JP5024750B2 - Rotary thermal fluid equipment - Google Patents

Description

  The present invention relates to a rotary engine as an external combustion engine and an internal combustion engine, and a rotary compressor.

The conventional rotary pumps and engines have a history of about 400 years, and the rotary piston type compressor originated from the Lamerie water pump devised in 1588 is still used as a compressor for air conditioners. (See Patent Document 1). In recent years, a compressor called a scroll type has become common. In the field of pumps, a screw type or a gear type in which two gears are combined is generally used as a fluid that can be driven directly from a rotational force. In the engine, the Wankel type rotary engine that appeared in the 1950s was installed in a passenger car and put into practical use, but a device for solving the problem that the vibration of the Wankel type is large has been devised (Patent Document 2, 3).
Grand Prix publication “History of the Mazda Rotary Engine” (Section 2-1) Japanese Patent Laid-Open No. 11-182201 (FIG. 2) Japanese Patent Laying-Open No. 2005-315205 (FIG. 1)

In the conventional rotary piston compressor as described above, the movable seal that partitions the compression region must always slide on the circumferential surface of the rotor housing. Further, even in a scroll compressor, it is necessary that the two scroll blades always slide relative to each other. For this reason both friction loss is likely to wear occur.
In addition, since the rotary engine using the three rotors of Patent Document 2 and Patent Document 3 that are operated in a perfect circle to suppress vibration due to eccentricity of the Wankel type rotary engine, the three rotors are connected by an external gear, It is necessary to make the alignment accurate so that the structure is complicated and the rotors do not collide with each other. However, even if the initial alignment is performed, there is a risk that the rotor may come into contact with play such as gear wear, and the rotor blade tips are likely to wear. In addition, the method of Patent Document 3 has a narrower blade root than the size of the tip of the blade, so there is an anxiety in strength due to the nature of the engine that repeatedly compresses and explodes. In the worst case, the blade breaks. There is a risk that
SUMMARY OF THE INVENTION An object of the present invention is to provide a rotary thermofluid device that is simple in structure, has low wear and is efficient and can be applied to both a compressor and an engine.

The rotary thermofluid device of the present invention is made to solve the above-described problems, and includes a rotor housing and a plurality of rotors housed in the rotor housing. In the shape of a gear having a plurality of teeth of the same shape at equal intervals, each tooth in the cross section perpendicular to the axis has a tooth tip portion of an arbitrary shape and one tooth surface connected to the tooth tip portion is a convex surface portion, and the other The tooth surface of the rotor is composed of a concave part, the convex part is the shape of an involute curve, and the concave part is engaged with this rotor when the rotor rotates at a constant speed, and the tooth tip of the other rotor that rotates backward at a constant speed Department has a shape formed when cutting out, facing the rotor is in contact is convex portions and the rotation luck tooth tip of one of the rotor simultaneously in contact with the concave portion of the other rotor Arranged such that the, the sealed region in the tooth bottom and the rotor housing of the teeth of one of the convex surface of the tooth and the other rotor of the rotor are formed, each tooth with the rotation of the rotor fitted into the fitting portion between the rotor The sealed region is continuously generated each time the operation is performed.

  Moreover, it is set as the structure which provided the notch in either the concave surface part or convex surface part of the tooth | gear of the said rotor.

  Further, concentric corrugation treatment is performed on the end surface of the rotor body and the end surface of the rotor housing facing the rotor.

  Moreover, the corrugation process which fits with the rotor which faced it to the involute curve convex part of the rotor was performed.

The rotary thermal fluid device of the present invention comprises a rotor housing and a plurality of rotors housed therein, and each rotor has a gear shape having a plurality of teeth of the same shape at equal intervals , and is perpendicular to the axis. Each tooth in the cross section consists of a tooth tip of an arbitrary shape, one tooth surface connected to the tooth tip is a convex surface portion, and the other tooth surface is a concave surface portion, the convex surface portion is an involute curve shape, concave surface The part is shaped so that when the rotor rotates at a constant speed, the tip of the tooth of the other rotor that engages with this rotor and reversely rotates at a constant speed is cut out. contacts, tooth tip of one of the rotor simultaneously arranged to the rotational movement against the concave portion of the other rotor, and convex portion of the tooth of one rotor fitting portion between the rotor Square of forming a sealed region in the tooth bottom and the rotor housing of the teeth of the rotor, each tooth with the rotation of the rotor was made to generate a continuously its closed area each time the fitting, when used as a rotary compressor, the rotor High compression and suction are possible only by rotating the shaft, and the frictional loss can be reduced because the sliding portion is small.

