JPH07185458A - Device for generating low frequency pulsating current - Google Patents

Abstract

PURPOSE:To generate a significant oscillation by driving an oscillator supported by a spring oscillation system using a drive means with low amplitude. CONSTITUTION:An oscillation generating device 1 is connected to a piston rod R1 through a coil spring S1, and the piston rod R1 is connected and firmly fixed to a piston P1 inside a cylinder C1. A coil spring S2 is attached in an aerial direction between the piston P1 and the cylinder C1 to support the piston P1. A spring oscillation system is formed by a mass such as the piston P1 and the rod R1, and the coil spring S2. If the oscillation generating device 1 is driven by an oscillation frequency close to the intrinsic oscillation frequency of the spring oscillation system, the oscillation is transmitted to the rod R1 and the piston P1 through the coil spring S1, and the piston P1 moves back and forth to generate an oscillation to allow a pulsating current to be output from a port H1.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a drying device, a heating device,
The present invention relates to a low-frequency pulsating flow generator used in a peeling / separating device, a cleaning device, a chemical reaction device and the like.

[0002]

2. Description of the Related Art Conventionally, as a low-frequency sound (pulsation of gas) generator, one disclosed in Japanese Patent Publication No. 3-505423 is known. As shown in FIG. 27, the vibrating body is composed of a diaphragm 12 supported by a spring 11, and the diaphragm 12 is reciprocally driven by a plunger 14 driven by an electromagnet 13.
By matching the operation timing of No. 4 with the natural frequency of the spring vibration system including the diaphragm 12 and the spring 11, resonance occurs and low frequency sound can be efficiently generated.

[0003]

However, in the diaphragm drive mechanism of this device, the plunger 14 driven by the electromagnet 13 and the diaphragm 12 are directly connected by the link mechanism 15. Although the link mechanism 15 is made of rubber or the like and has a slight flexibility, the reciprocating movement of the plunger 14 is transmitted to the diaphragm 12 as it is, and the vibration phase of the diaphragm 12 and the reciprocating phase of the plunger 14 are almost the same. Will match.
As a result, if the amplitude of the diaphragm 12 is increased to increase the output, the plunger 1
The stroke of 4 must also be changed to a long one.

Since the amplitude of the diaphragm 12 and the stroke of the plunger 14 are always the same as described above, resonance in the spring vibration system is not sufficiently exerted, so that low frequency sound can be efficiently generated. In this case, there is a usability problem that the usage conditions are limited.
The present invention has been made to solve the above problems,
It is an object of the present invention to provide a low-frequency pulsating flow generator capable of efficiently and efficiently driving a vibrating body supported by a spring vibrating system by a reciprocating actuator regardless of its amplitude.

[0005]

In order to achieve the above object, a first aspect of the present invention is to provide a closed container having a port for intake / exhaust of fluid and having a variable inner volume, and a part of a wall surface of the closed container. The vibrating body to be formed, spring means for connecting the hermetically sealed container and the vibrating body, and the mass of the vibrating body or the hermetically sealed container and the spring means formed by the spring means. In a low-frequency pulsating flow generator including a driving unit that applies force or displacement to a vibrating body or a closed container in a direction in which the volume changes, the displacement of the vibrating body is larger than the displacement given by the driving unit.

A second invention is characterized in that, in the first invention, the closed container is a cylinder and the vibrating body is a piston.

A third invention is characterized in that, in the second invention, both sides of the cylinder divided by the piston are used as hermetically sealed containers and ports are formed in each of them.

According to a fourth aspect of the present invention, in the second aspect, both sides of the cylinder divided by the piston are hermetically sealed containers, and both sides of the piston are supported by piston rods having a hollow structure. It is characterized in that the locating portion is opened to form a pulsating fluid extraction port.

According to a fifth aspect of the present invention, in the second aspect of the invention, both sides of the cylinder divided by the piston are hermetically sealed containers, a part of the piston is exposed to the outside of the cylinder, and the piston communicates with the inside and outside of the cylinder. It is characterized in that a passage is formed to serve as a pulsating fluid extraction port.

A sixth invention is characterized in that, in the second invention to the fifth invention, the pulsating fluid is a gas, and the elasticity is generated by the volume variation of the gas in the cylinder to form a spring means.

A seventh invention is characterized in that, in the first invention, the closed container and the spring means are constituted by a bellows, and a mass for resonance is provided at one end of the bellows.

According to an eighth aspect of the invention, in the seventh aspect, two bellows, each of which has a mass and an outer end portion, are axially connected to each other, and an intermediate connecting portion is axially driven by a drive means. It is characterized by

A ninth invention is characterized in that, in the eighth invention, both outer end portions of the bellows are integrally connected by the same connecting member.

