cross section of the blade side surface on the back side of the blade side surface of the same blade, which is created by the part on the tip side of the advancing side wall that forms the same depression. Within the line of the cross section of the wall on the lagging side,
It is constructed so that one of the lines is mutually generated by at least a relatively large portion of the other line, and further, focusing on the working chamber sandwiched between the blades of the male rotor and the female rotor, the working chamber The operating chamber is connected to the rotating hollow body from the intermediate volume state to the minimum volume state through the communication port formed in the fixed hollow body, the opening/closing port formed in the rotating hollow body, and the control port formed in the rotating body. The compressor configured as described above is connected to the turbine so as to communicate with the body, and the gas from the rotating hollow body compressed in the working chamber of the compressor is introduced into the heating chamber, and further heat is generated in the heating chamber. In a thermal motor that introduces energized gas into the turbine and expands it, by rotating the rotating body, the timing at which communication between the opening/closing port and the control port starts is varied, and the inside of the casing is The working chamber communicates with the suction side of the compressor from a maximum volume state to a predetermined volume state by opening a communication valve provided in a communication passage that opens in a wall surface and communicates with the suction side of the compressor, and A thermal engine characterized in that the communication cutoff timing between the working chamber and the suction side of the compressor can be varied by opening and closing a communication valve. (4) The thermal motor according to any one of claims 1 to 3, wherein the fixed hollow body is formed with a circular cutout portion in which the outer peripheral portion of the female rotor is in close contact.