JP3567331B2 - Fluid machinery - Google Patents

Description

[0001]
[Industrial applications]
The present invention relates to a fluid machine applied as a compressor, an expander or a pumping machine, and in particular, applies a driving force to a piston for performing a volume change indirectly without directly connecting a connecting rod or a drive shaft to the piston. The present invention also relates to a fluid machine that performs compression or expansion, and a device that enables optimal control of discharge pressure in the fluid machine.
[0002]
[Prior art]
Conventionally, a reciprocating compressor converts the rotation of a crankshaft into a reciprocating motion of a piston through a connecting rod to perform compression by changing the volume between the piston and the cylinder. The variable wings and screws are connected to a drive shaft connected to a motor, and are configured to perform compression while changing the volume formed between the variable wings and screws and the casing by rotation of the drive shaft. I have.
[0003]
In this type of device, a compression leakage prevention member such as a piston ring or an oil seal must be interposed between the drive system and the compression system such as a drive shaft and a connecting rod so that the compression system is directly connected. However, this leads to an increase in the number of parts and weight burden, or an increase in power consumption in proportion to these loads, resulting in a decrease in compression efficiency per input energy.
[0004]
In order to solve such a disadvantage, various reciprocating compressors have been proposed in which a piston drive mechanism employs a linear drive system using an electromagnetic solenoid. (JP-A-61-210576, JP-A-60-116883, etc.)
Japanese Patent Application Laid-Open No. 1-87879 proposes a compressor in which a linear displacement motion is generated by using a superconductor and a magnet to reciprocate a piston.
Each of these technologies employs a configuration in which a coil spring or the like is interposed as a reaction force of an electromagnetic driving force on the piston side, and uses the operation force of the electromagnetic driving force in the compression stroke, and uses the reaction force of the coil spring in the suction stroke. It is configured to perform a reciprocating motion.
[0005]
[Problems to be solved by the invention]
However, since these techniques are all linear reciprocating motions, the transition from the acting force (forward movement) to the reaction force (backward movement) is performed by the elastic force of the coil spring, so basically high speed is achieved. Driving is impossible, and it is impossible to increase the discharge amount per weight or volume.
Further, in the above-mentioned technology, it is difficult to increase the compression ratio because the compression stroke is subjected to the elastic force of the coil spring as it approaches the top dead center.
In addition, using a configuration in which a coil spring or the like is interposed as a reaction force of the electromagnetic driving force on the piston side involves settling of the coil spring and the like, and it is difficult to always obtain a stable compressor for a long period of time.
[0006]
In view of such technical problems, the present inventor has provided a compressor or an expander configured to be able to indirectly drive a piston only by electromagnetic force without using a coil spring together, and to provide a fluid machine applicable as a pump. A plurality of free pistons are arranged in an endless pipe provided with a fluid suction part and a discharge part at appropriate places on the pipe wall, and the pistons are indirectly moved in the pipe using electromagnetic force from outside. While rotating, the specific speed of the preceding piston is changed in accordance with the positions of the suction port and the discharge port to change the closed space formed between the preceding piston and the suction unit and the discharge port. A fluid machine characterized in that the suction stroke-compression or expansion and the pressure-feed stroke-discharge stroke are repeatedly performed in combination with the parts, has been proposed in a concurrently filed patent application (reference number P9364MA).
An object of the present invention is to provide a device suitable for implementing such a fluid machine.
[0007]
[Means for solving the problem]
The present invention is applied to a fluid machine in which the pipe is formed in a ring shape, and a piston in the pipe is configured to be able to orbit by using a magnetic force from the outside,
The rotation center of the magnetic rotating means that rotates while maintaining the magnetic holding force on the piston is set at a position eccentric with respect to the center of the pipeline, and the rotation of the rotating means causes the piston to move in the radial direction of the rotation center. The gist of the invention is that it is configured to be able to go around in the pipe while maintaining the degree of freedom of swinging.
In this case, the magnetic rotating means is provided with a number of magnetic blades radially extending from the rotation center side of the rotating means in a number corresponding to the piston, and the piston follows the rotation of the blade so that the piston is positioned at the rotation center. while swinging in the radial direction have good that orbiting configured to enable the conduit.
