KR102491036B1 - vane motor system - Google Patents

Abstract

Disclosed is a vane motor system characterized in that a plurality of vane motors are arranged in series and the rotor rotation shafts are arranged on a straight line to rotate together or to be shared. The sharing of the rotor axis of rotation may be fixed or variable, and for example, the rotor and the axis of rotation of the rotor may be formed in a one way clutch method.
According to the present invention, it is possible to provide a vane motor assembly that has a configuration with higher installation efficiency than conventional simple vane motors and can provide power with high efficiency ranging from small output to large output according to circumstances.

Description

Vane motor system {vane motor system}

The present invention relates to a vane motor, and more particularly, a vane motor capable of generating rotational force through pneumatic pressure, which can increase placement efficiency or operational efficiency when the surrounding space is limited or a wide output range is required. It is about the motor system configuration.

A vane motor is one of the mechanical devices that convert gas pressure into rotational power. 1 shows an example of a conventional vane motor.

Here, a rotating rotor is installed in the casing 211, and a portion of the casing 211 has a gas inlet 253 through which gas for applying pressure is introduced and a gas outlet 255 through which gas is discharged. When the pressure gas is introduced into the gas inlet 253, the gas pressure extends to the outside of the rotor and acts on the vane 235 whose extending length is variable. Accordingly, while the vane 235 moves in the pressure direction, the entire rotor rotates within the casing 211 . When the gas that has passed the pressure to the vane 235 reaches the gas outlet 255 of the case, it is discharged through the gas outlet 255 having a low pressure.

That is, when the pressure gas entering the gas inlet encounters the gas outlet having a low pressure, it exits through the gas outlet and in the process applies pressure to the vanes 235 to rotate the rotor.

At this time, the vane 235 is coupled to the rotor body 231, and the length of the vane 235 protruding from the body 231 may be variable. To this end, the vane 235 is inserted into the groove 231a of the rotor body 231 and may move in the longitudinal direction of the groove 231a. Since the distance between the inner wall surface of the casing 211 and the rotating shaft 233 of the rotor body 231 is different depending on the position of the inner wall surface of the casing, in a place where the distance is wide, a large portion of the vane 235 is the groove of the body 231 ( 231a), the protruding length of the vane 235 increases, and most of the vane is inserted into the main body groove where the gap is narrow, so the protruding length of the vane decreases.

In order for the vane 235 to smoothly enter and exit 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 235. Alternatively, a separate spring may not be installed because the vane may come out of the groove by the rotational centrifugal force of the rotor.

In a section where the gap between the rotor body 231 and the inner wall surface is narrowed, when the rotor body 231 rotates, the end of the vane 235 comes into contact with the inner wall surface and receives pressure to be inserted into the groove 231a.

Vane motors of this configuration are installed and used according to various situations as needed. In order for the vane motor to be used, the place of use must be where high-pressure gas can be used, and the output of the vane motor is highly dependent on the size of the vane motor and the amount and pressure of the supplied pressure gas.

However, there are cases where a vane motor needs to be used and can be used, but it is difficult to supply sufficient output through one large vane motor because the installation space is narrow compared to the output.

In addition, it is difficult to provide all the corresponding outputs with one vane motor due to the large change in required output. However, when the size of the vane motor is increased, it is rather difficult to control the output through the vane motor when a small output is requested, and the output efficiency Falling problems can also occur.

Therefore, in the case of using a vane motor, it is necessary to consider the increase in overall and general efficiency and to cope with these problems.

On the other hand, in order to increase the efficiency of the vane motor, it is necessary to obtain more output with a smaller amount of gas when supplying the same pressure of gas, and in the case of a mobile device, it is more important to obtain more output with the same amount of air. .

In order to increase efficiency, as mentioned above, the pressure gas supplied to the inside does not apply sufficient pressure to the vane and meets the outlet early and is released, or leaks undesirably through a gap, or occurs between a moving part and a fixed part adjacent to it. Although it is generally considered to reduce friction, it is necessary to develop a path and configuration for the pressure gas to act on the vane so that the pressure acts on the vane efficiently and the driving force or impact of the gas acting on the vane works efficiently. there is

Korean Registered Patent No. 10-1116511: Air vane motor with liner Korean Registered Patent No. 10-1874583: Vane Motor Republic of Korea patent application 10-2019-0171084: vane motor

An object of the present invention is to provide a vane motor system having a configuration with higher installation efficiency than the conventional one by overcoming the above-described difficulties in installation of the conventional vane motor.

An object of the present invention is to provide a vane motor system capable of providing power with high efficiency from a small output to a large output according to circumstances.

An object of the present invention is to provide a vane motor system capable of a layout configuration suitable for an installation environment even when a relatively large output is required and the installation space is limited.

The vane motor system of the present invention for achieving the above object is characterized in that a plurality of vane motors are arranged in series and the rotor rotation shaft is arranged on a straight line to rotate together or to be shared.

In the present invention, the sharing of the rotor rotational axis may be made of fixed.