According to a tenth aspect of the present invention, in the eighth aspect of the present invention, two bellows are axially connected to each other with the end portion having the mass inside and the inner end portion has a common structure. The outer end portions are integrally connected by the same connecting member, and the connecting member is axially driven by the driving means.

[0015]

In the first aspect of the invention, the vibrating body or the hermetically sealed container that generates relative displacement with each other is connected to the driving means. As a result, when the driving means reciprocates at a timing corresponding to the natural frequency of the spring vibration system formed by the mass of the vibrating body or the closed container and the spring means connecting them, the force or displacement of the vibrating body or the closed body The vibration is transmitted to the container, resonance is generated in the vibrating body or the closed container, vibrates with an amplitude larger than the displacement of the driving means, and a low-frequency pulsating flow is generated.

In the second aspect of the invention, the closed container is a cylinder and the vibrating body is a piston. By driving one of the cylinder and the piston and leaving the other freely supported, the cylinder and the piston move relative to each other. Then, low frequency pulsating flow is generated.

In the third aspect of the invention, the cylinder is bisected by the piston, and both sides thereof form a closed container and ports are formed in each. Accordingly, when a force or a displacement is applied to either the cylinder or the piston to oscillate the other, low-frequency pulsating flows whose phases are different from each other by 180 degrees are output from both ports.

According to the fourth aspect of the invention, the cylinder is divided into two parts by the piston so that both sides of the cylinder form a closed container.
Both surfaces of the piston are supported by piston rods each having a hollow structure, and portions of both rods located inside and outside the cylinder are opened to serve as pulsating fluid extraction ports. As a result, when a force or displacement is applied to the piston side to vibrate the cylinder, low-frequency pulsating flows whose phases are 180 degrees different from each other are output from both ports.

In the fifth aspect of the invention, the cylinder is bisected by the piston to form a closed container on both sides, and
A part of the piston is exposed to the outside of the cylinder, and a flow path that connects the inside and the outside of the cylinder is formed in the piston to serve as a pulsating fluid extraction port. As a result, when a force or displacement is applied to the piston side to vibrate the cylinder, low-frequency pulsating flows whose phases are 180 degrees different from each other are output from both ports.

In the sixth invention, the pulsating fluid is gas, and the elastic force generated by the compression or expansion of the gas by the movement of the piston in the cylinder acts on the reciprocating piston to serve as spring means. .

According to the seventh aspect of the invention, since the closed container and the spring means are constituted by the bellows and the mass for resonance is provided at one end of the bellows, a spring vibration system is formed in the bellows itself. Low frequency pulsating flow occurs.

In the eighth invention, the two bellows are axially connected to each other with the end portion having the mass as the outer side, and the intermediate connecting portion is axially driven by the driving means, whereby The bellows output low-frequency pulsating flows that are 180 degrees out of phase with each other.

In the ninth invention, since both outer ends of the bellows of the eighth invention are integrally coupled by the same connecting member, the vibrations of the ends of the bellows are surely synchronized.

In the tenth aspect of the invention, two bellows are axially connected to each other with the end portion having the mass inside and the inner end portion has a common structure, and both outer end portions of the bellows are connected. By being integrally connected by the same connecting member, the connecting member is axially driven by the driving means,
Low-frequency pulsating flows whose phases are different from each other by 180 degrees are output from both bellows.

[0025]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a configuration diagram of a first embodiment according to the second invention. In the figure, reference numeral 1 is a vibration generating device which is a drive means, and vertically oscillating is generated by rotating two eccentric rotors in opposite directions. Vibration generator 1
Is connected to the piston rod R1 via the coil spring S1. Piston rod R1 is cylinder C1
It is connected and fixed to the inner piston P1. Piston P
A coil spring S2, which is a spring means, is axially mounted between 1 and the cylinder C1 to movably support the piston P1. A port H1 for taking out the pulsating fluid is formed on the side wall of the cylinder C1 above the piston P1.

In this embodiment, since the cylinder C1 is fixed to the stationary portion G, the mass of the piston P1 and the rod R1 and the coil spring S2 form a spring vibration system. When the natural frequency of this spring vibration system is set in advance to the frequency of the required pulsating flow and the vibration generator 1 is driven at a frequency close to that frequency, the generated vibration causes the rod R1 to pass through the coil spring S1. And it is transmitted to the piston P1 and the piston P1 vibrates reciprocally. As a result, the volume of the cylinder C1 partitioned by the piston P1 periodically changes, and the fluid filled in the cylinder C1 flows in and out through the port H1 to obtain a pulsating flow.

