JP3599760B2 - Variable pitch propeller drive - Google Patents

Description

[0001]
[Industrial applications]
The present invention relates to a drive device for changing the mounting angle of a blade with respect to a rotating main shaft of a variable pitch propeller in a hydraulic machine or the like.
[0002]
[Prior art]
Generally, in a water turbine, a pump, a blower, or the like, a variable pitch propeller that can arbitrarily change the mounting angle of a blade with respect to a rotating main shaft is used, and the load or operation efficiency is adjusted by changing the mounting angle of the blade. There is something we can do.
[0003]
That is, a runner boss having a plurality of blades mounted radially is integrally connected to one end of the rotating main shaft, and a support shaft of each blade is rotatably supported around an axis in the runner boss. On the other hand, a hydraulic cylinder is formed in the middle of the hollow rotary main shaft, and one end of an operating rod concentrically inserted into the hollow rotary main shaft is connected to a piston disposed in the hydraulic cylinder. The other end is connected to a support shaft of each blade via a link mechanism.
[0004]
Then, pressure oil is supplied into the hydraulic cylinder from the end of the rotating main shaft through a pressure distribution valve, and the piston is moved in an arbitrary direction, whereby the operating rod is moved in the axial direction, and the movement causes the blade to move. Each support shaft is rotated around the axis to change the mounting angle of each blade.
[0005]
However, in such a device, it is necessary to adjust the mounting angle of the blade even during the driving rotation of the rotating main shaft. Therefore, the supply and discharge of the pressure oil to and from the hydraulic cylinder are performed via a rotary seal mechanism or the like. And there is a problem that the pressure oil sealing mechanism becomes complicated. In particular, in the case of a fluid such as a water turbine, which handles a fluid having a higher viscous resistance than air, the resistance to the blades becomes a large reaction force, and a load is applied to the hydraulic cylinder side. In addition, there is a possibility that an accident such as oil leakage or seizure at the seal portion may occur. In addition, oil leaks out into rivers, causing environmental pollution.
[0006]
On the other hand, there has been proposed a motor in which a drive motor is used instead of a hydraulic cylinder, and an output shaft of the drive motor is screwed into the operation rod so that the operation rod reciprocates. However, in such a case, the operating rod is driven by generating a relative rotation difference between the rotation shaft of the drive motor and the rotation spindle, and during normal operation, the rotation shaft of the drive motor and the rotation spindle are rotated. Must be rotated integrally so that the mounting angle of the blades does not change. However, there is a problem that the operation is not always performed reliably in the conventional device.
[0007]
Further, similarly to the above, a drive motor is used in place of the hydraulic cylinder, and a synchronization device is provided between the output shaft of the drive motor and the rotation spindle, and the difference in the relative rotation speed between the rotation spindle and the rotation spindle is provided by the synchronization device. U.S. Pat. No. 5,064,098 has also been proposed, which utilizes a technique to drive an operating rod that changes the mounting angle of each blade.
[0008]
[Problems to be solved by the invention]
However, the main function of a synchronization device that utilizes the difference in the relative rotation speed between the output shaft of the drive motor and the rotary spindle due to the use of the drive motor is to control synchronization or rotational deviation between the rotary spindle and the output shaft of the drive motor. Since it does not have a large boosting function by itself, it is necessary to transmit the rotation of the output shaft of the synchronizer to the operating rod by doubling the torque through some torque amplifying device.
[0009]
In addition, in Kaplan turbines and the like, the frequency of adjusting the blade mounting angle is generally about several times an hour, but the synchronizer needs to maintain the relative rotation speed with the stationary side at all times during operation of the turbine. For this reason, the rotation of the gear portion is continued, and frictional heat is generated from the gear portion and the bearing portion. Therefore, lubrication inside the synchronizer is a very serious problem.
[0010]
Furthermore, in the synchronous device, fine iron powder is generated due to wear due to gear contact due to relative rotation of the gear part and bearing part, and processing of this iron powder is an important issue in maintaining the life of the gear. Become.
