JPH0481502A - Turbine and turbocharger using it - Google Patents

Abstract

PURPOSE:To reduce a cost of a turbine through increasing its turning torque and simplifying its structure by providing a rotor supported rotatably in a casing, many blades mounted protrusively on an outer periphery of this rotor with an appropriate interval, and a flow passage formed on the circumference of the outer periphery of the above-mentioned rotor so as to adjoin the blades. CONSTITUTION:A turbine 10 has a rotor 12 having an approximately C-letter shaped cross section in a casing 11 having an approximately C-letter shaped cross section. This rotor 12 is supported rotatably in the case 11 by means of a rotary shaft 13. On the outer circumference of the rotor 12, two lines of blades 14 (fins or blades) are arranged protrusively on right and left sides with a constant interval so that the right and left blades are arranged zigzag respectively, and further, a passage 15 is formed at the middle part for making the working fluid flow. In the case where one side of the casing 11 is opened, a partition 16 is provided on an end of the outer periphery of the rotor 12. This partition 16 prevents leakage of the working fluid through a clearance between the blades 14 and the casing 11. Thus, it is possible to get high efficiency, high performance and large torque at a low speed.

Description

[Detailed description of the invention]

[0001]

[Industrial application field]

The present invention relates to a turbine and a turbocharger using the same, and more particularly, the present invention relates to a turbine and a turbocharger using the turbine.
The present invention relates to a turbine that can also be used as a gas turbine and a turbocharger, and a turbocharger using the same. [0002]

[Conventional technology]

A turbine generally consists of a casing and a rotor that is rotatably supported within the casing and has a large number of blades on its circumference.A turbine is generally composed of a casing and a rotor that is rotatably supported within the casing and has a large number of blades on the circumference. It is designed to eject water and rotate the rotor at high speed. Each blade of such a turbine has a concave shape and consists of a surface that generates positive torque and a surface that generates negative torque, so that the two torques cancel each other out. [0003] Therefore, in order to obtain a large rotational force in such a conventional turbine, there is a limit due to strength issues.
A rotor equipped with blades with the largest possible outer diameter is rotated at high speed, and this is slowed down by a reducer to obtain low-speed, high-torque output. Such conventional turbines are large, require many auxiliary devices, and are expensive. [0004] For this reason, even if the conventional upper air turbine was simply downsized in order to create a small, low-cost turbine, sufficient rotational force could not be obtained. Furthermore, since there is a space between the casing and the large number of blades, unused working fluid inevitably flows out, making it difficult to increase the rotational force. [0005] USP 47 for improving the conventional turbines described above.
No. 73818 has a turbine in which a spiral flow is formed by a casing having a spiral groove on the inner peripheral surface and a rotor having a spiral groove on the outer peripheral surface, and blades are provided at regular intervals in the spiral groove of the rotor. Proposed. [0006] Even though the improved turbine is small, a groove is formed on the inner circumferential surface of the casing, which allows low-speed, high-torque output to be obtained.Working fluid such as steam flows through the spiral groove and is discharged. This caused a decrease in efficiency without contributing to the rotation of the rotor. Furthermore, as the rotational speed of the rotor increases, the amount of working fluid flowing through the helical groove increases due to centrifugal force, resulting in a reduction in turbine efficiency. Additionally, when the working fluid flows through the grooves on the inner circumference of the casing, especially when it is pressed against the grooves by the action of centrifugal force, it increases friction loss and further reduces turbine efficiency.[0007]

[Problem to be solved by the invention]

The main object of the present invention is to solve the problems of the conventional upper air technology, and to create a turbine capable of obtaining rotational power of high torque at low speed and high efficiency even with low pressure, low speed, or a small amount of working fluid. is to provide. [0008] In addition to the above-mentioned main objective, another object of the present invention is that after the working fluid is introduced into the turbine, it leaks from between the rotor and the casing, causing damage to the rotor blades (fins or blades).
It is an object of the present invention to provide a turbine capable of efficiently converting the energy of the working fluid into the rotational force of the rotor by reducing the amount of working fluid that does not impart rotational force to the rotor. [0009] Further, another object of the present invention is to achieve high efficiency, which is the main object above.
An object of the present invention is to provide a turbine capable of realizing low speed and high torque with a simple structure and at low cost. [0010] In addition to the above main objective, another object of the present invention is to provide a turbine that is easy to assemble. [0011] Another object of the present invention is to provide a turbo that can always rotate efficiently so that efficient supercharging can be performed even when the internal combustion engine is running at low speed or high speed. The purpose is to provide a charger. [0012] Another object of the present invention is to provide a turbocharger that can purify exhaust gas in addition to the above object. [0013]

[Means to solve the problem]

