JP2807498B2 - Vane control device - Google Patents

Description

Description: BACKGROUND OF THE INVENTION The present invention relates to a vane control device, and more particularly, to a capacity control in a fluid machine such as a turbo compressor having a centrifugal impeller or an axial impeller. Control device suitable for driving the vane for the purpose.

[Conventional technology]

In a conventional device, for example, as described in Japanese Patent Publication No. 57-45759, the drive arms of the vane control devices at each stage are connected to connection arms attached to a drive shaft driven by an actuator, respectively. No consideration was given to the complicated structure and the large number of parts.

Means such as a variable vane 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. 57-45759 of the prior art will be described with reference to FIGS.

FIG. 8 is a longitudinal sectional view showing a conventional vane control device, FIG. 9 is a side sectional view showing a main part of a drive vane and a drive mechanism of the device shown in FIG. 8, and FIG. II
It is an arrow view.

In the drawing, 1 is an impeller of a centrifugal compressor, 2 is a casing, 2a is a suction bell mouth, 3 is a plurality of vanes mounted on the upstream portion of the impeller 1, and one of the vanes 3 is used. Is a drive vane 3a, and the vane 3 and the drive vane 3a
Alternatively, it is rotatably supported by a ball bearing 5 provided on the casing 2 via a drive vane shaft 4a. 6
Is a drive arm fixed to the drive vane shaft 4a, 7 is a connecting rod having one end attached to the drive arm 6 by a pin 8, and the other end of the connecting rod 7 is attached to an actuator 9, and the operation of the actuator 9 Drive vane shaft
4a rotates, and the driving vane 3a also rotates with the rotation of the driving vane shaft 4a.

A drive control arm 10 is attached to the drive vane shaft 4a.
10 ends are vane shaft 4 and drive vane shaft
It is connected via a ball joint 12 to a guide ring 11 provided to slide and rotate on the outer periphery of the casing 2 adjacent to 4a. Since the guide ring 11 is connected to the vane shaft 4 via the ball joint 13 and the driven control arm 14, when the drive vane shaft 4 a is rotated by the operation of the actuator 9, all the vanes are rotated via the guide ring 11. The shaft 4 is rotated in synchronization with the drive vane shaft 4a.

With such a configuration, the actuator 9
The vane control device can be opened and closed by giving a rotational motion to 3,3a.

As a problem in the conventional vane drive mechanism,
Since the guide ring 11 slides around the casing 2, the frictional resistance increases, and as a result, the torque of the actuator for driving each vane 3 increases. If the friction torque can be reduced, the only required torque is the air torque acting on each vane 3, so that the torque required for driving can be greatly reduced. In addition, a large frictional force decreases the response speed of the opening and closing of the vane, and is not appropriate when the friction is large and the vane is repeatedly opened and closed.

Thus, for example, Japanese Utility Model Application No. 58-54957 (Japanese Utility Model Application Laid-Open No. 59-160)
No. 895), as described in the microfilm,
A configuration in which the guide ring and the casing do not contact each other has been developed. However, in this device, the guide ring and the vane drive pin are connected via a groove,
Since the drive pin makes a sliding motion between the groove and the groove, the sliding portion is easily worn and has a short life. When friction occurs, the positional accuracy changes and the performance of the fluid machine is not reduced.

On the other hand, the mechanism described in Japanese Utility Model Publication No. 44-21729 uses a spherical bearing and a stationary blade rotating lever that requires spherical machining at the tip, but this requires complicated processing and high production cost. Was.

The present invention has been made in order to solve the problems in the prior art described above, and a vane control device that has good controllability and reduced production cost by reducing the frictional resistance of a guide ring and the frictional resistance of a vane drive mechanism. Its purpose is to provide.

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

[Means for solving the problem]

In order to achieve the above object, a first configuration of a vane control device according to the present invention is a vane control device for a plurality of vanes provided at an inlet of an impeller of a fluid machine, wherein the plurality of vanes is provided. A control arm that includes a guide ring that is located in the outer peripheral space of the support casing of the vane and that is movable in the circumferential direction and the axial direction, and as a drive mechanism that links the plurality of vanes, a control arm that rotates each of the plurality of vanes. A vane control device having a lever perpendicular to the axis of the arm, a pin perpendicular to the rotation plane of the lever, and a spherical bearing for supporting the pin, and mounting the spherical bearing on a guide ring; The ring is pivotable,
It is supported by a guide pin fixed to the casing via an axially movable bearing.