This device comprises a piston P1 and a vibration generator 1
And through the coil spring S1 which expands and contracts in the vibration direction, the piston P is compared with the amplitude of the vibration generator 1 at the time of startup.
Even if the amplitude of 1 is small, it expands over time. In the steady state, the amplitude of the piston P1 can be set to several times to several tens of times the amplitude of the vibration generator 1, and the amount of suction / discharge of fluid from the port H1 can be increased. You can Further, in this device, the coil spring S2 constituting the spring vibration system is a separate body from the piston P1 and the rod R1, and therefore the coil spring S2 can be easily replaced by replacing the coil spring S2 according to the weight of the piston P1 and the rod R1. The constant can be adjusted. Here, two eccentric rotors are used, but one eccentric rotor may be provided if a vertical guide is provided in the vibration generator 1.

FIG. 2 shows a second embodiment which is a modification of the first embodiment shown in FIG. In this embodiment, a coil spring S3 is attached to the inside of the cover portion of the cylinder C1 as a stopper to prevent the piston P1 from increasing in amplitude and crashing into the cover portion of the cylinder C1.

FIG. 3 shows a third embodiment which is also a modification of the first embodiment shown in FIG. In this embodiment, the damper 2 is attached to the inside of the cover portion of the cylinder C1 to prevent the piston P1 from increasing in amplitude and crashing into the cover portion of the cylinder C1.

FIG. 4 is a block diagram of a fourth embodiment according to the third invention. In this embodiment, the piston P2 is integrally supported from both sides by the piston rod R2, and
The piston P2 has coil springs S3 and S4 in the cylinder C2.
Is axially supported by. The cylinder C2, which is divided into two parts by the piston P2, has ports H2 and H3 formed therein, and the lower end thereof is fixed to the stationary fixing part G.

A spring vibration system is formed by the masses of the piston P2, the rod R2 and the like and the coil springs S3 and S4. The natural frequency of this spring vibration system is set in advance to the required frequency of the pulsating flow. Accordingly, when a force or a displacement is applied to the rod R2 in the vertical direction at a timing corresponding to the natural frequency by the driving means (not shown), the piston P
2 vibrates up and down, and pulsating flows having phases different from each other by 180 degrees are output from the ports H2 and H3.

FIG. 5 is a block diagram of a fifth embodiment according to the third invention. In this embodiment, in the fourth embodiment of FIG. 4, the rod R2 is supported by the stationary portion G via the coil spring S5 and the cylinder C2 is free. As a result, a spring vibration system is formed by the mass of the cylinder C2 and the like and the coil springs S3 and S4. The natural frequency of this spring vibration system is set in advance to the required frequency of the pulsating flow. Accordingly, when a force or a displacement is applied to the rod R2 in the vertical direction at a timing corresponding to the natural frequency by a driving unit (not shown), the cylinder C2 vibrates vertically with a larger amplitude than the piston P2, and the port H
Pulsating flows having phases different from each other by 180 degrees are output from 2 and H3.

FIG. 6 is a block diagram of a sixth embodiment according to the third invention. In this embodiment, the coil spring S6 is mounted between the cylinder C2 and the stationary fixed portion G in the fourth embodiment of FIG. 4, and the piston P2 and rod R2 are free. Thereby, the piston P2,
A spring vibration system is formed by the mass of the rod R2 and the coil springs S3 and S4. The natural frequency of this spring vibration system is set in advance to the required frequency of the pulsating flow. Accordingly, when a force or a displacement is applied to the cylinder C2 in the vertical direction at a timing corresponding to the natural frequency by a driving unit (not shown), the piston P2 vibrates up and down with a larger amplitude than the cylinder C2, and the ports H2, H3 Pulsating flows whose phases are 180 degrees different from each other are output.

FIG. 7 is a block diagram of a seventh embodiment according to the third invention. In this embodiment, a piston P2 is axially supported in a cylinder C3 by coil springs S3 and S4 to divide the cylinder C3 into two parts, each of which has a port H.
2, H3 are formed. As a result, the piston P2 and the coil springs S3 and S4 form a spring vibration system. The natural frequency of this spring vibration system is set in advance to the required frequency of the pulsating flow. Thereby, cylinder C
When a force or a displacement is applied in the up-down direction at a timing corresponding to the natural frequency by a driving means (not shown), the piston P2 vibrates up and down with a larger amplitude than the cylinder C3, and the phases from the ports H2 and H3 are 180 degrees. Different pulsating flow is output.