Also, the magnetic rotating means is symmetrically arranged on both sides of the piston, and the piston is configured to be able to circulate substantially in a floating state in the pipeline, so that unnecessary rubbing occurs between the piston and the pipeline. No pressure leakage occurs because the piston is not unevenly distributed on one side of the pipe, which is particularly advantageous for an oilless compressor.
[0008]
The second invention is particularly applicable to all of the basic inventions of the above-mentioned simultaneous application, and not only is the pipe formed in a ring shape but also to all endless pipes, and the driving force of the piston is not only magnetic. The present invention is also applied to a device utilizing electromagnetic induction, and particularly aims to provide a fluid machine incorporating a Vi automatic variable device that automatically adjusts an optimal discharge pressure. An opening variable means capable of changing a discharge opening of the discharge section , wherein the variable means is configured to be movable while maintaining a balance between a discharge pressure and a volume space pressure immediately before the discharge port. A slide valve forming a part of a pipe wall immediately before an outlet, and a piston having a cross-sectional area larger than a pressure-receiving cross-sectional area of a discharge pressure of the slide valve is connected to the slide valve. Can be configured to receive space pressure That it obtained and achieved by.
This makes it possible to automatically adjust the optimum discharge pressure by the internal pressure to prevent an increase in power loss due to excessive compression or insufficient compression in the compression process.
[0009]
Incidentally, Japanese Utility Model Laid-Open No. 4-119371 exists as a technique similar to the present invention.
Such a device proposes a compressor in which a plurality of pistons are built in a circular cylinder, a plurality of solenoids are arranged on the outer periphery of the cylinder, and only the piston is rotated slowly and rapidly in a linear manner to suck and compress.
However, the prior art does not disclose how the piston is slowly and rapidly rotated using a solenoid. Particularly, in ON / OFF driving of the solenoid, the piston is driven intermittently, and the specific speed with the preceding piston is reduced. It is impossible to make a continuous orbit while changing.
On the other hand, according to the present invention, the center of rotation of the magnetic rotating means which rotates while maintaining the magnetic holding force on the piston is set at a position eccentric with respect to the center of the pipeline, and the rotation of the rotating means causes the piston to rotate. Can rotate around the inside of the pipe while maintaining the degree of freedom to swing in the radial direction of the center of rotation, so that it can continuously rotate while changing the specific speed with the preceding piston. Therefore, the present invention can be smoothly achieved for the first time.
[0010]
【Example】
Hereinafter, embodiments of the present invention will be illustratively described in detail with reference to the drawings. However, unless otherwise specified, dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention thereto, but are merely illustrative examples. Not just.
First, a basic configuration of the present invention will be described with reference to FIG. First, a plurality (two or more) of free pistons 2 which closely resemble the inner shape of the pipe 1 and have a small clearance around the pipe 1 are arranged in the ring-shaped circular pipe 1 of the casing 11.
Each free piston 2 is configured to be floated by an external force such as a (rotating) magnetic field such as a (rotating) magnetic field and to move within the pipeline 1 at a predetermined position and at a predetermined speed.
For example, the free piston 2 has a built-in magnetic body or magnet body (S pole) 3, respectively, and the free piston 2 is configured to be rotated by the rotational movement of the magnet body (N pole) or the magnetic body 4 from the outside. .
At this time, by shifting the rotation center D of the external magnetic body 4 from the pipe center C, it is possible to change the specific speed between the preceding free piston 2 and the main free piston 2 as described later.
Therefore, in the stroke in which the specific speed of the free piston 2 preceding the free piston 2 becomes 1 or more, the volume (hereinafter, space) formed by the front surface of the free piston 2 and the back surface of the preceding free piston 2 and the wall of the pipe 1 In a process in which the volume 5) is gradually increased and the specific speed becomes 1 or less, the space volume 5 is gradually reduced.
Since the pipe line 1 is endless, the specific velocity is limited across a region (maximum volume region d) where the space volume 5 is maximum and a region (dead volume e) where the space volume 5 is minimum as shown in FIG. The stroke in which the specific speed is equal to or less than 1 and the stroke in which the specific speed is equal to or greater than 1 alternately appear in units of approximately half a revolution.
