JPH02291500A - Vane controller - Google Patents

Abstract

PURPOSE:To reduce frictional resistance of a guide ring, to cut cost, and so on by providing a vane on the periphery of a casing by which it is supported along the circumferential direction and along a shaft direction so as to move freely, and by installing a mechanism driving each vane on a guide vane. CONSTITUTION:An actuator (not depicted in the drawing) is driven, so as to rotate a control arm 20 for driving through a coupling rod 7 for driving and a driving arm 6, a driving vane 3a is rotated following this. A guide ring 30 moves in a circumferential direction through a level 22 provided on the control arm 20 for driving as well as a pin 23 perpendicular to the rotational plane of the lever 22. Through a spherical bearing housing 25 installed on several points on the circumference of the guide ring 30, a spherical bearing 24, a pin 23 supported by this and through the lever 22, control arms 21 are rotated, while vanes 3 are rotated by the same angle as that of the driving vane 3a.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a vane control device, and particularly to a vane control device that performs capacity control in a fluid machine such as a turbo compressor having a centrifugal impeller or an axial impeller. The present invention relates to a vane control device suitable for driving vanes for.

[Prior Art] In a conventional device, for example, as described in Japanese Patent Publication No. 57-49759, the drive arm of the vane control device at each stage is connected to a connecting arm attached to a drive shaft driven by an actuator. Because of this, no consideration was given to the fact that the structure was complicated and the number of parts was large.

In addition, means such as the stator vane variable mechanism described in Japanese Utility Model Publication No. 44-21729 have also been known.

[Problems to be Solved by the Invention] The vane control device described in Japanese Patent Publication No. Sho 57-49759 will be described with reference to FIGS. 8 to 10.

FIG. 8 is a vertical cross-sectional view showing a conventional vane control device, FIG. 9 is a side cross-sectional view of main parts showing the drive vane and its drive mechanism of the device shown in FIG. 8, and FIG. I-I in the diagram
It is an arrow view.

In the figure, 1 is the impeller of the centrifugal compressor, and 2 is the casing. 2a is a suction bell mouth, 3 is a plurality of vanes attached to the upstream part of the impeller 1, and one of the plurality of vanes 3 is a drive vane 3a; 3a has its base end rotatably supported by a ball bearing 5 provided in the casing 2 via a vane shaft 4 or a drive vane shaft 4a.

6 is a drive arm fixed to the drive vane shaft 4a;
Reference numeral 7 denotes a connecting rod whose one end is attached to the drive arm 6 by a pin 8, and the other end of this connecting rod 7 is attached to an actuator 9. When the actuator 9 operates, the drive vane shaft 4a rotates, and this drive vane shaft As the movement mechanism 4a rotates, the movement mechanism 3a also rotates.

Also. I[! A driving control arm 10 is attached to the moving vane shaft 4a, and an end portion of the driving control arm 10 is provided so as to slide and rotate on the outer periphery of the casing 2 adjacent to the vane shafts 1 and 4 and the driving vane shaft 4a. It is connected to a guide ring 11 via a ball joint 12. The vane shaft 4 is connected to the guide ring 11 via the control arm 14 for driven by the ball joint 13, so when the drive vane shaft 4a rotates due to the operation of the actuator 9, all the The vane shaft 4 is rotated in synchronization with the drive vane shaft 4a.

With such a configuration, the actuator 9 can move the vane 3
, 3a can be rotated to open and close the vane control device.

The problem with the conventional vane drive mechanism described above is that as the guide ring 11 slides around the casing 2, frictional resistance increases, and as a result, the torque of the actuator for driving each vane 3 increases. There's a problem. If the friction torque can be reduced, the only torque required is the air torque acting on each vane 3, so the torque required for driving can be significantly reduced.

Furthermore, a large frictional force slows down the response speed of the vane opening and opening, which is not suitable when the vane is repeatedly opened and closed due to the large friction.

On the other hand, in the mechanism described in Japanese Utility Model Publication No. 44-21729,
It uses a spherical bearing and a stator vane rotating lever that requires spherical machining at the tip, but this is complicated to machining and increases production costs.

The present invention was made in order to solve the problems in the prior art described above, and it reduces the frictional resistance of the guide ring.
The object of the present invention is to provide a vane control device that can reduce frictional torque, has a vane drive mechanism with less friction, and has reduced production costs.