FIG. 8 shows an eighth embodiment which is a modification of the seventh embodiment shown in FIG. In this embodiment, the rod R3 is attached to the center of the cylinder C3 and the piston P3 is attached.
Also, a hole for inserting the rod R3 is formed at the center, and the piston P3 slides on the cylinder C3 and the rod R3 to reciprocate. Further, the lower end of the cylinder C3 and the fixed portion G that does not move.
A coil spring S7 is mounted between and supported by.

As a result, a spring vibration system is formed by the mass of the piston P3 and the like and the coil springs S3 and S4. The natural frequency of this spring vibration system is set in advance to the required frequency of the pulsating flow. Accordingly, when a force or a displacement is applied to the cylinder C3 in the vertical direction at a timing corresponding to the natural frequency by a driving unit (not shown), the piston P3 vibrates vertically with a larger amplitude than the cylinder C3, and the ports H2, H3 Pulsating flows whose phases are 180 degrees different from each other are output.

FIG. 9 is a block diagram of the ninth embodiment according to the fourth invention. In this embodiment, the piston P4 in the cylinder C4 is axially supported by the coil springs S6 and S7, and both sides of the piston P4 are respectively supported by the hollow piston rods R4 and R5. Further, openings H4 to H7 are formed in the portions of the rods R4 and R5 located inside and outside the cylinder C4, respectively.
A spring vibration system is formed by the piston P4, the rods R4 and R5, and the coil springs S6 and S7. The natural frequency of this spring vibration system is set in advance to the required frequency of the pulsating flow.

As a result, when a force or a minute displacement is applied to the rod R4 in the vertical direction at the timing corresponding to the natural frequency by the driving means (not shown), the cylinder C4 vibrates vertically with a larger amplitude than the piston P4. A pulsating flow having a phase difference of 180 degrees is generated on both sides. This pulsating flow is output from the openings H4 and H6 to the outside through the rods R4 and R5 and the openings H5 and H7. In the case of this embodiment, since a port for taking out the pulsating fluid is not formed in the cylinder C4 itself having a large amplitude, accessories such as a waveguide to be connected to the cylinder C4 are unnecessary, and the cylinder C4 vibrates freely. It will be possible. A waveguide can be connected to the openings H5, H7 provided on the side of the rods R4, R5 with small amplitude for use.

FIG. 10A is a block diagram of the tenth embodiment according to the fifth invention. In this embodiment, two cylinders C5 and C6 are coaxially arranged with their openings facing each other, and their both end cover parts are connected by a connecting member 3 to be integrated. A piston P5 is commonly fitted in the cylinders C5 and C6, and both surfaces of the piston P5 are supported by the cylinders C5 and C6 by coil springs S8 and S9. The intermediate portion of the piston P5 is exposed from the cylinders C5 and C6, and the flow paths 4 and 5 are formed between the intermediate portion side surfaces where the piston P5 is exposed from inside the cylinders C5 and C6, and the ends thereof are the ports H8. , H9.

A spring vibration system is formed by the masses of the cylinders C5 and C6 and the coil springs S8 and S9.
The natural frequency of this spring vibration system is set in advance to the required frequency of the pulsating flow. As a result, when a force or displacement is applied to the piston P5 in the vertical direction at a timing corresponding to the natural frequency by the driving means (not shown), the cylinder C5
C6 vibrates up and down with a larger amplitude than the piston P5, and pulsating flows having phases different from each other by 180 degrees are generated in the cylinders C5 and C6, which are output from the ports H8 and H9. When the diameters of the cylinders C5 and C6 are the same, the discharge and suction amount of the fluid is as shown in FIG. 10B, and pulsating flows having the same amplitude but different phases of 180 degrees are generated from the two ports. Further, when the cylinders C5 and C6 have different diameters, FIG.
180 degrees out of phase with two different amplitudes from
Different pulsating flow occurs.

FIG. 11 is a block diagram of the eleventh embodiment according to the sixth invention. In this embodiment, gas is used for the pulsating flow, the piston P2 is integrally supported from both sides by the piston rod R2, and the piston P2 is vertically supported by the air springs S10 and S11 in the cylinder C2. ing. Air springs S10 and S11 here
Is a reaction that occurs when the volume of the gas in the cylinder C2 is compressed or expanded by the movement of the piston P2, that is, the elasticity of the gas is used, and is indicated by a broken line in the drawing. Further, the ports H2 and H2 are provided on both sides of the cylinder C2, which is bisected by the piston P2.
H3 is formed.