Further, the rotary type thermal fluid device having this structure has a round motion and little vibration, and when used as a rotary engine, it is highly efficient because the expansion energy of the gas can be directly converted into the rotational energy of the rotor. Since there are no gears on the outside, the structure is simple, and it is not necessary to accurately align the position of the rotor, making assembly easy, and there are no weak parts in terms of mechanical strength.
The rotary compressor that rotates with the pressure difference is the same structure as the rotary compressor, and since it is simple in structure, it can be manufactured in both large and ultra-small sizes, and two units can be connected to transmit one rotary operation to the other. It is also possible to change the number of rotations by changing the size of the two units.

  It can be used for both external combustion engines and internal combustion engines, and its operating characteristics can be changed by providing notches in the teeth.

  Further, in the rotary engine having this structure, the internal gas pressure leakage is suppressed by corrugation, and the loss can be suppressed.

Embodiment 1 FIG.
FIG. 1 is a sectional view of a rotary compressor according to the present invention. In the figure, reference numeral 10 denotes a rotor housing, and the first rotor 20 and the second rotor 30 are closely attached to the rotor housing 10 so as to be rotatable by the respective rotor shafts 2a and 3a. Reference numeral 2 denotes one tooth of the first rotor 20, and a plurality of teeth are formed around the rotor body 2b. The tooth 2 includes a tooth tip portion 2c, a concave surface portion 2d, and a convex surface portion 2e. Similarly, a plurality of teeth 3 of the second rotor are formed around the rotor body 3b, and are composed of a tooth tip portion 3c, a concave surface portion 3d, and a convex surface portion 3e. An intake port 11 and an exhaust port 12 are provided on the left and right sides of the central portion of the rotor housing 10. In the case of a rotary compressor, the second rotor 30 serves as a driving rotor and is driven by rotating the rotor shaft 3a counterclockwise. The first rotor 20 is rotated with the second rotor 30 by the rotation of the second rotor 30. A subordinate rotor that rotates in the opposite direction at the same speed.

FIG. 2 is an explanatory view showing the shape of the teeth of the rotor of the present invention. In the figure, 2c is the tip of the tooth 2 of the rotor 20, and its shape is circular. 2d is a concave portion of the rotor tooth 2 and smoothly connects to the tip 2c. When the other second rotor 30 rotates in the opposite direction at the same speed as the first rotor 20, the second rotor 30 The tip 3c of the tooth 3 is formed in a concave shape formed when the first rotor 20 is cut out, and the tooth tip 3c is an outer locus drawn on the rotor 20. Reference numeral 2e denotes a convex surface portion of the teeth of the rotor 2, which is in smooth contact with the concave surface portion 2d and the adjacent tip portion 2c ', and is formed in the same involute curve as a normal gear. It is known that the normal line of the involute curve is all directed toward the involute reference circle 2k, and the gear using the involute curve rotates at a constant speed. The first rotor 20 and the second rotor 30 have the same shape, and the same shape is used in the following description. However, the diameter of the rotor, the number of teeth, and the shape of the tooth tip may be different. Absent. For example, number M of the teeth of the first rotor 20, when the number of teeth of the second rotor 30 is N, when the first rotor 20 is the angle theta ₂ rotates, the rotation angle of the second rotor 30 May be obtained as θ ₃ = θ ₂ × M / N. The tooth tip portions 2c and 3c are basically substantially circular in shape, but may have a shape in which a seal or the like is added to the tooth tip portion in order to improve sealing between the rotors and between the rotor and the rotor housing. In particular, the shape is not specified.
By setting it as the above shapes, the 1st rotor 20 and the 2nd rotor 30 can perform the constant speed rotation without the speed fluctuation | variation by the angular velocity according to each number of teeth in the mutually opposite direction. The reason why the convex portion of the rotor teeth is an involute curve will be clarified in the explanation of the operation of the rotary engine described later.