Another object of the present invention is to extend the durability and improve the reliability of the entire vane control drive mechanism by periodically replacing the bearing interposed between the spherical bearing and the pin.

[Means for Solving the Problems] In order to achieve the above object, the most basic configuration of the vane control device according to the present invention is a vane control device for a plurality of vanes provided at the inlet of an impeller of a fluid machine. The control device includes a guide ring located in an outer peripheral space of a support casing for the plurality of vanes and movable in the circumferential direction and the axial direction, and a drive mechanism for interlocking the plurality of vanes is attached to the guide ring. This is how it was done. Its specific configuration consists of a control arm that rotates the plurality of vanes, a lever perpendicular to the axis of the control arm, and a lever perpendicular to the plane of rotation of the lever. A guide ring is provided with a pin having a shape of 1, and a spherical bearing that supports the pin, and the spherical bearing is mounted on a guide ring.

More specifically, an elastic member is installed between a pin provided perpendicular to the plane of rotation of the lever and a spherical bearing that supports this pin. The guide ring is supported by a guy pin fixed to the casing via a rotatable and axially movable bearing.

Further, the spherical bearing that supports the pin has a rotatable and axially movable bearing interposed between the spherical bearing and the pin.

Additionally, the idea behind developing the present invention is as follows.

In order to achieve the above object, it is necessary to float the guide ring 11 shown in FIG. 8 in the air as in the stator vane variable mechanism described in Japanese Utility Model Publication No. 44-21729. It is also necessary to develop an alternative to the expensive means described in the same publication, such as machining the tip of the stator vane rotating lever into a spherical surface.

In view of this, in the present invention, it was decided to make the guide ring float in the air. In addition, this guide ring was
In contrast to the structure in Japanese Patent No. 21729 that does not move in the axial direction, the present invention is designed to be movable in the axial direction as well.

The present invention is such that the movement of the guide ring and vane, which are movable in the axial direction, is configured so that there is little friction and machining is simple. [Operation] The operation of the above technical means will be explained with reference to Figures 4 to 7. FIG. 4 is an explanatory diagram showing the movement of the guide ring in the axial direction;
Fig. 5 is a side sectional view showing the main parts of the vane control device, Fig. 6 is a sectional view taken along arrow C in Fig. 5, and Fig. 7 is an enlarged view of the main parts showing the spherical bearing part in Fig. 6. It is. The guide ring 30 and the vane 3 are interlocked by a pin 23 attached to the lever 22 and a spherical bearing 24. If the vane 3 turns by an angle α in the direction of the arrow shown in FIG. 4 (to the right), the guide ring 30 moves by ΔX in the axial direction from the initial position (■) and comes to the position (■'). At this time, the spherical bearing 24 and the pin 23 move relative to each other by Δh, as shown in FIG. Although the pin 23 is perpendicular to the plane of rotation of the lever 22, the angular difference is easily absorbed by the spherical bearing 24 mounted on the guide ring 30. Therefore, the only sliding portion is the relative displacement Δh between the pin 23 and the spherical bearing 24, and the torque required for driving by friction is extremely small.

Spherical bearings are commercially available at low cost as a set together with a spherical bearing housing, and can be used.

Also, as shown in Fig. 6, this is an example in which a spherical bearing is attached to the guide ring 30, but even if a commercially available ball joint 35 is attached as shown in Figs. 11 and 12, which will be described later, the effect will be exactly the same. .

[Embodiment] An embodiment of the present invention will be described below with reference to FIGS. 1 to 7 and FIGS. 11 to 15.

First, FIG. 1 is a side cross-sectional view of a vane control device according to an embodiment of the present invention, FIG. The figure is
It is an enlarged sectional view taken in the direction of arrow B in FIG. 2. In each figure, the same reference numerals as in FIG. 8 indicate the same or corresponding parts as in the prior art.

In FIGS. 1 to 3, 20 is a driving control arm directly connected to the rotating vane 3a, 21 is a control arm directly connected to each of the other plurality of vanes 3, and 22 is perpendicular to the axis of the control arm 21. The lever 23 has a pin 24 provided perpendicular to the plane of rotation of the lever 22.
is a spherical bearing that supports the pin 23, and 25 is a spherical bearing housing that is attached to the guide ring. This spherical bearing 24 is commercially available as a set together with a spherical bearing housing 25 at low cost, and this can be used.

A spring 26 is an elastic member mounted between the pin 23 and the spherical bearing 24.

