JPH11218086A - Vane type fluid machinery - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vane type fluid machinery to rotate a vane without being slidable and free and making contact with a casing and a rotor, and be completely oilless. SOLUTION: A vane type fluid machinery is formed such that a rotary vane 5 is slid with a rotor 4 and a drive torque disc 6 being concentric to each other and further a drive torque disc 6 and the rotor 4 being concentric to each other. and rotation is effected with microgaps (s) and (t) provided between a rotary vane 5 and the inner periphery of a casing and between the rotary vane 5 and the rotor vane groove 4a at any angle. This constitution semipermanently prevents the occurrence of wear since a vane does not slide and ensures clean fluid since no wear powder is generated, reduces the number of parts compared with other fluid machinery having the same performance, and provides a completely oilless vane type fluid machinery, and reduces a cost.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil-free vane type fluid machine used for a blower or a vacuum pump.

[0002]

2. Description of the Related Art In a conventional vane type fluid machine, a rotor eccentric with respect to the center of a casing is rotated in contact with an inner periphery of the casing, and vanes are slidably fitted into a plurality of vane grooves provided in the rotor. Due to the rotation of the rotor, the vane is swung outward by the centrifugal force, and the vane tip rotates together with the rotor while contacting the inner periphery of the casing, enters and exits the vane groove, and forms an arc-shaped suction space. In this configuration, pressure is supplied from the suction side to the discharge side while reducing the volume.

[0003]

In a conventional vane type fluid machine, a vane is slidably fitted into a plurality of vane grooves provided in a rotor, and the centrifugal force generated by the rotation of the rotor causes the tip of the vane to have strength. Slides inside the casing while making contact. Further, the vane slides not only at the vane tip but also with the vane groove, and also slides with the side cover. Therefore, the vanes and the sliding parts wear out early. As a result, the performance and function of the fluid machine itself are constantly reduced. That is, the performance deteriorates early due to wear of the vane and the sliding parts. In addition, driving noise due to the metallic contact is loud, and noise becomes a problem. Furthermore, the structure cannot be operated unless lubricating oil is interposed in all the components.

Further, there is an example in which a self-lubricating material is used as a vane material in order to constitute an oil-free structure. However, in this example as well, the wear of the vane is remarkable not only at the tip but also at the vane side, and the generated clearance is generated. Impulsive noise has also become increasingly loud, necessitating early vane replacement. Along with the decrease in performance, various problems remain, such as wear powder being mixed into the fluid, impairing practical use as oil-free, and increasing maintenance costs.

[0005]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention provides a structure in which a vane is not slidable but is rotated synchronously with a rotor as a rotating vane. The structure in which the periphery rotates without contacting the vane grooves of the rotor, and the structure in which the vanes enter and exit the rotor grooves with the rotation is mechanically configured, and a configuration in which a non-self-lubricating material can be made oil-free is adopted.

[0006]

As described in the means for solving the above-mentioned problems, the end face of the driving torque disk which is fitted and mounted on the sliding inner wall of the rotating vane is fixed to the rotor side wall, and the rotor and the rotation of the driving torque disk are fixed. Accordingly, the rotating vane slides in the radial direction on the side surface of the driving torque disk, and at this time, the vane groove of the rotor and the side surface of the rotating vane are configured to be able to hold a small gap. Further, by the rotating structure of the driving torque disk and the driven torque disk, the tip of the rotary vane can be configured along the inner circumference of the casing with a small gap maintained. The drive and driven torque discs can be perfectly grease-lubricated by using a grease reservoir and high-temperature grease, and the inner periphery of the casing has an X at each rotation angle based on half the length of the rotating vane. , Y points are plotted and connected to form an inner circumference circle,
A uniform gap is maintained between the tip of the rotary vane and the inner circumferential circle at any rotational position, and a smooth rotational motion can be performed while maintaining a state of exerting a sufficient effect on the compression action.