Next, the operation of this rotary compressor will be described with reference to FIGS.
In FIG. 1, the first rotor 20 and the second rotor 30 are in contact with each other at two locations a and b. When the second rotor 30 is rotated counterclockwise, the first rotor is passed through an involute curve. 20 also rotates at the same speed. At this time, the area of the region V between the contact points a and b of the rotor increases, and gas is sucked into the rotor housing from the outside through the intake port 11. The sucked gas reaches the upper part of the rotor housing 10 through the outside of the rotor in accordance with the rotation of the rotor.

  Next, in the state of FIG. 3A, there are three contact points a, b, and c of the first rotor 20 and the second rotor 30, and gas is supplied to a region U between the contact points b and c of the rotor. Be trapped. As the rotor advances, the contacts b and c approach each other as shown in FIG. 3B, and the region U gradually becomes narrower. Next, in FIG. 3C, the contacts b and c become one point and the region U disappears. This indicates that high compression is possible. The compressed gas is discharged from the exhaust port 12 to the outside. The part that needs to be sealed for the compression operation of the region U is only the part of the region S indicated by the alternate long and short dash line in FIG. 3 (A) and the rotor shafts 2a and 3a. , Rotor friction can be minimized.

Embodiment 2. FIG.
FIG. 4 is a perspective view of a rotor in the rotary compressor of the second embodiment. The rotor housing is the same as that of the first embodiment. In FIG. 4, the first rotor 21 and the second rotor 31 are “helical gear” rotors in which the rotors 20 and 30 of FIG. 1 are twisted in the opposite directions in the axial direction so as to be in close contact with each other. It is. Therefore, the cross-sectional view perpendicular to the axis of the rotor of FIG. 4 is the same as that of FIG. 10 'shows the outline of the inner surface of the rotor housing. In FIG. 4, the intake port 11 is attached to the back side surface of the rotor housing, and the exhaust port 12 is attached to the front side surface. By twisting the rotor, the gas moves in the axial direction in accordance with the rotation of the rotor. Intake and exhaust become smooth.

Embodiment 3 FIG.
The rotary compressor shown in FIGS. 1 and 4 can rotate the rotor when a gas pressure difference is given to the intake port 11 and the exhaust port 12, and becomes a rotary engine that obtains a rotational force by the pressure difference. For example, in FIG. 1, when high pressure gas is injected from the outside through the intake port 11 and exhausted from the exhaust port 12, the first rotor 20 rotates clockwise and the second rotor 30 rotates counterclockwise, and the rotation output Is obtained from the shaft 2a of the first rotor. In this case, the vicinity of the intake date 11 and the exhaust port 12 needs to be improved in order to reduce loss due to pressure leakage. The details will be described in the following rotational operation due to a temperature difference.

Embodiment 4 FIG.
FIG. 5 is a block diagram of a remote control system combining a rotary compressor and a rotary engine according to the present invention. Reference numeral 100 in the figure denotes a rotary compressor, which is the same as that in FIG. 1, and the same reference numerals denote the same parts in the figure. Reference numeral 400 denotes a rotary engine drive unit that rotates by a pressure difference, 40 is a rotor housing, 50 is a first rotor, 5a is a shaft of the rotor, 60 is a second rotor, 41 is an intake port, and 42 is an exhaust port. The shape is the same as that of the rotary compressor 100. The exhaust port 12 of the rotary compressor 100 and the intake port 41 of the rotary engine drive unit 400, and the exhaust port 42 of the rotary engine drive unit 400 and the intake port 11 of the rotary compressor 100 are connected by connecting pipes 71 and 72, respectively.