In order to achieve the above object, a first aspect of the present invention includes a casing, a rotor rotatably supported within the casing, and a number of blades protruding from the outer periphery of the rotor at appropriate intervals. a flow path formed on the outer circumference of the rotor adjacent to the blade; and a flow path formed in the casing;
It is an object of the present invention to provide a turbine comprising an inlet for introducing working fluid into the flow path and an outlet for discharging the working fluid flowing through the flow path to the outside. [0014] It is preferable that the rotor has a pair of partitions protruding from both ends of its outer periphery, in which the blades are housed therebetween. Further, it is preferable that a guide for directing the flow direction of the working fluid toward the blades is disposed in the flow path. Also,
Preferably, the blades form two rows, and the flow path is formed between them. Moreover, it is preferable that the inner periphery of the casing has a spiral groove (flow path). Moreover, it is preferable that the width of the groove (flow path) of the casing becomes narrower toward its tip. [0015] Further, a second aspect of the present invention includes a casing, a rotor rotatably supported within the casing, a partition protruding spirally from the outer periphery of the rotor, and a partition between the partitions. A large number of blades protruding from the outer circumference of the rotor at appropriate intervals, a flow path formed in a spiral shape on the outer circumference of the rotor adjacent to the blades, and a flow path formed in the casing for directing the working fluid. An object of the present invention is to provide a turbine comprising an inlet for introducing the working fluid into the flow path and an outlet for discharging the working fluid flowing through the flow path to the outside. [0016] Preferably, the blade is inclined with respect to the partition. Further, it is preferable that one side of the blade is fixed to the partition. Further, it is preferable that the blades are arranged in one row between the partitions. Further, it is preferable that the blades are arranged in two rows between the partitions. Further, it is preferable that the blades are arranged in a row between the partitions, and the flow passages are provided on both sides of the blades. Further, it is preferable that a guide plate is provided on a side of the rotor from which the working fluid is discharged, which guides the working fluid to be discharged in a direction opposite to the rotational direction. [0017] Further, it is preferable that the diameter of the partition and the blade decreases toward the tip of the rotor, and the diameter of the casing decreases in accordance with the partition and the blade. [0018] Further, the inlet port is provided at the center in the longitudinal direction of the casing, the outlet port is provided at both longitudinal ends of the casing, and the partition protruding from the outer periphery of the rotor is provided at the longitudinal center of the casing. It is preferable that the spirals form opposite spirals from the center to both ends. [0019] Further, the inlet port is provided at both ends of the casing in the longitudinal direction, the outlet port is provided in the center of the casing in the longitudinal direction, and the partition protruding from the outer periphery of the rotor is provided at both ends of the casing in the longitudinal direction. It is preferable that the spirals form opposite spirals from both ends toward the center. In addition, the rotor is made into a tubular shape, and spiral partitions are provided protruding from the inner periphery of the rotor, and a large number of blades are protruded from the inner periphery of the rotor between the partitions at appropriate intervals, and adjacent to the blades. Preferably, a flow path is formed on the inner circumference of the rotor. [00201] Furthermore, it is preferable that the casing has a sealed structure. Moreover, it is preferable that the inner periphery of the casing further includes a flow path formed by a partition forming a reverse spiral with respect to a spiral partition provided protrudingly from the rotor. Moreover, it is preferable that the width of the flow path of the casing gradually narrows toward the tip of the casing along the rotor. [0021] Further, a third aspect of the present invention includes a rotor that is rotatably supported, a partition that protrudes in a spiral shape on the outer periphery of the rotor, and a partition that is fitted and fixed onto the partition and that is connected to the rotor. An annular casing to be integrated, blades fixed to at least one location among the rotor, partition, and casing and provided at appropriate intervals around the rotor's outer periphery; A flow path formed in a spiral shape on the outer circumference, a side plate placed on one side of the rotor with an appropriate clearance from the rotor, and surrounding the space between the mouth rotor and the casing from the side; The present invention provides a turbine comprising an inlet for introducing a working fluid and an outlet for discharging the working fluid. [0022] Further, a fourth aspect of the present invention is a spiral passage formed by a pair of discs, a spiral partition that connects both discs with an appropriate interval, and A blade fixed to at least one part of the partition at appropriate intervals toward the center, a flow path adjacent to at least one part of the top, bottom, right and left sides of the blade and formed along the passage, and of both discs. A turbine consisting of an opening for discharging or introducing working fluid formed in the axial center of one of the disks so as to communicate with a flow path, and a rotating shaft fixed to the axial center of the other disk. It provides: Preferably, the turbine of the above aspect fits into the casing and rotates within the casing. [0023] Further, a fifth aspect of the present invention includes a casing, a partition protruding along the inner periphery of the casing, and a plurality of recesses provided at appropriate intervals on the inner periphery of the casing between the partitions. , a plurality of recesses formed by a rotor rotatably supported within the casing, a partition protruding along the outer periphery of the rotor, and a plurality of recesses provided at appropriate intervals on the outer periphery of the rotor between the partitions. [0024] It is preferable that the partition of the casing and the partition of the rotor are both spiral-shaped. Further, it is preferable that the partition of the casing and the partition of the rotor form a reverse spiral shape. Moreover, it is preferable that the width of the flow path of the casing becomes narrower toward its tip. Preferably, the casing further includes a plurality of nozzles for spraying the working fluid onto the plurality of blades. Preferably, the width and the width of the partition of the rotor are the same. Further, it is preferable that the partition of the casing and the partition of the rotor have the same shape. Preferably, a plurality of partitions are provided between two partitions of the casing corresponding to adjacent partitions of the rotor. [0026] Further, a sixth aspect of the present invention includes a casing, a rotor rotatably supported within the casing, and a flow path that bends in opposite directions at regular intervals along the outer circumference of the rotor. a partition protruding from the outer periphery of the rotor in order to [0027] It is preferable that the flow path is zigzag. Moreover, it is preferable that the flow path has a wave shape. Further, the flow path is
Preferably, it is formed in a spiral shape along the outer periphery of the rotor. Further, it is preferable that the partition and the flow path have the same shape. [0028] Further, it is preferable that the inner periphery of the casing further includes a partition that forms a groove-like flow path along the inner periphery, and the flow path width of the casing is constant along the inner periphery of the casing. Preferably, the flow path bends in opposite directions at intervals. Moreover, it is preferable that the shape of the flow path and partition of the said casing is the same shape as the flow path and partition of the said rotor. Moreover, it is preferable that the flow path of the casing and the flow path of the rotor form a reverse spiral shape. [0029] In addition, a seventh aspect of the present invention includes a drum, a support shaft connected to the center of at least one side of the drum, and a support shaft that covers the outer periphery of the drum and is pivotally supported by the support shaft. a casing; a partition protruding from the inner periphery of the casing;
Blades protruding from the inner periphery of the casing between the partitions at appropriate intervals, a flow path formed on the inner periphery of the casing adjacent to the blades, and a flow path formed in the drum passing through the support shaft. The present invention provides a turbine comprising an inlet for introducing working fluid into the flow path and an outlet for discharging the working fluid flowing into the flow path to the outside. Preferably, the partition and the flow path have a spiral shape on the inner periphery of the casing. [00301] Further, an eighth aspect of the present invention provides a turbine according to each of the above aspects using exhaust gas of an internal combustion engine as a working fluid, a blower attached to the other end of the rotating shaft of the rotor, and a blower encapsulating the blower. The present invention provides a turbocharger comprising a blower casing having an inlet for inhaling charged air and an outlet for discharging charged air. [0031] It is preferable that a part or all of the portion constituting the flow path of the turbine be made of one or more of a catalyst material, a material to which a catalyst is attached, and a material containing a catalyst. [0032]

[Action of the invention]