The mass of the rod R2 and the piston P2 and the air springs S10 and S11 form a spring vibration system. The natural frequency of this spring vibration system is set in advance to the required frequency of the pulsating flow. Accordingly, when a force or a displacement is applied to the Linda C2 in the vertical direction at a timing corresponding to the natural frequency by a driving unit (not shown), the piston P2 vibrates up and down with an amplitude larger than that of the cylinder C2, and the ports H2, H3. Output pulsating flows whose phases are different from each other by 180 degrees. Further, in this embodiment, since the spring vibration system is formed by using the air springs S10 and S11, the number of spring parts is reduced accordingly, and the device structure is simplified.

FIG. 12 is a block diagram of a twelfth embodiment according to the sixth invention. This embodiment is a rodless embodiment of the embodiment of FIG. 11, and operates in the same manner as the embodiment of FIG. 11 except that the natural frequency of the spring vibration system changes due to the absence of the rod R2.

FIG. 13 is a block diagram of the thirteenth embodiment according to the sixth invention. In this embodiment, gas is used as the pulsating fluid, and the rod R3 is attached to the central axis of the cylinder C3, and a hole for inserting the rod R3 is formed in the center of the piston P3 so that the piston P3 is connected to the cylinder C3. The rod R3 is slid to reciprocate, and is further supported in the vertical direction by air springs S10 and S11. Further, the coil spring S is provided between the lower end of the cylinder C3 and the immovable fixed portion G.
12 is mounted and supported. Also, the ports H are provided on both sides of the cylinder C3, which is bisected by the piston P3.
2, H3 are formed.

These piston P3 and air spring S10,
A spring vibration system is formed by S11. The natural frequency of this spring vibration system is set in advance to the required frequency of the pulsating flow. As a result, when a force or a displacement is applied to the cylinder C3 in the vertical direction at a timing corresponding to the natural frequency by a driving unit (not shown), the piston P3 is moved to the cylinder C3.
Oscillates up and down with a larger amplitude than ports H2, H3
Output pulsating flows whose phases are different from each other by 180 degrees.

FIG. 14 is a block diagram of the fourteenth embodiment according to the sixth invention. In this embodiment, the embodiment shown in FIG. 12 is arranged horizontally and is supported by the stationary portion G via a coil spring S13 for horizontally displacing the left end portion of the cylinder C3. . Thereby, the cylinder C3
When a horizontal force or displacement is applied to the right end portion of the piston, the piston P3 vibrates horizontally with a larger amplitude than the cylinder C3, and pulsating flows having phases different from each other by 180 degrees are output from the ports H2 and H3. In the twelfth embodiment, a spring for holding the weight of the piston and the piston rod by itself and for holding the piston at a predetermined height is actually required due to the vertical arrangement, but in this embodiment, since the horizontal arrangement is provided, the piston is supported. There is an advantage that it works even if there is no spring for it.

FIG. 15 is a block diagram of the fifteenth embodiment according to the seventh invention. In this embodiment, one end of a bellows B1 having elasticity and elasticity in the axial direction is closed by a side plate D1 having a mass, a port H10 is formed at the other end, and a driving rod R6 is provided in a protruding manner. It was done. A spring vibration system is formed by the mass of the side plates D1 and the like and the bellows B1. The mass of the side plate D1 and the spring constant of the bellows B1 are set in advance so that the natural frequency of this spring vibration system becomes the required frequency of the pulsating flow. Accordingly, when a force or a displacement is applied to the rod R6 in the vertical direction at a timing corresponding to the natural frequency by a driving unit (not shown), the side plate D1 vertically vibrates more than the amplitude of the rod R6, and the volume of the cylinder B1 becomes cyclic. Pulsating flow is obtained as the fluid filled in the cylinder B1 flows in and out through the port H10.

FIG. 16 is a block diagram of the sixteenth embodiment according to the seventh invention. In this embodiment, one end of a bellows B2 having elasticity in the axial direction is replaced with a side plate D1 having a mass.
And a port H10 is formed at the other end of the side plate D1.
And a coil spring S14 is mounted in the bellows B2 in the axial direction. These, rod R
7, the mass of the side plate D1, etc., the bellows B2, and the coil spring S14 form a spring vibration system.

The masses of the rod R7, the side plate D1, and the spring constants of the bellows B1 and the coil spring S14 are set in advance so that the natural frequency of this spring vibration system is the required frequency of the pulsating flow. As a result, when a force or a displacement is applied to the upper end of the bellows B2 in the vertical direction at a timing corresponding to the natural frequency by a driving means (not shown), the side plate D1 vibrates vertically and the volume of the bellows B2 changes periodically,
A pulsating flow is obtained as the fluid filled in the bellows B2 comes in and out through the port H10.