When the drive shaft 3a of the rotary compressor is rotated counterclockwise, the gas moves from the exhaust port 12 to the intake port 41 of the rotary engine drive unit and from the exhaust port 42 of the rotary engine drive unit to the intake port 11 of the rotary compressor. The output shaft 5a of the rotary engine drive unit can be rotated in accordance with the rotation of the drive shaft 3a of the rotary compressor, and the connecting pipes 71 and 72 are extended so that the rotational force of the rotary compressor 100 is increased. Remote control to transmit to 400 is possible.
Since the rotary thermal fluid device of the present invention has a simple structure, it can be manufactured in both large and ultra-small sizes, and the number of rotations can be changed by changing the size of the rotary compressor 100 and the rotary engine drive unit 400. .

Embodiment 5 FIG.
The fifth embodiment is a rotary engine using a temperature difference. First, the rotational force generating mechanism of the rotary engine of the present invention will be described with reference to FIG.
In FIG. 6, reference numeral 43 denotes a rotor housing, which does not have an intake port and an exhaust port. Instead, a superheater 81 and a cooler 82 are attached, and a temperature difference is given up and down with respect to the gas confined in the rotor housing. The first rotor 50 and the second rotor 60 are the same as those in the fourth embodiment. When the lower part of the rotor housing 43 is heated and the upper part is cooled as shown in this figure, the gas expands in the space P between the heater 81 and the rotors 50 and 60, and the space between the cooler 82 and the rotors 50 and 60. In the Q portion, the gas contracts and pushes the teeth of the rotors 50 and 60. The force that pushes the teeth is applied to the left side (outside) of the first rotor 50, the right side (outside) of the second rotor 60, and the central portion where the teeth between the two rotors overlap. The two directions on the left and right outer sides and the central portion are opposite in the direction of rotating the rotor, but the total force is approximately 2: 1. Therefore, the first rotor 50 is clockwise and the second rotor 60 is counterclockwise. Rotate around.

Explain in detail how force is applied.
For convenience of explanation, first, consider the case where there is no inflow of air from the upper part to the lower part through the central part between the rotors.
When the portion P at the lower part of the rotor on the heating expansion side is viewed, in the state shown in FIG. 6A, the second rotor 60 is balanced by the counterclockwise rotation force A and the clockwise rotation force B. However, since the second rotor 60 blocks the force applied to the central portion of the first rotor 50, only the force C rotating in the clockwise direction is applied, and the first rotor 50 tries to rotate in the clockwise direction. This force is transmitted as it is to the shaft 5a of the first rotor, which is the main shaft. Since the tip a portion of the first rotor tooth is in contact with the second rotor 60, the second rotor 60 also rotates counterclockwise. At this time, if a load is not taken out from the shaft 6a of the second rotor 60, a large force is not applied to the tip a portion of the first rotor tooth.

In FIG. 6B, which is in a slightly rotated state, the first rotor 50 rotates counterclockwise by generating a force D that rotates counterclockwise as the expanded air hits the center portion. It becomes balanced with the force C and the rotational force is lost. However, since the second rotor 60 generates a force E that rotates counterclockwise, the second rotor 60 rotates counterclockwise, and the combined force F of the forces A, B, and E acting on the second rotor 60 is a tooth contact. It is transmitted to the shaft 5a of the first rotor via part b. Since the convex shape of each tooth is the same involute curve as that of the gear, the rotational force of F can be directly transmitted to the shaft 5a of the first rotor at any position. This is the first reason for using an involute curve for the convex portion.
When the rotor further rotates, a rotational force G is generated in the first rotor 50 as shown in FIG. 6C, and thus the clockwise rotation is continued. On the way, only in the position of FIG. 6D, the clockwise and counterclockwise rotational forces of the respective rotors balance on the heating expansion side, and the rotational force disappears. However, the rotor cooling and the upper cooling on the opposite side are eliminated. The rotation is continued by the rotational force due to the contraction force of the gas at the side Q portion.

The gas heated in the lower part passes through the outside of the rotors 50 and 60 and is cooled and contracts. If the cooled gas is sent to the lower part through the central portion in accordance with the rotation of the rotor, it can be heated and expanded again, and continuous rotation can be performed. However, if the rotor shape of FIG. is there. This is because, as explained in the rotary compressor of the first embodiment, a strong compression operation is generated at the U portion in the center of FIG. 6 (D). is there.
This problem does not occur when a pressure difference is applied from the outside through the intake and exhaust ports.