[0011]
The present invention has been made in view of the above circumstances, and an object thereof is to quickly discharge iron powder generated in a synchronization device, reduce stagnation in the synchronization device, and reduce frictional heat generated in a gear portion. An object of the present invention is to provide a drive device for a variable pitch propeller having an operation mechanism capable of increasing the cooling effect and doubling the torque of the output shaft of the synchronizer and transmitting the torque to the operation rod to reduce the capacity of the drive motor. is there.
[0012]
[Means for Solving the Problems]
In order to achieve the above object, the present invention changes the mounting angle of a variable pitch blade attached to the rotating main shaft by relatively rotating the rotating main shaft and an output shaft arranged concentrically. In the variable pitch propeller drive device described above, a synchronizing device capable of relatively rotating the rotating main shaft and an output shaft arranged concentrically, and a deceleration rotationally driven by the synchronizing output shaft of the synchronizing device. An operating mechanism, which is composed of a device and a housing, is housed in a case which is mounted on the top of the rotating spindle and is filled with lubricating oil therein, and the synchronous mechanism is mounted on the inner peripheral surface of the case. A partition wall having a plurality of holes communicating with the synchronizer unit and the reduction gear unit is provided so as to project from and surround the device and the reduction gear unit.
[0013]
[Action]
Iron powder generated in the synchronizer quickly falls into the reduction gear unit through a plurality of holes provided in the partition wall separating the synchronizer unit and the reduction gear unit, and the stagnation in the synchronizer is reduced. Friction heat generated in the gear portion is accommodated in a case where the synchronizing device portion and the speed reducing device portion are integrated, and both devices are cooled by a large amount of common lubricating oil, so that the cooling effect is enhanced. In addition, since the speed reducer that doubles the torque is interposed between the output shaft of the synchronizer and the operation rod, the capacity of the operation motor can be reduced.
[0014]
【Example】
An embodiment of the present invention will be described below with reference to the accompanying drawings.
[0015]
FIG. 2 is a diagram showing a schematic configuration of a variable pitch propeller turbine to which the operating mechanism of the present invention is applied, showing only a rotating part of the turbine, and omitting a stationary part. A rotating main shaft 1 having a runner boss 1a integrally mounted on a lower end is rotatably supported by a bearing 2. A plurality of blades 3 are attached to the runner boss 1a in the radial direction. The support shaft 3a of each blade is supported in the runner boss 1a, and by rotating the support shaft 3a, the mounting angle of the blade 3 is increased. Can be changed.
[0016]
On the other hand, the rotary main shaft 1 is formed in a hollow shape, and an operating rod 4 is concentrically disposed in the rotary main shaft 1 so as to be movable only in the axial direction, and an arm 4a fixed to a lower end of the operating rod 4 is provided. Are connected to each support shaft 3a of the blade 3 via a link and a lever mechanism 5. Therefore, by reciprocating the operation rod 4 in the axial direction, the mounting angle of each blade 3 can be changed via the link and lever mechanism 5.
[0017]
An operating mechanism 6 (accommodated in a case 15), which is a main part of the variable pitch propeller driving device according to the present invention, is fixed to the top end of the rotary spindle 1, and an input shaft to the operating mechanism 6 is provided. 7 is connected to a drive motor 10 via a coupling 8 and an intermediate shaft 9. The output shaft 38 at the other end of the operation mechanism 6 supports a large thrust by the thrust bearing 14, and a screw portion 38 a formed at the lower end thereof is screwed to the top 4 b of the operation rod 4. Have been.
[0018]
Therefore, when the drive motor 10 is operated to drive the operation mechanism 6 to generate relative rotation between the rotary main shaft 1 and the output shaft 38, the operation rod 4 moves in the axial direction, and the link and lever mechanism The mounting angle of each blade 3 is changed via 5. When the drive motor 10 is in a stationary state, the rotating main shaft 1 and the output shaft 38 rotate integrally, so that the operating rod 4 does not move in the axial direction, and the mounting angle of each blade 3 does not change to a predetermined value. Will be maintained.