The plurality of vanes 3 (including the movable vane 3a) are rotatably supported by the casing 2 by ball bearings 5.

30 is a guide ring located in the outer peripheral space of the casing 2, and this guide ring 30 is movable in the circumferential direction and the axial direction.

31 is a guide pin fixed to a fixing member on the casing 2 side.

Next, the operation of the vane control device of this embodiment will be explained with reference to FIGS. 1 to 3 and FIGS. 4 to 7.

As shown in FIG. 2, in order to rotate the movable vane 3a, an actuator (not shown, see 9 in FIG. 9) is actuated to connect the vane shaft to the vane shaft via the driving link 7 and the movable arm 6. The corresponding motion control arm 20 rotates. As a result, the drive vane 3a rotates, and the guide ring 30 is moved in the circumferential direction by a lever 22 provided on the control arm 20 for moving the food tray, and a pin 23 perpendicular to the rotation plane of the lever 22. A spherical bearing housing 25, a spherical bearing 24, and a pin 2 supported by the spherical bearing housing 25 and the spherical bearing 24 are mounted at multiple locations around the circumference of the guide ring 30.
3 and the lever 22, each of the plurality of control arms 21 rotates, and each of the plurality of vanes 3 also rotates through the drive vane 3a.
It will rotate by the same angle.

In this case, a spring 26 is attached to each pin 23 in order to rotate the guide ring 30 circumferentially and concentrically. More specifically, the spring 26 is provided at the pin 23 between the lever 22 and the spherical bearing 24, and can be considered to be functionally set between the pin 23 and the guide ring 30.

This allows the guide ring 30 to be kept concentrically.

Also, on the outer circumference of the guide ring 30 (see Figures 1 and 2),
Alternatively, a guide pin 31 may be provided on the inner circumference (not shown) to allow the guide ring 30 to move concentrically. The details are shown in FIG.

In FIG. 3, 32 is a stroke bearing attached to the outer periphery of the guide pin 31, and 33 is a bearing housing of the stroke bearing 32, which contacts the guide ring 30. That is, this stroke bearing 32 is a bearing that is rotatable around the guide pin 31 and movable in the axial direction, and a commercially available bearing can be used. If the guide ring 30 is supported by the guide pin 31 using such a bearing, the guide ring 30 moves in the axial direction at the same time as in the circumferential direction, thereby reducing friction at the contact portion. Is possible.

According to this embodiment, the prior art Japanese Patent Publication No. 57-49759
Frictional torque can be reduced compared to the vane moving mechanism described in the above publication, and a drive with less wear is possible.

In addition, there is no need for special processing or special bearings, such as the spherical bearing mechanism of the stator blade rotating lever for the guide ring floating in the air, as described in Japanese Utility Model Publication No. 44-21729, and a commercially available spherical bearing can be used at a low price. This has the effect of providing a vane control device.

Incidentally, the same effect can be expected even if a push bearing is press-fitted into the bearing housing 33 instead of the stroke bearing 32 shown in FIG. 3.

In addition, the stroke bearing 32 and the bearing housing 33
If these are integrally machined using bearing material, the number of parts can be further reduced.

Next, FIG. 11 corresponds to a view of FIG. 12 from above,
An explanatory view showing the movement of the guide ring in the axial direction, FIG. 12 is a side sectional view of a vane control device according to another embodiment of the present invention, FIG. 13 is a detailed view of the ball joint part of FIG. 12, FIG. 14 is a view along the YY arrow in FIG. 13, and FIG. 15 is a sectional view showing another embodiment of the spherical bearing portion. In the figure, the same reference numerals as those in FIG. 1 are the same parts as in the previous embodiment, so the explanation thereof will be omitted.

In the figure, 35 is a commercially available ball joint that includes a spherical bearing 24A, and 36 is a spherical bearing 24A and a pin 23.
A push bearing 37 interposed between the spherical bearing 24A and the pin 23 is a stroke bearing interposed between the spherical bearing 24A and the pin 23.

As shown in FIGS. 11 to 14, the pin 23 provided perpendicularly to the rotation plane of the lever 22 is mounted on a spherical bearing 24A.
This ball joint 35 is supported by a commercially available ball joint 35 having a ball joint 35, and this pole joint 35 is fastened to a guide ring 30. When the lever 22 rotates in the direction of the arrow, the ball joint 35 moves from A to A', and the guide ring 30 moves from B to B' in the circumferential and axial directions. The interlocking of the vanes associated with this is the same as that described in the previous embodiment.

