JPS642784B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a fluid machine equipped with a blade angle control device.

The blade angle control device is equipped with a blade angle control operating shaft for driving the movable blade in a rotary shaft on which a movable blade of a fluid machine is attached, so that the blade angle control operation shaft can be moved in the axial direction. There are those that support the rotary shaft and those that support it by a stationary object other than the rotary shaft. If the movable blade is operated by supporting the blade angle control force with a stationary object, this acting force will act between the rotating shaft and the stationary object, so this force will be applied to the thrust bearing that supports the rotating shaft. The disadvantage is that a larger capacity thrust bearing is required due to the additional acting force. On the other hand, in the case where the blade angle control force is supported by the rotary shaft, the blade angle control force is not applied to the thrust bearing that supports the rotary shaft because the rotary shaft is equipped with a means for operating the blade angle control control shaft. .

Conventionally, as a means for operating a blade angle control operating shaft on a rotating shaft, a hydraulic cylinder is generally provided on the rotating shaft concentrically with the rotating shaft, and the piston of the hydraulic cylinder and the blade angle controlling operating shaft are connected. It had been taken. However, in the case of such a hydraulic drive device, it is necessary to include a hydraulic supply device, a feedback mechanism for controlling the blade angle, etc., making the device large and complicated.
Additionally, there was a problem with hydraulic seals, and hydraulic pressure had to be applied even during operation with a constant blade angle, resulting in considerable operating costs.

Therefore, mechanical drive devices are often used to control the blade angle of relatively small fluid machines. However, conventional mechanical drive devices, such as the
- Like the invention described in Publication No. 6078, the thrust of the blade angle control operating shaft is supported by a stationary object other than the rotating shaft, so the drawback is that the thrust bearing that supports the rotating shaft becomes large. It was hot.

In order to eliminate the above-mentioned drawbacks in a fluid machine equipped with a blade angle control device, the present invention provides a mechanical actuation means that does not use hydraulic pressure and has a structure in which the thrust of a blade angle control operating shaft is supported on a rotating shaft. It is intended to.

Embodiments of the present invention will be described below with reference to the drawings. Figure 1 is a cross-sectional view taken along the line A-A in Figure 4, Figure 2 is a partially enlarged view of Figure 1, Figure 3 is a partial vertical cross-sectional view at a different position from Figure 1, and Figure 4 is a cross-sectional view of Figure 4. FIG. 2 is a sectional view taken along line BB in FIG. 1;

Hollow main shaft 1 of fluid machine with blade angle control device
A blade angle control operation shaft 5 is inserted into the inside of the blade angle control shaft 5 so as to be freely movable in the axial direction. Although not shown, a direct operating member connected to the movable wing is engaged with this operating shaft 5 for controlling the blade angle. The blade angle control operating shaft 5 is fitted into a disk-shaped crosshead 6 via a key, and is fixed by a shaft nut 7 screwed into the blade angle control operating shaft 5. A plurality of connecting rods 8 are fitted into axial holes on the circumference of the crosshead 6, and are fixed to nuts 9 screwed into the connecting rods 8. The connecting rod 8 passes axially displaceably through the coupling ring 10 and is connected to a sliding ring 11 which is slid onto the coupling ring 10 so as to be axially displaceable. The sliding ring 11 is coupled to the piece 12 via a bearing 13 so that it does not move in the axial direction and is rotatable.

A female thread 12d coaxial with the main shaft 1 is cut in the bridge 12, and the female thread 12d engages with an external thread 10d of a coupling ring 10 fitted and fixed to the main shaft 1.
This male thread 10d may be provided on a member that rotates integrally with the main shaft 1 or directly on the main shaft 1. A spur gear 12a coaxial with the main shaft 1 is cut on the outer periphery of the bridge 12, and the spur gear 12a is supported via a bearing 4 on a blade angle control force transmission shaft 2 parallel to the main shaft 1. It meshes with spur gears 2a, 2b, and 2c.
The blade angle control force transmission shaft 2 is rotatably supported by a casing 17 fixed to a fixed frame 19 via bearings 15 and 16 so as not to move in the axial direction. Electromagnetic clutches 3a, 3b, and 3c are provided on the blade angle control force transmission shaft 2 to connect and disconnect the blade angle control force transmission shaft 2 and the spur gears 2a, 2b, and 2c.