[0019]
Next, the operating mechanism 6, which is a main part of the variable pitch propeller driving device of the present invention, will be described in detail with reference to FIG.
[0020]
FIG. 1 is a longitudinal sectional view showing an embodiment of the operation mechanism 6. In FIG. 1, an actuating mechanism 6 is provided within a case 15 with a synchronizing device 6a disposed above the drawing and a deceleration device disposed therebelow and driven by a synchronizing output shaft 11 of the synchronizing device 6a described later. 6b. These two devices 6a and 6b are protruded substantially at the middle of the inner peripheral surface of a case 15 for accommodating the two devices 6a and 6b integrally therein, and are formed integrally with the synchronous output shaft 11. The lower end of the arm 12 penetrates and is separated by a partition wall 25 that supports a bearing 25a that supports the penetrating portion. The partition wall 25 collects dust and the like generated by the operation of various gears and the like constituting the synchronizing device 6a to be described later near the inner peripheral surface of the case 15 by centrifugal force, and the lower portion ( A plurality of holes 25b for opening the precipitate quickly in the reduction gear unit 6b) are opened.
[0021]
As described above (see FIG. 2), the case 15 is integrally mounted on the top of the rotary spindle 1, and the fixed shaft 16 is inserted through the top wall of the case 15, and a bearing 16a is provided. Thereby, the case 15 is rotatable around the fixed shaft 16. As shown in FIG. 2, the rotation of the fixed shaft 16 is restricted by an arm 17 and a stopper 18.
[0022]
Hereinafter, the synchronizer 6a will be described first.
[0023]
The input shaft 7 is concentrically inserted through the fixed shaft 16, and the input shaft 7 is provided at a top end of the input shaft 7 and a bearing 19 provided between the fixed shaft 16 and the input shaft 7. It is rotatably supported by a shaft support 20. A first sun gear 21 is integrally formed below the input shaft 7, and a plurality of planetary gears 22 that revolve around the sun gear 21 while rotating around the first sun gear 21 are meshed with each other. I have. The planetary gear 22 is rotatably mounted on a support shaft 23 provided on an arm 12 formed integrally with the output shaft 11, and revolves around the first sun gear 21 while rotating around itself. The output shaft 11 is rotated by the revolution.
[0024]
An internal gear 24 is provided on the outer periphery of the planetary gear 22, and a first gear 24 a of the internal gear 24 is meshed with the planetary gear 22. The synchronous output shaft 11 is provided on the same axis as the input shaft 7 and is supported by a bearing 25a supported by the above-mentioned partition 25 protruding substantially at the center of the inner peripheral surface of the case 15. The shaft 15 is rotatably supported so as to be able to rotate relative to the gear 15.
[0025]
On the other hand, a second sun gear 26 having the same diameter as the first sun gear 21 is provided at the lower end of the fixed shaft 16 which supports the case 15 by a bearing 16a inserted into the case 15. A plurality of planet gears 27 having the same diameter as the plurality of planet gears 22 that revolve around the sun gear 26 while rotating around the sun gear 26 are meshed with the outer periphery of the sun gear 26. The planetary gear 27 is meshed with a second gear 24b of the internal gear 24 disposed on the outer periphery thereof. The planetary gear 27 is rotatably mounted on a shaft 29 protruding from an arm 28 fixed to the inner wall of the case 15.
[0026]
Further, packings 30a and 30b are provided between the case 15 and the fixed shaft 16 and between the fixed shaft 16 and the input shaft 7, respectively. The case 15 is filled with lubricating oil 30. Have been.
[0027]
Further, a disassembled oil supply disk 41 for supplying the lubricating oil 30 to the bearings 19 and 16a is mounted on the fixed shaft 16 at a position immersed in the lubricating oil 30. Although not shown, the refueling disk 41 is divided into two parts at the center, and has a structure that can be disassembled and attached by bolts from the left and right sides of the fixed shaft 16.