[0007]

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment will be described with reference to the necessary drawings in FIGS. 1 and 2 show an embodiment using a driving torque disk and a driven torque disk according to the present invention. As shown in FIGS. 1 and 2, four rotors are eccentrically mounted on one casing via a two-drive side cover in one casing with a ten-ball bearing and rotatably fitted into a boss portion of the two-drive side cover. ing. The 6-drive torque disk and the 7-drive shaft are integrally formed, and are fixedly fitted to the boss of the 4 rotor by a key. Reference numeral 5 denotes a rotary vane having a sliding surface formed on an inner wall 5b. The rotor 4 has a rotor vane groove 4a having a small gap between the rotary vane 5 and t. The 6-drive torque disc is constructed inside the 5-turn vane by slidingly fitting the 6a drive torque disc side wall. 5d is a sliding end surface of a 6-drive torque disk, and together with a sliding end surface of an 8 driven torque disk of 5e, 1 casing and 5 rotation vanes;
The configuration is such that the minute gap of u is rotated and held in the longitudinal direction of the 4a rotor vane groove of the four rotors. 16, 19 are grease reservoirs,
Reference numerals 17 and 20 denote grease supply holes.

Reference numeral 5a denotes a driven torque disk guide. An 8 driven torque disk is mounted by sliding fitting on the 5c guide sliding surface and the 8a driven torque disk sliding surface. At the rear center point. 9
Is a driven shaft integrally formed with an eight driven torque disk. Next, the rotation operation will be described with reference to FIG. (0 °) In the figure, the 5-turn vane is on the X-ray, and the driven torque disk is on the Y-line. (30 °) In the figure, if the four rotors are rotated 30 ° leftward by the seven drive shafts, the nine driven shafts rotate 30 ° together with the eight driven torque disks about the point A. At this time, since the five-turn vane and the driven torque disc guide 5a are integrally formed, their center line intersections, O in FIG.
The point comes to point D on the R circumference in the (30 °) diagram. That is, point D is the center point of both ends of the 5-turn vane at 30 °. At this time, since the drive torque disk 6 rotates about the point O, the sliding surface of the inner wall 5b and the side wall of the drive torque disk 6a in FIG. 2 slide, and the points A, O, and D secure their respective positions. . Similarly, in the (45 °) diagram, the center of both ends of the five-turn vane becomes the point F on the R circumference and smoothly rotates. In this manner, when the drive shaft is rotated from (60 °) to (150 °), the 5-rotation vane is rotated as shown in FIG. It rotates in a configuration in contact with the inner wall of the casing, and sequentially compresses the arc-shaped suction space. Since the four rotors, the six drive torque discs, and the five-rotation vanes rotate concentrically and synchronously, the minute gap of t with the five-rotation vanes in the 4a rotor vane groove does not change, and therefore, the clearance can be configured to be minimum. . Similarly, since the S minute gaps at both ends of the 5-turn vane do not change at each rotation position, this numerical value can also be configured to the minimum value in rotation. In addition, 16 and 19 grease reservoirs are provided on the 6 drive torque disk and the 8 driven torque disk, and the rectangular portions of both torque disks are grease-lubricated. The grease can be supplied from the end of the 7 drive shafts and the end of the 9 driven shafts. The grease lubrication surface of both torque discs has a low sliding speed on the sliding surface and maintains a wide sliding area, so by supplying grease compatible with high temperature, perfect grease lubrication with less grease consumption is provided. it can. If the five-turn vane is made of an oil-impregnated sintered metal, the reliability of grease lubrication is further increased.

As in the present invention, a configuration in which the fluid is mechanically pumped into and out of the 4a rotor vane groove as a five-rotation vane, and the distance between the tips of the five-rotation vane, that is, the dimension of 2L in FIG. 5, the tip is rotated along the inner circumference of one casing. As shown in FIG. 5, as shown in FIG. A large S gap occurs between the tip of the rotary vane and the inner circumference of the casing, and mechanical performance cannot be maintained. In other words, the inner diameter of the casing cannot be made uniform with a minute gap unless the circular configuration is such that the X and Y points at each rotation angle are plotted and connected based on the tip length of the rotating vane. This drawing method will be described with reference to FIG. 2L around the point O is the total length of the rotary vane in the casing inner diameter direction. If m is the amount of eccentricity between the casing and the rotor, the rotation circumference of the rotary vane is R
Becomes If the rotating vane now rotates by _α゜, the rotating vane center at point O comes to point P. The Z point at that time is msin
_α゜ + L. The W point is obtained by L-msin _α゜. The coordinates X and Y at this time are X _z = (msin _α゜ + L)
cos _α゜, Y _z = (msin _α゜ + L) cos (90
° _- α °) In _{addition, X w = (L-msin} α) cos α °,
Y _w = (L-msin _α °) cos (90 ° - _alpha DEG) and _alpha゜Wo 0.5 ° X for each, if connecting seeking Y coordinate, Q casing inside diameter can be constructed.