FIG. 17 is a block diagram of the seventeenth embodiment according to the eighth invention. This embodiment is constructed by combining two bellows having the same structure as the bellows B1 of the embodiment of FIG. That is, the bellows B3 and B4 are coaxially connected with the common rod R8 inside, side plates D2 and D3 are arranged at both ends, and ports H11 and H12 are formed at the inner ends of the bellows B3 and B4. is there. These one
Mass of pair of side plates D2, D3, etc. and pair of bellows B3, B
4 forms a spring vibration system.

The masses of the side plates D2 and D3 and the spring constants of the bellows B3 and B4 are set in advance so that the natural frequency of this spring vibration system will be the required frequency of the pulsating flow. Accordingly, when a force or a displacement is applied to the rod R8 in the vertical direction at a timing corresponding to the natural frequency by a driving unit (not shown), the side plates D2 and D3 vibrate vertically and the bellows B
The volumes of B3 and B4 change periodically, and the ports H11 and H1
A pulsating flow is obtained when the fluid with which the bellows B3 and B4 are filled in and out from 2 flows in and out.

FIG. 18 is a block diagram of the eighteenth embodiment according to the ninth invention. In this embodiment, the same connecting member 6 is connected to the side plates D2, D3 of the embodiment of FIG.
D3 is integrally fixed. Thereby, the mass of the connecting member 6 is added to the spring vibration system. Also,
During operation, the vibrations of the side plates D2 and D3 are forcibly synchronized, so that the pulsating flows output from the ports H11 and H12 have phases that are exactly 180 degrees different from each other.

FIG. 19 is a block diagram of the nineteenth embodiment according to the ninth invention. This embodiment is a modification of the embodiment shown in FIG. 18, and the connecting member is arranged on the central axis through both bellows B3 and B4. That is, the side plates D2,
The end of the rod R9, which is a connecting member, is connected to the inner side of D3, and the inner ends of the bellows B3 and B4 are penetrated to freely move the end in the axial direction. The operation of this embodiment is the same as that of the embodiment of FIG. 18, but the outer shape can be made smaller by disposing the connecting member as the rod R9 inside the bellows B3, B4.

FIG. 20 is a block diagram of a twentieth embodiment of the tenth invention. This embodiment is a modification of the embodiment of FIG. 18, and the direction of the bellows of the embodiment of FIG. 18 is reversed. That is, a common side plate D4 is arranged in the middle, bellows B5 and B6 are connected to both sides thereof, ports H11 and H12 are formed at the outer ends of the bellows B5 and B6, and the ends are formed by the same connecting member 7. It is fixed integrally. In this embodiment, a spring vibration system is formed by the mass of the side plate D4 and the pair of bellows B5, B6.

The mass of the side plate D4 and the spring constants of the bellows B5, B6 are set in advance so that the natural frequency of this spring vibration system becomes the required frequency of the pulsating flow. Accordingly, when a force or a displacement is applied to the connecting member 7 in the vertical direction at a timing corresponding to the natural frequency by a driving unit (not shown), the side plate D4 vibrates vertically and the volumes of the bellows B5, B6 change periodically. A pulsating flow is obtained when the fluids filled in the bellows B5, B6 flow in and out through the ports H11, H12.

FIG. 21 is a block diagram of the twenty-first embodiment.
In this embodiment, both ends of the cylinder 8 are closed by a pair of diaphragms F1 and F2 having no spring function to form a closed container, a port H13 is formed in the diaphragm F1, and a vibration having a mass at the center of the diaphragm F2. The body 9 is provided. Further, the coil spring S is provided between the diaphragms F1 and F2.
14 is mounted, and a driving rod R10 is projectingly provided outside the center of the diaphragm F1.

In this embodiment, the mass of the vibrating body 9 and the coil spring S14 form a spring vibrating system. The mass of the vibrating body 9 and the spring constant of the coil spring S14 are set in advance so that the natural frequency of the spring vibrating system becomes the required frequency of the pulsating flow. As a result, when a force or displacement is applied to the rod R10 in the vertical direction at a timing corresponding to the natural frequency by a driving means (not shown), the vibrating body 9 vibrates vertically and the inside of the sealed container surrounded by the diaphragms F1 and F2. A pulsating flow is obtained when the volume changes periodically and the fluid filled in the closed container enters and leaves through the port H13.

In this embodiment, when the gas is filled inside, the elasticity of the gas itself can be used instead of the coil spring S14. In addition to the vibration generator 1 for rotating the eccentric rotor shown in FIG. 1, a hydraulic pulsator shown in FIG. 22, a crank mechanism shown in FIG. 23, and a drive mechanism shown in FIG.
4, a cam mechanism as shown in FIG. 4, an electromagnet as shown in FIG.
A piezo element or the like as shown in FIG. 26 can be used. Further, as the spring means in each of the above-described embodiments, a tension coil spring, rubber, an air spring or the like can be used in addition to the compression coil spring used in the embodiments.