[0028]
A lubricating oil supply hole 42 extending in the radial direction is formed in the lubrication disk 41, and a lubricating oil suction port 43 is formed at the tip end thereof, the lubricating oil suction port 43 opening in a direction facing a swirling flow of lubricating oil described later. The base end of the lubricating oil supply hole 43 communicates with the bearing 19 via a communication hole 44 formed in the fixed shaft 16 and an annular gap 45 between the fixed shaft 16 and the input shaft 7. Further, it is communicated with the bearing 16a via the communication passage 46.
[0029]
When the main spindle 1 rotates, the case 15 also rotates, and the lubricating oil 30 filled in the case 15 turns in the same direction as the case 15 due to its viscosity. Due to the turning of the lubricating oil 30, the lubricating oil 31 flows into the lubricating oil supply hole 42 from the lubricating oil inlet 43 of the lubrication disk 41 mounted on the fixed shaft 16, and passes through the communication hole 44 and the annular gap 45. Then, a part of the lubricating oil that has flowed into the bearing 19 is further supplied to the bearing 16a through the communication passage 46, so that the bearings 19 and 16a are lubricated and cooled. In this way, the lubricating oil that has lubricated and cooled the bearings 19 and 16a drops downward, and the same cycle is repeated during the rotation operation of the rotary spindle 1.
[0030]
The configuration of the synchronizer 6a has been described above. Next, the configuration of the speed reducer 6b disposed below the partition 25 will be described.
[0031]
The synchronous output shaft 11 is supported by the bearing 25a as described above, extends through the partition wall 25 downward in the drawing, and has a first reduction sun gear 31 integrally formed at the lower end thereof. , Rotatably supported by a shaft support 11a provided at the top end.
[0032]
A plurality of reduction planetary gears 32 that revolve around the first reduction sun gear 31 while rotating around the first reduction sun gear 31 are meshed with the first reduction sun gear 31. These deceleration planetary gears 32 are supported by an arm 34 formed integrally with a second deceleration sun gear 33 rotatably supported by a shaft support 33a provided at the top end thereof. It is rotatably mounted on the shaft 35 and revolves around the first deceleration sun gear 31 while rotating, and the second deceleration sun gear 33 is rotated by the revolution. The planetary gear 32 for reduction is meshed with a first internal gear 36 provided on the inner peripheral surface of the case 15 so as to protrude.
[0033]
The second reduction sun gear 33 meshes with a plurality of reduction planetary gears 37 that revolve around the reduction sun gear 33 while rotating. These reduction planetary gears 37 are rotatably mounted on a support shaft 39 a provided on an arm 39 formed integrally with the output shaft 38, and are provided around the second reduction sun gear 33. Revolves while rotating, and the output shaft 38 is rotated by the revolution. The planetary gear 37 for reduction is meshed with a second internal gear 40 protruding from the inner peripheral surface of the case 15.
[0034]
In addition, around the second internal gear 40 and the first internal gear 36 described above, generated by the operation of the synchronizing device 6a disposed above the case 15, the above-mentioned partition 25 A plurality of holes 15c and 15b are formed for quickly settling down the abrasion powder and the like that has dropped after passing through the hole 25a provided at the bottom, and the abrasion powder and the like accumulate on the bottom 15a of the case 15. It is configured as follows.
[0035]
At the center of the bottom wall of the case 15, a support frame 38a for the output shaft 38 is provided. The output shaft 38 penetrates the support frame 38a and the bottom wall of the case 15, and is provided with bearings 38b, 38c. The case 15 is rotatably supported by the case 15. Reference numeral 38d denotes packing, and it goes without saying that the second sun gear 33 for reduction and the output shaft 38 are arranged on the same axis as the synchronous output shaft 11.
