JP2023508892A - vane motor - Google Patents

Abstract

A casing having an inlet and an outlet through which pressure fluid is introduced and discharged, and a rotor that receives the pressure of the pressure fluid in the casing and rotates around a rotating shaft that is placed in the casing. A generally cylindrical main body having a central axis coinciding with the rotation axis, vanes provided in grooves formed on the side surfaces of the main body and projecting from the grooves with varying widths depending on the rotational phase. The rotor is accommodated in the casing, and the vane ends are in contact with the inner wall surface while holding the pressure fluid inside until the pressure fluid introduced through the inlet of the casing is discharged through the outlet of the casing. A vane motor is disclosed, characterized in that it comprises a cylindrical inner cylinder, the center of rotation of which is spaced apart from the axis of rotation, but which is adapted to rotate together with the rotor when it rotates. According to the present invention, in existing vane motors, when the rotor rotates, the ends of the vanes cause friction with the inner surface of the casing, and the inner surface of the casing and the vanes all wear out, requiring frequent replacement and repair. Since the energy consumed by friction is reduced and can be used to generate rotational force, the energy switching efficiency of the vane motor can be improved. [Selection drawing] Fig. 4

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vane motor, and more particularly, to a vane motor capable of generating rotational force through air pressure, which can improve output efficiency.

A vane motor is a mechanical device that converts fluid pressure into rotational power. FIG. 1 shows an example of an existing vane motor.

Here, a rotating rotor is provided in a casing 211, and a part of the casing 211 has a fluid inlet 253 into which a fluid for exerting pressure is introduced and a fluid outlet 255 through which the fluid is discharged. When pressurized fluid is caused to flow into the fluid inlet 253, the fluid pressure extends to the outside of the rotor and acts on the vanes 235 whose extending length is variable. Therefore, the entire rotor rotates within the casing 211 while the vanes 235 move in the pressure direction. When the fluid that has transmitted pressure to the vanes 235 reaches the fluid outlet 255 in the case, it is discharged through the lower pressure fluid outlet 255 .

That is, when the pressurized fluid coming in from the fluid inlet comes into contact with the fluid outlet having a low pressure, it leaves from the fluid outlet and applies pressure to the vanes 235 to rotate the rotor.

At this time, the vanes 235 are coupled to the rotor body 231, and the protruding length of the vanes 235 from the body 231 may be varied. Thus, the vanes 235 may be inserted into the grooves 231a of the rotor body 231 and move longitudinally within the grooves 231a. Since the distance between the inner wall surface of the casing 211 and the rotating shaft 233 of the rotor body 231 varies depending on the position of the inner wall surface of the casing, the majority of the vanes 235 are pulled out of the grooves 231a of the main body 231 and the vanes 235 The protruding length of the vane increases, and at narrower intervals, most of the vane is inserted into the groove of the main body and the protruding length of the vane decreases.

In order for the vane 235 to smoothly move in and out of the groove 231a of the main body 231, an elastic body such as a spring may be included at the bottom of the groove between the vane and the vane. Alternatively, since the vanes may come out of the grooves due to the rotational centrifugal force of the rotor, no separate springs may be provided.

In the section where the distance between the rotor body 231 and the inner wall surface is narrowed, when the rotor body 231 rotates, the end of the vane 235 receives pressure to be inserted into the groove 231a while contacting the inner wall surface. become.

However, in existing vane motors, if the gap between the end of the vane 235 and the inner wall surface of the casing 211 is too large, the fluid will escape through this gap and cause pressure loss. There is a problem that the friction between the vane and the wall surface is severe, a considerable part of the energy due to the fluid pressure is lost due to the friction, and the wear of the vane and the inner wall surface increases replacement and maintenance costs. These problems are in a trade-off relationship and cannot be completely solved by existing vane motors. The most efficient and durable appropriate gap size must be determined experimentally.

In addition, in order to increase the rotational force of the rotor due to the fluid pressure, the total force of the fluid acting on the vanes must be increased. Since it is a value multiplied by the area, it is necessary to increase the area of contact between the vanes and the fluid when the rotor rotates.

However, if the vanes protrude too far from the grooves, they may completely deviate or vibrate or become unstable in the process of rubbing against the inner wall of the casing. It is important to have a design form that increases the area of contact with the fluid within the limits that are maintained.

Korea Registered Patent 10-1116511: Air vane motor with liner Republic of Korea Registered Patent 10-1874583: Vane Motor

SUMMARY OF THE INVENTION It is an object of the present invention to overcome the limitations of existing vane motors described above and to provide a vane motor having a structure with higher efficiency than existing vane motors.