At this time, the rotor and the rotor rotation shaft of the multi-vane motor are made of a one-way clutch method, so that when the rotor rotates, the rotational force of the rotor can be transmitted to the rotor rotation shaft, and the rotor does not rotate only by the rotation of the rotor rotation shaft. It may have been made so that

According to the present invention, a detachable device, for example, a clutch, capable of connecting and selecting between the rotor rotational axes of the plurality of vane motors may be installed so that the rotational axis of the rotor can be shared as needed.

In the present invention, the plurality of vane motors may be vane motors that can be replaced with each other having the same configuration, or may be vane motors having different configurations. At this time, the different configurations may include motors with different outputs as well as different structures, and the different structures may include rotor configurations or phases, the number of inlets of pressure gas, and the remaining vanes in one or more of shapes or positions. It may be formed differently from the motor.

In the present invention, when vane motors of different configurations are coupled, at least one of them preferably has a structure with good startability. In this case, the vane motors may be driven together, but it is preferable that the vane motor having good start-up is driven first and the remaining vane motors are driven later. Motors with good startability include cases with a special starting structure, but the moment of inertia of the rotor and rotational shaft is relatively small, and a large amount of pressure gas can be supplied per cycle. it can be At this time, as a special starting structure of the vane motor, a structure in which pressure gas is supplied to the bottom of the vane groove to function as an air spring may be exemplified.

In at least one of the vane motors constituting the system in the present invention, gas inlet grooves connected to the rear surface of the vane are formed on both ends of the rotor body in the axial direction, and the casing is composed of a cylindrical portion and a closing plate closing both ends of the cylindrical portion of the casing. In the closing plate, a gas inlet may be formed at a position overlapping the trajectory of the gas inlet groove when the rotor body rotates to supply pressure gas to the space behind the vane.

In this case, the vane motor may have a cylindrical inner cylinder between the rotor and the cylindrical portion of the casing and rotate according to the rotation of the rotor inside the cylindrical portion, and the rotor may rotate in the inner cylinder.

At least one of the vane motors constituting the system in the present invention is made so that the vanes of the rotor perform angular motion when entering and exiting the vane groove, and the vane and the vane groove may have an arc shape in a cross section perpendicular to the axial direction .

In the present invention, at least one of the plurality of vane motors may have both an injection section in which pressure gas is introduced and a non-injection section in which pressure gas is not introduced among sections between vanes in one rotation period.

According to the present invention, it is possible to provide a vane motor assembly having a configuration with higher installation efficiency than conventional simple vane motors.

According to the present invention, through the configuration of the vane motor assembly, it is possible to provide power with high efficiency ranging from small output to large output according to circumstances.

According to the present invention, a vane motor system with high efficiency can be provided, in which the required output can be changed in a large range, including a relatively large output, and even when the installation space is limited, through a layout configuration suitable for the installation environment.

1 is a perspective view showing a conventional vane motor configuration;
2 is an exploded perspective view of a first type vane motor that can be used in the present invention;
Figure 3 is a perspective view separately showing the rotor body of Figure 2;
4 is a perspective side view further showing the relative positional relationship between the gas inlet of the closing plate, the gas outlet, the gas inlet groove of the rotor, and the vane in a side view showing the coupling relationship between the cylindrical inner surface of the casing and the rotor in the vane motor, and a part thereof. magnified view for
Fig. 5 is an exploded perspective view showing a partially assembled state to show a coupling relationship between a rotor and a cylindrical inner surface of an inner cylinder of a type 2 vane motor that can be used in the present invention;
Figure 6 is a perspective side view showing the coupling relationship between the casing, the inner surface of the inner cylinder and the rotor in the vane motor shown in Figure 5, and the relative positional relationship between the gas inlet and gas outlet of the closing plate and the gas inlet groove and vane of the rotor;
7 is a side view of a type 3 vane motor that can be used in the present invention;
Figure 8 is a side view showing a state in which the closing plate is removed from the vane motor of Figure 7;
9 and 10 are perspective and side views of a rotor portion of a type 4 vane motor that can be used in the present invention;
11 is a perspective side view showing the relative positional relationship of the gas inlet, gas inlet and gas outlet for the air spring, the inner surface of the casing and the gas inlet groove, groove and vane of the final plate when the closing plate is further coupled to FIG. 10;
12 is a perspective view showing the key components and coupling relationships of one embodiment of the present invention;
13 to 15 are perspective views showing key components and coupling relationships of the second embodiment of the present invention;
Figure 16 is a perspective view showing the key components and coupling relationship of the third embodiment of the present invention;
Fig. 17 is a perspective view showing important components and coupling relationships of a vane motor constituting a fourth embodiment of the present invention;
Fig. 18 is an exploded perspective view showing important components and coupling relationships constituting a fifth embodiment of the present invention;
Fig. 19 is a conceptual cross-sectional view showing important components and coupling relationships constituting a sixth embodiment of the present invention;
Fig. 20 is a conceptual cross-sectional view showing important components and coupling relationships constituting a seventh embodiment of the present invention.