[0036]
As described above with reference to FIG. 2, the output shaft 38 has a screw portion 38 a formed at the lower end thereof, and is screwed to the top 4 b of the operation rod 4.
[0037]
As is clear from the above description, the speed reducer 6b in the present embodiment meshes with the first reduction sun gear 31 and revolves around the first reduction sun gear 31 while rotating. A first reduction gear mechanism including a reduction planetary gear 32, and a second reduction sun mechanism having the same configuration as the first reduction gear mechanism and cascaded to the first reduction gear mechanism. The second reduction gear mechanism is composed of a plurality of reduction planetary gears 37 that mesh with the gear 33 and revolve around the second reduction sun gear 33 while rotating around the second reduction gear. However, it goes without saying that the number of stages of the reduction gear mechanism connected in cascade is not limited to two.
[0038]
Next, the operation of the operation mechanism 6 having the configuration described above will be described.
[0039]
In the synchronizer 6a and the speed reducer 6b disposed above and below the case 15, the drive motor 10 is in a non-drive state while the rotating main shaft 1 (case 15) is rotating, and the input shaft 7 When the rotation is stopped (since the fixed shaft 16 does not rotate, of course), the planetary gears 22 and 27 revolve around the first and second sun gears 21 and 26, respectively, while rotating around the planetary gears. The revolution of the gear 22 causes the synchronous output shaft 11 to rotate. Therefore, the synchronous output shaft 11 performs the same rotation as the case 15 (the rotating main shaft 1).
[0040]
Due to the rotation of the case 15 and the synchronous output shaft 11 (first deceleration sun gear 31), the deceleration planetary gear 32 revolves around the first deceleration sun gear 31 while rotating, and the deceleration planetary gear. The rotation of the gear 32 is transmitted to the first internal gear 36. However, as described above, in the case of this embodiment, the relative speed between the first reduction sun gear 31 and the case 15 (the first internal gear 36) is zero, and therefore, the reduction planetary gear Since the relative rotational speed between the first internal gear 32 and the first internal gear 36 (case 15) is also zero, the relative rotational speed between the case 15 and the second reduction sun gear 33 is also zero. It becomes.
[0041]
As described above, since the speed reducer 6b is formed by cascading two-stage reduction gear mechanisms having the same configuration, the relative rotational speed between the case 15 and the output shaft 38 becomes zero in the same manner. Become. Therefore, the output shaft 38 performs the same rotation as the case 15 (the rotating main shaft 1), the operating rod 4 does not move in the axial direction, and the mounting angle of the blade 3 is not changed.
[0042]
Then, when the drive motor 10 is driven to rotate the input shaft 7 of the synchronizer 6a, the first sun gear 21 rotates, and this rotation causes the planetary gear 22 to start revolving, and the rotating main shaft 1 and the synchronous output shaft are rotated. 11 (the first deceleration sun gear 31 of the reduction gear 6b) generates a relative rotation.
[0043]
The above relative rotational speed is reduced to two stages by a two-stage reduction gear mechanism cascade-connected in the reduction gear 6b, transmitted to the output shaft 38, moves the operation rod 4 in the axial direction, and moves the blade 3 The mounting angle is changed.
[0044]
It should be noted that the torque obtained from the output shaft 38 has a larger value than the torque obtained from the synchronous output shaft 11, which is substantially proportional to the reduction ratio of the reduction gear 6b. Therefore, the present invention can be applied as a drive device for a large-capacity variable-pitch propeller turbine without increasing the capacity of the drive motor 10.
[0045]
On the other hand, the plurality of planetary gears constituting the synchronizing device 6a revolve around the sun gear in a fixed state while revolving even during normal operation in which the mounting angle of the blades is not changed. The heat generated by the sliding is lubricated and cooled by the lubricating oil 30 filled in the case 15 accommodating the synchronizing device 6a.
