JPS60164699A - Blade angle operator for movable blade fluid machine - Google Patents

Abstract

PURPOSE:To enable operation of blade angle by regulating relative rotation against inner or outer drive ring to be rotated through power of drive side spindle by means of a brake mechanism while driving a drive mechanism through said rotation. CONSTITUTION:When performing blade angle operation, any one of brake calipers 34a, 34b to be driven through pneumatic systems 35, 35 constituting a brake mechanism 36 is functioned to produce relative differential rotation between inner drive ring 25 or outer drive ring 31 to be rotated through power of drive side spindle 4 and coupling 6. Under this state, an idler 11 journaled rotatably while penetrating through a coupling 6 to gear the gear 9 at one end with transmission gear 7 and guide the gear 10 at the other end into the coupling 6 is rotated with said differential rotation thus to drive mechanism 13 for driving a blade angle operating shaft 12 inserted into a hollow shaft 3. Consequently, the blade angle can be operated by power applied onto the drive side spindle 4 resulting in reduction of power loss.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a device for controlling the blade angle of an impeller such as a pump.

As shown in Figure 1, the blade angle operating device of the nf rotary vane type fluid machine is a type of the n1 rotor vane type fluid machine.
is provided between the pump-side hollow shaft 3 and the drive-side drive shaft 4 in order to change the blade angle of the blades 2. This wing angle control bag z
15 is adapted to change the blade angle of the blade 2 by rotating or moving the operating shaft 12 inserted through the shaft 3 in the axial direction.

By the way, the applicant of the present invention has developed the following blade angle operating device 5. As shown in Fig. 2, this device connects a main shaft 4 on the drive side and a hollow shaft 3 on the pump side by a campliner 6 having a space inside, and aligns the central axis with the outer circumference of either of the two shafts. A transmission gear 7 rotatably supported by Ia1 is provided, and this transmission gear 7 is rotationally driven by a motor 8, which is an external power mechanism. - An idler 11 is provided which is rotatably supported through the coupling 6 so that the gear 10 at the other end is fitted into the coupler ring 6.
A drive mechanism 13 for driving the blade angle operating shaft 12 inserted into the hollow shaft 3 by the rotation of the blade is housed in the coupling 6.

In this conventional example, since the motor 8 is disposed outside the coupling 6, it has advantages such as easy power supply to the motor 8, but it has the following incompatibility.

That is, even when the blade angle of the motor 8 is not changed, the rotational speeds of the main shaft 4 and the operating shaft 12 must be made to match, so it is necessary to keep the motor 8 constantly rotating while the pump is operating. For this reason, the motor 8, transmission gear 7, idler 11, etc. continue to rotate even when no yellow operation is required, resulting in a problem in that the power required for these rotations is lost.

This problem occurred because the power required for controlling the blade angle was supplied from the motor 8 placed outside.

The technical problem to be solved by the present invention is to operate the blade angle using the power applied to the drive-side main shaft.

The technical steps taken to solve this technical problem are:
The driving side main shaft and the pump side hollow shaft are connected by a coupling having a space inside, and the central axis is aligned with the outer periphery of the driving side main shaft to freely rotate an inner drive ring having a brake disc and an external gear. A friction transmission mechanism set to a predetermined friction coefficient for transmitting the power of the drive side shaft to the inner drive ring is provided, and the center axis is aligned with the upper part of the coupling to connect the brake disc and the inner drive ring. A braking mechanism is provided which rotatably supports an outer drive ring having a contact gear, and brakes a brake disc of the outer drive ring and a brake disc of the inner drive ring individually and with freely adjustable braking force, An idler having gears at both ends, one end of the vi1 gear engaged with the external gear and the internal tooth width, and the other end of the idler introduced into the coupling so as to pass through the coupling and be rotatably supported. A drive mechanism that drives the blade angle operating shaft inserted into the pump-side hollow shaft by the rotation of this idler is housed within the coupling.Thus, the inner drive rotates with the power of the drive-side main shaft. The relative rotational speed with the ring or the outer drive ring is adjusted by a braking mechanism to control the lot rotation speed and rotational direction of the idler to operate the drive mechanism.

Therefore, the above technical problem is solved, and the drive side -, F
The blade angle can be controlled using the power applied to the shaft. Further, since the direction of rotation of the idler is changed by braking either the inner drive ring or the outer drive ring, the blade angle can be increased or decreased as desired.

In addition, in the present invention, the relative rotational speed between the inner drive ring or the outer drive ring and the coupling is adjusted by the braking mechanism, so when the blade angle operation is not required, the braking mechanism does not brake the two rings. No power loss occurs due to the mechanism,
Furthermore, even if the braking mechanism becomes inoperable, the sheath machine itself can still be operated, improving reliability.

Hereinafter, the present invention will be explained in detail with reference to FIG. In FIG. 3, the same reference numerals as in FIGS. 1 and 2 indicate the same or equivalent parts.

The drive-side main shaft 4 and pump-side hollow shaft 3 in FIG. This coupling 6 consists of a main body 20 and a top plate 21, and has a space 22 formed therein. The main body 2o is fitted onto the upper end of the hollow shaft 3, and the E-face plate 21 is fitted onto the lower end of the L shaft 4. A bearing 2 is provided on the outer periphery of the boss portion 23 of the top plate 21.
4, an inner drive ring 25 is rotatably supported with its central axis aligned with the main shaft 4. Drive ring 25
A disc-shaped brake disc 26 is formed on the upper part of the disc, and a circumferential gear 27 is carved in the corner.