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

Before describing the system of the present invention, for ease of understanding, several vane motor configurations that can be used to increase efficiency that can be used in this system will be described.

(Type 1 vane motor)

Referring to FIGS. 2 to 4, the vane motor casing includes a substantially cylindrical casing body 11 and closing plates 13 and 15 closing both ends of the body 11 in the longitudinal direction. ), and each of the finishing plates 13 and 15 has a rotation shaft installation hole through which the rotation shaft 33 connected to the rotor is mounted or passes, an arc-shaped gas inlet 135 into which external high-pressure gas is introduced, and a high-pressure gas An arc-shaped gas outlet 133 discharged through the inside is arranged. A bearing 17 is installed in the rotation shaft installation hole so that the rotation shaft 33 does not come into direct contact with the finishing plate 13 and friction during rotation can be reduced by the bearing 17. In this configuration, the rotor rotates while contacting the inner surface 11a of the casing body 11 . A gear 37 for power transmission to the outside may be formed on one side of the rotating shaft 33 .

The groove 31a formed to install the vane 35 on the rotor body 31 may be formed in various other shapes as needed. In this embodiment, a plurality of grooves 31a are installed parallel to each other along the longitudinal direction in the portion forming the cylindrical side of the body 31, and when viewed in the longitudinal direction, the same circumferential angle or They are spaced the same circumferential distance and installed at equal intervals. The vane moving outwardly and inwardly along this groove 31a is made of a substantially rectangular plate material. Depending on the angle at which the groove 31a is installed on the rotor body, the vane may also be formed vertically on the side surface of the cylindrical rotor body 31, but here, the vane protrudes in an inclined direction at an angle with the vertical surface.

Here, the vane 35 is installed to have a slight gap in the groove 31a, and when the rotor rotates, it always has a tendency to protrude outward according to the centrifugal force, but is limited by the inner wall surface of the casing body 11, and the vane 35 is limited by the inner wall surface of the casing body 11. As the rotor rotates, the inner wall surface 11a applies force to the vane 35 in the direction of the groove 31a.

At least one of both ends in the longitudinal direction of the groove connecting the rotor body and the vane, here, the rear entrance at the rear in the rotational direction among the inlets forming the groove is partially removed to further expose the rear surface of the vane 35. A gas inlet groove 31b is installed. It can also be seen that these gas inlet grooves are formed on the surfaces of both ends of the rotor body. Here, the curved surface constituting the gas inlet groove 31b forms a concave surface when viewed from the inlet of the groove to the inside of the groove and when the rotor body is viewed from the longitudinal end to the center, so that the pressure gas injected into the gas inlet passes through the rear surface of the vane. It is formed to facilitate the application of pressure.

Among the closing plates, a gas inlet 135 and a gas outlet 133 are installed on the closing plate opposite to the surface on which the gas inlet groove of the rotor body is installed, but the gas inlet 135 is viewed from the side view in the direction of the rotation axis 33 As the rotor rotates, the gas inlet groove (31b) is formed in an arc shape that overlaps the trajectory that passes, and when the rotor rotates and the gas inlet groove (31b) overlaps the gas inlet 135 of the closing plate 13, the gas inlet ( 135), pressure gas is introduced into the space between the rotor body 31 and the casing body 11 through the gas inlet groove, and forces are applied to the rear surface of the vane 35.

(Type 2 vane motor)

In the example of the vane motor shown in FIGS. 5 and 6, a cylindrical inner cylinder 20 is further installed inside the casing compared to the example of the vane motor of FIGS. 2 to 4 above. The inner cylinder 20 has substantially the same length as the casing body 11, so that the inner surface of the casing's closing plates 13 and 15 and both ends in the longitudinal direction of the inner cylinder 20 are in contact with each other through a slight gap, so that the inner cylinder ( 20) may generate sliding friction with the inner surfaces of the closing plates 13 and 15 when they rotate. When installed, the inner cylinder 20 is placed on the plurality of rolling means 19 of the concave portion 119 installed in the inner wall of the casing body 11. Here, the rolling means is composed of a rolling rod and a roller, and the rolling rod may be formed in the form of a cylinder or a rotating shaft, and is rotatably installed in parallel with the rotating shaft 33 so that when the inner cylinder 20 rotates within the casing body 11, the inner cylinder The rolling table in contact with the outer surface rotates to prevent sliding friction between the inner cylinder 20 and the inner wall of the casing body 11 due to the rotation of the inner cylinder.

In the inner cylinder 20, a cylindrical rotor body 31 having a rotating shaft 33 and a rotor having vanes 35 coupled to grooves 31a of the rotor body 31 are installed. The rotational axis 33 of the rotor is installed parallel to the virtual rotational center axis of the inner cylinder 20 but spaced apart from each other by a certain distance. The casing closure plates 13 and 15 have holes through which the rotation shaft 33 thus installed is passed or caught. The position of the hole is also spaced a certain distance from the rotation center axis of the cylinder formed by the casing.

