JP2003343478A - Spiral vortex fluid machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a highly functional spiral vortex fluid machine which has simple structure and a high-performance rotor, no gas leakage at the intake side and can be used as a simple body or a plurality of stages. <P>SOLUTION: Circular inner peripheral surface is formed to a casing communicating to an intake air port and exhaust port. Outer peripheral surface opposing to the inner peripheral surface is provided on the outer peripheral surface of the spiral partition of the rotor. A gas vortex flow path is provided in spiral annular shape in the groove part and many vanes are radially formed in the groove. The spiral partition which completely divides the intake air and the exhaust gas is provided in the groove so that vortex flow generates in the groove, and a stageless and a multistage vortex fluid machine can be formed by laminating in the axial direction. Since new compression structure is simply made at low cost, the high-performance one can be simply manufactured. The spiral structure is the constitution to be made by model casting. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vortex type fluid machine having a rotor configured of radial vanes for pressurizing a gas and maintaining a high compression ratio.

[0002]

2. Description of the Related Art Conventional vortex type fluid machinery is currently
One turn as a commercially available device, one step as shown in FIG.
And there is a configuration as shown in FIG. That is, between the casing 1 and the casing cover 2, the rotor 4 having the radial blades 5 is rotated at a high speed with a small clearance kept between the casing 1 and the casing cover 2.
5, a gas swirl flow path 6 is formed between them, and the blades 5 provided on the rotor 4 are rotated in the gas swirl flow path 6 at high speed so as to pressurize the swirl flow. The gas is pressurized and exhausted from the port 14 to the exhaust port 15. Next, in the structure shown in FIG. 8, in a casing C having an intake port A on one side and an exhaust port B on the other side, a plurality of pump stators D are arranged in the axial direction, between the intake port and the exhaust port. And a plurality of annular gas vortex flow passages E are provided, these gas vortex flow passages E are communicated with each other through a communication passage R, and a pump rotor G having a plurality of discs F is connected to a pump stator D. The blades H, which are rotatably supported inside and are provided on the outer peripheral portion of the disk F, are rotated at high speed in the gas swirl flow path E to pressurize and exhaust gas from the intake port A to the exhaust port B. ing.

Further, the structure shown in FIGS. 9 and 10 has an intake port 14
A circular inner peripheral surface is formed on the pump stator 1A connected to the exhaust port 15, and a small clearance is maintained on the outer peripheral surface of the pump rotor 4 facing the inner peripheral surface so as to continue from the intake port 14 to the exhaust port 15. To form a spiral groove 6 in the spiral groove 6, and while the vortex flow is generated by the blades 5 in the spiral groove 6 by the rotation of the pump rotor 4, the gas sucked into the spiral groove 6 from the intake port 14 is pressurized and exhausted to the exhaust port 15. I am letting you. FIG. 10 shows a state in which the blade 5 is provided in the spiral groove 6, but details of the mounting method are unknown.

[0004]

A fatal problem to be solved in FIGS. 6 and 7 in the structure shown in the prior art will be described. Between the set positions of the intake port 14 and the exhaust port 15, in the casing 1 and the casing cover 2, swirl preventing walls 17 and 17A are provided, and the gas swirl flow passage 6 is provided.
Is not provided. In this structure, the vortex flow is generated between the blade 5 and the gas vortex flow path 6 by rotating at high speed in the arrow direction,
A pressurized fluid is generated in the vicinity of the exhaust port 15 and is pressurized and discharged from the exhaust port 15. The rotor 4 is surrounded by the eddy current blocking walls 17 and 17A that partition the intake and exhaust ports. The space 18 constituted by the thickness of the blades and the blades 5 has a structure in which the pressurized fluid always leaks from the exhaust port 15 side to the intake port 14 and leaks. Due to the pressurized fluid leaking to the intake port 14, the amount of fluid air discharged from the exhaust port 15 is greatly reduced, and the performance is extremely low. Further, due to the presence of the space 18, the pressurizing performance of the fluid machine is deteriorated, and furthermore, the pressurized fluid leaking from the cylinder at the intake port 14 expands to the pressure of the intake port 14 at the position of the intake port 14. As a result, the actual intake air volume at the intake port 14 is also significantly reduced. Further, since the fluid flowing into the intake port 14 due to the cylinder escape leaks to a high temperature due to the pressurization, the temperature rise of the fluid is viciously cycled by this repeated operation, resulting in an extremely high temperature, and the minute clearance causes a trouble such as contact due to a high temperature. Also occurs.