[0011]
FIG. 4A shows the rotation angle of the piston 2 and the specific speed of each of the preceding piston and the following piston as the speed cycle of each piston. FIG. 4B shows the rotation angle and the ratio between the preceding piston and the following piston. The speed (the ratio between the leading piston speed and the trailing piston speed) is expressed as a specific speed between pistons, and (C) is a diagram showing the change in the rotation angle and the space volume 5 expressed as a volume ratio with respect to the center of space. It is a graph of.
Therefore, as shown in FIG. 1, a suction section is provided in a stroke where the specific speed becomes 1 or more to be a suction stroke a, and a pipeline 1 closed space in which neither a suction section nor a discharge section is provided in a stroke where the specific speed becomes 1 or less. The above mechanism can be applied to a compressor by dividing into a compression stroke b and a discharge stroke c portion provided with a discharge portion.
FIG. 4D is a graph showing the relationship between the main shaft rotation angle and the pressure ratio in such a stroke. As can be understood from this figure, the ratio between the compression stroke b portion and the discharge stroke c portion is appropriately changed. , The compression ratio can be set arbitrarily.
[0012]
FIG. 2 shows an example in which the above mechanism is applied as a non-compressible liquid pump. Basically, there is no compression stroke, and the upstream side is a suction stroke a and the downstream side is a pressure pump with a maximum volume d and a dead volume e interposed therebetween. (Discharge stroke) b.
FIG. 3 shows an example in which the above mechanism is applied as an expander. The maximum volume d is expanded as an expansion stroke b, and a suction stroke a, an expansion stroke b, and a discharge stroke c are provided after the dead volume e.
The present invention will be described in more detail with reference to FIG. 1. In the suction stroke a (opening range of the suction port), the specific speed sequentially increases to 1 or more in the rotation direction of the piston 2 as is apparent from FIG. At the same time, the space volume 5 gradually increases in proportion to this, and the maximum volume of gas can be sucked from the suction portion.
In the compression stroke, as the piston 2 advances in the rotational direction, the specific speed gradually decreases to 1 or less, and in proportion to this, the space volume gradually decreases, and the predetermined space volume 5 is reduced to the discharge portion. FIG. 4D shows a pressure change corresponding to the compression stroke, and it can be understood that the pressure is increased to a predetermined pressure ratio in the compression stroke b.
In the discharge stroke c, the specific velocity of the piston 2 is further reduced, so that the space volume 5 is reduced to about 0, so that the compressed gas can be smoothly discharged from the discharge port.
Therefore, according to the present invention, the suction-compression-discharge process can be continuously and repeatedly performed since the pipe 1 is formed in an endless shape, that is, a ring shape.
The number of pistons 2 may be arbitrarily set according to the capacity per rotation.
[0013]
5 to 7 show a compressor according to an embodiment of the present invention,
5 is a sectional view taken along line AA of FIG. 6, FIG. 6 is a longitudinal sectional view of the compressor main body 10, and FIG. 7 is a direct connection type compressor in which the main body is assembled to a motor.
In FIG. 4, reference numeral 11 denotes a casing formed of a resin body or a non-magnetic metal, and further, graphite or the like. Two casing plates 11A and 11B each having a circular hole 111 formed at a position slightly offset from the center position are provided. A ring-shaped pipe 1 centering on the point C on the surface of the overlapped portion, a suction port 112 at a position corresponding to the suction stroke of the pipe 1, and a discharge stroke A discharge port 113 is formed at a position close to the volume, and the ports 112 and 113 are respectively provided with a discharge hole 113a and a suction hole 112a at positions deviating from the rotation space of the magnetic plate 20 described later.
Eight free pistons 2 each of which is an arc-shaped piece that closely resembles the inner shape of the pipe 1 and has a small clearance around the pipe 1 are arranged in the ring-shaped circular pipe 1.
The free piston 2 is made of a material having good slidability, such as graphite, and has a cylindrical magnetic body or magnet body 2a (S pole) embedded therein.
On both sides of the casing 11, a pair of magnetic plates 20A and 20B rotatably supported by a rotation shaft 12 having a rotation center D at a position vertically displaced from the point C at the center of the pipe 1 by a predetermined distance. It is arranged.