Further, the second aspect of the vane control device according to the present invention
The configuration of the vane control device for a plurality of vanes provided at the inlet of the impeller of the fluid machine,
A control mechanism that includes a guide ring that is located in an outer peripheral space of a support casing of the plurality of vanes and is movable in a circumferential direction and an axial direction, and that rotates the plurality of vanes as a driving mechanism that links the plurality of vanes. A vane control comprising an arm, a lever perpendicular to the axis of the control arm, a pin perpendicular to the plane of rotation of the lever, and a spherical bearing for supporting the pin, and mounting the spherical bearing on a guide ring. In the device, the spherical bearing that supports the pin has a rotatable and axially movable bearing interposed between the spherical bearing and the pin.

Note that the concept of developing the present invention is as follows.

In order to achieve the above object, the guide ring 11 shown in FIG. 8 is floated in the air like the vane variable mechanism described in Japanese Utility Model Publication No. Sho 44-21729 (the guide ring is located in the outer peripheral space of the casing. There is a need to. Further, it is necessary to develop an alternative to expensive means such as spherical machining of the tip portion of the stationary blade rotating lever described in the publication.

In view of this, in the present invention, the guide ring is floated in the air. In addition, this guide ring,
In Japanese Patent No. 21729, the structure is not movable in the axial direction, whereas in the present invention, the structure is also movable in the axial direction. The movement of the guide ring and the vane, which are movable in this axial direction,
The present invention is configured so that the friction is small and the processing is simple.

[Action]

4 to 7
This will be described with reference to the drawings.

FIG. 4 is an explanatory view showing the axial movement of the guide ring, FIG. 5 is a side sectional view showing a main part of the vane control device, FIG. 6 is a sectional view taken along the arrow C in FIG. FIG. 7 is an enlarged view of a main part showing the spherical bearing of FIG.

The guide ring 30 and the vane 3 are linked by a pin 23 attached to the lever 22 and a spherical bearing 24. Vane 3
However, if the guide ring 30 is rotated by an angle α in the direction of the arrow (rightward) shown in FIG. 4, the guide ring 30 moves from the initial position by Δx in the axial direction to the position of '. At this time,
The spherical bearing 24 and the pin 23 move relatively by Δh as shown in FIG.

The pin 23 is perpendicular to the plane of rotation of the lever 22, but the angular difference is easily absorbed by the spherical bearing 24 mounted on the guide ring 30. Therefore, only the relative displacement Δh between the pin 23 and the spherical bearing 24 is provided as the slip portion, and the torque required for driving by friction becomes extremely small.

As the spherical bearing, a set together with a spherical bearing housing is commercially available at low cost, and can be used.

In addition, although this is an example in which a spherical bearing is attached to the guide ring 30 as shown in FIG. 6, the operation is exactly the same even if a commercially available ball joint 35 is attached as shown in FIGS. .

In particular, according to the first configuration of the present invention, the guide ring is supported by the guide pin fixed to the casing via the rotatable and axially movable bearing, so that the guide ring 30 is circumferentially mounted. While it moves in the axial direction as well as in the direction, the friction at the contact portion can be reduced, and the friction can be reduced.

Further, according to the second configuration of the present invention, a rotatable and axially movable bearing is interposed between the spherical bearing and the pin.
The durability of the entire vane control drive mechanism can be extended and reliability can be improved.

〔Example〕

Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1 to 7 and FIGS. 11 to 15.

First, FIG. 1 is a side sectional view of a vane control device according to an embodiment of the present invention, FIG. 2 is a front view of a vane side of a turbo compressor according to a sectional view taken along the arrow A of FIG. The figure is an enlarged sectional view as viewed from the direction of the arrow B in FIG.

In each figure, the same reference numerals as those in FIG. 8 indicate the same or corresponding parts as in the prior art.