In the turbine of the first aspect of the present invention, the rotor rotatably supported within the casing is provided with a large number of blades on its outer periphery and a flow path adjacent to the blades, and the working fluid flows through the flow path. As it flows, a portion of it shines on each blade one after another, pushing each blade to move and rotating the rotor. Even if the force applied to each blade is small, when the working fluid hits a large number of blades, it becomes a large force and generates a large rotational torque. When the load that rotates the rotor increases, the resistance of the blades increases and a large rotational torque is generated. When a load to the extent that rotation is not possible is applied, the working fluid passes through the flow path and is discharged from the discharge port. [0033] In the turbine according to the second aspect of the present invention, a spiral flow path is formed by a partition protruding in a spiral shape on the outer periphery of the rotor, and a large number of blades are provided within the flow path. In this turbine, the working fluid rotates around the rotor several times and is discharged.
This makes effective use of the kinetic energy of the working fluid. [0034] In each of the above turbines, the casing does not require any processing on the inner periphery and constitutes only about 1/4 of the cross section of the flow path, so the working fluid that comes into contact with the casing is extremely small, and therefore the friction with the casing is small. Loss is reduced, and more of the kinetic energy of the working fluid contributes to the rotation of the rotor. [0035] Further, in a turbine according to another example of this aspect, a spiral groove that rotates in one direction is formed on the outer circumference of the rotor, a spiral groove that rotates in the opposite direction is formed on the inner circumference of the casing, and blades are provided in the spiral groove on the outer circumference of the rotor. It will be done. In this turbine, the working fluid returns to the inlet side through the helical groove of the casing, increasing static pressure, and the amount of working fluid discharged through the helical groove of the casing decreases or almost disappears, making the working fluid effective. As a result of its utilization, the rotational force of the rotor increases. [0036] In the turbine of the third aspect of the present invention, the rotor and the casing are connected and integrated by a partition of a spiral groove, and a fixed plate is provided on one side of the rotor to laterally surround the space between the rotor and the casing. The fixed plate is provided with a nozzle for ejecting a working fluid into the space. In this turbine, since the casing is integrated with the rotor, the rotational force of the rotor increases due to frictional resistance with the casing. [0037] Among the above-mentioned turbines, in those in which a spiral flow path is formed, the casing is formed into a cylindrical shape with an opening wider than the bottom, and a shaft-shaped or cylindrical rotor that is fitted into the casing is provided with a deep groove on the outer periphery. A spiral partition is formed that gradually becomes shorter in length. After inserting the rotor, the lid is closed. In this turbine, it is easy to assemble and remove for repair or inspection, and the flow path gradually narrows toward the discharge side at the back, so that no drop in pressure occurs. [0038] Further, in the turbine according to the fourth aspect of the present invention, a pair of discs are connected by a spiral partition, and a large number of blades are provided in the spiral flow path formed thereby. A rotating shaft is fixed to the axial center of one of the disks, and a nozzle or a discharge port is provided to the axial center of the other disk. In this turbine, the working fluid introduced from the nozzle provided at the end of the flow path on the outer periphery flows in a spiral shape and is discharged from the outlet at the shaft center, or the working fluid introduced from the nozzle provided at the shaft center Fluid is discharged from a discharge port provided at the end of the flow path on the outer periphery. In any case, the working fluid hits each blade in the flow path and rotates the rotor between the time it is introduced and the time it is discharged. [0039] In the turbine of the fifth aspect of the present invention, serrations, gears, waves, or curved irregularities are provided in the circumferential direction on the inner periphery of the casing and the outer periphery of the rotor, and spaces are formed in the casing by the recesses. When a nozzle is provided at the location and the convex part of the rotor matches the convex part of the casing,
The pressure of the working fluid introduced into the space formed by the recess increases and causes the rotor to rotate. When the convex part of the rotor separates from the convex part of the casing and coincides with the concave part, a flow path connected to the discharge port is formed on the outer periphery of the rotor. [0040] In a turbine according to another example of this aspect, irregularities are formed in a spiral shape on the inner periphery of the casing and the outer periphery of the rotor. In this case, each time the rotor rotates once, the flow path on the casing side and the flow path on the rotor side coincide once, and the rotor convex portion coincides with the convex portion of the casing at one or several locations. In this case, a nozzle is therefore provided for each adjacent flow path. [0041] Furthermore, in the turbine of the sixth aspect of the present invention, a zigzag or wavy convex portion is formed on the inner periphery of the casing, and a zigzag or wavy concave portion is formed on the outer periphery of the rotor, and as the rotor rotates, the concave portion is formed by the convex portion. When the concave portion is closed, the pressure of the working fluid introduced into the casing increases, and when the concave portion moves away from the convex portion, the working fluid flows into the concave portion and rotates the rotor. [0042] In a turbine according to another example of this aspect, a zigzag or wavy convex portion is formed in a spiral shape on the inner periphery of the casing, and a concave portion is formed in a spiral shape on the outer periphery of the rotor. In this turbine, the concave portion on the rotor side is once closed by the convex portion on the casing side every time the rotor rotates once, and a pressure difference is generated between the concave portion on the rotor side and the concave portion on the casing side. When the recess on the rotor side and the recess on the casing side communicate with each other due to rotation of the rotor, the working fluid on the high pressure side flows into the recess on the rotor side and rotates the rotor. [0043] In each of the above turbines, the rotor rotates within the casing, but in the turbine of the seventh aspect of the present invention, the casing rotates around a fixed rotor (drum). In this case, vanes are attached to the inner periphery of the casing, and working fluid is introduced through a nozzle provided on the drum. [0044] The working fluid used in each of the turbines described above is usually air, steam, combustion gas, or exhaust gas, but other than these, fluorocarbon gas, water, or any other fluid can be used. [0045] One suitable use of each of the above turbines is the turbocharger of the eighth aspect of the present invention, in which case the working fluid is exhaust gas. When used as a turbocharger, a catalyst such as carbon monoxide in the exhaust gas, unburned hydrocarbons, HC, nitrogen oxide, oxides of transition metals such as Ni and manganese Mn, and alloys of copper and nickel are placed in part or the entire flow path. It is desirable that the rotor outer periphery, blades, and housing inner periphery, which come into contact with the working fluid, be made of the catalyst, or that a catalyst layer be formed on the surface of the above-mentioned parts. [0046]

【Example】

Below, each aspect of the turbine and turbocharger according to the present invention will be specifically described based on preferred embodiments shown in the accompanying drawings. [0047] FIG. 1 is a longitudinal sectional view of a specific embodiment of a turbine according to the present invention, and FIG. 2 is a view taken along the line II-II in FIG. 1. [0048] As shown in these figures, the turbine 10 according to the first aspect of the present invention has a rotor 12 having a substantially C-shaped cross section disposed within a casing 11 having a substantially C-shaped cross section. It is rotatably supported on the casing 11 by a rotating shaft 13, and on the outer periphery of the rotor, as shown in FIGS. Moreover, the left and right blades are protruded in an alternating manner, and the central part has a flow path 1 through which the working fluid passes.
It is 5. [0049] As in the illustrated example, when one side of the casing 11 is open, a partition 16 is provided on the outer periphery of the end of the rotor 12.
It is preferable to provide This is blade 14 and casing 1
This is because it is possible to prevent the working fluid from leaking from between the opening and the opening. In the illustrated example, the blades 14 can be fixed or fixed to the partition 16, which is more preferable because the strength of the blades 14 can be increased. Furthermore, at both ends of the rotor 12,
Although it is preferable to provide a partition so that the blades 14 are contained therein, it is not necessary to provide a partition if a lid is provided on the open side of the casing 11 in FIG. 1 and the casing 11 is sealed. [0050] In this flow path 15, one V-shaped guide 17 that protrudes from the inner peripheral surface of the casing 11 is arranged (Fig. 3
reference). Although one guide 17 is arranged in the illustrated example, a plurality of guides 17 may be arranged at regular intervals in the circumferential direction of the casing, and has the function of distributing the working fluid to the left and right and applying it to the left and right fins, and also has the function of It also functions as a backflow stopper to prevent the flow of working fluid from the inside.