The distance between the rotor body 31 and the inner wall surface of the inner cylinder 20 is minimized at the place where the rotor touches the inner cylinder 20 while pushing, so that the vane 35 completely enters the groove and the rotor body 31 connects to the inner cylinder 20. The width where the vane 35 protrudes from the main body 31 becomes small. On the opposite side (opposite to the axis of rotation), the distance between the rotor body 31 and the inner wall surface of the inner cylinder 20 is maximized, so that the protruding width of the vanes 35 from the rotor body 31 is increased.

Even here, the action or operation of the components in the vane motor is similar to the example of FIGS. 2 to 4 . That is, when the high-pressure gas is supplied to the arc-shaped gas inlet 135, the high-pressure gas passing through the arc-shaped gas inlet of the closing plate begins to overlap the gas inlet groove 31b at the rear of the vane 35 in the rotor. Through (31b), it is injected into the space between the rotor body at the rear of the ship and the inner wall surface of the inner cylinder.

All of the pressure gas introduced in the process applies rotational force to the rotor while impacting the rear part of the vane connected to the gas inlet groove through the gas inlet groove, and the pressure gas filling the space also affects the vane, which is part of the interface dividing the space. A relatively high pressure is applied to the rear surface to cause the rotor to rotate. Since the entire rotor on which the vanes are installed is rotatably fixed by the rotating shaft 33, only rotational movement is performed without parallel movement. After the position of the gas inlet (135, 155), the space between the rotor and the inner cylinder (20) is enlarged, the vane (35) is also maximally protruded from the groove (31a), and after the position of the maximum gap, the arc-shaped gas outlet (133, 153) starts, so the gas escapes through this gas outlet and the gas pressure decreases.

(Type 3 vane motor)

7 is a side view of another example of the vane motor, and FIG. 8 is a side view showing a state in which the closing plate is removed from the example of FIG. 7 . Referring to the second type vane motor with reference to these drawings, in this vane motor example, the first type vane motor in that the gas inlet 235 is installed along the trajectory along which the gas inlet groove 31b' moves when the rotor rotates. , but at least some of the sections between the plurality of vanes are non-injection sections in which pressure gas is not introduced. In order to achieve the non-injection section, a gas inlet groove 31b' connected to the space between the vane 35 and the vane 31' is formed on the end surface of the rotor body 31', and the rotor body 31' rotates on the closing plate. When the gas inlet groove (31b') moves, an arc-shaped pressure gas inlet (gas inlet: 235) is formed at a position overlapping the moving trajectory to supply pressure gas to the space between the vanes, but when the rotor rotates, the gas inlet 235 The gas inlet grooves 31b' communicating with are formed in a smaller number than the number of vanes 35 so that only some of the spaces between the plurality of vanes are connected to the gas inlet grooves 31b.

Therefore, there is no corresponding gas inlet groove 31b' in the remaining section or space between the vanes, and since the gas inlet 235 does not communicate with the gas inlet 235, the inflow of pressure gas does not occur, and these sections form a non-injection section. In particular, in the section between the vanes, the non-injection section and the injection section are alternately located, and the size of the non-injection section and the injection section is the same, but depending on the embodiment, the length of the section between the injection section and the non-injection section is different, The installation ratio may vary, such as one injection section for every two non-spray sections, or two injection sections for each non-spray section.

In addition, if the gas inlet 235 is composed of three arcs instead of simply one arc, and the central angle corresponding to the arc in the type 1 vane motor is approximately 60 degrees, here, as shown in FIG. 7, three arcs There is a difference that the gas inlet is formed over a larger range as the central angle corresponding to , for example, reaches 111.7 degrees.

Due to this difference, at least one of the three arcs constituting the gas inlet overlaps the gas inlet groove 31b' of the injection section. An overlapping state with such an injection section may have a very important meaning in starting the vane motor.

For example, when the vane motor is initially driven, the gas inlet may be located at a position overlapping the gas inlet groove of the injection section, but may be completely blocked by surfaces of both ends of the rotor body in the non-injection section.

If the gas inlet overlaps the gas inlet groove, as soon as the pressure gas is introduced through the gas inlet, the same action as described above takes place and the rotor receives rotational driving force from the pressure gas, so that the rotor can rotate, but the gas inlet is non-injected If it is located in the section and blocked by the surfaces of both ends of the rotor body, the rotor cannot receive rotational force at all and the vane motor cannot start its operation.

In this case, when the vane motor is started, if the rotor is forcibly rotated a little by external force, the gas inlet may enter the injection section overlapping the gas inlet groove according to the rotation, and thus the rotor may continuously rotate. However, it requires a separate starting device or manual operation to force return, which can make vane motor operation very cumbersome.

However, in the case of this example, no matter which rotational position or phase the rotor body 31' is in, at least a portion of the gas inlet 235 overlaps the injection section in which the gas inlet grooves 31b' are formed on the surface of both ends of the rotor body. do. Accordingly, the vane motor can always be started without any problems without a separate starting device or manual operation.

