JPS6119802B2 - - Google Patents

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to an axially sliding vane type fluid such as a fluid pressure machine or a fluid prime mover that transmits energy between a rotating machine part and a fluid such as air or oil. Regarding rotating machines.

[Conventional technology]

Generally, a fluid rotary machine has a rotor having a plurality of grooves rotatably inserted in a hollow cylindrical casing.
A plate-shaped vane is slidably mounted in the groove, and most of the vanes have a shape in which the axes of the casing and the rotor are eccentric. However, in this type of rotor, since the fluid pressure acts in a direction perpendicular to the rotor rotational axis, there are certain disadvantages such as bearing wear due to lateral loads and other disadvantages. For this reason, a so-called axial sliding blade type fluid rotary machine has been proposed in which the axes of the casing and rotor are concentric with each other in order to avoid the generation of the above-mentioned lateral load.

FIG. 2 is a partial sectional view showing an example of such an axially sliding vane type fluid rotating machine. In the figure, reference numeral 1 denotes a hollow cylindrical casing, which has a fluid inlet 2 and a fluid outlet 3 on its upper and lower cylindrical surfaces, respectively. A rotor 5 to which a shaft 4 is fixed is arranged concentrically and rotatably within the casing 1. A plurality of (eight) grooves 6 are bored in the rotor 5 in the axial direction, and plate-shaped vanes 7 are slidably accommodated in the grooves 6 . Next 8,9
are cam members having cam surfaces 10 and 11, respectively, and are provided in the casing 1 to face each other with the rotor 5 and the vane 7 interposed therebetween. cam surface 10,
11, as disclosed in Japanese Utility Model Publication No. 35-23855, are each concave and convex in a sinusoidal shape in the circumferential direction, and the distance between them is always kept constant. Both ends of vane 7 are always cam surface 1
0 and 11, the vanes 7 move back and forth in the axial direction in accordance with the rotation of the rotor 5. As a result, the volume of the space formed by the cam surfaces 10 and 11, the inner surface of the casing 1, the rotor 5, the rotating shaft 4, and the vane 7 increases and decreases periodically. The left and right sides of the rotor 5 communicate with the suction port 2 and the discharge port 3 as appropriate.
Side plates 12 and 13 are provided at both ends of the casing 1.

When the fluid rotary machine as described above is used as a compressor or a pump, first, the rotor 5 is rotated via the shaft 4, and the space increases or decreases, so that the fluid is sucked through the suction port 2. It becomes high pressure and is discharged from the discharge port 3. On the other hand, in the case of a fluid motor, the rotor 5 is rotated and the energy of the fluid is transmitted to the rotor 5 based on the inverse relationship described above.

The fluid rotary machine in which the cam curved surface is formed as a sine in this manner is excellent in that the vane can be moved evenly and extremely smoothly in the axial direction.

[Problem that the invention seeks to solve]

However, the axial distance between two sinusoidal surfaces that are 180° out of phase is the same at any point, but when a vane with a certain width touches the two sinusoidal surfaces, the width The larger the gap, the larger the gap will be in some parts. For this reason, it is conceivable to make both ends of the vane 7 sharp as shown in FIG. 3, but these sharp parts are easily worn and cause a leakage phenomenon of high-pressure fluid. Also, as shown in Fig. 4, the vane 7 is divided and a spring 1 is placed between them.
There is also a proposal to interpose a spring 14 and curve both ends of the vane 7 to widen the contact surface with the cam surfaces 10 and 11, but it is necessary that the spring 14 has an expansion force that exceeds the pressure applied to the end surface of the vane 7. Not only that, but also it is not necessarily preferable in terms of preventing fluid pressure from leaking from the high pressure side to the low pressure side via the groove 6.

Therefore, an object of the present invention is to eliminate the drawbacks of the conventional fluid rotary machine as described above, to completely prevent fluid pressure leakage, and to provide an axial sliding mechanism that reduces wear on the sliding portion of the vane. An object of the present invention is to provide an airfoil-type fluid rotating machine.

[Means for solving problems]

The axial sliding vane type fluid rotary machine of the present invention includes a hollow cylindrical casing, a rotor having a plurality of axial first grooves, a rotating shaft of the rotor, and each first groove of the rotor. a pair of cam members each having a cam surface in contact with an axial end of the vane, the vane having curved ends, and the cam surface having a curved surface. It is obtained when the center of the curved surface moves on a periodic curve. It is characterized by being formed by an envelope. The curved surface of the vane end is preferably arcuate, and the periodic curve is preferably a sine curve.

[Effect]

In the present invention, the cam surface is formed by an envelope obtained when the center of the curved surface of the vane end moves along a periodic curve, so the curved end of the vane end slides on the cam surface. They always touch at one point. This can prevent fluid leakage. Furthermore, since the contact points move all over the vane end face, wear on the vane can be minimized.