The casing 11 has an inlet (hereinafter referred to as a nozzle) 18 for introducing working fluid, an outlet 19 for the same, and holes (not shown) for passing cooling water to cool the casing.The pressure of the working fluid in the casing is A hole connected to a valve for adjusting the flow rate is also provided. Although the position of the nozzle 18 and the discharge port 19 is not particularly limited, it is preferable that the nozzle 18 and the discharge port 19 be positioned so that the working fluid can perform sufficient work on the blades 14. Further, it is desirable that the nozzle 18 and the discharge port 19 be oriented in the tangential direction of the rotor 12. [0052] The opening of the nozzle 18 may be provided on any of the circumferential surface of the casing 11 as long as it is upstream from the sharp end of the guide 16; It is preferable to provide it at the center of the casing 11 in the longitudinal direction. Moreover, with respect to the peripheral surface of the casing 11, in the illustrated example, 1
In addition to the number of nozzles 18 provided, a plurality of nozzles may also be provided at predetermined intervals. [0053] The outlet 19 may be installed anywhere on the circumferential surface of the casing 11 as long as it is downstream from the rear end of the guide 16; It is preferable to provide the blades 14 so as to face the blades 14 so that the working fluid can flow out after doing work and converting energy into the rotational force of the rotor 12. In the illustrated example, there are two rows of blades 14, so it is preferable to provide two discharge ports 19 on the same circumferential surface of the casing 11 facing these rows of blades, but either one of them may be provided. Furthermore, although the outlet 19 is provided at one location on the circumferential surface of the casing in the illustrated example, it is not particularly limited, and like the nozzle 18, it may be provided at a plurality of locations at predetermined intervals. [0054] In the above specific example, the flow path 15 is provided in the center of the rotor 12, and two rows of blades 14 are provided on both sides of the flow path 15.
), partitions 16 may be provided at both ends of the rotor 12, blades 14 may be protruded from the center of the rotor 12, and the space between the partitions 16 on both sides may be used as a flow path 15. As shown in (b), the side surface is fixed to the partition 16 on one side and the blade 14 is provided protrudingly, and the partition 1 on the other side
6 may be used as a flow path. In these cases, instead of the V-shaped guide 17, an inclined plate-shaped guide that is inclined with respect to the flow is used. [00551 The blades 14 in the specific example shown in the drawings may all be flat and of the same size, perpendicular to the flow, and the left and right blades may be alternated, and may be constructed of blades of different lengths or shorter sizes or larger and smaller blades. , each vane may be bent or curved in a V-shape, and may be inclined back and forth with respect to the flow. Further, when the blades are formed in an orifice shape, the flow path may not be provided in the center, one end, or both ends, and the orifice-shaped opening of each blade may be used as the flow path. Also,
In the illustrated example, the left and right blades 14 are alternated so as to easily obtain a large resistance to the flow, but the left and right blades may be arranged in parallel, that is, the left and right blades may be arranged in parallel. [0056] In the above embodiment, if necessary, the side surface of the casing 1 may be made into a lattice-like shape to allow cool air to circulate, and in addition, in order to increase the cooling effect of the rotor, the outside of the rotor 11 may be Wings may be provided protruding from the sides. Further, a groove may be provided on the inner circumferential surface of the casing 1, this groove may be formed in a spiral shape, and the width of this groove may be narrowed toward the tip. By making the turbine of this embodiment multi-stage, it is possible to obtain a turbine with even higher performance. [0057] Turbine 2 according to the second aspect of the present invention shown in FIGS. 5 and 6
0 has a spiral partition 23 protruding from the outer peripheral surface of a rotor 22 disposed in a casing 21 to form a spiral passage, and blades 24 are attached at regular intervals to the negative side of the partition 23 on the other side. A guide 26 is provided for each blade on the discharge side of the rotor to guide the working fluid to be discharged in a direction opposite to the rotational direction of the rotor 22. In the illustrated example, only one guide 26 may be provided instead of a plurality of guides 26. [0058] In the following description, the turbine of this embodiment has a spiral partition, and a plurality of blades are protruded between the partitions. Since it has basically the same configuration as the turbine of the embodiment, different parts will be explained and detailed explanation of the similar configuration will be omitted. [0059] Further, the inlet 27 for introducing working fluid and the outlet 28 for working fluid are oriented in the tangential direction of the rotor 22 in the casing 2.
1 at an appropriate position. In the illustrated example, the inlet 27 is provided at the right end in the longitudinal direction of the casing 21 in FIG. 5, and at the end opposite to the end of the outlet 28. The formation positions of the inlet 27 and the outlet 28 may be appropriately selected depending on the shape of the blades 24 and the flow path 25 provided on the outer periphery of the rotor 22. [0060] The rotor 22 is supported by a rotating shaft 29 in the casing 21 via a bearing 29a. [0061] Here, in the present invention, the position and direction of attachment of the blade 24 to the partition 23, and the method of forming the flow path 25 are not particularly limited. For example, FIGS. 7(a) to 7(d)
) can be applied in various ways, such as shown developed along the outer periphery of the rotor 22 and along the partitions 23. As shown in FIG. 7(a), the blades 24 are attached to the partition 23 in one row at an angle with respect to the partition 23, and one side of the blade row may be used as a flow path. It may be mounted horizontally or vertically. Further, as shown in FIG. 7(b), the blade 24 is separated by a partition 23.
Alternatively, as shown in FIG. 7(C), the channels 23 may be arranged in the center between the partitions 23 and extend beyond the center between the partitions 23 at predetermined intervals from the partitions 23 on both sides, as shown in FIG. 7(C). A blade may be provided so that the flow path 25 is bent and has a zigzag shape. In addition, as shown in FIG. 7(d), two rows of blades 24 are provided from the partitions 23 on both sides, and the center part is connected to the flow path 24.
It may be set to 5. [0062] As one of the other specific embodiments of this aspect, as shown in FIG. A partition 33 and a blade 34 protruding from the outer circumference of the rotor 3
The cone-shaped turbine 30 is a cone-shaped turbine whose diameter decreases toward the tip of the turbine. In this cone-type turbine 30, since the diameter of the casing 31 and the parts 91J and 33 of the rotor 32 (o and blades 34) are reduced toward the tip, assembly is easy. Therefore, the distance between the casing 31 and the rotor 32, especially the partition 33, can be made as small as possible, the leakage of the working fluid can be reduced, and the efficiency of using the working fluid can be increased. [00631] Furthermore, in the cone-type turbine 30, the flow path 35 is formed between the partition 33 and the blade 34 whose diameter decreases toward the tip, so the flow path naturally becomes narrower toward the tip. , most of the working fluid is directed toward the rotor 32 and does work on the blades 34, contributing to their rotation. Furthermore, although the installation positions of the working fluid inlet and outlet are not particularly limited, it is preferable that the inlet 36 be provided on the larger diameter side and the outlet 37 be provided on the smaller diameter side. Therefore, the amount of unused working fluid that is not used to rotate the rotor 32 can be extremely reduced. [0064] In addition, as another specific example of this aspect, as in the turbine 40 shown in FIG. 9, a working fluid inlet (nozzle) 46 is provided in the longitudinal center of the casing 41, and a A working fluid outlet 47, 47 is provided respectively, and a partition 43 protruding from the outer periphery of the rotor 42 is spirally moved from a position corresponding to the inlet 46, that is, from the center position in the longitudinal direction of the rotor 42 toward both ends. In this case, blades 44 are provided between the partitions at predetermined intervals, and a flow path 45 is formed between the partitions 43 and the blades 44. [0065] In this turbine 40, the flow path 45 has a reverse spiral (reverse thread) from the center of the rotor 42 toward both ends, so that unused working fluid that does not contribute to the rotation of the rotor flows into the casing as in the conventional case. It can prevent leakage. [0066] In the turbine 40 shown in FIG. 9, the inlet 46 may be an outlet and the outlet 47.47 may be an inlet.From the viewpoint of preventing leakage of unused working fluid, the inlet is located in the longitudinal direction of the casing. It is preferable to provide it in the central part. [0067] Moreover, the turbine 50 shown in FIG. 10 is another specific example of the turbine of this aspect. This turbine 50 includes a rotor 52 having a tubular shape, a spiral partition 53 protruding from the outer periphery of the rotor 52, blades 54 provided at a predetermined interval between the partitions 52, and blades 54 formed between the partition 53 and the blades 54. The rotor 52 not only has a spiral flow path, but also has these spiral partitions 53, blades 54, and spiral flow paths 55 on the inner periphery of the rotor 52. The casing 51 has a bag structure so as to enclose the rotor 52, and the output shaft 5 of the rotor 52 is connected to the casing 51 by the flange 51a.