The present invention for achieving the above object is
a casing having an inlet and an outlet through which pressurized fluid is introduced and discharged;
Equipped with a rotor configured to rotate around a rotating shaft installed in the casing under the pressure of the pressurized fluid in the casing,
The rotor is a vane motor having a generally cylindrical body having a central axis coinciding with the rotation axis, and vanes provided in grooves formed in the side surfaces of the body and protruding from the grooves with varying widths according to the rotational phase. in
The rotor is housed in the casing, and the vane ends are brought into contact with the inner wall surface of the casing while the pressure fluid introduced through the inlet of the casing is retained until the fluid is discharged through the outlet of the casing. The center of rotation within the rotor is characterized by having a cylindrical inner cylinder spaced apart from the axis of rotation, but capable of rotating together with the rotor when it rotates.

In the present invention, the center of rotation of the cylinder and the axis of rotation of the rotor in the casing maintain a constant position to reduce the friction between the outer wall surface of the cylinder and the inner wall surface of the casing when the cylinder rotates in the casing. A rolling means may be further provided.

In the present invention, the casing may be configured such that both ends of a cylindrical outer cylinder having a diameter larger than that of the inner cylinder are closed with a disk-shaped closing plate as a whole.

At this time, at least one of the closing plates can be pulled out by the rotating shaft of the rotor to transmit rotational power, and a bearing may be interposed to reduce friction between the rotating shaft and the closing plate.

In the present invention, the closing plate and both ends in the longitudinal direction (rotational axis direction) of the inner cylinder, and the closing plate and both ends of the rotor body and vanes may be provided so as to have fine gaps that allow sliding and prevent pressure fluid from leaking. good.

At least one or both of the closure plates may be provided with inlets and outlets for pressure fluid. In such a case, the inlet and the outlet are provided so that at least a part thereof communicates with the space which is the inner space of the cylindrical inner cylinder and the outer space of the rotor body when viewed from the direction of the rotation axis, and is elongated in the direction of the cylinder. It may consist of an arch shape.

In the present invention, especially when the inlet and outlet are provided to communicate with a space that is inside the cylindrical inner cylinder and outside the rotor body at the same time, it is preferable that the rotor body and the vanes are coupled when viewed from the direction of the rotation axis. At the entrance of the groove, there may be an extension to further expose the vane on the rear side in the direction of rotation so as to communicate with the entrance of the pressure fluid.

At this time, the extensions may be formed at both longitudinal end portions of the rotor, and when viewed in the longitudinal direction, in particular the arcuate inlet is formed such that the extension overlaps from the start of the arcuate inlet. may be

According to the present invention, in existing vane motors, when the rotor rotates, the ends of the vanes cause friction with the inner surface of the casing, and the inner surface of the casing and the vanes all wear out, requiring frequent replacement and repair. Since the energy consumed by friction is reduced and can be used to generate rotational force, the energy switching efficiency of the vane motor can be improved.

FIG. 1 is a perspective view showing an existing vane motor configuration;
FIG. 2 is an external perspective view showing an embodiment of the vane motor of the present invention;
FIG. 3 is an exploded perspective view showing an embodiment of the vane motor of the present invention;
4 is a perspective view of the vane motor showing a state in which the rotor and the inner cylinder in FIG. 3 are assembled;
FIG. 5 is a side view of the assembly of the rotor and the inner cylinder of FIG. 4, viewed from the side;
6 is a perspective side view showing the relative positional relationship between the fluid inlet and outlet of the closing plate and the rotor and the inner cylinder, further combining the closing plate with FIG. 5;
7 is a perspective view showing a rotor body including a rotating shaft of the vane motor of FIG. 3. FIG.

Hereinafter, the present invention will be described in more detail through specific embodiments with reference to the drawings.

Referring to one embodiment of the vane motor of the present invention illustrated in FIGS. 2-7,
First, the overall vane motor 1 comprises a casing forming the outermost shell, a cylindrical inner cylinder 20 and a rotor positioned within the inner cylinder 20 .

The casing includes a substantially cylindrical casing body 11 and closing plates 13 and 15 that close both ends of the body 11 in the longitudinal direction. A rotating shaft 33 connected to a rotor is placed or passes through each of the closing plates. Rotating shaft mounting holes 131, 151, arc-shaped fluid inlets 135, 155 into which external high-pressure fluid is introduced, and arc-shaped fluid outlets 133, 153 through which the high-pressure fluid is discharged are arranged. Bearings 17 are provided in the rotary shaft mounting holes 131 and 151 , and the rotary shaft 33 does not come into direct contact with the closing plates 13 and 15 so that the bearings 17 can reduce friction during rotation.