The electromagnetic clutches 3a, 3b, 3c are of known construction and are shown in FIG. A core 21 is fixed to the blade angle control force transmission shaft 2, an electromagnet 23 is attached to the core 21 via a bearing 22, and the electromagnet 23 is locked to the casing 17 by a member not shown so as not to rotate. . Spur gears 2a, 2b,
External toothed adapter 24 and core 21 fixed to 2c
Friction plates 26 are alternately engaged with each other so as to be movable in the axial direction, and an armature 25 faces the core 21 with the friction plates 26 in between. By energizing the electromagnet 23, the armature 25 is magnetically attracted, the friction plate 26 comes into close contact with the armature 25, and the spur gears 2a, 2b, 2c become integral with the blade angle control force transmission shaft 2.
The spur gears 2a, 2b, and 2c are mounted on the blade angle operating force transmitting shaft 2 via bearings 4 so as to be rotatable with respect to the blade angle operating force transmitting shaft 2 and not to move in the axial direction. A spur gear 18 is fitted into the main shaft 1 via a key, and meshes with a spur gear 14 fitted into the blade angle operating force transmission shaft 2 via a key.

Spur gears 12a, 2a, 2b, 2c, 18, 14
The number of teeth Z _12a , Z _2a , Z _2b , Z _2c , Z ₁₈ , Z ₁₄ is Z ₁₈ /Z ₁₄ ×Z _2a /Z _12a = 1 (1) Z ₁₈ /Z ₁₄ ×Z _2b /Z _12a ＞1 (2) It is set so that Z ₁₈ /Z ₁₄ ×Z _2c /Z _12a <1 (3). In the configuration of this embodiment, such a gear ratio is obtained by using spur gears 2b and 2c as shifted gears. Since the spur gear 12a moves in the axial direction while meshing with the spur gears 2a, 2b, and 2c, the tooth width of the spur gear 12a is set to a length that takes into account the amount of axial movement in order to maintain meshing at all times.

The opponent's cup ring is 20 for the cup ring of 10.
is fixed, and a power transmission shaft (not shown) is fixed to a coupling 20, so that the main shaft 1 and the power transmission shaft are connected.

A cylindrical shaft sealing material 27 with a flange is fixed to the casing 17, and the shaft sealing material 27 is attached to the coupling ring 20.
The cylindrical shaft sealing material 28 fixed to the shaft sealing member 28 and the cylindrical end loosely fit into each other to form a shaft seal. Casing 17
The space between the main shaft 1 and the main shaft 1 is sealed by a sealing material 29.

FIG. 3 is a diagram showing means for detecting axial movement of the piece 12. The bearing holder fixed to the piece 12 is a disc 31, and a shifter 32 that engages with the disc 31 engages with the axial guide of the casing 17, and a sensitive piece 33 at the tip of the shifter 32, for example, The position is detected by a position detector 34 fixed to the casing 17, such as a potentiometer.

Next, the operation of the fluid machine equipped with the blade angle control device of the present invention will be explained. During operation of a fluid machine with movable blades, the main shaft 1, couplings 10, 20, power transmission shaft, blade angle control operating shaft 5, shaft nut 7, crosshead 6, connecting rod 8, sliding ring 11, etc. are always integrated. Rotate.

When keeping the blade angle constant, the electromagnetic clutch 3a is connected and the other electromagnetic clutches 3b and 3c are connected.
Leave it free. If the rotation speed of the main shaft 1 is N ₁ , the spur gears 2a and 14 on the blade angle operating force transmission shaft 2 rotate at the same rotation speed Z _12a /Z _2a N ₁ =Z ₁₈ /Z ₁₄ N ₁ , and the piece 12 The number of rotations N ₁₂ = Z _2a /Z _12a ×Z ₁₈ /Z ₁₄ ×N ₁ =N ₁ , and the piece 12 does not rotate relative to the main shaft 1. In other words, since the blade angle control operating shaft 5 does not move in the axial direction, the blade angle is kept constant. When the spindle 1 accelerates or decelerates, or even if the piece 12 attempts to rotate due to vibration, etc., the spur gear 18-
The piece 12 is connected to the spur gear 14, the blade angle operating force transmission shaft 2, the electromagnetic clutch 3a, and the spur gear 2a.
is braked so as not to rotate relative to the main shaft 1. And by this, screw 1
It is also possible to increase the lead angles of 2d and 10d to improve screw efficiency. Incidentally, when the lead angles of the screws 12d and 10d are small, the spur gear 2a, electromagnetic clutch 3a, etc. can be omitted.