8 via a bearing 59. [0068] The working fluid inlet (nozzle) 56 is provided at the side end of the casing 51, and is configured to flow the working fluid from the tip of the rotor 52 to both the outer and inner flow paths 55 and 55 of the rotor 52. It is configured. Working fluid outlet 57, 57.
are provided on the casing 51 corresponding to the outer circumferential side and the inner circumferential side on the base end side of the rotor 52. [0069] The working fluid inlet 56 and outlet 57 are connected to the rotor 52.
The present invention is not limited to what is shown in the drawings, as long as the working fluid can be distributed to channels 55.55 on the inner and outer peripheries of the body, and the working fluid can be discharged from these channels 55.55. [0070] This turbine 50 has flow passages 55 on both the inner and outer surfaces of the rotor 52.
．． 55, twice as much working fluid can be used as the rotational force of the rotor 52, resulting in improved efficiency, compactness, and high performance. By making this turbine 50 multistage like the above-mentioned turbine, it is possible to achieve further compactness, higher efficiency, and higher output. [0071] In another specific example of this aspect, as in the turbine 60 shown in FIG. A flow path (in the casing 61 grooves) 69. This turbine 6
The casing 61 of No. 0 has a flange 61a, and the casing 61 is provided with a working fluid inlet 66 and an outlet 67 at both ends, respectively. [0072] In this turbine 60, the flow path 65 of the rotor 62 and the flow path (groove) 69 of the casing 61 are spirally reversed, so the working fluid entering from the nozzle 66 passes through the flow path 69 of the casing. The working fluid tries to flow out to the opposite side, but the working fluid that has entered the rotor 62 flows in the opposite direction because its flow path 65 is opposite to the flow path 69. As a result, the pressure increases and the working fluid flows through the channel 69 of the casing 61, causing the impeller 64
to rotate the rotor 62 and open the flow path 65 of the rotor 62.
By repeating the process of entering the flow path 69 of the casing 61 and increasing the ability to rotate the rotor 62, the torque increases. This is a big difference from conventional turbines in which when the rotor and the flow path of the casing are in the same direction, working fluid is sucked in from the tip and counter torque acts on the blades, making it impossible to obtain high torque. [0073] Furthermore, since the flow path 65 of the rotor 62 and the flow path 69 of the casing 61, which has a reverse spiral (reverse thread), also serve as a labyrinth seal, the working fluid flowing out from between the rotor 62 and the casing 61 is prevented. Since it can be reduced, there is also the effect of increasing efficiency. [0074] Of course, in this turbine 60 and in each of the above-mentioned turbines, the casing 6 on the opposite side to the flange 61a
It is also possible to provide a flange on the end face of 1 to make it a closed type, thereby preventing leakage of working fluid and increasing efficiency. [0075] Note that the rotor partition and the casing partition in each of the above turbines may be a spiral spiral,
It may also consist of a plurality of spirals. In the turbine of the above embodiment, the width of the flow path of the casing may be made narrower toward the tip to further increase the efficiency of the working fluid. Of course, each turbine of this embodiment may be multi-staged to improve performance. [0076] A turbine 70 according to a third aspect of the present invention shown in FIGS. 12, 13, and 14 includes a cylindrical casing 71 and a rotor 72.
are connected by a spiral partition 73 to form a spiral passage, vanes 74 are installed at regular intervals in the passage, and a flow passage 75 and a flow passage 76 are formed between the casing 71 and the rotor 72, respectively. Rotor 7
2 and the casing 71 rotate together, and a fixed plate 78 is provided on the inlet side of the flow path to have an appropriate clearance with the rotor 72 and to pivotally support the rotating shaft 77. The fixed plate 78 is provided with an inlet (not shown) (nozzle) for ejecting the working fluid into the flow path, and an outlet (not shown) is provided on the outlet side of the flow path. [0077] A turbine 80 according to the fourth aspect of the present invention shown in FIG. It has blades (fins) 83 protruding from one side at regular intervals, the other side is configured as a flow path 84, and the axis of one side plate 81 is provided with a discharge port 85 communicating with the path, which fits into the casing 86. It is designed to rotate within the casing. 8 in the diagram
7 is an introduction port. [0078] In this embodiment, the spiral passage is formed by the side plate and the partition, but in another embodiment, tubes having circular, rectangular or other arbitrary shapes in cross section may be spirally wound and integrally connected. It is formed by [0079] In the turbine 90 according to the fifth aspect of the present invention shown in FIGS.
A vane) 93 and a recess 94) are formed. casing 91
A V groove 95 is formed on the inner circumference of the rotor 92 to correspond to the recess 94 of the rotor 92, and an annular duct 98 connected to the inlet 97 is formed inside. (2) Working fluid can be ejected from the duct 98 through the nozzle 100 for each groove 95. Moreover, when the turbine 90 is a closed type, the rotor 92 is made into a cylindrical shape,
Rotor nozzle 1 communicating with the inside of recess 94 of rotor 92
01 may be provided for each recess 94. [00801 By doing this, the working fluid is compressed by the rotation of the rotor 92 and ejected from the rotor nozzle 101 as a reaction force, the inside of the rotor 92 becomes high pressure, and a flow path is formed between the rotor 92 and the casing 91. At times, the working fluid may conversely be ejected from the inside into the flow path to increase the rotational force of the rotor 92, making it possible to achieve higher efficiency. [0081] In this turbine, the rotor 92 rotates, and the rotor 9
When the convex portion 93 of No. 2 matches the convex portion 96 formed by the groove 95 on the inner circumference of the casing (Fig. 16), the static pressure of the working fluid filling the space formed by the groove 95 and the concave portion 94 increases. Then, the rotor 92 is rotated. When the protrusion 93 of the rotor 92 is removed from the protrusion 96 of the casing (Fig.
7) A flow path connected to the discharge port 99 is formed, and the working fluid is discharged. [0082] In another specific embodiment of this aspect shown in FIG. 18, a partition 102 is provided in a spiral shape on the outer periphery of the rotor 92, and a spiral partition 103 is also provided in the casing 91, both of which have a spiral shape. The configuration may be such that unevenness is provided between the partitions. Further, both of the spiral partitions may be spirally reversed from each other. [0083] The turbine 110 shown in FIGS. 19 and 20 has a rotor 1
A spiral passage is formed on the outer periphery of the rotor 112 by a partition 113, and sawtooth irregularities (convex portions (vanes) 114, recessed portions 115) are formed on the outer periphery of the rotor 112 along this passage. (2) Grooves 116 are formed between the spiral partitions 118 at the same pitch as the passages. In this turbine, the passages on the casing 111 and rotor 112 sides are aligned once every time the rotor 112 rotates once, and each convex portion 117 of the casing 111 and the convex portion 1 of the rotor are aligned with each other.