A cylindrical inner cylinder 20 is provided inside the casing main body 11 . The inner cylinder 20 has substantially the same length as the casing main body 11, and the inner surfaces of the closing plates 13 and 15 of the casing and both ends of the inner cylinder in the longitudinal direction are in contact with each other with fine gaps interposed therebetween to form the casing. As the inner cylinder 20 rotates therein, it may slip against the inner surfaces of the closure plates 13, 15 and cause friction. When installed, the inner cylinder 20 is placed on a plurality of rolling means 19 provided in the inner wall recess 119 of the casing body 11, here the rollers 19a of the rolling base 19b. The rolling base 19b may have a cylindrical shape or a shaft shape, and is parallel to the rotating shaft 33 and rotatably provided. Also, the rotation of the rolling base 19b prevents the occurrence of sliding friction between the inner cylinder 20 and the inner wall of the casing body 11 due to the rotation of the inner cylinder.

A cylindrical rotor body 31 having a rotating shaft 33 and a rotor having vanes 35 coupled to grooves 31 a of the rotor body 31 are provided in the inner cylinder 20 . The length of the cylinder forming the rotor main body 31 is substantially the same as the length of the casing main body 11, and a minute gap is interposed between the inner surfaces of the closing plates 13 and 15 and the both end surfaces of the cylindrical rotor main body 31 when the rotor rotates. Sliding friction is generated while contacting with the

The coupling form of the rotor body 31 and the vanes 35 may be the same as the coupling form of the existing vane motor, and the operation of the vanes 35 in the grooves 31a is well known, so further detailed description thereof will be omitted.

However, here, unlike the existing rotor, the rotor is not provided so as to directly contact the inner surface of the casing body 11, but is provided so as to directly contact the inner surface of the inner cylinder 20.

The rotation axis of the rotor is parallel to the imaginary center axis of rotation of the inner cylinder 20 and is spaced apart by a constant distance. The closure plates 13, 15 of the casing have holes 151, 131 through which the rotating shafts 33 thus provided pass or are locked. The position of the hole is also separated by a constant distance from the imaginary center axis of rotation of the cylinder formed by the casing body 11 .

With such a configuration, the rotor in the casing presses the cylindrical inner cylinder 20 against one side of the casing where the rolling base 19b is located, and rotates between the virtual rotation center axis of the cylinder forming the casing main body and the virtual inner cylindrical cylinder 20. The rotation center axes of are also spaced apart from each other by a constant distance. The distance between the rotor main body 31 and the inner wall surface of the inner cylinder 20 is minimized where the rotor presses against the inner cylinder and the inner wall surface of the inner cylinder 20 becomes the minimum, and the vanes 35 completely enter the grooves 31a. The width protruding from the main body is reduced. On the opposite side (opposite side with respect to the rotation axis), the distance between the rotor main body 31 and the inner wall surface of the inner cylinder 20 is maximum, and the width of the vane 35 protruding from the rotor main body 31 is large.

In such a configuration, the groove 31a may be formed in various forms as desired, and the vanes 35 moving outwardly and inwardly along this groove are perpendicular or constant from the side of the cylindrical rotor body 31. It may protrude in an inclined direction so as to have an angle of In this embodiment, the groove 31a is formed from the side surface of the rotor body 31 over the entire longitudinal direction, and is slightly inclined in the direction of rotation of the rotor at a certain angle with respect to the radial direction about the rotation axis 33. As a result, the vane 35 also protrudes from the side surface of the main body so as to be slightly inclined in the direction of rotation with respect to the vertical direction.

Here, the vanes 35 are provided so as to have a slight gap in the groove 31a, and have a tendency to always protrude outward due to centrifugal force when the rotor rotates. The inner wall surface of the cylinder applies force to the vane 35 in the direction of the groove 31a as the rotor rotates. Therefore, the vane can move outwardly or inwardly along the groove while the rotor rotates, even if an elastic body such as a spring is not provided in the groove.

Considering the action or operation of the constituent elements in the vane motor having such a configuration, first, a feeder (not shown) for supplying high-pressure fluid from the outside is coupled to the inlet of the vane motor. Here, fluid inlets 135, 155 and fluid outlets 133, 153 are formed in all closing plates 13, 15 on both longitudinal sides of the vane motor, so that the high-pressure fluid supply is branched midway to both inlets. Supply high pressure fluid to all. Similarly, the high pressure fluid collector is forked midway to collect the depressurized fluid used by the motor from all of the outlets.