The magnetic plates 20A and 20B have a plurality of blades 21 extending radially from the center of the rotation shaft 12. The number of the blades 21 is equal to the number of the free pistons 2, and is eight at equal angle (45 °) intervals. The free piston 2 may be extended and formed of a magnet having a polarity opposite to that of the free piston 2 (N-pole).
The magnetic plates 20A and 20B are assembled using the spacer portion 12a provided on the rotary shaft 12 so as to sandwich the casing 11 while maintaining a small clearance with respect to the wall surface of the casing 11. In addition, as shown in FIG. 6, only the region where the piston 2 moves in the radial direction may be formed of a magnet.
The rotating shaft 12 is supported at both ends by a support frame 15 via bearings 14, and one end of the rotating shaft 12 is directly connected to a motor 17 via a coupling 16 as shown in FIG.
Reference numeral 18 in FIG. 6 denotes mounting screws for fixing the motor support frame 19 and the compressor main body 10, and integrally connects the bearing support frame 15 on the compressor main body 10 side and the casing 11 via the spacer 19. ing.
[0014]
According to this embodiment, the free piston 2 in which the cylindrical built-in magnet body 2a is embedded is magnetically sandwiched between the blades 21 of the magnetic plates 20A and 20B located on both sides thereof. The clearance between the built-in magnet body 2a and the blade 1 of the magnetic plate 20 is increased by a magnetic force generated between the built-in magnet body 2a and the blade 1 at a predetermined position corresponding to the direction in which the blade 21 extends. It will be in a state of floating.
The magnetic force generated between the two has a degree of freedom in the radial direction along the blade body 21, and the center of the rotating shaft 12 and the center of the pipe 1 are displaced as shown in FIG. When the free piston 2 is rotated, the free piston 2 moves radially along the blade body 21 while being restricted by the pipe in the circumferential direction, and the rotational curvature of the free piston 2 in the pipe 1 may be apparently changed. I can do it.
As a result, as described above, in the suction stroke a, the specific speed gradually increases to 1 or more, and suction can be performed efficiently.
Further, in the compression stroke b after passing through the suction stroke a, the specific volume is gradually reduced at a specific speed of 1 or less, and a compression ratio of a predetermined volume ratio can be obtained while performing a predetermined compression.
Then, in the discharge stroke c, the discharge from the discharge port 113 is completed in a state where the specific speed is further reduced and the space volume 5 becomes zero.
[0015]
FIG. 8 shows another embodiment in which a Vi automatic variable device is incorporated, and the details thereof will be described with reference to FIG.
Reference numeral 31 denotes a slide valve which forms a part of the pipe wall immediately before the discharge port. The discharge start point of the discharge port 113, in other words, the discharge opening volume varies depending on the slide position of the slide valve 31.
The slide valve 31 is connected to a piston 33 via a connecting rod 32.
The piston 33 is housed in a cylinder 35 connected to the volume space 5A by a communication pipe 34 so as to be able to receive the pressure Po 'of the volume space 5A formed between the free pistons 2 immediately before the discharge opening 113, and The pressure receiving cross-sectional area of the piston 33 is set to a cross-sectional area that sufficiently overcomes the friction between the piston 33 and the slide valve 31 and the resistance due to the differential pressure across the slide valve 31.
According to this embodiment, for example, when the discharge pressure Po increases, the differential pressure (Po-Po ') from the volume space pressure Po' increases, and the piston 33 slides toward the back pressure space side of the cylinder 34. On the other hand, the slide valve 31 moves to the discharge side following the movement of the piston 33, causing a delay in the discharge start point. As a result, the space volume between the free pistons 2-2 decreases, in other words, the internal pressure of the space volume 5A decreases. The slide valve 31 moves up to the point where Po '= Po.
On the other hand, when the discharge pressure Po is low, the reverse operation is performed.
As a result, as shown in FIG. 9, the optimum discharge pressure can be automatically adjusted by the internal pressure in order to prevent an increase in power loss due to excessive compression or insufficient compression in the compression process of the fluid machine.
Therefore, according to this embodiment, the above-described operation of the present invention can be smoothly achieved.