14 can now match. [0084] Both upper half views of FIGS. 19 and 20 show a state in which the convex portion 114 of the rotor 1 and 12 has come off the convex portion 114 of the casing 111 to form a flow path between the rotor 112 and the casing 111. Both lower half views of FIGS. 19 and 20 show a state in which the two coincide, the flow path is closed, and the working fluid applies rotational force to the convex portion 114 of the rotor 112 [0085] Here, in this aspect, The shape and number of the irregularities formed on the outer circumference of the rotor and the casing are not particularly limited, and are not limited to sawtooth shapes as shown in the illustrated example; for example, various irregularities such as smooth irregularities such as waveforms can also be applied. can do. In addition, in this embodiment, the width of the rotor partition and the flow path (interval between partitions) in the casing are made the same, so that the flow paths overlap each other every rotation of the rotor, and the rotor partition and the flow path in the casing overlap. You can do it like this. [0086] Also, by narrowing the flow path (interval between partitions) of the casing,
By providing a plurality of casing channels between the rotor channels (intervals between partitions), the number of overlaps between the rotor partitions and the casing partitions can be increased, thereby increasing the labyrinth seal effect. In these cases, the widths of the rotor and casing partitions are preferably the same. [0087] The turbine 120 of the sixth aspect of the present invention shown in FIG.
A zigzag-shaped groove partition 123 is provided on the outer circumferential surface of the rotor 122, and a zigzag-shaped flow path (groove) 124 is formed in the inner circumferential direction.
A zigzag-shaped convex portion 125 of the same size as the convex portion 125 and a flow path (groove) 126 are provided on both sides of the convex portion 125.
The working fluid introduced by 27 flows through each channel 124, 126.
, and are discharged from the outlet 128 , and the rotation of the rotor 122 opens the flow path 124 .
The convex portion 125 is designed to be well closed or opened. [0088] Here, when the flow path 124 on the rotor side is blocked by the convex portion 125, a pressure difference is generated between the flow path 126 and the flow path 124. When the flow path 124 is removed from the convex portion 125, the flow path 126 and the flow path 12
4 are in communication with each other, and the rotor 122 is rotated by the working fluid that has flowed into the flow path 124. Additionally, the turbine 120 shown in FIG.
In this example, a zigzag partition 123 and a flow path 124 are spirally formed around the outer circumference of the rotor 122, and the casing 1
A flow path 126 is formed between the zigzag-shaped convex portions 125 and the convex portions 125 having the same size as the flow path 124 on the inner periphery of the rotor 1.
22 rotates once, the variable flow path 124 and the convex portion 125 are aligned, and the flow path 124 is blocked by the convex portion 125. [0089] In this embodiment, the partition 12 formed in the rotor 122
3 and the flow path 124 may be zigzag as shown in FIGS. 22(a) and 22(b), or may be a smooth waveform as shown in FIGS. 22(c) and 22(d). There may be. In addition, FIGS. 22(a) and 22(c)
), the width of the partition 123 and the width of the flow path 124 may be different, or the width of the partition 123 and the width of the flow path 124 may be the same as shown in FIGS. 22(b) and 22(d). You may let them. Convex portion 125 of casing 121 and flow path 1
The pattern 26 may be the same as the pattern of the rotor 122. [0090] In the example shown in FIG. 21, the turbine of the zigzag type in which the zigzag-shaped flow passage 126 is also formed on the inner periphery of the casing 121 is not limited to this, and the zigzag-shaped flow passage 126 is also formed on the inner periphery of the casing. There may be no groove, or there may be a flow path.
The groove serving as the flow path does not need to be curved, may be a spiral flow path, or may be a reverse spiral flow path. Further, the width of the flow path may be constant or may become narrower toward the tip. [0091] A turbine 150 according to a seventh aspect of the present invention has a rotor fixed as a drum 152 as shown in FIG. Around the drum there are 153 partitions and 1 blade.
54 and a casing rotor 15 having a flow path 155 formed therein.
1 is rotated. [0092] In this turbine 150, an inlet nozzle 156 is provided on the side of the drum 152, an outlet 157 is provided outside the casing rotor 151, and a forward or reverse spiral flow path 158 is formed on the outer periphery of the drum 152. In addition, casing rotor 1
A rotating shaft 159 fixed to the drum 51 is rotatably supported via a bearing 160 by the drum 152 and a support frame 161 that fixedly supports the drum 152. [0093] The turbocharger 130 according to the eighth aspect of the present invention shown in FIG.
A spiral partition 133 is provided protruding from the outer periphery of the partition 1, and a blade 134 is provided between the partition 133, and the blade 134 and the partition 1
A turbine 138 has a flow path 135 formed therebetween, and an inlet (nozzle) 136 and an outlet 137 that communicate with an exhaust pipe of an engine (internal combustion engine) of an automobile or the like in a casing 131. Rotor 1
Blower 1 attached to one end of rotating shaft 139 of 32
40 and the casing 145 of the blower 140 and the axial air and charge inlet 1 formed in the casing 145
41 and a supply port 142 provided in the radial direction and communicating with the intake pipe of the engine. [0094] The casing 131 of the turbine 138 and the casing 145 of the blower 140 may be integrated. Further, the rotating shaft 139 is supported by at least a bearing 143. [0095] The turbine used in this turbocharger 130 is not limited to the illustrated example, and any of the turbines according to the embodiments of the present invention described above can be used. [0096] The turbine 138 of the present invention efficiently performs high torque rotation even with a working fluid of low pressure, low speed, and low flow rate, so that sufficient supercharging can be performed even when the engine rotates at low speed. Furthermore, the time lag in supercharging the turbocharger can also be reduced. On the other hand, even when the engine rotates at high speed, the turbine 138 rotates at high speed and high output due to the high pressure, high speed, and high flow rate of the working fluid, so that sufficient supercharging can be performed. [0097] Therefore, compared to conventional turbochargers, there is no need to install two turbochargers, one for low pressure and one for high pressure, and use them separately, and if you especially want to use them separately,
One of the low-pressure and high-pressure turbochargers may be the turbocharger of the present invention, and the other may be of a conventional type, or the turbocharger of the present invention may be used for both. The performance of the turbocharger may be adjusted by the size of the flow path 135 and the shape, size, and number of the blades 134. [0098] Further, in the turbocharger 130 of the present invention,
The constituent materials of the turbine 138, particularly the materials of the parts that come into contact with the exhaust gas, which is the working fluid, such as the partition 133, the blades 134, the outer peripheral surface of the rotor 132, and the inner peripheral surface of the casing 131, are made of materials that have an exhaust treatment catalytic effect. It is better to keep it. [0099] For example, these catalyst materials include heavy metals such as platinum (pt), rhodium (Rh), ruthenium (Ru), and palladium (Pd), alloys of copper and nickel, and copper (CU).
Examples include oxides of transition metals such as ) chromium (Cr), nickel (Ni), and manganese (Mn), and catalysts in which oxides of copper and chromium are supported on granular alumina. [0100] The above-mentioned components may be directly constructed from the above-mentioned materials.As shown in FIG. You may also arrange it. [0101] By doing this, it is possible to not only purify the engine exhaust gas, but also use the combustion heat from the combustion of carbon monoxide (CO) and unburned hydrocarbons (HC) in the exhaust gas as energy for the turbine 138. , the supercharging efficiency of a turbocharger can also be mentioned. [0102] As in the above example, a turbine whose constituent material is a material having an exhaust treatment catalytic action can also be applied to an exhaust turbine. [0103] (Experimental Example) A steel turbine similar to the turbine of the second aspect of the present invention shown in FIG. The rotational speed and torque of this turbine were measured. Turbine Dimensions Rotor outer diameter 114 mm, width 43 mm Flow path Pitch 12 mm Inner periphery of helical casing - No flow path (groove) [0104] Rotational speed measurement result Pressure Kg/Cm2G0.511 Rotational speed rpm 2700 4000400O
No measurements were taken above rpm. [0105] Torque measurement results Using the mechanism shown in FIG.
71 is pressed against the support rod 172 by the pressing plate 174,
A moment is applied to the support rod 172, and the support rod 1 is
The shaft torque of the turbine was measured by measuring the pressing force of 72. [0106] The pressure and flow rate of the working fluid that drives the turbine at this time were as follows: [0107] Compressor pressure 5.2 kg/cm 2 , pressurized air flow rate 0. 528Nm3/min rotation speed rpm
0 300 1500 3000 Torque g-
cm 2000 1850 1800 1
600 [0108]