On the other hand, since the gas inlet grooves 31b' are not installed on the surfaces of both ends of the rotor body 31' in the section between the vanes between the front vane and the rear vane constituting the non-spray section, both ends of the rotor body 31' in the non-spray section. Even if it overlaps with the gas inlet 235, the gas inlet 235 is closed by the surfaces of both ends of the rotor body 31', and the gap between the rotor body 31' and the casing body 11' according to the rotation of the rotor. As are gradually spaced apart, there is no pressure gas inflow even if the space between them is increased, so there is no impact or pressure action of the pressure gas on the rear surface of the front vane, and there is no contribution to rotor rotation in the vane motor.

However, when the volume of the space is increased in the non-injection section without gas inflow, the space becomes a vacuum state where a significant negative pressure is applied. This negative pressure can increase the concern that the pressure gas in the injection section will leak into the non-injection section, can interfere with the rotation of the rotor, and when the space of this negative pressure non-injection section meets the gas outlet 233, the gas outlet 233), a rapid inflow of gas into the space occurs, causing problems of causing vibration and noise, and accordingly, a problem of reducing the efficiency of the vane motor may occur.

In order to solve this problem, in this embodiment, a passage connected to the space of the non-spray section is installed. As such a passage, for example, as shown in FIG. 8, when viewed from the center of the rotation axis 33 on both ends of the rotor body 31 ', a ring-shaped passage toward the center of the innermost end of the groove 31a while being outside the rotation axis groove 31c) may be formed, and a passage hole 31d may be formed in a part of the passage groove 31c.

The passage hole 31d is connected to the connection hole on the side of the rotor body in the non-injection section through the rotor body 31', although it is not clearly shown here. Also, the side surface of the rotor body in any non-injection section is connected to at least one of the passage holes 31d. In addition, here, all the passage holes 31d are connected to each other so that air can be exchanged by means of a ring-shaped passage groove 31c. As a result, the space between the side of the rotor and the case of all non-injection sections is connected to each other so that air can be exchanged.

If at least one of the non-injection sections is connected to the pressure gas outlet or the gas outlet 233, the space of all non-injection sections can always have an air pressure close to the air pressure of the gas outlet 233, and excessive negative pressure is applied to the vane motor. Vibration, noise and inefficiency can be effectively prevented.

In addition, in this case, a gas inlet 235 for an air spring capable of supplying pressure gas to a lower part that is not completely filled even when the vane 35 is completely inserted in the groove 31a is installed on the closing plate.

During the rotation of the rotor, after the position where the vane 35 is maximally inserted into the groove 31a, and before the pressure gas is supplied to the space behind the vane, the gas inlet 237 for the air spring connects to the bottom and bottom of the groove 31a. It may overlap temporarily, and at this time, the pressure gas for the air spring is introduced into the lower space of the groove 31a through the gas inlet 237 for the air spring. The pressure gas input into the lower space of the groove causes a high pressure to act on the lower space of the groove, and a high pressure also acts on the lower end of the vane 35 to lift the vane toward the inlet of the groove.

Conventionally, in the initial stage of vane motor operation, if the rotor does not reach sufficient angular velocity, the vane cannot move outward from the groove because the centrifugal force is not sufficient, and the gap between the end of the vane and the inner surface of the casing widens, causing the pressure gas to give rotational force to the vane rotor. Since the configuration of supplying pressure gas to the lower part of the groove as in the present invention is particularly important because it may leak into the adjacent space without applying sufficient pressure to the vane, the gas inlet 237 for the air spring acts only at the beginning of the operation, and sufficient After the rotor is rotated, it is also possible to block the gas inlet 237 for the air spring by a separate means, or to block the pipe supplying pressure gas to the gas inlet for the air spring.

(Type 4 vane motor)

9 and 10 are perspective and side views of a rotor portion in another example of a vane motor for the present invention, and FIG. 11 is a gas inlet 345 of the closing plate when the closing plate is further coupled to FIG. 10, air It is a perspective side view showing the relative positional relationship between the gas inlet 347 and gas outlet 343 for the spring and the gas inlet groove 331b, groove 331a, and vane 335 of the rotor.

Similar to the previous example, in this example, the vane motor also includes a casing forming the outermost shell and a rotor positioned within the casing. Except for what is specifically described here, the vane motor may be made similar to the configuration of the existing casing and rotor. there is. For example, the casing includes a substantially cylindrical casing body 311 and closing plates closing both ends of the casing body 311 in the longitudinal direction.

The rotor body 330 is formed in a cylindrical shape or a thick disc shape, and a vane guide groove 331a in which a vane 335 is installed is formed on a side surface of the cylinder. At least one of the finish plates, in this case all of them, is provided with a rotation shaft installation hole through which the rotor rotation shaft 333 is mounted or passes. The rotating shaft 333 may be integrally formed with the rotor.

However, unlike the previous embodiment, in this embodiment, there is a difference in the mutual coupling and operation method of the rotor and the vane, and the vane 335 and the vane, which is a groove formed on the side of the rotor body 330 to guide the vane 335 accordingly. There is a difference in the shape of the guide groove (331a). That is, the vane 335 is made of a thick plate shape having an arc shape when viewed from a side view, and the vane guide groove 331a is made of an arc-shaped groove capable of accommodating the vane 335.