[0046]
In the speed reducer 6b, there is no change in the relative speed between the gears except when the mounting angle of the blade 3 is changed, so that no heat is generated in the gears. Therefore, the temperature of the lubricating oil filled in the case 15 is suppressed to be lower than that in the case where only the synchronizing device 6a is stored.
[0047]
Further, the sliding friction powder generated in the plurality of planetary gear portions constituting the synchronizer 6a is generated by the plurality of holes 25b provided in the partition 25 between the synchronizer 6a and the speed reducer 6b and the first and second internal gears. After passing through a plurality of holes 15b and 15c provided in 36 and 40, respectively, it accumulates at the bottom 15a of the speed reducer 6b. In the speed reducer 6b, as described above, there is no change in the relative speed between the gears except when the angle of attachment of the blades 3 is changed, so that the lubricating oil is not agitated by the rotation of the gears. Further, since the sun gear and the planetary gear at the last stage of the speed reducer 6b are decelerated, even when the mounting angle of the blade 3 is changed, the relative rotation speed with the case 15 is extremely small, and the bottom portion 15a has The accumulated sliding friction powder and the like are not wound up by the rotation of the gear.
[0048]
【The invention's effect】
As described above, according to the present invention, the operating mechanism for changing the mounting angle of the variable pitch blade is constituted by the synchronizer unit and the reduction gear unit, and both of these units are provided in the case filled with lubricating oil. The case is provided with a partition wall protruding from the inner peripheral surface of the case to separate the synchronizer section and the reduction gear section, and a plurality of holes are provided in the partition wall so as to communicate the two device sections. In the synchronizer section, a small amount of wear powder that is constantly generated during operation can be quickly discharged from the synchronizer section and settled below the case of the reduction gear section. There is little stagnation around the device, and it is possible to prevent the gears and bearings of the synchronous device itself from being damaged by wear powder. The abrasion powder settled in the lower part of the case has a low possibility of being wound up in the lubricating oil because the relative speed between the gears is small even when the reduction gear operates.
[0049]
Further, since the synchronizer unit and the reduction gear unit are lubricated and cooled by a large amount of lubricating oil in the same case, the temperature rise of the lubricating oil is larger than that of the synchronizer alone. It is kept low and the cooling effect of the friction part is great.
[0050]
Further, as compared with the case where the synchronizing device section and the reduction gear section are separately provided, the number of shaft seal portions is reduced, maintenance becomes easy, and the apparatus can be made more compact.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing one embodiment of an operation mechanism according to the present invention.
FIG. 2 is a diagram showing a schematic configuration of a variable pitch propeller turbine to which the operating mechanism of the present invention is applied.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Rotating main shaft 3 Blade 4 Operating rod 6 Operating mechanism 6a Synchronizing device 6b Reduction gear 7 Input shaft 10 Operating motor 11 Synchronous output shaft 15 Case 15a Case bottom 15b First internal gear hole 15c Second Internal gear hole 16 Fixed shaft 21 First sun gear 22 Planetary gear 25 Partition wall 25b Partition hole 26 Second sun gear 27 Planetary gear 30 Lubricating oil 31 First reduction sun gear 32 Reduction planetary gear 33 2 reduction sun gear 36 first internal gear 37 reduction planetary gear 38 output shaft 40 second internal gear

Claims (1)

A drive device for a variable pitch propeller configured to change an attachment angle of a variable pitch blade attached to the rotating main shaft by relatively rotating a rotating main shaft and an output shaft arranged concentrically, An actuating mechanism comprising a synchronizing device for relatively rotating a rotating main shaft and an output shaft disposed concentrically, and a speed reducer rotationally driven by a synchronizing output shaft of the synchronizing device, It is mounted on the top of the rotating main shaft and is housed in a case filled with lubricating oil, and on the inner peripheral surface of the case, the synchronizer and the reduction gear are separated from each other and around it. A drive device for a variable pitch propeller, wherein a partition wall having a plurality of holes for communicating the synchronizer unit and the reduction gear unit is protruded.

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