Further, in the embodiment of FIGS. 5 to 21, the portion of the port for sucking and discharging the fluid also vibrates,
It is necessary to join the port portion with a flexible waveguide. Then, in order to reduce the vibration of the port portion as much as possible, it is desirable to provide the port at the vibrating portion as in the embodiment of FIGS. 9 to 21. Further, in each of the embodiments described above, the force or the displacement was applied at the timing corresponding to the natural frequency in order to activate the device, but this does not have to be the same interval as the natural frequency, and the natural frequency Resonance can be generated even by intermittent driving if it matches the cycle of an integral multiple of or the vibration phase of the vibrating body.

Furthermore, the low frequency pulsating flow generator according to the present invention is used for heating or humidifying powder or granular material stored in a hopper, silo or the like, in addition to promoting reaction in a drying device or a heating device. It can be used to promote uniform temperature and humidity. Further, it can also be used for the purpose of separating and removing foreign matter such as minute dusts on the surface of a work or in a pipe. Furthermore, it can also be used for electric discharge machining, plating, etc. for uniformization and promotion of machining.

[0061]

As described above, according to the first invention,
By connecting the driving means with the vibrating body or hermetically sealed container that generates relative displacement with each other, when the driving means is actuated at the timing corresponding to the natural frequency, resonance occurs in the vibrating body or hermetically sealed container It vibrates with a larger amplitude than the displacement of the means. As a result, even if the driving means has a small amplitude, it is possible to efficiently reciprocate the vibrating body or the closed container having a large amplitude. As a result, it is possible to generate a pulsating flow efficiently using resonance, versatility,
An easy-to-use low frequency pulsating flow generator can be obtained.

According to the second invention, since the closed container is the cylinder and the vibrating body is the piston, the spring constant of the spring means can be set relatively easily.

According to the third aspect of the invention, the pulsating flows having phases different from each other by 180 degrees can be easily obtained by utilizing the space on both sides of one cylinder partitioned by the piston.

According to the fourth aspect of the invention, since the piston rod has a hollow structure and the pulsating flow is taken out from the piston rod, a pipe for taking out the pulsating flow is unnecessary on the cylinder side. This makes it possible to apply a force or displacement to the piston side and vibrate the cylinder in a completely free state.

According to the fifth aspect of the invention, the piston is exposed to the outside of the cylinder and the pulsating flow is taken out by forming the flow path in the piston itself, so that the pipe for taking out the pulsating flow is unnecessary on the cylinder side. This makes it possible to apply a force or displacement to the piston side and vibrate the cylinder in a completely free state.

According to the sixth aspect of the invention, the elasticity of the gas in the cylinder itself is used as the spring means, so that the structure is simplified.

According to the seventh aspect of the invention, since the airtight container and the spring means are formed of bellows, the structure is simplified.

According to the eighth aspect of the present invention, the two bellows are axially connected to each other with the end portion having the mass on the outside, so that pulsating flows having phases different from each other by 180 degrees can be easily obtained.

According to the ninth aspect of the invention, since both outer end portions of the bellows are integrally connected by the same connecting member,
The vibrations at the ends of both bellows will be synchronized accurately,
Pulsating flows with 0 ° different phases are obtained.

According to the tenth aspect of the invention, the outer end portion is integrally connected with the end portion having the mass inside.
The structure is simplified, and the vibrations of the end portions of both bellows are reliably synchronized, so that a pulsating flow whose phase is exactly 180 degrees different can be obtained.

[Brief description of drawings]

FIG. 1 is a configuration diagram of a first embodiment according to the second invention.

FIG. 2 is a configuration diagram of a second embodiment according to the second invention.

FIG. 3 is a configuration diagram of a third embodiment according to the second invention.

FIG. 4 is a configuration diagram of a fourth embodiment according to the third invention.

FIG. 5 is a configuration diagram of a fifth embodiment according to the third invention.

FIG. 6 is a configuration diagram of a sixth embodiment according to the third invention.

FIG. 7 is a configuration diagram of a seventh embodiment according to the third invention.

FIG. 8 is a configuration diagram of an eighth embodiment according to the third invention.

FIG. 9 is a configuration diagram of a ninth embodiment according to the fourth invention.

FIG. 10 is a configuration diagram of a tenth embodiment according to the fifth invention.

FIG. 11 is a configuration diagram of an eleventh embodiment according to the sixth invention.

