JP2004162777A - Fixed structure of rotary shaft part and gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fixed structure of a rotary shaft part and a gear capable of dispensing with special finish machining in a connection part of the rotary shaft part and the gear, fixing them simply, simultaneously, and firmly, and achieving meshing accuracy and alignment accuracy of the rotary shaft part and the gear simultaneously and allowing easy assembly and disassembly of the rotary shaft part and the gear with reduced cost. <P>SOLUTION: Rotation force of the rotary shaft part 16 is transmitted to a helical gear 19 through a spline connection part 20 between an outer peripheral face of the rotary shaft part 16 of a step-up gear 6 and an inner peripheral face of the helical gear 19. Load applied in the radial direction of the spline connection part 20 is received by annular in-low parts 21, 22 arranged in both side parts of the spline connection part 20. The inner peripheral face of the helical gear 19 is fitted and inserted into the outer peripheral face of the rotary shaft part 16 to perform alignment of the rotary shaft part 16 and the helical gear 19 smoothly. Since the rotary shaft part 16 and the helical gear 19 are supported by the in-low parts 21, 22, it is possible to prevent play due to internal wear for the spline connection part 20 and prevent the helical gear 19 from falling down. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a fixing structure of a rotating shaft and a gear used for a power transmission device of general machinery, for example, and particularly, can easily and firmly fix the rotating shaft and a gear, and disassemble the rotating shaft and the gear. The present invention relates to a structure for fixing a rotating shaft portion and a gear, which can be easily and inexpensively assembled.
[0002]
[Prior art]
The fixed structure that supports the inner peripheral surface of the gear by the spline connection on the outer peripheral surface of the rotating shaft portion that is the power transmission shaft is used for large-sized machines such as civil engineering construction machines, various vehicles, general industrial machines, and finally wind power generators. ing. The rotating shaft portion and the gear are arranged in the power transmission portion in a state where the rotating shaft portion and the gear do not rotate relative to each other. For this reason, when a minute vibration is generated in the spline coupling portion between the outer peripheral surface of the rotating shaft portion and the inner peripheral surface of the gear, wear is generated on each spline meshing surface, and the rattling is increased by the wear. Become. When the rattling of the spline connection increases, large vibrations and noises are generated, which not only leads to a significant decrease in the performance of the power transmission unit, but also shortens the service life.
[0003]
In order to solve such a problem, as an example of a fixing structure by spline coupling, according to Japanese Utility Model Publication No. 6-3204, for example, a clutch hub is fitted and fixed to a rotating shaft portion of a gear transmission and a shoulder portion of a boss portion. Discloses a synchronous meshing device for transmitting power by rotatably supporting a gear having an outer spline and engaging an outer spline of the gear with an inner spline of a sleeve splined to the outer periphery of the clutch hub. The synchronous meshing device includes a boss of the gear via a supply oil passage extending radially from an injection oil passage through which lubricating oil is injected along the axis of the rotation shaft along with rotation of the rotation shaft. The thin oil film is formed by being guided to the spline meshing surface between the outer periphery and the inner peripheral surface of the sleeve.
[0004]
[Patent Document 1]
Japanese Utility Model Publication No. 6-3204
[0005]
[Problems to be solved by the invention]
Usually, the rotating shaft and the gears are formed by forging. After the forging, the outer splines formed on the outer peripheral surface of the rotary shaft and the inner splines formed on the inner peripheral surface of the gear are heated. After the heat treatment, each spline is finished by polishing or the like to ensure the coaxial accuracy of both. However, it is extremely difficult to finish the valleys of the inner spline of the gear with high dimensional accuracy, and there are various problems that variations are likely to occur in each product and defective products are often generated. Therefore, there was a problem that strict quality control had to be performed.
[0006]
In addition, after finishing the inner spline of the gear, the inner and outer diameters are measured, and the outer spline of the rotating shaft is finished based on the measured value, so that the center of the rotating shaft and the gear is There is a method of performing alignment. However, in such a method, the manufacturing process becomes extremely complicated, which leads to an increase in manufacturing cost in mass production.
[0007]
Also, if heat treatment is performed after forging of the rotating shaft or gear, deformation due to heat treatment will occur, so heat treatment cannot be performed after finishing the spline, and the allowable stress on the tooth surface of the spline will increase, Various problems occur that the strength cannot be increased.
[0008]
On the other hand, in a fixed structure in which a gear is supported on a rotary shaft by a key connection, several key members are usually provided with a required phase difference in a circumferential direction of the rotary shaft in order to prevent a reduction in strength of the rotary shaft. Be placed. Therefore, as compared with the fixing structure by the spline connection, the rotating shaft portion and the gear are partially engaged with each other, so that the allowable stress is reduced and the mounting strength is weakened. For this reason, it is necessary to tightly fit the inner peripheral surface of the gear to the outer peripheral surface of the rotating shaft portion by tightly fitting the outer peripheral surface. However, in this case, replacement, disassembly at the time of repair or inspection, and assembly are extremely difficult.
[0009]
By the way, as another example of the fixed structure supported by the spline connection, there is a speed increaser used for a wind power generator. In this wind power generator, a nacelle capable of turning horizontally is provided at the upper end of a tower (post), and a blade (propeller) that rotates about a horizontal axis by wind force is supported at one end of the nacelle. In the nacelle, a gearbox for increasing the rotation of the horizontal shaft and a generator connected to the gearbox are mounted. The height of the tower is as large as 30 to 60 m, and the length of a blade provided on a nacelle mounted on the tower is as large as 30 m.
