JPH06280758A - Compressor - Google Patents

Abstract

PURPOSE:To reduce size, to provide a high delivery amount, to reduce the generation of vibration, and to facilitate high-precise machining by a method wherein the main part of a compressor comprises outer and inner runners and a compression chamber is formed between the inside of the peripheral wall thereof and an arcuate vane. CONSTITUTION:A main part comprises outer and inner runners 13 and 14. In which case, a partially cylindrical peripheral wall 13c and a tip protrusion part 27 in a semicircular shape in cross section protruded inward in a manner to approach a rotation axis are disposed to the inner runner 13, and a space is formed inside the peripheral wall 13c. Meanwhile, an arcuate vane 25 extending from a fixed axis to the outside is disposed to the inner runner 14 and a compression chamber 24 is formed between the outer runner 13 and the peripheral wall 13c. The volume of the compression chamber 24 is changed along with rotation of the outer runner 13. A delivery port 14b is opened to a portion where a volume is minimized and a suction port 13a is opened to a part of the peripheral wall 13c.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a compressor, and more particularly to a compact compressor having high compression efficiency.
The compressor of the present invention also includes a pump and a vacuum pump.

[0002]

2. Description of the Related Art Conventionally, as a compressor, a reciprocating compressor in which a gas such as a refrigerant gas in the cylinder is compressed by a reciprocating motion of a piston in the cylinder, or a compressor which is biased in a cylinder constituting a casing. A rotary piston compressor or the like is generally known in which a rotary piston mounted with a center is configured to perform a compression action by rotating a constant eccentric path while maintaining contact between the inner surface of the cylinder and the sealing edge of the tip of the slide vane. .

However, in the reciprocating compressor and the rotary piston compressor, since the piston reciprocates or eccentrically rotates in the cylinder, not only becomes a source of vibration and noise but also inertia energy and There is a problem that efficiency is deteriorated due to loss of friction energy.

Therefore, when two scrolls (spirals) are set out of phase with each other by 180 °, one scroll is fixed, and the other scroll is circularly moved, a space formed between the two scrolls is formed. A scroll-type compressor has been developed which compresses a gas such as a refrigerant gas by utilizing the fact that the volume of the space decreases while moving from the outside toward the center.

Since the scroll type compressor has a relatively small fluctuation in driving torque and a gradual fluctuation, not only the operation is smooth and the movement is very quiet, but also the high speed operation is possible and the scrolling is performed smoothly. It is characterized in that very high volumetric efficiency can be obtained because the mutual contact is close to surface contact.

[0006]

However, in the above scroll type compressor, since the two scrolls (fixed scroll and movable scroll) are arranged at positions out of phase with each other, they are formed between the two scrolls. The volume of the space used for compression is relatively small, and the discharge amount of the gas discharged by one orbit of the scroll is small. Therefore, in order to increase this discharge amount, the compressor itself must be upsized. Not only that, but there was also the problem that high-precision machining of the scroll was extremely troublesome.

In view of the above, the present invention makes it possible to obtain a small discharge amount and a large discharge amount while maintaining the advantages of the scroll type compressor, and to easily perform highly accurate machining with less vibration. The purpose is to provide a compressed compressor.

[0008]

In order to achieve the above object, a compressor according to the present invention comprises an outer runner which is rotatable around a rotation axis and is rotationally driven by a drive source.
A main part is constituted by an inner runner that is rotatable about a fixed axis that is eccentric with respect to the rotational axis of the outer runner, and that is inside the outer runner and is driven to rotate around the fixed axis with the outer runner. The outer runner has a partially cylindrical peripheral wall and a tip projection having a semicircular cross section that protrudes inward from the peripheral wall so as to approach the rotation axis, and at least one space is provided inside the peripheral wall. Formed, the inner runner has at least one arcuate vane in the form of an arc plate extending outwardly from its fixed axis, the arcuate vane having an inner surface of a peripheral wall of the outer runner due to the eccentricity. And a rotation chamber of the outer runner so as to rotate together with it while forming a compression chamber between the inner wall of the peripheral wall and the arcuate vane, and thereby the volume of the closed compression chamber to the rotation of the outer runner. Which is configured to vary the discharge port to the position where the volume is minimized, characterized in that the inlet part of the peripheral wall are provided, respectively.