In addition, the vane 335 is connected to a hinge shaft 339 installed on a part of the rotor body 330 by a link rod 337 installed on one side of the vane (front side, which is the front side when considering the rotation direction), and the link rod 337 and the hinge shaft 339 are rotatably coupled to the rotor body 330.

The link rod 337 is coupled to the top of the vane 335 (outermost with respect to the rotation center axis of the rotor), and the hinge shaft 339 is installed on the surface layer (outer layer) of the rotor body 330. Therefore, here, when the vane 335 is maximally accommodated in the vane guide groove 331a, the link rod accommodating groove of the rotor is formed to a minimum depth at one end to facilitate installation and minimize the volume occupied by the link rod. However, it is preferable that the link rod receiving groove have a slight extra depth so that the link rod 337 does not directly collide with the rotor body 330 and cause vibration when the vane 335 moves, and the vane guide groove 331a ) is also desirable to have some extra depth.

Here, when the gas inlet groove is formed, the rear part is located at the rear of the vane guide groove 331a at both ends in the longitudinal direction of the rotor body 330 and the vane guide groove 331a. The rotor body 330 is partially removed from the inlet, and the gas inlet groove 331b is installed so that the rear surface of the vane 335 is further exposed. The curved surface constituting the gas inlet groove 331b is concave so that the pressure gas injected into the gas inlet 345 can easily apply pressure to the rear surface of the vane.

In addition, as shown in FIG. 11 here, as in the previous example, the gas inlet 347 for the air spring that can supply pressure gas to the lower part that is not completely filled even when the vane 335 is completely inserted in the groove 331a is closed. installed on the plate.

During the rotation of the rotor, the gas inlet 347 for the air spring may temporarily overlap the lower end of the groove at a position before the pressure gas is supplied to the space behind the vane after the vane is maximally inserted into the groove, and at this time, the air spring The pressure gas for the air spring is introduced into the lower space of the groove through the service gas inlet. The pressure gas input into the lower space of the groove causes a high pressure to act on the lower space of the groove, and a high pressure also acts on the bottom of the vane to lift the vane toward the inlet of the groove.

Hereinafter, the vane motor system of the present invention, which may have the above-described vane motor as a component and can efficiently combine these elements, will be described with reference to the drawings.

(First embodiment)

Referring to FIG. 12, the vane motor system has rotors 430a, 430b, and 430c of three vane motors installed side by side in series, and shares a rotation axis 433 thereof. The rotors of the vane motor used here are all the same as those of the type 4 vane motor discussed above, and the rotational shaft 433 is integrally formed to form a straight line, and the rotational shaft and the rotor are fixedly coupled. And, for convenience of description, here, the cylindrical casing body and the closing plates closing both ends thereof are omitted.

The three rotors 430a, 430b, and 430c are common in that they have basically the same structure as the rotor of the type 3 vane motor, but have a difference in length or thickness in the direction of the rotation axis 433, so the first rotor 430a is the most long, and the third rotor 430c is formed the shortest. Accordingly, if compressed gas having the same pressure is supplied, the vane motor including the first rotor will generate the greatest output.

In this configuration, the rotation axis is common, and the rotation axis 433 and the rotor are fixedly coupled so that a design suitable for an arbitrary output is possible. In addition, when compressed gas is supplied to the vane motor, the three rotors and the common rotation shaft rotate together. When a large output is required, compressed gas is supplied to the three vane motors to drive them together, and when less output is required, the required vane motor combination is selected from among the three vane motors, compressed gas is supplied only to the vane motor, and compressed gas is supplied. The vane motor without this can provide the output of the vane motor supplied with the corresponding compressed gas by reducing the rotation resistance due to the generation of negative pressure by arbitrarily connecting or controlling the air inlet and the exhaust port.

On the other hand, in this configuration, the three rotors and a common long rotational shaft have a large mass or moment of inertia because they rotate together, so it is difficult to quickly increase the rotational speed at initial startup, and it is difficult for the vane to come out of the groove easily by centrifugal force. there is.

Therefore, it is preferable to operate by forming a gas inlet for an air spring at the end plate of at least one vane motor as a structure advantageous to start-up as already discussed in the previous type 3 and type 4 vane motors.

In addition, in order to favor the start-up, in the case of having an injection section and a non-injection section, it is preferable to form a gas inlet that spans a fairly long arc section for the inflow of pressure gas. It is also possible to supply pressure gas to all, and when sufficient rotational speed is reached, pressure gas is supplied only to the vane motors that form a vane motor combination suitable for the required output.

On the other hand, here, although the rotational phases of the three rotors 430a, 430b, and 430c are all shown to form the same arrangement, if the rotational phase arrangements are shifted from each other, although there may be advantages or disadvantages in starting, the injection section and the non-injection section Even in the case of having a gas inlet, there is no need to form a gas inlet spanning a long arc section for the inflow of pressure gas, and rotational stability may be increased, just as a 4-cylinder engine is more stable than a 2-cylinder engine in an automobile.