1 to 3, reference numeral 20 denotes a drive control arm directly connected to the drive vane 3 a, reference numeral 21 denotes a control arm directly connected to each of the other plurality of vanes 3, and reference numeral 22 denotes a direction perpendicular to the axis of the control arm 21. Lever, 23 is a pin provided perpendicular to the rotation plane of the lever 22, and 24 is the pin
Reference numeral 23 denotes a spherical bearing for supporting the spherical bearing, and reference numeral 25 denotes a spherical bearing housing mounted on the guide ring. As the spherical bearing 24, a set as a bearing together with the spherical bearing housing 25 is commercially available at low cost, and can be employed.

26 is a spring related to the elastic member mounted between the pin 23 and the spherical bearing 24.

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

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

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

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

As shown in FIG. 2, in order to rotate the drive vane 3a, the drive vane 3a corresponds to a vane shaft via a drive connecting rod 7 and a drive arm 6 by the operation of an actuator (not shown, see 9 in FIG. 9). The drive control arm 20 rotates. As a result, the drive vane 3a rotates, and a guide ring is provided by a lever 22 provided on the drive control arm 20 and a pin 23 perpendicular to the rotation plane of the lever 22.
30 is moved in the circumferential direction. Then, a plurality of control arms 21 are rotated via a spherical bearing housing 25, a spherical bearing 24, a pin 23 supported on the spherical bearing housing 25, and a lever 22 mounted on a plurality of circumferential positions of the guide ring 30, and a plurality of vanes 3 also rotates by the same angle as the drive vane 3a.

In this case, a spring 26 is mounted on each pin 23 in order to rotate the guide ring 30 in a circumferential direction on a concentric circle. More specifically, the spring 26 is provided on the pin 23 between the lever 22 and the spherical bearing 24, and may be functionally set between the pin 23 and the guide ring 30.

Thus, the guide ring 30 can be kept concentric.

A guide pin 31 may be provided on the outer circumference (see FIGS. 1 and 2) or on the inner circumference (not shown) of the guide ring 30 so that the guide ring 30 moves concentrically. The details are shown in FIG.

In FIG. 3, reference numeral 32 denotes a stroke bearing relating to a bearing mounted on the outer periphery of the guide pin 31, and reference numeral 33 denotes a bearing housing of the stroke bearing 32, which is a guide ring 30.
Contact with. That is, this stroke bearing 32
Is a bearing 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 circumferential direction as well as in the axial direction, but the friction of the contact portion is reduced and the friction is reduced. It is possible.

According to the present embodiment, the friction torque can be reduced with respect to the vane driving mechanism as described in Japanese Patent Publication No. 57-49759, and driving with less wear can be performed.

Also, there is no need for special machining and special bearings, such as the spherical bearing mechanism of the stationary blade rotating lever for the guide ring floating in the air described in Japanese Utility Model Publication No. 44-21729, and a commercially available spherical bearing with low cost vanes. There is an effect of providing a control device.

The same operation and effect can be expected by using a bush bearing press-fitted into the bearing housing 33 instead of the stroke bearing 32 shown in FIG.

Further, if the stroke bearing 32 and the bearing housing 33 are integrally processed using a bearing material, the number of parts can be further reduced.

Next, FIG. 11 corresponds to a view of FIG. 12 as viewed from above, and is an explanatory view showing the axial movement of the guide ring. FIG. FIG. 13 is a detailed view of the ball joint portion of FIG. 12, FIG. 14 is a view taken along the line YY of FIG. 13, and FIG. 15 is another embodiment of the spherical bearing portion. FIG. In the figure, those having the same reference numerals as those in FIG. 1 are the same as those in the previous embodiment.
The description is omitted.

In the figure, 35 is a commercially available ball joint including a spherical bearing 24A, 36 is a bush bearing interposed between the spherical bearing 24A and the pin 23, and 37 is a ball bearing between the spherical bearing 24A and the pin 23. It is an interposed stroke bearing.

As shown in FIGS. 11 to 14, the pin 23 provided perpendicular to the rotation plane of the lever 22 is supported by a commercially available ball joint 35 having a spherical bearing 24A, and the ball joint 35 is attached to the guide ring 30. Has been concluded. Lever 22
When is rotated 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 associated movement of the vanes is the same as that described in the previous embodiment.

The pin 23 and the ball joint 35 shown in FIGS.
Since they rotate relative to each other and move in the axial direction, durability is inferior as they are. Therefore, oil lubrication or a bearing must be provided inside the spherical bearing 24A.