【Effect of the invention】

The present invention is configured as described above, and has the following effects. [0109] According to the turbine of the present invention, spiral grooves are formed on the outer circumferential surface of the rotor and the inner circumferential surface of the casing.Compared to the above-mentioned turbine, most of the working fluid flows through the rotor side, and there is less frictional resistance with the casing, so that the working fluid can be easily operated. The energy of the fluid is effectively used to rotate the rotor, which not only increases the rotational torque, but also eliminates the need to process spiral grooves on the casing, simplifying the structure and reducing costs. . [01101] In the turbine of the present invention, since the working fluid can rotate several times on the rotor and be discharged, the frictional resistance with the blades increases, and the energy of the working fluid can be used more effectively. [0111] In the turbine of the present invention, by providing the guide, the flow of the working fluid is directed toward the blades, and the frictional resistance due to the blades is increased, and backflow of the working fluid can also be prevented. [0112] According to the turbine of the present invention, since the casing is integrated with the rotor, the frictional resistance with the casing contributes to the rotation of the rotor, increasing the rotational force of the rotor and further improving efficiency. [0113] According to the turbine of the present invention, all the frictional resistance with the working fluid contributes to the rotational force of the rotor, and the energy of the working fluid can be effectively used. [0114] The turbine of the present invention provided with a guide plate increases the rotational force of the rotor and can also provide a cooling effect on the turbine. [0115] According to the turbine of the present invention, various types of rotary bodies such as round blades for grinding, polishing, and cutting can be directly attached to the rotating outer casing and driven to rotate. [0116] According to the turbine of the present invention, the introduced working fluid can be used efficiently, and its energy can be efficiently converted into rotational force of the rotor. [0117] In the turbine of the present invention, by simply switching the valves of the working fluid introduction pipe and the discharge pipe, the working fluid is introduced from the discharge port, and the working fluid is discharged from the introduction port, thereby making it possible to easily rotate the turbine in reverse. I can do it. [0118] According to the turbocharger of the present invention, sufficient supercharging can be performed even when the engine is running at low rotation speeds, and the supercharging can be performed efficiently, and exhaust gas can also be purified.

[Brief explanation of drawings]

[Figure 1] FIG. 1 is a longitudinal sectional view of an embodiment of a turbine according to the present invention.

[Figure 2] 2 is a view taken along the line II-II in FIG. 1. FIG.

3 is a front view of a rotor used in the turbine shown in FIG. 1. FIG.

FIG. 4 is another embodiment (a) and (b) of a partial cross-sectional view of a rotor used in a turbine according to the present invention.

[Figure 5] FIG. 3 is a longitudinal cross-sectional view of another embodiment of a turbine according to the invention.

[Figure 6] FIG. 6 is a cross-sectional view of FIG. 5;

FIG. 7 is a developed view along the outer periphery of the rotor, showing various attachment states (a), (b), (C), and (d) of the blades protruding from the outer periphery of the rotor used in the present invention.

[Figure 8] FIG. 3 is a longitudinal cross-sectional view of another embodiment of a turbine according to the invention.

[Figure 9] FIG. 3 is a longitudinal cross-sectional view of another embodiment of a turbine according to the invention.

FIG. 101 is a longitudinal cross-sectional view of another embodiment of a turbine according to the present invention. FIG. 1 is a longitudinal sectional view of another embodiment of the turbine according to the invention; FIG. 12 is a partial longitudinal sectional view of another embodiment of the turbine according to the invention.

[Figure 13] 13 is a cross-sectional view of FIG. 12.

[Figure 14] 14 is a view taken along line BB in FIG. 13. FIG.

[Figure 15] FIG. 3 is a cross-sectional view of another embodiment of the turbine of the present invention.

FIG. 16 is a cross-sectional view showing one operating state of another embodiment of the turbine of the present invention.

17 is a cross-sectional view of the turbine shown in FIG. 16 in another operating state; FIG.

[Figure 18] FIG. 6 is a longitudinal sectional view of another embodiment of the turbine of the present invention.

FIG. 19 is a vertical sectional view showing an upper half view and a lower half view together for explaining different operating states of another embodiment of the turbine of the present invention.

[Figure 201 FIG. 20 is a cross-sectional view of FIG. 19; [Figure 21] FIG. 6 is a longitudinal sectional view of another embodiment of the turbine of the present invention.

[Figure 22] Different partition and channel patterns (a)
(b) It is a diagram showing (C) and (d).

FIG. 23 is a longitudinal sectional view of an embodiment of a turbocharger according to the present invention.

FIG. 24 is a schematic structural diagram of one embodiment of a blade used in the turbocharger of the present invention.

[Figure 25] FIG. 6 is a longitudinal sectional view of another embodiment of the turbine of the present invention.

[Figure 26] FIG. 2 is an explanatory diagram of a torque measuring device used in an example of the present invention.