[0009]

According to the present invention constructed as described above, the inner runner is interlocked with the outer runner being rotationally driven to rotate about the eccentric axis in the outer runner. As a result, the volume of the compression chamber formed between the peripheral wall and the arcuate vane gradually changes, and the fluid sucked into the compression chamber from the suction port is compressed in the compression chamber and discharged from the discharge port.

[0010]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 shows a sectional view along the axis of a compressor according to the invention. In the figure, the compressor is generally indicated by reference numeral 1, and the compressor 1 is provided with a rotary drive shaft 3 connected to a motor M as a rotary drive source. The drive shaft 3 has a bearing 4 on the compressor body 2.
Is supported by and is rotatable around the axis F. The compressor body 2 integrally has a cylindrical casing 4 that is concentric with the drive shaft 3. The drive shaft 3 extends near the entrance of the casing 4.

An outer runner 13 is rotatably provided inside the casing 4. The outer runner 13 has a radial disk portion 12, and a cylindrical protrusion 11 is integrally provided on one side in the axial direction thereof, and the cylindrical protrusion 11 is formed on the key 10.
Is connected to the outside of the drive shaft 3. Tubular protrusion 11
Is rotatably supported by a bearing 9 inside the compressor body 2. A seal 8 is provided between the bearing 4 and the bearing 9. Disc portion 12 of outer runner 13
A partial cylindrical peripheral wall 13c, which will be described later, is integrally formed on the opposite side of the cylindrical projection 11.

Inside the outer runner 13, the inner runner 14 is provided.
Is provided. The inner runner 14 has a disc portion 14
a, a wall portion 25 axially extending from the disc portion 14a toward the inside of the outer runner 13, and a boss portion 17 are integrally provided. A cylindrical portion 19 is integrally provided on the disk portion 14a on the side opposite to the wall portion 25 so as to project.

A fixed shaft 20 is fixed to the end plate 4a of the casing 4. The fixed shaft 20 has a flange 20a,
This flange 20a contacts the inner surface of the end plate 4a,
Fixed nut 22 screwed into the outer end of fixed shaft 20
Is fixed in a stationary state. The axis G of the fixed shaft 20 is
It is eccentric with respect to the axis F of the drive shaft 3 by an eccentric amount e. The fixed shaft 20 has a tip portion 20b inserted into a hole in the boss portion 17 of the inner runner 14, and a bearing 26 is interposed between the boss portion 17 and the tip portion 20b. A thrust receiving disk 18 is interposed between the hole of the boss portion 17 and the end surface of the fixed shaft tip portion 20b. An axial passage 20c is formed inside the base of the fixed shaft 20, and a plurality of branch passages 20d are provided near the tip thereof.

A partial cylindrical peripheral wall 13c of the outer runner 13
The space between the inner runner 14 and the wall portion 25 of the inner runner 14 is a compression chamber 24, which will be described later, and the outer runner 13 is formed with a suction port 13a communicating with the inside of the compression chamber 24.
In order to send the fluid to be compressed to the suction port 13a, the casing 4
An intake port 21 is formed in the.