〔Example〕

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

FIG. 1 shows a cam surface 10 at a position separated by an arbitrary distance in the radial direction from the rotation axis of a fluid rotary machine.
11 is a developed view. The vane 7 has a thickness of t, a distance between center points O and O' of T, and end portions 7a and 7b formed of circular arcs of radius R centered on the center points O and O'. Center point O,
O' moves on sinusoidal curves 15 and 16. Therefore, the axial distance 17 between the sinusoids 15, 16 is always constant with T.

Cam surfaces 10 and 11 are envelopes formed by circles of radius R that move on sinusoidal curves 15 and 16. Although the vane 7 moves on the cam surfaces 10 and 11 having such a shape, the end surfaces 7a and 7b of the vane 7 always touch the envelope lines 10 and 11 at one point. Here, within one rotation of the vane 7 (θ=360°), the vane end face 7
Observe the movement of the points of contact between a, 7b and envelopes 10, 11. Since vane 7 is symmetrical,
Although only the upper end 7a in the figure will be discussed, the same applies to the end 7b. When θ=90°,
Contact point 10a is located at the right end of end surface 7a. θ is 90
When the angle exceeds θ, the contact 10a moves to the left on the end surface 7a, and when θ=180°, the contact 10a moves to the left on the end surface 7a.
Come to the center of a. When θ increases further, contact 1
0a moves to the left and contacts 10 when θ=270°
a reaches the left end of the end surface 7a. When θ becomes even larger, the contact point 10a moves toward the right end. In this way, the end surfaces 7a and 7b of the vane 7 are always connected to the cam surface 1.
0 and 11, but also move all over the end surfaces 7a and 7b, which provides an excellent fluid sealing effect and reduces wear.

The thickness t of the vane 7 should theoretically satisfy the relationship t≦2R.

FIG. 5 is a schematic diagram showing an example of the relationship between the shape of the vane 7 and the cam surface 10. For simplification, the radius of curvature of the end surface 7a of the vane 7 is R, and the thickness t is
It will be 2R. In this embodiment, the radius R increases in proportion to the distance of the center point O from the rotation axis 4a. As a result, the end surface 7a of the vane 7 becomes the cam surface 10.
It is in contact with the radial length. Furthermore, if the end surface 7a of the vane 7 is formed by a rotatable conical roller, there will be no wear when it comes into contact with the cam surface 10. Furthermore, if the intersection angle β between the central axis 20 and the rotational axis 4a is 1/2 (π-α) (α is the apex angle of the conical surface), then the cam surfaces 10 and 11 can be made perpendicular to the rotational axis 4a. I can do it.

〔Effect of the invention〕

With the above configuration, the present invention has the following effects.

(1) Since the end face of the vane and the cam face always touch at one point (a straight line in the radial direction), pressure leakage of high-pressure fluid can be effectively prevented and resistance is minimized. This improves the efficiency of the fluid rotating machine.

(2) Since the contact point between the end face of the vane and the cam surface moves all over the end face of the vane, local wear of the end face can be prevented. This increases the lifespan of the fluid rotating machine.

(3) Since the end face of the vane and the cam face are both curved surfaces, the distance between them narrows relatively gently.
It is easy to form an oil film due to the wedge effect of the oil.

(4) The end face and cam face of the vane have no sharp corners or irregular parts, so machining is easy.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram showing the relationship between a vane and a cam surface, FIG. 2 is a partial sectional view of an axially sliding vane type fluid rotating machine, and FIG. 3 is a schematic diagram showing one aspect of the vane. FIG. 4 is a schematic diagram showing another aspect of the vane, and FIG. 5 is a schematic diagram showing the relationship between the vane and the cam surface. 1: Casing, 5: Rotor, 7: Vane,
8, 9: cam member, 10, 11: cam surface, 15,
16: Sine curve.

Claims (1)

[Scope of Claims] 1. A hollow cylindrical casing, a rotor having a plurality of first grooves in the axial direction, a rotating shaft of the rotor, and a rotor that is slidably accommodated in each of the first grooves of the rotor. In the axially sliding vane type fluid rotating machine, the vane has a pair of cam members each having a cam surface in contact with an axial end of the vane, and the vane has curved ends, and the vane has a curved end. An axial sliding vane type fluid rotary machine, wherein the surface is formed by an envelope obtained when the center of the curved surface moves on a periodic curve. 2. The axial sliding vane type fluid rotary machine according to claim 1, wherein both ends of the vane are arcuate. 3. The axially sliding vane type fluid rotary machine according to claim 1 or 2, wherein the periodic curve is a sine curve.