  When rotating at a temperature difference, in order to avoid this problem, the rotor is deformed as shown in FIG. In the figure, 51 is the first rotor, 61 is the second rotor, and 43 'is the contour of the inner surface of the rotor housing. Each of the first rotor 51 and the second rotor 61 has the tooth shape described in FIG. 2 and has gear portions 51g and 61g that maintain accurate rotation of the left and right rotors, and a tooth convex surface portion is cut away. It consists of blade portions 51f and 61f. The blade portions 51f and 61f form an air passage between the U and V regions in FIG.

The operation in the rotor shape of FIG. 7 will be described with reference to the cross-sectional views of FIGS. In FIG. 8, the same components as those in FIG. The first rotor 51 and the second rotor 61 are the rotors of FIG. 7, and the rotor thin lines represent the shapes of the gear portions 51g and 61g, and the rotor thick lines represent the shapes of the blade portions 51f and 61f. Yes.
In FIG. 8A, when the tip portions of the blades of the first rotor 51 and the second rotor 61 are in contact at the point c, the cooled gas at the top is taken in between the blade portions 51f and 61f (W portion). . As shown in FIG. 8B → FIG. 8C, the gas in the W portion can move to the lower portion with almost no compression except for the gear portion. In FIG. 8C, the gas is also taken in between the concave portions of the blade (Z portion) and moved to the lower part when it moves as shown in FIG. 8D. The mechanism by which the rotational force is generated by the expanded gas is the same as described above.

  However, as shown in FIGS. 8A to 8D, the method of providing a notch in the convex portion is used when the gas pressure on the heating side is relatively low. This is because when the gas pressure on the heating side is very high, when the region W is opened to the high temperature side in FIG. 8C, the high temperature side gas flows back to the region W and a smooth rotational force cannot be obtained. .

Embodiment 6 FIG.
When the heating side is very hot and the gas pressure is high and high efficiency is required, the engine is divided into a low temperature side and a high temperature side as shown in FIG. In FIG. 9, the high temperature side includes a rotor housing 44, a first rotor 50 and a second rotor 60 housed therein, and a heater 81 attached to the rotor housing 44. A port 45 and an exhaust port 46 are provided. Similarly, the low temperature side includes a rotor housing 47, a first rotor 52 and a second rotor 62 housed in the rotor housing 47, and a cooler 82 attached to the rotor housing 47. And an exhaust port 49 is provided. The first rotor 50 on the high temperature side and the first rotor 52 on the low temperature side are connected by the rotating shaft 5a, and this is the final output shaft. Further, the exhaust port 46 on the high temperature side is connected to the heat exchanger 83 via a connection pipe 75, and the outlet of the radiated gas is connected to the intake port 48 on the low temperature side via a connection pipe 76. On the contrary, the low temperature side exhaust port 49 is connected to the heat exchanger 83 by a connection pipe 73, and the outlet of the absorbed gas is connected to the high temperature side intake port 45 by a connection pipe 74. 84 is an auxiliary cooler when the cooling is insufficient. Reference numeral 85 denotes an auxiliary superheater when heating is insufficient.

The operation in this case is as follows.
The contraction force is applied to the gas in the upper Q portion (directly under the cooler) in the rotor housing 47 where the gas temperature is the lowest in this system, and the rotor rotates in the direction of the arrow in the figure. Therefore, the cooled gas is discharged from the exhaust port 49 to the heat exchanger 83 through the connection pipe 73. The cooling gas absorbs heat by the heat exchanger 83, and when there is an auxiliary heater 85, the cooling gas is heated by the auxiliary heater 85, sent to the high-temperature side inlet 45, and further heated and expanded by the heater 81. The expanded gas rotates the rotors 50 and 60 in the direction of the arrow. The gas that has gone around the rotor is discharged from the exhaust port 46, passes through the connection pipe 75, and dissipates heat in the heat exchanger 83, and if there is an auxiliary cooler 84, is cooled by the auxiliary cooler 84 to the low temperature side intake port 48. Sucked.