Next, in the structure shown in FIG. 8, a plurality of rotors 4 are laminated while still having the fatal problem of the structure described in FIGS. 6 and 7 in which the pressurized fluid leaks out of the cylinder from the exhaust port to the intake port. The pump rotor G is provided between the pump stator D.
The disc is held and incorporated, and the blades H are arranged in the gas swirl flow passage E provided between the pump stators D, and the fluid compressed in the upper gas swirl flow passage E is supplied to the gas swirl flow passage E. Since the gas flows from the exhaust port to the intake port of the lower gas vortex flow passage E through the communication passage R, the intake and exhaust ports of each of the gas vortex flow passages E are provided close to each other in the circumferential direction. There is. Further, between the suction and exhaust ports in the gas vortex flow path E of each stage, a vortex flow blocking wall that partitions them is provided. Although the communication passage R that connects the gas swirl flow passages E to each other is provided with this configuration as it is, the above-mentioned cylinder escape leak where the pressurized fluid flows to the suction side is the same. Therefore, the structure is complicated as a whole and the driving performance is low, which is a fatal drawback.

Further, since the disk F of the pump rotor G is held between the pump stators D, the pump stator D needs to be formed in a half-split shape, and there is a problem that the structure is further complicated. Further, in order to prevent the pump stator D and the pump rotor G from coming into contact with each other due to thermal expansion, it is necessary to provide a large clearance in the axial direction, but it is difficult to manage the clearance because it is necessary to manage the accumulated clearance of the number of the discs F. There was also.

Next, FIGS. 9 and 10 show a structure in which when a gas swirl flow path is provided at right angles to the axis in a conventional swirl type fluid machine, the harmful effect of the swirl fluid is that various cylinders escape from the exhaust side to the intake side. In order to exclude the gas, the gas swirl flow path 6 having a single thread is constructed and a large number of blades 5 are fitted in the grooves, but it is extremely difficult to configure the blade 5 for the gas swirl flow path 6. . That is, when the blade 5 rotates at high speed, the blade 5 exerts a strong centrifugal force on the blade itself, and the vortex pressure acts on the plane of the blade in the counter-rotational direction of the rotor 4 as an operating reaction force. Therefore, consideration must be given to mounting to withstand these forces. It is conceivable that the blade 5 is formed in an inverted T shape and is screwed to the screw bottom of the gas swirl flow path 6. Although the attachment is performed firmly by this method, the interval between the blades 5 is widened and the required number of blades cannot be secured. This problem is that the required swirl pressure is not generated and the function of the pump cannot be exerted, and the arc of the groove bottom surface cannot be formed, which makes it difficult to generate a swirl flow, which causes a problem.

An object of the present invention is to improve a structure in which a vortex fluid is leaked from an exhaust side to an intake side in a hollow cylinder state by a spiral vortex flow passage and a blade without providing a vortex flow generation space perpendicular to an axis, Even if there are a plurality of stages, an attempt is made to provide a simple structure that prevents leakage of the cylinder in each stage and greatly reduces the number of parts.