When high-pressure fluid is supplied to the arc-shaped fluid inlets 135 and 155, the high-pressure fluid that has passed through the arc-shaped fluid inlets of the closing plate, as shown in FIG. injected into the space between The pressure of the fluid comes to act on the vanes 35 forming part of the boundary surface of the space. If the pressure acting on the rear face of the vane is higher than the pressure acting on the front face of the vane, the vane will move forward, but the entire rotor on which the vane is mounted is rotatably fixed by the axis of rotation 33, so translational displacement Now only rotates without moving. After the positions of the fluid inlets 135, 155, the space between the rotor and the inner cylinder expands, the vanes 35 also protrude from the grooves 31a to the maximum, and the pressure acting on the vanes gradually increases. An arcuate outlet begins after the maximum spacing position, through which fluid escapes and the fluid pressure is reduced.

In this operation, the rotor of the present invention rotates through the pressure difference without any particular difference from the rotor of the conventional vane motor, but here, instead of the casing, the cylindrical inner cylinder 20 acts on the high-pressure fluid. make space. Since the inner cylinder is not fixed, when the rotor rotates, the rotational force is also transmitted to the cylindrical inner cylinder that is in contact with the end of the vane by friction, and the linear velocity of the inner cylinder is almost the same as that of the rotor. to rotate.

Such rotation of the inner cylinder 20 is performed within the casing body 11, and a rolling means 19 such as a rolling table is provided between the inner cylinder and the casing body to prevent sliding between the inner cylinder and the casing. can reduce the friction caused by

As a result, energy consumption due to abrasion and frictional heat due to sliding between the vanes 35 and the inner wall surface of the inner cylinder 20 is reduced, and the efficiency of generating rotational force by the pressurized fluid is increased while the energy consumption is reduced.

Of course, even in this process, the closing plates 13 and 15 of the casing are stopped, and the cylindrical inner cylinder 20 and the rotor in contact with these closing plates rotate. Both ends slide in contact with the closing plates 13 and 15 to generate frictional heat and consume energy. Of course, in order to further improve the efficiency, the dimensional control and surface control of the closing plate, the rotor body and the vanes must be performed as before, and the bearing 17 between the closing plates 13, 15 of the casing and the rotating shaft 33 should be used to reduce friction.

Although the present invention has been described through limited examples, this is merely an exemplary description to facilitate understanding of the present invention, and the present invention is limited to these specific examples. not.

Accordingly, a person having ordinary knowledge in the field to which the invention pertains can implement various modifications and applications based on the invention, and such modifications and applications are subject to the scope of the appended claims. Naturally, it belongs to the range.

Reference Signs List 11 casing body 13, 15 closing plate 17 bearing 19 rolling means 19a roller 19b rolling base 20 inner cylinder 31, 231 rotor body 31a, 231a groove 31b extension 33, 233 rotating shaft 35, 235 vane 119 inner wall recess 135, 155 , 253 fluid inlet 133, 153, 255 fluid outlet 211 casing

Claims (3)

a casing having an inlet and an outlet through which pressurized fluid is introduced and discharged;
A rotor configured to rotate around a rotating shaft placed in the casing under pressure of the pressurized fluid in the casing,
The rotor includes a generally cylindrical rotor body having a center axis coinciding with the rotation axis, and a groove formed in a side surface of the rotor body. In a vane motor with varying vanes,
The rotor is housed in the casing, and the vane ends are brought into contact with the inner wall surface while retaining the pressure fluid introduced through the inlet of the casing until the pressure fluid is discharged through the outlet of the casing. and the virtual center axis of rotation in the casing is parallel to and separated from the rotation axis, but provided with a cylindrical inner cylinder that can rotate together when the rotor rotates. A vane motor characterized by: The virtual rotation center axis of the inner cylinder and the rotation axis of the rotor in the casing maintain a constant position, and when the inner cylinder rotates in the casing, the outer surface of the inner cylinder and the casing rotate. 2. The vane motor of claim 1, further comprising rolling means to reduce friction with the inner wall surface. The casing is configured such that both ends of a cylindrical outer cylinder having a diameter larger than that of the inner cylinder are closed by disk-shaped closing plates,
At least one of the closing plates has a mounting hole so that the rotating shaft of the rotor can be pulled out to transmit rotational power to the outside, and the mounting hole absorbs friction between the rotating shaft and the closing plate. A bearing is interposed to reduce
Both ends of the closing plate and the inner cylinder in the longitudinal direction, and both ends of the closing plate, the rotor body, and the vanes are provided so as to have fine gaps that are slidable and that pressure fluid is difficult to leak,
At least one or both of the closing plates are provided with an inlet and an outlet for pressure fluid, and the inlet and the outlet are inside the inner cylinder and the rotor when viewed in a side view seen from the direction of the rotation axis. 3. The vane motor according to claim 1, wherein the vane motor is provided in a space outside the main body and has an arcuate shape elongated in the cylindrical direction of the circle formed by the inner cylinder.

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