  The auxiliary cooler 84 and the auxiliary heater 85 are actively used so that the low temperature side exhaust port 49 and the high temperature side intake port 45 do not open at the same time, and the high temperature side exhaust port 46 and the low temperature side intake port 48. If the rotor position is shifted so that they do not open at the same time, a rotary Stirling engine is obtained. In this case, the cooling gas discharged from the low temperature side exhaust port 49 is absorbed by the heat exchanger 83 through the connection pipe 73, heated by the auxiliary heater 85, and temporarily accumulated in the connection pipe 74. . When the rotor on the high temperature side rotates and the intake port 45 opens, the heated gas expands at the P portion in the rotor housing, and the rotational force of the rotor is obtained. The gas used for rotation passes through the connection pipe 75 from the exhaust port 46, dissipates heat in the heat exchanger 83, is cooled by the auxiliary cooler 84, and is temporarily accumulated in the connection pipe 76, so that the low temperature side intake port 48 is opened. And is taken into the rotor housing 47 on the low temperature side. By using the inertia of the rotor and continuing the above operation, rotational force can be obtained. The rotor on the low temperature side serves as a displacer that sends the cooling gas to the rotor on the high temperature side by this rotational force.

Embodiment 7 FIG.
FIG. 10 is a sectional view of a rotary engine as an internal combustion engine showing Embodiment 7 of the present invention. This figure has substantially the same configuration as that of the fourth embodiment (FIG. 5). In the figure, the same components as those of the fourth embodiment are denoted by the same reference numerals and the description thereof is omitted. In FIG. 10, reference numeral 400 denotes a rotary engine drive unit, and 110 denotes a rotary compressor that operates with the rotational force of the rotary engine drive unit 400. Compared with the rotary compressor 100 of FIG. 5, the rotary compressor 110 is reversed left and right, and the shaft of the drive rotor 30 of the rotary compressor 110 is connected to the output shaft 5 a of the rotary engine drive unit 400.

Next, the operation of the internal combustion engine will be described.
The mixed gas is sucked in from the intake port 11 of the rotary compressor 110 and goes around the rotors 20 and 30 and is compressed in the U portion. The compressed mixed gas is injected from the exhaust port 12 through the connection pipe 71 to the intake port 41 (V portion) of the rotary engine drive unit 400. When the second rotor 60 closes the intake port 41, ignition and explosion occur at the V portion. Let At this time, since the clockwise rotational force 1 and the counterclockwise rotational force J almost antagonize with the second rotor 60, only a slight counterclockwise rotational force is generated, and the explosion force is almost the first. Served to push out the teeth of the rotor 50. In the first rotor 50, this explosive force is almost applied to the convex portion of the tooth, but since the convex portion is an involute curve, all the forces H applied to the convex portion are directed to the involute reference circle where the normal line is in contact, and the rotor 50 efficiently Is converted into clockwise rotation energy. This is the second reason for using involute curves.
The exhaust gas goes around the rotor and is discharged from the exhaust port 42 of the rotary engine drive unit.

Embodiment 8 FIG.
FIG. 11 is an explanatory diagram of countermeasures against pressure leakage of the rotary engine of the present invention, and FIG. 12 is a cross-sectional view taken along the line AA ′ of FIG. In both figures, 40 is a rotor housing, 5 and 6 are teeth of a first rotor and a second rotor, respectively, 5b and 6b are body parts of the first rotor and the second rotor, and 91 is a first body. And corrugation generated concentrically on the end face of the second rotor body, 92 is the corrugation on the rotor housing side to be fitted into the corrugation 91 of the rotor, and 93 is the convex portion of the first rotor tooth and the second rotor tooth. This is a corrugation that is applied to the convex surface part and fits each other.
FIG. 13 is a diagram showing the necessity of corrugation. In the rotor housing 40, there are a high pressure portion due to combustion and a low pressure portion after expansion. If there is a gap between the rotor housing and the rotor, high-pressure gas leaks through the gap as shown in this figure.
Among these, the corrugations 91 and 92 shown in FIG. 11 have a greater resistance to the gas leakage in the body portion at the center of the rotor as the pressure increases in the radial direction, and do not affect the direction of the rotation axis.
Further, gas leakage from the boundary surface of the convex portion of the rotor tooth is prevented by corrugation 93 in FIG.
For leakage between the teeth of the rotor and the case, a sealing part such as a seal used in the compressor may be attached to the tip of the tooth.