(Second embodiment)

13 to 15 show another embodiment of the system of the present invention, and for convenience of description, here, the cylindrical casing body and the closing plates closing both ends thereof are omitted. 13 shows a state in which the respective rotors 530a, 530b, and 530c and the coupling means 535) and the common rotation shaft 533 are all separated, and FIG. 14 shows a state in which only the coupling means 535 and the common rotation shaft 533 are coupled. 15 shows a state in which the rotors 530a, 530b, and 530c are coupled in FIG. 14.

Most of the same description as in the embodiment of FIG. 12 can also be applied here. Here, the vane motor system also has rotors 530a, 530b, and 530c of three vane motors installed side by side in series, and shares the rotation shaft 533. The rotors of the vane motors used here are all the same as the rotors of the type 4 vane motors discussed above. In addition, most of the configurations for power adjustment, combination of rotors, and convenience of starting can be applied in the same way.

However, here, each rotor of the three vane motors is always coupled through a rotating shaft 533 and a coupling means 535, but this coupling means is a one way clutch. Therefore, when each rotor rotates, rotational force can be transmitted to the common rotation shaft, but if pressure gas (compressed air) is not supplied to the corresponding rotor, the rotor may not rotate even if the common rotation shaft rotates.

Here, the coupling means 535 may be formed of one or two according to the length or thickness of the rotor of each vane motor in the direction of the rotational axis, and even if there are two, they may be installed without mutual spacing or at regular intervals.

In this embodiment, also, compared to the embodiment of FIG. 12, the coupling relationship between each rotor and the common rotational axis is not completely fixed, but coupled only when there is an output of the vane motor, so the moment of inertia can be reduced, and when operated at low power Since only the rotor supplied with compressed air is included in the moment of inertia, startability can be improved.

(Third Embodiment)

16 shows another embodiment of the system of the present invention, and for convenience of explanation, here, the cylindrical casing body and the closing plates closing both ends thereof are omitted.

Most of the same description as in the first embodiment can be applied here as well. Here, the vane motor system also has rotors 630a, 630b, and 630c of three vane motors installed side by side in series, and shares the rotation shaft 633. In addition, most of the configurations for power adjustment, combination of rotors, and convenience of starting can be applied in the same way.

However, the rotors of the vane motors used here are all the same as those of the type 3 vane motors discussed above. In this type, the injection section and the non-injection section are separated, and negative pressure may be formed in the non-injection section, and when this negative pressure section meets the gas outlet, rather rapid gas inflow may occur, causing vibration and noise. In order to solve the problem, in this embodiment, a passage connected to the space of the non-spray section is installed.

(Fourth embodiment)

Also in the fourth embodiment, the rotor is the same as that of the vane motor of the third type. Even in this embodiment, a passage connected to the space of the non-spray section is installed.

As such a passage, a ring-shaped passage groove 631c is formed on the surface of both ends of the body of the rotor 630c, outside the rotation axis when viewed from the center of the rotation axis 633, and slightly more centered than the innermost end of the groove 631a, A passage hole 631d is formed in a part of the passage groove 31c, and the passage hole 631d is connected to the connection hole 631e on the side of the rotor body in the non-spray section through the rotor 631 body. do.

Any side of the rotor body in the non-injection section is connected to at least one of the passage holes 631d, and all passage holes 631d are connected to each other through a ring-shaped passage groove 631c to exchange air. Therefore, the spaces between the vanes 635 of all non-injection sections are connected to each other.

However, the vane motor here is not exactly the same as the third type of vane motor. That is, here, as shown in FIG. 17, an inner cylinder 620 as in the second type of vane motor is installed between the rotor and the casing body to reduce inefficiency resulting from sliding friction between the vane and the casing body when the rotor rotates. That is, the inner cylinder 620 can rotate with respect to the casing body through the rollers 619 without sliding friction between the inner cylinder 620 and the casing body (not shown in FIG. 17), and thus reduce efficiency reduction due to sliding friction.

In terms of operation, simply thinking, the casing body of the third embodiment can be seen as being replaced by the inner cylinder 620 of the fourth embodiment, and the space between the vanes into which the pressure gas flows is instead of the side of the rotor and the inner surface of the casing. It becomes a space limited by the rotor side surface and the inner wall surface.

(Fifth embodiment)

Fig. 18 shows another embodiment of the system of the present invention, which is different from the second embodiment in that the rotor of the fourth type vane motor is replaced with the rotor of the third type vane motor.

Here, as in the second embodiment, each of the rotors 730a, 730b, and 730c of the three vane motors are always coupled through a rotating shaft 733 and a coupling means 735, but the coupling means 735 rotates in one direction. Since it is a one-way clutch, when each rotor rotates, rotational force can be transmitted to a common rotation shaft 733, but if pressure gas (compressed air) is not supplied to the rotor, the rotor rotates even if the common rotation shaft rotates. may not

Therefore, since the rotor that is not driven here can be excluded from integral rotation, the moment of inertia can be reduced to facilitate starting compared to the third embodiment.