When performing blade angle control, the electromagnetic clutch 3b
is connected, and the other electromagnetic clutches 3a and 3c are released. Spur gears 14, 2b on the blade angle operating force transmission shaft 2
rotates at the same number of revolutions Z ₁₈ /Z ₁₄ ×N ₁ , and the number of revolutions of the piece 12 N ₁₂ = Z _2b /Z _12a ×Z ₁₈ /Z ₁₄ ×N ₁ >N ₁ , and the piece 12 rotates on the main shaft 1. On the other hand, the bearing 13 rotates relative to the bearing 13. The rotational movement of the bridge 12 with respect to the main shaft 1 is caused by the female thread 12d of the bridge 12 and the male thread 10 on the coupling ring 10.
d into an axial motion, the sliding ring 11 is slid axially on the coupling 10 via the bearing 13, and the blade angle control operating shaft 5 is moved axially via the connecting rod 8 and crosshead 6. The blade angle changes. When the electromagnetic clutch 3c is connected and the other electromagnetic clutches 3a and 3b are released, the spur gears 14 and 2c on the blade angle control force transmission shaft 2 rotate at the same rotation speed Z ₁₈ /Z ₁₄ ×N ₁ Then, the rotation speed of the bridge 12 is N ₁₂ = Z _2c /Z _12a ×Z ₁₈ /Z ₁₄ ×N ₁ <N ₁ , and the bridge 12 rotates relative to the main shaft 1 in the opposite direction to that when the electromagnetic clutch 3b is connected. do. In other words, the blade angle changes in the opposite direction to that when the electromagnetic clutch 3b is actuated.

Incidentally, when operating the blade angle, the spur gear 12a is replaced by the spur gear 2a,
It moves in the axial direction while meshing with the spur gears 2b and 2c, but the axial resistance due to the tooth load based on the operating force between the tooth surfaces is caused by the coupling between the spur gears 2b and 2c driven by the electromagnetic clutch and the spur gear 12a. The loss of power due to the operation is small because it occurs only in between and is minute and the axial movement speed is slow.

The axial thrust as the blade angle operating force is carried by the threaded surfaces of the female thread 12d of the bridge 12 and the male thread 10d of the coupling ring 10. In other words, since the coupling ring 10 is fixed to the main shaft 1, the blade angle operating force is supported by the main shaft 1. In this way, as the piece 12 moves, the disk 31 also follows, the shifter 32 moves up and down the guide of the casing 17, and the sensitive piece 33 moves. The position detector 34 detects the position of the sensitive piece 33, and the position of the sensitive piece 33, that is, the position of the blade angle control operating shaft 5, is displayed via a control circuit (not shown), and the position of the operating shaft 5 is displayed in accordance with the position of the operating shaft 5. The wing angle is determined.

As may be clear from the above explanation, in this embodiment, a spur gear rotatably provided on a single blade angle operating force transmission shaft 2 parallel to the main shaft 1 is used to connect the spur gear 12a of the bridge and the spur gear 14. 2a, 2b, 2c as spur gear 1
2a, and the spur gear 14 fixed to the blade angle control force transmission shaft 2 is meshed with the spur gear 18 fixed to the main shaft 1, and between the spur gears 2a, 2b, 2c and the blade angle control force transmission shaft 2. Although an electromagnetic clutch is used, the present invention uses a spur gear with a gear ratio such that when the main shaft rotational speed is _N1 , the rotational speed _N12 of the piece 12 rotates at _N12 > _N1 or _N12 < _N1 . The gear train is not limited to the embodiment as long as it is a uniaxial back gear device that can selectively connect 12a and 18.

FIG. 5 is a longitudinal sectional view of another embodiment of the invention. The same functional parts as in the first embodiment are given the same reference numerals. In this embodiment, a mechanical clutch is used to engage the blade angle control force transmission shaft 2 and the spur gears 2b, 2c without using an electromagnetic clutch. Clutch pawls 2b-1 and 2c-1 are cut into the end faces of the spur gears 2b and 2c, and the clutch pawls 2b-1 and 2c-1 are slid onto the blade angle manipulation force transmission shaft 2 via a sliding key 36 fixed to the blade angle manipulation force transmission shaft 2. A pawl clutch 35 is provided. The pawl clutch 35 is fixed to the casing 17 in parallel to the blade angle operating force transmission shaft 2 as a means for moving the pawl clutch 35 in the axial direction so that the pawl clutch 35 selectively engages with either of the clutch pawls 2b-1 and 2c-1. A shifter yoke 38 fitted onto a splined shaft 37 engages with the pawl clutch 35, and a pinion 39 integral with the operating shaft engages with the latch of the pawl clutch 35. The operating shaft extends outside the casing 17 and is provided with a rotating means.

In this embodiment, one of the clutch pawls at both ends of the pawl clutch 35 is connected to the clutch pawls 2b-1 and 2c-1.
By engaging with, the piece 12 moves in the axial direction to perform blade angle control.