  It is sectional drawing of the rotary type thermal fluid apparatus which shows Embodiment 1 of this invention.   It is explanatory drawing which shows the tooth | gear shape of the rotor of this invention.   It is operation | movement explanatory drawing of the rotary compressor of Embodiment 1 of this invention.   It is a perspective view of the rotor which shows Embodiment 2 of this invention.   It is a block diagram of the remote control system of Embodiment 4 of this invention.   It is explanatory drawing of the rotational force generation mechanism of the rotary engine which operate | moves with the temperature difference of Embodiment 5 of this invention.   It is a perspective view of the rotor of the rotary engine of Embodiment 5 of this invention.   It is rotary engine operation explanatory drawing of Embodiment 5 of this invention.   It is rotary engine operation explanatory drawing of Embodiment 6 of this invention.   It is rotary engine operation explanatory drawing of Embodiment 7 of this invention.   It is explanatory drawing of the pressure leak countermeasure of the rotary engine of Embodiment 8 of this invention.   FIG. 12 is a cross-sectional view of the rotary engine taken along line A-A ′ of FIG. 11.   It is explanatory drawing of the pressure leak of a rotary engine.

Explanation of symbols

10, 40, 43, 44, 47 Rotor housing,
20, 21, 50, 51, 52 First rotor,
30, 31, 60, 61, 62 second rotor,
2a, 3a, 5a rotor shaft, 2b, 3b, 5b, 6b rotor body,
2,3,5,6 teeth, 2c, 3c tooth tips,
2d, 3d concave surface portion, 2e, 3e convex surface portion 11, 41, 45, 48 intake port, 12, 42, 46, 49 exhaust port,
71, 72, 73, 74, 75, 76 connecting pipe,
DESCRIPTION OF SYMBOLS 81 Heater, 82 Cooler 83 Heat exchanger, 84 Auxiliary cooler, 85 Auxiliary heater 91, 92, 93 Corrugation 100, 110 Rotary compressor, 400 Rotary engine drive part

Claims (4)

In a rotary thermal fluid apparatus having a rotor housing and a plurality of rotors housed in the rotor housing,
Each of the plurality of rotors has a gear shape having a plurality of teeth having the same shape at equal intervals, and each tooth has a tooth tip portion having an arbitrary shape and one tooth surface connected to the tooth tip portion in a cross section perpendicular to the shaft. There a convex portion, and the other tooth surface becomes asymmetric shape composed of the concave portion, the convex portion has a shape of involute curve, the concave portion in the rotor when the rotor is rotated at a constant speed It has a shape that can be formed when the tooth tip of the other rotor that engages and reversely rotates at a constant speed is notched, and the opposite rotors are in contact with each other, and at the same time the tooth tip of one rotor is arranged to the rotational movement against the concave portion of the other rotor, form an enclosed area in the tooth bottom and the rotor housing of the teeth of one tooth of the convex portion and the other rotor rotor fitting portion between the rotor And, a rotary type heat fluid device, characterized in that each tooth with the rotation of the rotor to generate a continuously its closed area each time the fitting.   2. The rotary thermofluid device according to claim 1, wherein a notch is provided in either the concave surface portion or the convex surface portion of the teeth of the rotor.   3. The rotary thermofluid device according to claim 1, wherein concentric corrugation treatment is applied to the end surface of the body portion of the rotor and the end surface of the rotor housing opposed to the end surface.   The rotary thermofluid device according to any one of claims 1 to 3, wherein a corrugation process is performed on a convex portion of the involute curve of the rotor so as to engage with a rotor facing the rotor.

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