(Sixth embodiment)

Referring to Fig. 19, here, the vane motor system has rotors 830a, 830b, and 830c of three vane motors installed side by side in series, and the rotating shafts 833a, 833b, and 833c of each rotor are formed integrally and fixedly. Although not, they are arranged so that they can be spaced apart or coupled to each other on a straight line.

For coupling with each other, some vane motors or rotational axes of the vane motors are movable, and coupling means (835a, 835b, 835c) such as clutch plates are installed in portions where rotational shafts of adjacent vane motors are coupled.

In this case, a moving means according to the movement of the vane motor itself or the rotating shaft belonging thereto must be provided, but since the rotor rotating shaft itself can be separated, the moment of inertia can be reduced and advantages can be obtained accordingly. In addition, when a problem occurs in only one vane motor, maintenance is convenient because only the corresponding vane motor can be replaced, and it may be possible to operate the system with the remaining vane motors even while replacing or repairing the corresponding vane motor.

(Seventh Example)

Referring to Fig. 20, here the vane motor system has rotors 930a, 930b, 930c of three vane motors installed in series and side by side, and the rotors have a common axis of rotation, and the common axis of rotation is relative to some of the rotors. It may be a position where it is combined with some rotors through movement.

For coupling with each other, some vane motors or common rotation shafts 933 are movable, and coupling means 935a, 935b, and 935c such as clutches are installed at portions where the rotor and the rotation shaft come into contact with each other.

Even in this case, similar to the embodiment of FIG. 19, a moving means according to the movement of the vane motor itself or the rotating shaft belonging to it must be provided, but it can have advantages accordingly.

In the above, the present invention has been described through limited examples, but this is only illustratively described to help understanding of the present invention, and the present invention is not limited to these specific examples.

Therefore, those skilled in the art to which the present invention pertains will be able to make various changes or applications based on the present invention, and it is natural that such modifications or applications fall within the scope of the appended claims.

11, 11 ', 311: casing body 11a: inner casing
13, 15: closing plate 17: bearing
19: rolling means (roller)
20, 620: inner cylinder 31, 31 ', 330: rotor body
31a, 331a: groove (vane guide groove) 31b, 31b', 331b: gas inlet groove
31c, 631c: passage groove 31d, 631d: passage hole
33, 333, 433, 533, 633: rotary shaft 35, 335, 635: vane
119 inner wall concave portion 135, 155, 235, 345 gas inlet
133, 153, 233, 343: gas outlet 237, 347: gas inlet for air spring
337: link rod 339: hinge axis
430a, 430b, 430c, 530a, 530b, 530c, 630a, 630b, 630c: rotor
631e: connection hole

Claims (13)

Multiple vane motors are arranged in series, and the rotor rotation axis is arranged on a straight line so that they can rotate together or share,
The rotor of the multi-vane motor and the rotor rotation shaft are made of a one-way clutch method, so that when the rotor rotates, the rotational force of the rotor can be transmitted to the rotor rotation shaft, and the rotation of the rotor rotation shaft alone A vane motor system, characterized in that the rotor is not rotated. delete delete According to claim 1,
The vane motor system, characterized in that it is made to arbitrarily select a combination of vane motors driven by controlling the supply of pressure gas to each of the plurality of vane motors. According to claim 1,
A vane motor system, characterized in that a detachable device capable of connecting and selecting is installed between the rotor rotational axes of the plurality of vane motors to control mutual coupling between the rotor rotational axes of the individual vane motors so that the rotor rotational axes can be shared. According to claim 1,
The vane motor system, characterized in that the plurality of vane motors are composed of a plurality of mutually replaceable vane motors of the same structure. According to claim 1,
At least one of the plurality of vane motors is a vane motor having a different configuration,
The different configurations include different structures or different outputs,
The different structures are different from each other in one or more of the rotational phase of the rotor, the presence or absence of a gas inlet for an air spring, whether or not a one-way coupling clutch is adopted when coupling the rotating shaft and the rotor, the number, shape or position of pressure gas inlets for providing rotational force. A vane motor system characterized in that it is formed differently. According to claim 7,
A vane motor system, characterized in that at least one vane motor of the plurality of vane motors has a structure with better startability than other vane motors. According to claim 8,
The structure with good startability has a relatively small moment of inertia of the rotor and a rotating shaft, a large amount of pressure gas supply per rotation period, a large number of vanes and a small gap or angle between vanes, or a lower vane guide groove. A vane motor system, characterized in that any one of the structures for supplying pressure gas to function as an air spring. delete delete According to claim 1,
At least one of the plurality of vane motors is made to perform angular motion when a vane enters and exits the vane guide groove, and the vane and the vane guide groove have an arc shape when viewed in a cross section perpendicular to the direction of the rotation axis. vane motor system. According to claim 1,
The vane motor system, characterized in that at least one of the plurality of vane motors has both an injection section in which pressure gas flows and a non-injection section in which pressure gas does not flow among sections between vanes in one rotation period.

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