[0010]

As described above, according to the present invention, since the rotating vane rotates mechanically, the casing, the tip of the rotating vane, the rotor vane groove and the rotating vane width can be rotated without contacting each other. Each of the gaps t, s, and u can be a minute gap in consideration of a value required for rotation such as expansion. That is, since the engagement can be performed with a small gap, there is no wear of the vane and its corresponding parts. Clean fluid can be used without generating abrasion powder like carbon blades. In addition, rotating vanes can reduce running costs due to their semi-permanent life. The driving and driven torque discs have a large sliding area, so that the friction temperature does not increase, the use of heat-resistant grease does not cause grease to flow out, and the related parts do not deform or wear. Grease can be replenished. The fluid operating section can easily constitute an oil-free vane type fluid machine that is completely lubricated and free of wear powder.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a vane type fluid machine according to the present invention.

FIG. 2 is a sectional view of the vane type fluid machine shown in FIG.

FIG. 3 is an operation explanatory view of the vane type fluid machine according to the present invention.

FIG. 4 is a diagram showing a casing inner diameter machining method of the vane type fluid machine according to the present invention.

FIG. 5 is a diagram showing the inner periphery of a casing and a vane relating to a conventional configuration.

[Explanation of symbols]

Reference Signs List 1 casing 2 driving side cover 3 driven side cover 4 rotor 4a rotor vane groove 5 rotating vane 5a driven torque disk guide 5b rotating vane inner wall sliding surface 5c guide sliding surface 5d driving torque disk sliding end surface 5e driven torque disk sliding End face 6 Drive torque disk 6a Drive torque disk side wall 7 Drive shaft 8 Drive torque disk 8a Drive torque disk sliding surface 9 Drive shaft 10, 13 Ball bearing 15 Suction port 16, 19 Grease reservoir 17, 20 Grease supply hole 21 Discharge port R Rotating vane center circumference m Eccentricity t Vane groove and rotating vane clearance S Casing inner diameter and rotating vane tip clearance u Rotating vane end face and side cover clearance

Claims (3)

[Claims] 1. A casing, a side cover, a rotor and a rotary vane, a drive and a driven torque disk,
The rotor is mounted on the drive shaft eccentrically with the casing,
The rotary vane, which rotates around the drive shaft and is fitted in the vane groove of the rotor, rotates synchronously with the rotor and the drive torque disk around the R circumference having the diameter of the eccentricity m as the rotation center. The inner surface of the rotating vane constitutes a space with both walls as sliding surfaces, and a drive torque disk integrated with the drive shaft is mounted in the space with a sliding surface in a sliding fit, and is driven by the drive torque disk. A vane type fluid machine characterized in that, at each rotation angle constituted by a torque disk, the tip of the rotary vane rotates along the inner diameter of the casing, sucks fluid into an arc space and compresses the fluid. 2. A casing comprising a casing, a side cover, a rotor, a rotary vane, a drive and a driven torque disk, the rotor being eccentrically mounted on a drive shaft, rotating around the drive shaft, and fitted into a vane groove of the rotor. The rotary vane is a vane-type fluid machine configured to rotate synchronously with the rotor and the drive torque disk around the R circumference having the diameter of the eccentricity m as the center of rotation. With reference to the intersection O of the half L and the X and Y lines, the upper arc is X _z = (msin _α ) at each rotation angle on the circumference of R.
{+ L) cos _α゜, Y _z = (msin _α゜ + L) co
X and Y values as s (90 ° _−α゜), and the lower arc _Xw =
(L-msin _α゜) cos _α゜, Y _w = (L-wsi
n _alpha DEG) cos (90 ° - _alpha DEG) and the same X, and plots the Y values, said, connects the plotted casing in vane type fluid machine is characterized in that a circular. 3. A grease reservoir is provided on a driving torque disk and a driven torque disk having a sliding surface fitted with a sliding surface of a guide and an inner space of a rotating vane, and the rotating vane and the two torque disks are slid by grease lubrication. The vane type fluid machine according to claim 1, wherein the vane type fluid machine is configured to move and rotate.