[0016]
【effect】
As described above, according to the present invention, it is possible to provide the most suitable device of a fluid machine in which compression or expansion is performed by orbiting a plurality of free pistons in an endless conduit, and in particular, claim 4 In the present invention, it is possible to effectively prevent an increase in power loss due to excessive or insufficient compression in the compression process.
And so on.
Although the present embodiment has been described by exemplifying a compressor, it is easily understood by those skilled in the art that the present invention can be applied as an expander and as a liquid pressure pump as easily understood from the above description.
[Brief description of the drawings]
FIG. 1 shows a basic configuration of the present invention when applied to a compressor.
FIG. 2 is a basic configuration diagram of the present invention and shows a case where the present invention is applied to a liquid pump machine.
FIG. 3 is a basic configuration diagram of the present invention and shows a case where the present invention is applied to an expander.
4 (A) shows the rotation angle of the piston of FIG. 1 and the specific speed of each of the preceding piston and the following piston as the speed cycle of each piston, and FIG. 4 (B) shows the rotation angle, the preceding piston and the following piston. that represents the specific speed between rows piston as a piston between specific speed, (C) is a representation in a volume ratio a change of the rotation angle and the spatial volume 5 on the basis of the space center, FIG. 4 (D) is the spindle rotation angle 7 is a graph showing the relationship between pressure and pressure ratio.
5 to 7 are specific examples for carrying out the present invention, and FIG. 5 is a sectional view taken along line AA of FIG.
FIG. 6 is a vertical sectional view of a compressor body according to the embodiment of the present invention.
FIG. 7 is a direct connection type compressor in which the main body of FIG. 6 is assembled to a motor.
FIG. 8 shows another embodiment that incorporates a Vi automatic variable device capable of automatically adjusting an optimum discharge pressure by an internal pressure to prevent an increase in power loss due to excessive compression or insufficient compression in a compression process.
FIG. 9 is a graph showing the power loss of FIG. 8;
[Explanation of symbols]
112 Suction part 113 Discharge part 1 Endless conduit 2 Free piston 5, 5A Space volume 31 Slide valve 32 Connecting rod 33 Piston

Claims (3)

A plurality of free pistons are arranged in a ring-shaped pipe provided with a fluid suction part and a discharge part at appropriate places on the pipe wall, and the piston can be circulated in the pipe using magnetic force from outside. Fluid machine,
The rotation center of the magnetic rotating means that rotates while maintaining the magnetic holding force on the piston is set at a position eccentric with respect to the center of the pipeline, and the rotation of the rotating means causes the piston to move in the radial direction of the rotation center. And the magnetic rotating means is symmetrically arranged on both sides of the piston, and the piston is substantially suspended in the pipeline. A fluid machine characterized in that it can be rotated around . A plurality of free pistons are arranged in a ring-shaped pipe provided with a fluid suction part and a discharge part at appropriate places on the pipe wall, and the piston can be circulated in the pipe using magnetic force from outside. Fluid machine,
The rotation center of the magnetic rotating means that rotates while maintaining the magnetic holding force on the piston is set at a position eccentric with respect to the center of the pipeline, and the rotation of the rotating means causes the piston to move in the radial direction of the rotation center. Along with being configured to be able to circulate in the pipeline while maintaining the degree of freedom of swinging, magnetic blades extending radially from the rotation center side of the magnetic rotating means are arranged in a number corresponding to the piston, A fluid machine wherein the piston is configured to be able to orbit in the pipeline while swinging in the radial direction of the rotation center following the rotation of the blade body . A plurality of free pistons are arranged in an endless pipe line provided with a fluid suction unit and a discharge unit at an appropriate position on the pipe wall, and the pistons circulate in the pipe line using electromagnetic force from the outside, A fluid machine configured to change a specific speed of a preceding piston in accordance with the positions of the suction port and the discharge port so as to change a volume space formed between the preceding piston and
An opening variable means capable of changing a discharge opening of the discharge unit is provided, and the variable means is configured to be movable while balancing a discharge pressure and a volume space pressure immediately before the discharge opening. A slide valve that forms a part of the pipe wall immediately before, a piston having a cross-sectional area larger than a pressure receiving cross-sectional area of the discharge pressure of the slide valve connected to the slide valve, and a volume space immediately before the discharge port is connected to the piston. A fluid machine characterized in that it can receive pressure .

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