[0009]

In order to achieve the above object, according to the present invention, a rotor 4 having a large number of blades 5 on its outer peripheral portion is provided in a casing 1 connected to an intake port 14 and an exhaust port 15.
In a vortex type fluid machine configured to rotate freely, a casing 1 has a circular inner peripheral surface 1A and a rotor 4
While forming the outer peripheral surface of the spiral partition wall 7 facing the circular inner peripheral surface of the casing 1, the spiral partition wall 7 is constituted by one lead by one rotation, and the inter-blade vortex groove 6 is formed at the center of this one lead.
A is constructed, the gas vortex flow passages 6 are provided on both sides of the spiral partition wall 7, and the vanes 5 for causing the vortex are radially formed.
Although the vortex flow generating air space communicating with the intake and exhaust ports is formed through the blades 5, the spiral partition wall 7 does not form the space 18 for leaking air out of the cylinder, which is a drawback of the conventional type. In order to generate a higher compression ratio, the rotors 4 are stacked in a plurality of stages in the axial direction, and the spiral partition wall 7 is formed continuously to form a spiral vortex flow generation air space with a plurality of leads, which serves as an intake port and an exhaust port. And are completely divided. Therefore, the configuration is such that the communication passage R that connects the space 18 where the fluid comes out of the cylinder and each stage is eliminated.

[0010]

The vortex flow generated by the blades 5 in the gas vortex flow passage 6 by the rotation of the rotor 4 described above is completely divided into intake air and exhaust air by the spiral partition wall 7, and the vortex air flows from the intake port 14 to the exhaust port 15. Exhausted. In addition, in the configuration in which the rotor 4 has a plurality of stages, while maintaining a high compression ratio similar to the action of the screw type molecular pump or the axial flow turbo pump, the first stage intake port 14 and the final stage exhaust port 15 are By the gas vortex flow path 6 of the stage,
Although it continuously pressurizes in multiple stages in a spiral shape and communicates with the spiral partition wall 7 through the blades 5, it is possible to continuously pressurize and exhaust without leaking air through the cylinder unlike the conventional type.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The construction and operation will be described with reference to an embodiment shown in FIGS. 1 and 2 show the structure of the spiral vortex type blower having the structure of the present invention, which eliminates the space for leaking air, which is the biggest drawback of the conventional type by one rotation of the rotor 4 and one-step operation, and eliminates the spiral partition wall 7. Completely separate the intake side 14B and the exhaust side 15,
The blades 5 are continuously provided in the gas vortex flow path 6 in a spiral radial manner with a space maintained, and kinetic energy is given as a vortex from the blade 5 to the next blade 5 provided in the spiral by the rotation of the rotor 4.
The configuration is shown in which the intake port 14 and the exhaust port 15 are continuously compressed to a required compression ratio. FIG. 5 shows a spiral vortex type vacuum pump having a structure according to the present invention in which rotors 4 are stacked in five stages, and in the gas vortex flow passages 6 in each stage, the repetitive operation energy due to the space between the blades spirally becomes vortex pressurization. , A structure in which the compression is performed steplessly from the first rotor to the final rotor to a required compression ratio. FIG. 3 shows a one-stage structure, and FIG. 4 shows a rotor structure in which blades are spirally and radially arranged and are laminated in a plurality of stages.

1 and 2, the casing 1 and the casing cover 2 are mounted on the motor 20 while keeping the center thereof. The casing 1 has a circular inner peripheral surface 1A, and the rotor 4 for fitting the outer peripheral surface of the spiral partition 7 so as to face the outer peripheral surface of the spiral partition 7 is fitted to the shaft of the motor 20 while maintaining a small clearance in the circular inner peripheral surface. A gas vortex flow path 6 is provided in the groove formed by the spiral partition wall 7, and the blades 5 are provided on both sides of the spiral partition wall 7 between the blade vortex flow grooves 6A.
Is left and is provided integrally in a radial pattern. A spiral partition 7 is provided on the intake side as an outer peripheral surface facing the circular inner peripheral surface 1A of the casing 1,
The exhaust side is provided so as to be completely separated. The rotor 4 is rotatably provided with respect to the casing 1 and the casing cover 2 while maintaining a small clearance on both sides of the rotor 4. The casing 1 is provided with an intake port 14B, and the casing cover 2 is provided with an exhaust port 15. Inter-blade vortex groove 6A, groove bottom arc 5A,
The outer circumferential arc 5B and 8A indicate the rotor dividing line when the rotor 4 is cast, but the details will be described later.