On the other hand, the disk portion 14a of the inner runner 14
Is provided with the same number of discharge ports 14 b as the number of the compression chambers 24 for discharging the compressed fluid compressed in the compression chambers 24. All the discharge ports 14b are normally closed by a leaf spring 23 that functions as a discharge valve. Leaf spring 23
Has a shape in which a plurality of spring pieces are integrally projected radially inward from the ring-shaped main body, and each spring piece
b is closed. The ring-shaped main body of the leaf spring 23 has an annular leaf spring retainer 2 provided inside the tubular portion 19.
It is held by screws 9 through screws 28. The leaf spring retainer 29 is prevented from coming out of the tubular portion 19 by the stopper member 30 and presses the leaf spring 23 against the disc portion 14a so as to close the discharge port 14b. Each outlet 1
4b opens when the pressure in the compression chamber 24 exceeds a specified value, and the leaf spring 23 bends to the left in FIG. 1, so that the compressed fluid flows into the branch passage 2 at a position facing each discharge port 14b.
It is discharged through the passage 20c via 0d.

The details of the outer runner 13 are shown in FIG. 2, the details of the inner runner 14 are shown in FIG. 3, and the state in which the outer runner 13 and the inner runner 14 are combined is shown in FIG. In this embodiment, the thickness t of the partial cylindrical peripheral wall 13c of the outer runner is
To 4 mm (t = 4 mm) and the eccentricity e is 5.5 mm (e = 5.
The inner diameter R1 of the casing 4 to 67 mm (R1 = 6)
7 mm), the number of compression chambers is set to three, which is the most efficient.

That is, a total of three compression chambers 24 are provided inside the peripheral wall 13c of the outer runner 13, and each compression chamber 24 is configured as follows.

First, a first reference circle having a radius R2 (R2 = 10.97 mm) and a radius R3 (R3 = 10.97 + 5.5 + 4 = 20.20) obtained by adding the thickness t to the deviation amount e from this reference circle.
47 mm) second concentric reference circles are drawn, and three intersections A and B of these reference circles and lines drawn through the centers of these reference circles at intervals of 120 ° are obtained.

A semi-circular arc having a radius R4 (R4 = 2 mm) which is half the wall thickness t centering on each intersection point A, and a displacement amount e and half the wall thickness t centering on each intersection point B are added. And a semi-circular arc having a radius R5 (R5 = 5.5 + 2 = 7.5 mm) are drawn in mutually opposite curved lines in opposite directions. Furthermore, the radius R
Radius R6 (R6
= 7.5 × 2 + 2 = 17 mm) is drawn concentrically with the arc having the radius R4 centering on each intersection A, one end of the arc having the radius R5 and the other end having the radius R4 adjacent to the arc. By connecting each of the arcs with a continuous curved line,
The contours of the three compression chambers 24 are determined.

That is, each compression chamber 24 has four arcs smoothly connected to each other in a curved shape, that is, an arc of radius R5 and an arc of radius R6, and two arcs of radius R4 continuous to these arcs. It is defined by the inner wall of the arc. Then, the circular arc portion having the radius R4 is the inward tip projection 27.
(FIG. 4).

A radius R7 is obtained by adding a wall thickness t to the radius R6 concentrically with the arc A having the radius R6.
An arc of (R7 = 17 + 4 = 21 mm) is drawn, and the outer wall of the peripheral wall 13c forming each compression chamber 24 is defined by a plurality of arcs that are smoothly connected in a curved line continuous with the arc.

On the other hand, the wall portion 25 of the inner runner 14 is
As shown in FIG. 3, the arcuate vanes 25 are formed as three arcuate plate-shaped arcuate vanes 25.
Is configured as follows.

First, like the outer runner 13, three reference arcs having a radius R10 (R10 = R2 = 10.97 mm) and three lines passing through the center of the reference arc and drawn at 120 ° intervals from each other. Find the intersection C.

A radius R11 (R11 = R5 =), which is obtained by adding a half of the wall thickness t to the displacement amount e, with each intersection C as the center.
5.5 + 2 = 7.5 mm) and radius R12 (R12 = 7.5 + 4 = 11.5 mm) which is the radius R11 plus wall thickness t
And the arcs of radius R11 and radius R12 adjacent to each other are connected in a continuous curved line,
The contours of the three arc vanes 25 are obtained by connecting the tips projecting from the line drawn at intervals of a radius R13 (R13 = 2 mm), which is half the wall thickness t.