Pin 23 and ball joint 35 shown in Figure 11.12
Because they perform rotational motion and relative motion in the axial direction,
If left as is, it will be inferior in terms of durability, so it may be necessary to lubricate it with oil.
The bearing must be interposed inside the spherical bearing 24A.

In the example shown in Figure 13.14, the push bearing 36
is press-fitted inside the spherical bearing 24A of the ball joint 35 (between the pin 23 and the spherical bearing 24A). At positions A and A' shown in FIG. 14, the pin 23 is smoothly sliding in the axial direction along the inner diameter of the push bearing 36.

In the example shown in FIG. 15, the stroke bearing 37 is mounted inside the spherical bearing 24A, and the
The same effect as the example shown in Figure 4 is expected.

According to the embodiments shown in FIGS. 11 to 15, the same effects as those of the previous embodiments are expected, and in addition, the rotatable and axially movable By regularly replacing the rotatable bearings, you can extend the durability and reliability of the entire vane control drive mechanism. [Effects of the Invention] As described above in detail, the present invention provides a vane control that can reduce the frictional resistance of the guide ring, reduce the frictional torque, use a vane drive mechanism with less friction, and reduce production costs. equipment can be provided.

Furthermore, by periodically replacing the bearing interposed between the spherical bearing and the pin, the durability and reliability of the entire vane control drive mechanism can be extended and the reliability can be improved.

[BRIEF DESCRIPTION OF THE DRAWINGS] FIG. 1 is a sectional side view of a vane control device according to an embodiment of the present invention, and FIG. 2 is a sectional view of a vane side of a turbo compressor taken along arrow A in FIG. 3 is an enlarged sectional view taken in the direction of arrow B in FIG. 2, FIG. 4 is an explanatory diagram showing the movement of the guide ring in the axial direction, and FIG. 6 is a sectional view taken along arrow C in FIG. 5, FIG. 7 is an enlarged view of the main part showing the spherical bearing in FIG. 6, and FIG. , FIG. 9 is a longitudinal cross-sectional view showing a conventional vane control device, FIG. 9 is a side cross-sectional view of essential parts showing the perturbing vane of the device shown in FIG. 8 and its active mechanism, and FIG.
-I arrow view, FIG. 11 corresponds to a view from above of FIG.
2 is a side cross-sectional view of a vane control device according to another embodiment of the present invention, FIG. 13 is a detailed view of the ball joint shown in FIG. 12, and FIG. 14 is a view along the Y-Y arrow in FIG. The perspective view, FIG. 15, is a sectional view showing another embodiment of the spherical bearing part. DESCRIPTION OF SYMBOLS 1... Impeller, 2... Casing, 3... Vane, 3a... Drive vane, 20... Active control arm, 21... Control arm, 22... Lever, 23...・Pin, 24, 24A... Spherical bearing,
25... Spherical bearing housing, 26... Spring, 3o
...Guide ring, 31...Guide pin, 32...
・Stroke bearing, 33...Bearing housing.
35... Ball joint, 36... Push bearing, 37... Stroke bearing.

Claims (1)

[Scope of Claims] 1. A vane control device for a plurality of vanes provided at an inlet of an impeller of a fluid machine, the vane control device being located in an outer circumferential space of a support casing for the plurality of vanes, What is claimed is: 1. A vane control device comprising: a guide ring movable in a direction; and a drive mechanism for interlocking the plurality of vanes is attached to the guide ring. 2. A drive mechanism for interlocking a plurality of vanes includes a control arm that rotates each of the plurality of vanes, a lever perpendicular to the axis of the control arm, a pin perpendicular to the rotation plane of the lever, and a control arm that rotates each of the plurality of vanes. The vane control device according to claim 1, further comprising a spherical bearing that supports the pin, and the spherical bearing is mounted on a guide ring. 3. The vane control device according to claim 2, wherein an elastic member is installed between a pin provided perpendicularly to the rotational plane of the lever and a spherical bearing that supports this pin. 4. The vane control device according to claim 1, wherein the guide ring is supported by a guide pin fixed to the casing via a rotatable and axially movable bearing. 5. The vane control device according to claim 2, wherein the spherical bearing supporting the pin is a rotatable and axially movable bearing interposed between the spherical bearing and the pin.