Next, the rotation operation of FIGS. 1 and 2 will be described.
When the rotor 4 is rotated in the direction of the arrow by the motor 20, the atmosphere is sucked into the casing 1 through the suction port 14 and is sucked into the gas swirl flow path 6 through the suction port 14B of the casing 1.
The sucked air is pressurized and reaches the exhaust side of the spiral partition 7 by the repeated spiral vortex motion of the blades 5. The pressurized fluid does not leak to the intake side because the intake port 14B and the exhaust port 15 are completely separated by the spiral partition 7. In this series of operations, the outer peripheral surface and both side surfaces of the spiral partition wall 7 of the rotor 4 rotate with a minute clearance maintained between the casing 1 and the circular inner peripheral surface 1A and the side surface 1B of the casing cover 2. , Fluid is gas vortex flow path 6
Does not leak to the intake side. Needless to say, the leakage air from the cylinder, which occurs in the conventional type, is completely prevented. The inter-blade vortex groove 6A
Which has a radial vane 5 and is formed into a spiral.
Since the bottom surface of the gas swirl flow path 6 and the inner surface of the outer peripheral surface of the spiral partition wall 7 are respectively provided with arcs 5A and 5B, the swirl flow smoothly occurs. As shown in the arrow in FIG. 1, the vortex flow is generated in the outer peripheral direction to the left and right around the inter-blade vortex flow groove 6A.

In the configuration shown in FIG. 5, the casing 1, the power side cover 2 and the reaction side cover 3 are connected to the motor 2.
The center of the rotor shaft 11 is held at the center of 0. The casing 1 is formed with a circular inner peripheral surface 1A, and the circular inner peripheral surface 1A is fitted in five steps with a small clearance maintained, and the spiral partition walls 7 of the laminated rotor 4 are opposed to each other and fitted to the rotor shaft 11. Fix with clothes, keys, and knock pins. A gas vortex flow path 6 formed in a spiral shape by a spiral partition wall 7 is provided on the outer peripheral portion of the rotor 4 at each stage, and the blades 5 are provided integrally with the rotor 4 in a spiral radial shape leaving a vortex flow space. In the gas vortex flow path 6, a spiral partition 7 is provided up to the outer peripheral surface facing the circular inner peripheral surface 1A of the casing 1 so that the intake side and the exhaust side are completely separated. Rotor 4
In this configuration, the openings of the gas swirl flow passages 6 provided on both side surfaces of the spiral partition wall 7 open to the intake port 14. A plurality of rotors 4 are stacked and fitted in the axial direction, and the spiral partition walls 7 are provided so as to be continuous. The power side cover 2 and the reaction side cover 3 are configured to be rotatable with side surfaces 2B and 3B facing the rotor 4 each having a small clearance. As for the laminated rotors 4, each of the rotors 4 is fixed with the tightening bolts 9, and the key 1
2 and the rotor shaft 11 are fitted and fixed.

Next, the rotation operation of FIG. 5 will be described. Motor 2
The rotors 4 stacked by 0 rotate in the arrow direction. The gas is sucked into the suction space 3A through the suction port 14 and further sucked into the gas swirl flow path 6 through the fluid inlets 4A and 4B of the rotor 4. The gas sucked in the first stage is a spiral blade 5
Due to the repeated and continuous vortex motion due to, the pressure is increased and arrives at the final blade portion 4C on the side surface of the spiral partition wall 7. The pressure-increased gas is further pressurized by two stages from the fluid inlet 4D of the rotor 4 of the second stage to the gas vortex flow path 6 and accelerates the pressurized state to the end vane portion 4E. This operation is repeated for the third, fourth, and fifth rotors 4 to be pressurized to a high pressure and exhausted and held in the exhaust space 2A. If this operation is replaced with a vacuum pump, the intake space 3A
Is capable of maintaining a high degree of vacuum by a series of eddy current pressurizing mechanisms. The circular inner peripheral surface 1A of the casing 1 and the outer peripheral surface of the spiral partition wall 7 of the rotor 4 are held up to the smallest clearance required for rotation, which is the same as the configuration of FIG.