That is, each circular arc vane 25 has three circular arcs smoothly connected in a continuous curved line, that is, a radius R.
It is defined by 11 arcs and an arc of radius R12, and a peripheral wall of an arc of radius R13 connecting the tips of these arcs. More specifically, three semi-circular tubular members having a predetermined width having an inner diameter R11 and a thickness t of 210 ° are arranged at 120 ° intervals from each other, and the tip end portion and the connecting portion are arcuately shaped. By doing so, three arc vanes 25 are formed.

As shown in FIG. 4, the circular arc vanes 25 of the inner runner 14 are positioned in the compression chambers 24 of the outer runner 13, and the center of the outer runner 13 and the center of the inner runner 14 are aligned with each other. Deflection amount e (= 5.5 mm)
By arranging them while shifting them, the positional relationship between the both 13 and 14 is set.

At this time, the outer runner 13 and the inner runner 14
Means that they come into contact with each other at 4 to 5 points over the entire length in the width direction, and the volume partitioned by the contact portions changes continuously.

FIG. 5 shows a planar shape of the compressor constructed as described above.

Next, the principle of the compressor, that is, the principle of compressing and discharging a gas such as a refrigerant gas by the outer runner 13 and the inner runner 14 will be described with reference to the operation cycle diagrams shown in FIGS. 6 to 9. .

First, FIG. 6 shows a state in which gas is sucked into one compression chamber 24. At this time,
The gas introduced into the casing 4 from the suction port 21 provided in the casing 4 is sucked into the compression chamber 24 through the suction port 13a (the gas sucked at this time is in many points). This is the same as below).

In this state, when the outer runner 13 rotates in the direction of arrow K with the rotation of the rotary drive shaft 3 by the motor M, the peripheral wall 13c of the portion marked with arrow K is inward due to the eccentricity of both runners. By pushing the arcuate vanes 25 in contact with each other in the counterclockwise direction in FIG. 6, the inner runner 14 starts to rotate counterclockwise relative to the outer runner 13 and reaches the compression start position (suction end position) shown in FIG. 7. . That is, at this time, a space which is sealed by the inner wall of the compression chamber 24 and the arcuate vane 25 of the inner runner 14 is formed.

When the outer runner 13 further rotates and the inner runner 14 relatively rotates with respect to the outer runner 13, the volume of the sealed space 24 gradually decreases, as shown in FIG. The gas contained in the volume is compressed. That is, the inner runner 14 is replaced by the outer runner 13.
By revolving with respect to each other, each part constituting the inner runner 14 makes an arc motion having a radius of the eccentric amount e, whereby the sealed space 2
The volume of 4 can be gradually reduced.

Due to this compression, the pressure of the sealed gas increases, and when this pressure becomes larger than the elastic force of the leaf spring 23, the leaf spring 23 is displaced and the discharge port 14b is opened.
The compressed gas is discharged from here and discharge is started as shown in FIG. Then, this volume finally becomes zero, and at that time, the compression work in this compression chamber 24 is completed. The phase angle at this time is 205 to 210 °.

The compression work is also performed in the other two compression chambers 24 with the phases shifted by 120 °, and the compression work is sequentially continued as the outer runner 13 rotates. That is, in FIG. 4, one compression chamber 24 (A) indicates the compression start position and the other compression chamber 24 (B) indicates the compression start position.
Indicates the suction position, and the other compression chamber 24 (C) indicates the discharge position after compression. Any part of the outer runner 13 is in contact with the inner runner 14 in any rotational position, and the outer runner 13 always rotates when the inner runner 14 rotates.
Continue to be transmitted to. The rotation of the inner runner 14 by the outer runner 13 should be performed by a proper means for linking the runners 13 and 14 so as to restrain the above-described relational movement of the runners 13 and 14 without direct contact. You can also

In the case of the above-mentioned embodiment, it is possible to obtain a discharge amount which is increased by several percentages per one rotation as compared with the scroll type compressor of the same size.