[Explanation of symbols]

10.20,30,40,50,60,70,80,9
0,110,120°138.150 Turbine 11.21,31,41,51,61,71,86,9
1,111,121゜131.141 Casing 12.22, 32, 42, 52, 62, 72, 92, 1
12,122°132 Rotor 14.24,34,44,54,64,74,83,1
34,154 Feather 15.25, 35, 45, 55,
65, 69, 75, 76.84, 124°126.13
5,155,158 flow path 16.23, 33, 43,
53, 63, 68, 73, 82, 102, 103゜11
8.123,133,153 Partition 18.27,3
6,46,56,66.87,97,100,101゜127.136,142,152 Inlet (nozzle)
19.28, 37, 47, 57, 67.85, 99, 1
28,137 outlet 93.96,114,117,
125 Convex portion 94.95, 115, 116 Concave portion (
V groove) 130 Turbocharger 140 Blower 144 Granular catalyst

【Document name】

[Figure 1] drawing

[Figure 2]

[Figure 3]

[Figure 4] <a> (b)

[Figure 5] chu

[Figure 6]

[Figure 7]

[Figure 8]

[Figure 9]

[Figure 11]

[Figure 12]

[Figure 13]

[Figure 14] C'-

[Figure 15]

[Figure 16]

[Figure 17]

[Figure 18]

[Figure 20]

[Figure 21]

[Figure 22] (a) (C) (b) (d)

[Figure 23] N-year-old

[Figure 24]

[Figure 25]

[Figure 26]

Claims (19)

[Claims] Claims: 1. A casing, a rotor rotatably supported within the casing, a number of blades protruding from the outer periphery of the rotor at appropriate intervals, and a plurality of blades protruding from the outer periphery of the rotor adjacent to the blades. A turbine comprising a flow path formed on a circumference, an inlet formed in the casing for introducing working fluid into the flow path, and an outlet for discharging the working fluid flowing through the flow path to the outside. Claim 2: A casing, a rotor rotatably supported within the casing, partitions protruding spirally from the outer periphery of the rotor, and partitions protruding from the outer periphery of the rotor between the partitions at appropriate intervals. a plurality of blades, a flow path formed in a spiral shape on the outer periphery of the rotor adjacent to the blades, an inlet formed in the casing for introducing working fluid into the flow path, and A turbine consisting of a discharge port that discharges the working fluid flowing through the channel to the outside. 3. The turbine according to claim 2, wherein a guide plate is provided on a side of the rotor from which the working fluid is discharged, for guiding the working fluid to be discharged in a direction opposite to the rotational direction. 4. The turbine according to claim 2, wherein the partition and the blade have a diameter reduced toward the tip of the rotor, and the casing has a diameter reduced in accordance with the partition and the blade. 5. The inlet port is provided at the center in the longitudinal direction of the casing, the outlet port is provided at both longitudinal ends of the casing, and the partition protruding from the outer periphery of the rotor is provided in the longitudinal direction of the casing. The turbine according to any one of claims 2 to 4, wherein the turbine has a spiral shape that is opposite to the other from the center to both ends. 6. The rotor is tubular, further provided with spiral partitions protruding from the inner periphery of the rotor, and a number of blades protruding from the inner periphery of the rotor between the partitions at appropriate intervals. The turbine according to any one of claims 2 to 5, wherein a flow path is formed on the inner circumference of the rotor adjacent to the rotor. 7. The inner periphery of the casing further includes a flow path formed by a partition forming a reverse spiral with respect to the spiral partition protruding from the rotor.
6. The turbine according to 6. 8. A rotor that is rotatably supported, a partition that protrudes in a spiral shape from the outer periphery of the rotor, and an annular casing that is fitted and fixed onto the partition and is integrated with the rotor. The blades are fixed to at least one place among the rotor, the partition, and the casing, and are provided at appropriate intervals around the outer circumference of the rotor. A flow path is formed, a side plate is placed on one side of the rotor with an appropriate clearance from the rotor and surrounds the space between the rotor and the casing from the side, and an inlet for introducing a working fluid is formed in the side plate. and an outlet for discharging the working fluid. 9. A spiral passage formed by a pair of discs, a spiral partition connecting the two discs at an appropriate interval, and a spiral passageway formed by a spiral passageway formed by a pair of discs and a spiral partition connecting the discs at an appropriate interval; a flow path formed along a passage adjacent to at least one of the top, bottom, right and left sides of the blade, and an axial center of one of the two disks; A turbine consisting of an opening for discharging or introducing a working fluid formed in communication with a flow path, and a rotating shaft fixed to the axial center of the other disc. 10. A casing, a partition protruding along the inner circumference of the casing, a plurality of recesses provided at appropriate intervals on the inner circumference of the casing between the partitions, and a shaft rotatably mounted in the casing. A supported rotor, a partition protruding along the outer periphery of the rotor, a plurality of blades formed by a plurality of recesses provided at appropriate intervals on the rotor outer periphery between the partitions, and a plurality of blades formed in the casing. ,
A turbine comprising an inlet for introducing working fluid into the casing and an outlet for discharging the working fluid out of the casing. 11. The turbine of claim 10, wherein the casing partition and the rotor partition are both spiral-shaped. 12. The turbine according to claim 10, wherein the casing partition and the rotor partition are spirally opposite to each other. 13. A casing, a rotor rotatably supported within the casing, and a rotor provided protruding from the outer periphery of the rotor to form a flow passage bent in opposite directions at regular intervals along the outer periphery of the rotor. a partition formed in the casing, an inlet for introducing working fluid into the flow path, and an outlet for discharging the working fluid flowing through the flow path to the outside. 14. The turbine according to claim 13, wherein the flow path is formed in a spiral shape along the outer periphery of the rotor. 15. The turbine according to claim 14, further comprising a partition on the inner periphery of the casing that forms a spiral flow path that bends in opposite directions at regular intervals along the inner periphery. 16. A drum, a support shaft connected to the center of at least one side of the drum, a casing enclosing the outer periphery of the drum and pivotally supported by the support shaft, and a casing provided on the inner periphery of the casing. A protruding partition, blades protruding from the inner periphery of the casing between the partitions at appropriate intervals, a flow path formed on the inner periphery of the casing adjacent to the blade, and the support shaft. A turbine that is formed in the drum and includes an inlet for introducing working fluid into the flow path and an outlet for discharging the working fluid flowing into the flow path to the outside. 17. The turbine according to claim 16, wherein the partition and the flow path have a spiral shape on the inner periphery of the casing. 18. A turbine that uses exhaust gas from an internal combustion engine as a working fluid according to any one of claims 1 to 17, a blower attached to the other end of the rotating shaft of the rotor, and encapsulating the blower, A turbocharger consisting of a blower casing having an inlet for inhaling charged air and an outlet for discharging charged air. 19. The turbine according to claim 18, wherein a part or all of the part constituting the flow path of the turbine is made of one or more of a catalyst material, a material to which a catalyst is attached, and a material containing a catalyst. Turbocharger listed.