FIGS. 3 and 4 show the shape of the rotor 4 alone, FIG. 3 shows a single-stage type, and FIG. These are formed by high-strength die-casting or equivalent molding. Therefore, it is easy to secure the required inclination of the blades 5 in the rotation direction, and the blade spacing and the spiral structure required for generating the vortex, or the groove bottom arc 5
A and 5B can be arbitrarily configured. The rotor shaft can be fitted with the key groove 12A not only in the direction perpendicular to the axis, but also by positioning the knock pin 10 and firmly fitting and tightening the bolts, one rotor can be firmly constructed even if they are stacked. .

Next, the rotor 4 is formed with a spiral partition wall 7 in a screw shape in which one lead is maintained. Therefore, there remains a problem in molding with this form. Therefore, in FIG. 3 and FIG. 4, in an arbitrary circle D, the direction of the rotor division line 8A is 1
With reference to the semicircular arc surface 13 of the 80 ° semicircle, the points a, b, c, d, e, and a ′ that form the rotor dividing line 8A,
A method of tightening and fixing a rotor-adapter 8 and two pieces of cast molding, which are divided by a 180 ° line passing through b ′, c ′, d ′ and e ′, and the rotor 4 main body with a plurality of tightening bolts 8B. If the above is adopted, the rotor 4 shown in FIGS. 3 and 4 can be molded without difficulty, and the functioning rotor 4 is obtained.

[0018]

As shown in the description of the gist of the conventional single-rotation, single-stage vortex type fluid machine shown in FIGS.
In the space of the vortex block wall that divides the intake and exhaust ports in the configuration of the gas vortex flow path, the vortex-pressurized fluid leaks to the intake side due to a hollow cylinder, the pressure rise is insufficient, the exhaust air volume drops, and the exhaust temperature There are many fatal problems such as high temperature. In FIG. 8, the configurations of FIG. 6 and FIG. 7 are stacked to form a multi-stage structure, but the fatal drawbacks described above are still left in the product structure, so the major drawbacks are doubled to function as a pump. Can not.

In the spiral vortex type fluid machine according to the present invention, however, the gas vortex flow path 6 housing the blades 5 has the spiral partition wall 7 of the rotor 4, the casing 1, and the circular inner peripheral surface of the casing cover 2. In the spiral volume surrounded by the side surface and the side surface, the structure enables spiral vortex pressure, and
Since the hollow space like the above-mentioned conventional type is eliminated and the intake and exhaust ports are completely separated by the spiral partition wall 7, the pressurized fluid does not leak to the intake side and becomes a spiral vortex flow. Since the air moves from the intake side to the exhaust side in the axial direction, overall leakage is small and high efficiency can be maintained. In addition, as shown in FIG. 5, the multi-layered structure having three layers and five layers has a simple structure, so that the structure is simple and the cost can be reduced. High vacuum, high pressure and low cost can be realized.

[0020]

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a one-stage spiral vortex flow type fluid machine of the present invention.

FIG. 2 is a cross-sectional view of the one-stage spiral vortex type fluid machine of the present invention.

FIG. 3 is a front view of a rotor of the spiral vortex type fluid machine of the present invention.

FIG. 4 is a partial cross-sectional configuration diagram of a rotor of a spiral vortex type fluid machine of the present invention.

FIG. 5 is a vertical cross-sectional view of a multi-stage spiral vortex flow type fluid machine of the present invention.

FIG. 6 is a vertical cross-sectional view of a conventional one-stage vortex type fluid machine.

FIG. 7 is a cross-sectional view and outline drawing of a conventional one-stage eddy current type fluid machine.