In the above embodiment, the compression chamber 24
Although three are provided, it is also possible to provide one or two. The compressor can also be used as a pump, in which case the instantaneous discharge rate can be almost the same.

10 to 12 show a second embodiment of the present invention. This embodiment has the same principle as the first embodiment already described, but has a better effect.

FIG. 10 shows a view corresponding to FIG.
In addition, the same parts as those of the first embodiment described above are designated by the same reference numerals and the description thereof will be omitted.

The main difference between the second embodiment and the first embodiment is that, as is apparent from FIG. 10, the width of the circular arc vane 25 of the inner runner 14 is gradually increased from its radial tip toward its center. Is what you are doing. The basic design of the circular arc vane 25 is the same as that described with reference to FIG. 3, but in the case of the second embodiment, the circular arc vane 25 shown in FIG.
By making it thicker toward the center, a shape as shown in FIG. 12 is obtained. By designing the arcuate vanes 25 in this way, the central portion where the arcuate vanes 25 gather becomes thick as a whole, so that a large circular hole 31 can be formed in this central portion. The large circular hole 31 serves as a hole into which the fixed shaft tip 20b shown in FIG. 1 is inserted.

In the second embodiment, the outer runner 13 is shown in FIG.
It is configured as shown in 0. The outer runner 13 can be designed as shown in FIG. That is, after the shape of the inner runner 14 is determined as described above, the inner runner 1 is
The inner surface of the outer runner 13 is defined on the outside of the outer shape of No. 4 by a width corresponding to the eccentric amount e. By defining the shape of the outer runner 13 in this manner, it goes without saying that
The peripheral wall 13c of the outer runner 13 has a non-uniform thickness as shown in FIG. 10, and the thickness gradually increases from the front portion of the protrusion 27 toward the outside. As can be seen from the comparison between FIG. 4 and FIG. 10, there is no fundamental change in the positions of the suction port 13a and the discharge port 14b. Inside the outer runner 13 configured as described above, the inner runner 14 is eccentrically inserted by e as shown in FIG. 10 in a manner similar to that shown in FIG. Similarly, the compression chamber 24 is formed.

In the compressor of the present invention, the inner runner 1
When the axial dimension of 4 is lengthened to a certain extent or more, the axial thrust due to the compressed fluid pressure acting on the disk portion 14a,
The radial force balance due to the compressed fluid pressure acting on the arcuate vanes 25 is broken, and a couple of force is generated between the arcuate vanes 25 of the inner runner 14 and the fixed shaft 20. As a result, the inner runner 14 is moved to the axial line of the compressor. It will rotate while tilting. When this happens, the outer runner 1
Unnecessary friction is generated between the surfaces of the inner runner 3 and the inner runner 14 which face each other, which causes damage.

According to the second embodiment, such a problem is solved. That is, since the circular arc vane 25 of the inner runner is thickened toward the base portion, a relatively large diameter long circular hole 31 for the fixed shaft 20 can be formed in the central portion of the inner runner. Then, by inserting the long and relatively large fixed shaft 20 into this circular hole, all the force exerted on the circular arc vane 25 of the runner by the compression pressure is received by the fixed shaft 20, so that no couple force is generated, and The inner runner 14 operates smoothly. In addition, the axial dimension of the inner runner is fixed to the fixed shaft 2.
Since it can be increased within the range of 0 strength,
It is possible to measure the increase in the discharge amount.