In the example shown in FIGS. 13 and 14, the bush 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 the positions A and A 'shown in FIG. 14, the pin 23 slides smoothly in the axial direction along the inner diameter of the bush bearing 36.

In the example shown in FIG. 15, the stroke bearing 37 is mounted inside the spherical bearing 24A, and the same operation and effect as the examples shown in FIGS. 13 and 14 are expected.

According to the embodiment shown in FIGS. 11 to 15, the same effects as those of the previous embodiment can be expected, and the rotatable, axially movable member provided inside the spherical bearing (between the pin and the spherical bearing) is provided. By periodically replacing the free bearing, the durability of the entire vane control drive mechanism can be extended and the reliability can be increased.

〔The invention's effect〕

As described above in detail, according to the present invention, it is possible to provide a vane control device that has good controllability and reduced production cost by reducing the frictional resistance of the guide ring and the frictional resistance of the vane drive mechanism. .

In addition, by periodically replacing the bearing provided between the spherical bearing and the pin, there is an effect that the durability of the entire vane control drive mechanism is extended and the reliability is improved.

[Brief description of the drawings]

1 is a side sectional view of a vane control device according to an embodiment of the present invention, FIG. 2 is a front view of a vane side of a turbo compressor according to a sectional view taken along the arrow A of FIG. 1, and FIG. 2 is an enlarged sectional view taken in the direction of arrow B in FIG. 2, FIG. 4 is an explanatory view showing the axial movement of the guide ring, FIG. 5 is a side sectional view showing a main part of the vane control device, and FIG. FIG. 5 is a sectional view taken along the arrow C in FIG. 5, FIG. 7 is an enlarged view of a main part showing the spherical bearing portion in FIG. 6, FIG. 8 is a longitudinal sectional view showing a conventional vane control device, and FIG. , FIG. 10 is a side sectional view of a main part showing a driving vane and its driving mechanism of the apparatus of FIG. 8, and FIG.
I arrow view, FIG. 11 is equivalent to FIG. 12 viewed from above,
Explanatory diagram showing the axial movement of the guide ring, FIG. 12,
FIG. 13 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 a ball joint portion of FIG. 12, FIG. FIG. 15 is a sectional view showing another embodiment of the spherical bearing portion. 1 impeller, 2 casing, 3 vanes, 3a
… Drive vane, 20 …… drive control arm, 21 ……
Control arm, 22 Lever, 23 Pin, 24, 2
4A ... Spherical bearing, 25 ... Spherical bearing housing, 26 ... Spring, 30 ... Guide ring, 31 ... Guide pin, 32 ... Stroke bearing, 33 ... Bearing housing, 35 ... Ball joint, 36 ... ... bush bearings, 37 ... stroke bearings.

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-63-23100 (JP, A) JP-A-59-160895 (JP, U) JP-A-59-45298 (JP, U) JP-A-56-23 71995 (JP, U) JP-A-59-64495 (JP, U) JP-B-57-49759 (JP, B2) JP-B-44-21729 (JP, Y1) (58) Fields investigated (Int. Cl. ⁶ , DB name) F04D 29/46

Claims (2)

(57) [Claims] A vane control device for a plurality of vanes provided at an inlet of an impeller of a fluid machine, wherein the vane control device is located in an outer peripheral space of a support casing of the plurality of vanes and is movable in a circumferential direction and an axial direction. A control arm that rotates each of the plurality of vanes, a lever that is orthogonal to the axis of the control arm, and a lever that is perpendicular to the rotation plane of the lever. And a spherical bearing for supporting the pin, wherein the spherical bearing is mounted on a guide ring, wherein the guide ring includes a casing that is rotatable and axially movable via a bearing. A vane control device supported by a guide pin fixed to the side. 2. A vane control device for a plurality of vanes provided at an inlet of an impeller of a fluid machine, wherein the vane control device is located in an outer peripheral space of a support casing of the plurality of vanes and is movable in a circumferential direction and an axial direction. A control arm that rotates each of the plurality of vanes, a lever that is orthogonal to the axis of the control arm, and a lever that is perpendicular to the rotation plane of the lever. And a spherical bearing that supports the pin, wherein the spherical bearing is mounted on a guide ring, wherein the spherical bearing that supports the pin is located between the spherical bearing and the pin. A vane control device comprising a rotatable and axially movable bearing.