FIG. 12 is a configuration diagram of a twelfth embodiment according to the sixth invention.

FIG. 13 is a configuration diagram of a thirteenth embodiment according to the sixth invention.

FIG. 14 is a configuration diagram of a fourteenth embodiment according to the sixth invention.

FIG. 15 is a configuration diagram of a fifteenth embodiment according to the seventh invention.

FIG. 16 is a configuration diagram of a sixteenth embodiment according to the seventh invention.

FIG. 17 is a configuration diagram of a seventeenth embodiment according to the eighth invention.

FIG. 18 is a configuration diagram of an eighteenth embodiment according to the ninth invention.

FIG. 19 is a configuration diagram of a nineteenth embodiment according to the ninth invention.

FIG. 20 is a configuration diagram of a twentieth embodiment according to the tenth invention.

FIG. 21 is a configuration diagram of a twenty-first embodiment related to the present invention.

FIG. 22 is an explanatory view showing another embodiment of the driving means according to the present invention.

FIG. 23 is an explanatory view showing another embodiment of the driving means according to the present invention.

FIG. 24 is an explanatory view showing another embodiment of the driving means according to the present invention.

FIG. 25 is an explanatory view showing another embodiment of the driving means according to the present invention.

FIG. 26 is an explanatory view showing another embodiment of the driving means according to the present invention.

FIG. 27 is an explanatory diagram showing a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Vibration generator 2 Damper 3 Connecting member 4,5 Flow path 6,7 Connecting member 8 Cylindrical 9 Vibrating body B1 to B6 Bellows C1 to C4 Cylinder D1 to D4 Side plate F1 and F2 Diaphragm G Fixed part H1 to H3 Port H4 to H7 Openings H8 to H13 Ports P1 to P4 Pistons R1 to R2 Piston rods R3 Rods R4, R5 Piston rods R6 to R10 Rods S1 to S9 Coil springs S10, S11 Air springs S12 to S14 Coil springs

Claims (10)

[Claims] 1. A closed container having a port for intake / exhaust of fluid, the internal volume of which changes, a vibrating body forming a part of a wall surface of the closed container, and a spring means connecting the closed container and the vibrating body. , At the timing corresponding to the natural frequency of the spring vibration system formed by the mass of the vibrating body or closed container and the spring means,
In a low-frequency pulsating flow generator comprising a driving means for applying force or displacement to the vibrating body or the closed vessel in a direction in which the volume of the closed vessel changes, the displacement of the vibrating body is larger than the displacement given by the driving means. Low frequency pulsating flow generator. 2. The low-frequency pulsating flow generator according to claim 1, wherein the closed container is a cylinder and the vibrating body is a piston. 3. The low frequency pulsating flow generator according to claim 2, wherein a cylinder is divided into two parts by a piston, and both ports are formed as a closed container to form a port in each of them. 4. The low-frequency pulsating flow generator according to claim 2, wherein both sides of the cylinder divided by the piston are sealed containers, and both sides of the piston are supported by piston rods each having a hollow structure and both rods are supported. A low-frequency pulsating flow generator characterized in that a portion located inside and outside the cylinder is opened to form a pulsating fluid extraction port. 5. The low-frequency pulsating flow generator according to claim 2, wherein both sides of the cylinder bisected by the piston are hermetically sealed containers, a part of the piston is exposed to the outside of the cylinder, and the inside and outside of the cylinder are connected to the piston. A low-frequency pulsating flow generator characterized in that a pulsating fluid extraction port is formed by forming a communicating channel. 6. The low frequency pulsating flow generator according to claim 2, wherein the pulsating fluid is a gas, and the elasticity is generated by the volume variation of the gas in the cylinder, and the spring means is used. A low frequency pulsating flow generator characterized in that 7. The low-frequency pulsating flow generator according to claim 1, wherein the closed container and the spring means are constituted by a bellows, and a mass for resonance is provided at one end of the bellows. apparatus. 8. The low-frequency pulsating flow generator according to claim 7, wherein two bellows whose mass-equipped end portions are on the outer side are axially connected, and an intermediate connecting portion is axially driven by a driving means. A low-frequency pulsating flow generator characterized by being driven to. 9. The low frequency pulsating flow generator according to claim 8, wherein both outer ends of the bellows are integrally connected by the same connecting member. 10. The low-frequency pulsating flow generator according to claim 7, wherein two bellows are axially connected to each other with the end having the mass inside and the inner end has a common structure. A low-frequency pulsating flow generator, characterized in that both outer ends of the bellows are integrally connected by the same connecting member and the connecting members are axially driven by a driving means.