In the state of FIG. 10, the force due to the compression pressure in the lower compression chamber 24 is divided into two parts at the contact points P and Q of the inner runner 14 and the outer runner 13 in FIG. At the contact points P and Q, the inner runner 14 slides by directly contacting the outer runner 13 with the help of lubricating oil. The portion of the contact points P and Q is the place where the fluid leaks most easily, but the sealing property is good because this portion is in sliding contact. In addition, most of the surfaces of both runners have large radii of curvature and have radii of curvature that are close to each other, so there are many parts that are relatively parallel to each other in the vicinity of the near points, and the sealing performance is good with the help of the lubricating oil.

The compressor of the present invention can be an aluminum die-cast product except for the crankshaft, and can be machined to the minimum required.

[0046]

According to the present invention, even though the outer runner and the inner runner are eccentric as described above, since the respective runners themselves have a good rotational balance, the vibration of the compressor can theoretically be zero, and therefore the drive can be performed. Since the torque fluctuation is small and the fluctuation is gradual, not only the operation is smooth and the operation noise is very low, but also high-speed operation can be performed, and the energy loss due to friction is small, so high efficiency is achieved. Obtainable.

Further, since both the outer runner and the inner runner can be formed by a continuous arc-shaped curve, it is possible to easily perform highly accurate machining by keeping the center of each constituent circle accurate. There is.

[Brief description of drawings]

FIG. 1 is an axial sectional view of a compressor of the present invention.

2 is an enlarged end view of the outer runner of the compressor of FIG.

3 is an enlarged end view of the inner runner of the compressor of FIG.

FIG. 4 is an enlarged end view of a state in which the outer runner and the inner runner of FIGS. 2 and 3 are combined.

5 is a plan view of the compressor shown in FIG. 1. FIG.

FIG. 6 is an explanatory view showing a certain operating state of the compressor of FIG. 1.

7 is an explanatory diagram showing a compression start state of the compressor following FIG. 6. FIG.

FIG. 8 is an explanatory diagram showing a compression completed state of the compressor.

FIG. 9 is an explanatory view showing a discharge state of the compressor.

FIG. 10 is a view similar to FIG. 4 showing a second embodiment of the present invention.

FIG. 11 is an end view of the inner runner according to the second embodiment.

FIG. 12 is an explanatory diagram of the design principle of the second embodiment.

[Explanation of symbols]

 1 Compressor 3 Rotational Drive Shaft e Eccentricity M Motor 4 Casing 12 Disk Part 13 Outer Runner 13a Suction Port 13c Outer Runner Peripheral Wall 14 Inner Runner 14a Disk Part 14b Discharge Port 17 Boss 20 Fixed Shaft 21 Suction Port 23 Leaf Spring (Discharge Valve) ) 24 compression chamber 25 arc vane 27 tip projection

Claims (2)

[Claims] 1. An outer runner which is rotatable around a rotation axis and is driven to rotate by a drive source, and a fixed axis which is eccentric to the rotation axis of the outer runner, and is disposed inside the outer runner. The outer runner is composed of an inner runner that is driven to rotate around a fixed shaft center together with an outer runner, and the outer runner has a partially cylindrical peripheral wall and an inner runner that approaches the rotating shaft center from the peripheral wall. Has a semi-circular cross-section tip projection projecting toward
Spaces are formed and the inner runner has at least one arc vane in the form of an arc plate extending outwardly from its fixed axis, the arc vanes being due to the eccentricity, the outer runner. The outer runner is adapted to rotate with the inner surface of the peripheral wall of the outer runner by the rotation of the outer runner, whereby the volume of the closed compression chamber defined by the inner side of the peripheral wall and the arcuate vane is reduced to the outer runner. The compressor, which is configured to change with the rotation of the compressor, has a discharge port at a position where the volume is minimized, and a suction port at a part of the peripheral wall. 2. The inner contour of the peripheral wall and the tip projection of the outer runner and the outer contour of the arcuate vane of the inner runner are separated by a distance corresponding to the eccentricity when both runners are placed concentrically. The compressor according to claim 1, wherein the compressor is configured.