A friction ring 28, which is a friction transmission mechanism, is interposed between the inner peripheral surface of the inner drive ring 25 and the outer peripheral surface of the boss portion 23. The friction ring 28 is annularly formed of a friction material having a predetermined coefficient of friction, and is configured to transmit power within a certain limit from the main shaft 4 to the inner drive ring 25.

A projecting circumferential wall 29 is protruded from the upper surface plate 21, and an outer drive ring 31 is rotatably supported on the inner side of the projecting circumferential wall 29 via a bearing 30 with its central axis aligned with the main shaft 4. has been done. This outer drive ring 31 is provided with a brake disc 32 whose outer diameter matches that of the brake disc 26 of the inner drive ring 2'5, and an internal gear 33.

Brake calipers 34a and 34b are provided to brake both brake discs 26 and 32 individually and with freely adjustable braking force, and these brake calipers 34a and 34b are driven by pneumatic devices 35 and 35. It looks like this. These pneumatic devices 35.
An idler 11 is provided passing through the upper plate 21 on which a braking mechanism 36 is formed with brake calipers 34a and 34b, and a gear 9 formed at one end of the idler 11 is connected to the external gear 27 and the internal gear. The center 10 at the end of the idler 11F meshes with the gear 37 of the drive mechanism 13, so that the rotation of the idler 11 is transmitted from the drive mechanism 13 to the operating shaft 12.

Further, a rotating shaft 38 is suspended from the lower end of the idler l'l, and a threaded portion 39 is formed at the lower end of the rotating shaft 38. A phase opening 40 that is slidably attached to the outer periphery of the upper end of the main body 20 is screwed into this threaded portion 39, and the amount of movement of this pointer 40 corresponds to the number of rotations of the idler 11, that is, the number of rotations of the idler 11.
The wing angle is displayed.

In the embodiment with such a configuration, when no blade angle operation is required, the brake calipers 34a and 34b are not operated, and the inner drive ring 25 and the outer drive ring 31 are rotated at the same speed as the main shaft 4. In this state, the idler 11 does not rotate the gear 37 and the drive mechanism 13 does not operate. When operating the blade angle, either one of the brake calipers 34a and 34b is operated and the inner drive ring 25 or the outer drive ring 31 is operated. A relative rotational speed difference is generated between the coupling 6 and the coupling 6. In this state, the idler 11 is rotated at a rotational speed that is the difference between the rotational speeds, the gear 37 rotates by this rotation, and the drive mechanism 13
is driven. And brake caliper 34a, 3
Coupling 6 depending on which of 4b is activated.
The direction of rotation of the idler 11 is switched relative to the rotation direction.

Note that the present invention is not limited to the above embodiments. For example, in a brake caliper, 34a and 34b are not necessarily separate parts, but can be integrated as long as they can brake both brake discs 26 and 32 individually, and the operation source is not limited to the pneumatic device 35. , may be hydraulically powered, electrically powered or manually operated.

Further, the friction ring 28 is provided with a bracket 41 on the main shaft 4, as shown by the two-dot chain line in FIG.
The shoe 42 attached to the drive ring 25 may be brought into pressure contact with the friction ring 4'3 at one upper end of the drive ring 25. Furthermore, the operation shaft 12 may be moved not only by rotation but also in the axial direction.

[Brief explanation of drawings]

1 and 2 are diagrams showing a conventional example, in which FIG. 1 is an overall configuration diagram of a movable vane pump, FIG. 2 is a vertical cross-sectional view of a vane angle operating device 5, and FIG. 3 is an embodiment of the present invention. It is a longitudinal cross-sectional view showing an example. 3... Pump side hollow shaft 4... Drive side main shaft 6... Coupling 11... Idler 13... Drive mechanism 25... Inner drive ring 31... Outer drive ring 36...・Braking mechanism patent applicant: Kubota Iron Works Co., Ltd. Representative: Takashi Suzusha, Physician

Claims (1)

[Claims] An inner drive ring is provided which connects the driving side main shaft and the pump side hollow shaft with a camp ring having a space inside, and aligns the central axis with the outer periphery of the driving side main shaft to align the brake disc and the external gear. A friction transmission mechanism is rotatably supported and set to a predetermined friction coefficient for transmitting the power of the drive side main shaft to the inner drive ring, and the center axis is aligned with the upper part of the camp ring to connect the brake disc. An external drive ring having an internal gear is rotatably supported, and this external drive,
A braking mechanism is provided that brakes the brake disc of the ring and the brake disc of the inner drive ring individually and with freely adjustable braking force, and has gears at both ends, with the gear at one end meshing with the external gear and the internal gear. The gear at the other end is introduced into the coupling, and an idler is provided which is rotatably supported by passing through the coupling.The rotation of this idler causes the blade angle control shaft to be inserted into the hollow shaft on the front side of the pump. ++(Retard angle operating device for a moving vane type wave body machine), characterized in that a drive mechanism for driving the ++ is accommodated in the coupling.