FIG. 6 is a drive system diagram showing still another embodiment of the present invention. A spur gear 18 fixed to the main shaft 1 has electromagnetic clutches 3a, 3b,
Spur gears 2a, 2b, 2c are selectively connected to the shaft 2 via gears 3c. Spur gear 12 of piece 12
A spur gear 14 is meshed with a. The other configurations are the same as those of the previously described embodiments. The code of each spur gear is Z
When the number of teeth is expressed as an auxiliary number, the number of teeth ratio is Z _12a /Z ₁₄・Z _2a /Z ₁₈ = 1 Z _12a /Z ₁₄・Z _2b /Z ₁₈ ＞1 Z _12a /Z ₁₄・Z _2c /Z ₁₈ <1, and by energizing the electromagnetic clutch 3a,
The spur gear 12a of the piece 12 rotates together with the main shaft 1.
does not move in the axial direction. Electromagnetic clutch 3b, 3c
The spur gear 12a of the piece 12 rotates relative to the main shaft 1 due to the energization of either of the screws 10d, 1.
2d to move in the axial direction and perform blade angle control.

Although an electromagnetic clutch is used in FIG. 6, when a pawl clutch is used, a spur gear 2a and an electromagnetic clutch 3a are not provided, but spur gears 2b and 2c that mesh with a spur gear 18 are provided on the blade angle operating force transmission shaft 2, and the coaxial 2a is not provided. The shaft 2 and the spur gear 2b are selectively connected by a pawl clutch provided above.
2c is connected (not shown).

In the present invention, a mechanical operating means for controlling the blade angle is provided on the rotating shaft of a fluid machine equipped with a blade angle control device, so that the blade angle control force does not act on the thrust bearing of the rotating shaft. can be made smaller. Furthermore, when converting an existing fixed-blade pump into a movable-blade pump, there is no need to change the thrust bearing, so the movable-blade pump can be achieved without changing the main motor that drives the pump. Since the rotation of the piece relative to the rotation axis is converted into axial motion using a pair of screws, the piece does not rotate due to the friction of the screw even if the blade angle control operating shaft receives thrust due to the fluid force applied to the blade. In other words, no power is required to keep the blade angle constant except during blade angle control operations.

Since the blade angle control power is transmitted from the rotating shaft,
A drive unit for controlling the blade angle is not required.

A back gear mechanism is used to transmit the rotation of the main shaft to the piece 12, and a plurality of gears are provided on one back gear shaft (blade angle operating force transmission shaft) via clutches so as to be selectively connected to the shaft. Because of this, the number of gears, shafts, bearings, etc. is small and the configuration is simple.

[Brief explanation of drawings]

All drawings show embodiments of the present invention.
The figure is a cross-sectional view taken along line A-A in Figure 4, Figure 2 is a partially enlarged view of Figure 1, Figure 3 is a vertical cross-sectional view at a different position from Figure 1, and Figure 4 is B in Figure 1. -B sectional view, FIG. 5 is a longitudinal sectional view of another embodiment, and FIG. 6 is a drive system diagram of still another embodiment. 1...Main shaft, 2...Blade angle control force transmission shaft, 2a,
2b, 2c... Spur gear, 2b-1, 2c-1...
Clutch pawl, 3a, 3b, 3c...electromagnetic clutch, 4...bearing, 5...operating shaft for blade angle control, 6...
...Crosshead, 7...Shaft nut, 8...Connecting rod, 9...Nut, 10...Coupling, 10
d...male thread, 11...sliding ring, 12...
Piece, 12a...Spur gear, 12d...Female thread, 13
... bearing, 14 ... spur gear, 15, 16 ... bearing, 17 ... casing, 18 ... spur gear, 20
... Coupling ring, 21 ... Core, 22 ... Bearing, 23 ... Electromagnet, 24 ... External toothed adapter,
25... amateur, 26... friction plate, 27...
Cylindrical shaft sealing material, 28... Shaft sealing material, 29... Sealing material, 31... Disc, 32... Shifter, 33... Sensing piece, 34... Position detector, 35... Pawl clutch, 36 ...Sliding key, 37...Spline shaft,
38...Shifter yoke, 39...Pinion.

Claims (1)

[Claims] 1. A fluid machine equipped with a blade angle control device that has a blade angle control operating shaft inserted through a hollow main shaft provided with movable blades and controls the blade angle by moving the operating shaft in the axial direction. a piece provided with a screw that engages with a screw provided on the main shaft and rotatably connected in the axial direction to the sliding ring via a bearing; a first gear provided on the main shaft; The rotational speed N ₁ of the first gear is increased through the second gear which is connected to the second gear, and a clutch that can connect and disconnect the first gear and the second gear.
When the rotational speed of the second gear is N ₂ , N ₁ < N ₂ and
A back gear device on a single blade angle control force transmission shaft parallel to the main shaft connected with a gear ratio such that the second gear rotates at either N ₁ > N ₂ , and a blade angle control operation. A fluid machine equipped with a blade angle control device consisting of a sliding ring that is rigidly connected to a shaft and is movable in the axial direction but cannot rotate with respect to the main shaft.