FIG. 8 is a vertical cross-sectional view of a conventional multistage vortex type fluid machine.

FIG. 9 is a vertical cross-sectional view of a conventional spiral vortex type fluid machine.

FIG. 10 is a cross sectional view of a spiral groove of a conventional spiral vortex type fluid machine.

[0021]

[Explanation of symbols]

1 ………… Casing 1A ………… Casing circular inner peripheral surface 2 ………… Casing cover 3 ………… Anti-power side cover or power side cover 4 ……… Rotor 5 ……… Blades 5A, 5B ……… Groove bottom,
Circumferential arc 6 ... Gas vortex flow path 6A ...... Vortex vortex groove between blades 7 ...... Helical partition 8 ...... Rotor adapter 8A ...... Rotor dividing line 9 ...... Connection bolt 9A ...... Bolt tap hole 9B ......... Bolt hole 11 ......... Rotor shaft 12 ......... Rotor shaft key 13 ......... Semi-circular surface (rotor) 14 ......... Intake port 15 ......... Exhaust port 16 ......... Coupling 20 ... …motor

Claims (2)

[Claims] 1. A vortex type fluid machine in which a rotor 4 having a large number of blades on its outer periphery is rotatably supported around a motor in a casing 1 having an intake port 14 and an exhaust port 15, and an axial direction is provided in the casing 1. A circular inner peripheral surface 1A having a length, and a spiral partition wall 7 formed on the rotor 4, and the spiral partition wall 7 of the rotor 4 has a circular inner peripheral surface 1A.
The casing 1 and the casing cover 2 are formed such that the outer peripheral surfaces facing each other are formed with a minute clearance, and the side surfaces 1B of the rotor 4 are also opposed to the inner surface with a minute clearance.
The spiral swirl partition 7 is provided with gas swirl flow paths 6 on both outer peripheries, and an inter-blade swirl groove 6A is provided in the axial center between the spiral partition 7 and a large number of radial blades are provided on both sides of the spiral partition 7. 5, the intake port 14B provided in the casing 1 and the exhaust port 15 provided in the casing cover 2 are separated by the spiral partition 7, and the rotation of the rotor 4 causes the gas swirl flow path 6 and the blade gap to be separated from each other. A spiral vortex type fluid machine characterized in that a structure for generating a vortex and pressurizing the sucked fluid is provided in the vortex groove 6A, the groove bottom arc 5A and the outer peripheral arc 5B provided on the blade 5. 2. A vortex type fluid machine in which a rotor 4 having an intake port 14 and an exhaust port 15 and having a large number of blades in the outer peripheral portion is rotatably supported around a motor in a casing 1. A circular inner peripheral surface 1A having a length extending in the direction is formed, and a spiral partition wall 7 is formed in the rotor 4, and a small clearance is formed in the circular inner peripheral surface 1A of the casing 1 in the spiral partition wall 7 of the rotor 4. With the outer peripheral surfaces facing each other, the gas swirl flow paths 6 are provided on both outer peripheries of the spiral partition wall 7, and the inter-blade swirl groove 6A is formed in the axial center between the spiral partition walls 7. A large number of blades 5 are radially formed on both sides, a plurality of rotors 4 are provided in the axial direction, each spiral partition wall 7 is continuous, and the side surface 3B of the first-stage rotor 4 and the side surface 2B of the final-stage rotor 4 are also minute gaps. With the inner surfaces facing each other A power side cover and a reaction side cover are attached, and each rotor 4 is integrated with the rotor shaft 11 and the connecting bolt 9. The fluid sucked from the intake port 14 by rotating the rotor 4 is A gas vortex flow path 6, an inter-blade vortex flow groove 6A connected by a partition wall 7, a vortex flow is generated in the groove bottom arc 5A and the outer peripheral arc 5B provided in the vane 5, and the vortex flow is communicated in series and continuously. A spiral vortex type fluid machine characterized by being configured to continuously pressurize.