[0010]
The blade rotates around the horizontal axis by receiving wind at the upper end of the tower. This rotation is performed at a low speed of, for example, 20 rotations per minute due to the large size and heavy weight of the blade. The rotation is transmitted to the gearbox via the horizontal axis, and the rotation speed is greatly increased to about 2,000 revolutions via the gearbox, transmitted to the generator, and the generator is driven to generate electricity. . A large helical gear is attached to the rotating shaft of the gearbox by spline coupling.
[0011]
Unless there are special reasons such as typhoons or strong winds, the wind turbines will continue to operate. It is desirable that the major components that make up this type of wind power plant be replaced as little as possible for a reasonable service life, for example about 30 years. Under such circumstances, as a component of the gearbox arranged in the nacelle that turns at the upper end of the tower at a high position, for example, the helical gear is formed with a considerably wide tooth width, and the durability is high. Is increasing.
[0012]
In the helical gear, since the tooth streaks are inclined with respect to the axis, point contact starts at one end of the tooth surface, and then the contact width of the tooth gradually increases to a maximum, and then gradually decreases to a tooth. At the end of the surface, meshing ends at point contact on the opposite side of the tooth width. Due to its structure, an excessive load is applied to each tooth surface in the radial direction. For this reason, when the spline coupling portion between the outer peripheral surface of the rotating shaft portion and the inner peripheral surface of the gear is set or deformed, the helical gear falls down, and power is transmitted in a state where the tooth surfaces are biased and meshed. Will be communicated. Therefore, in order to prevent the helical gear from falling, complicated machining and high dimensional accuracy are required for the spline connection part, and the positioning between the outer diameter of the rotating shaft and the inner diameter of the gear is required. Must be performed accurately, and in addition to an increase in equipment costs and manufacturing costs, strict quality control must be performed.
[0013]
However, Patent Literature 1 does not specifically specify fitting accuracy of the spline connection portion between the rotating shaft portion and the gear (tooth surface) and center alignment of the rotating shaft portion and the gear. . As in the case of the above-mentioned wind power generator, the conventional technology has not been able to simultaneously satisfy the spline meshing accuracy and the alignment accuracy between the center of the rotating shaft and the center of the gear.
[0014]
The present invention has been made to solve such a conventional problem, and a specific object of the present invention is that no special finishing work is required at a joint between a rotating shaft and a gear, and at the same time, it is easily and firmly fixed. It is possible to simultaneously achieve the meshing accuracy between the rotating shaft and the gear and the alignment accuracy between the rotating shaft and the gear, and to perform the disassembly and assembly of the rotating shaft and the gear at low cost and easily. It is an object of the present invention to provide a structure for fixing a rotating shaft portion and a gear, which is possible.
[0015]
Means for Solving the Problems and Functions and Effects
The invention according to claim 1 is a structure for fixing a rotating shaft portion and a gear, comprising a spline coupling portion and a spigot portion between an outer peripheral surface of the rotating shaft portion and an inner peripheral surface of the gear. And a structure for fixing the rotating shaft portion and the gear.
[0016]
The fixing structure of the present invention is configured such that an outer spline formed on an outer peripheral surface of the rotating shaft portion and an inner spline formed on an inner peripheral surface of the gear mesh with each other, and an outer peripheral surface of the rotating shaft portion and the gear The inner peripheral surface is mirror-finished, and is fitted to an annular spigot portion extending in the circumferential direction to support the inner peripheral surface.
[0017]
According to the present invention, although the rotational force of the rotating shaft portion acts on the gear at the spline coupling portion as in the related art, the load in the radial direction is received by the spigot portion. There is no need to receive a radial load as strong as the difference. That is, in the fixing structure of the rotating shaft portion and the gear of the present invention, the rotational force of the rotating shaft portion is directly transmitted to the gear through the spline connecting portion, but most of the load applied in the radial direction of the spline connecting portion. Is received at the spigot section.
[0018]
The spigot portion has a function of supporting the outer peripheral surface of the rotary shaft portion and the inner peripheral surface of the gear in full contact with each other in the circumferential direction, and a centering in which the center position of the rotary shaft portion matches the center of the gear. It has a function. Therefore, by inserting the inner peripheral surface of the gear into the outer peripheral surface of the rotating shaft portion, the center of the rotating shaft portion and the center of the gear are automatically aligned on the same straight line, and the rotating shaft portion In addition, the centering of the gears is performed smoothly without difficulty.
[0019]
Since the peripheral surface of the fitting portion between the rotating shaft portion and the gear can be supported on the entire surface by the spigot portion, the spline coupling portion as in the related art, particularly the finishing of the valley portion, which is conventionally difficult to process, is finished. There is no need to improve the processing and the strict processing accuracy at the tooth contact of the spline joint. As a result, the surface hardness of the spline joint can be significantly increased by performing quenching / tempering by carburizing, high frequency, or the like.
[0020]
Therefore, it is possible to prevent rattling due to internal wear on the spline connection portion, and it is possible to completely prevent the gear from falling down. For this reason, it is possible to secure the initially set good tooth contact for a long period of time, and it is possible to extremely increase the allowable stress. As a result, the durability of the rotating shaft portion and the gear can be greatly improved without generating vibration or noise.
[0021]
Further, since the rotating shaft portion and the gear can be supported by the spigot portion as described above, the spline coupling portion can be fitted and fixed with a clearance having a moderate clearance ordinarily allowed in the spline coupling portion. This makes it easy and inexpensive to disassemble and assemble the rotating shaft and gear during replacement, repair and inspection.
[0022]
In the invention according to claim 2, the spline coupling portion is disposed at an intermediate portion between an outer peripheral surface of the rotating shaft portion and an inner peripheral surface of the gear, and the spigot portions are disposed at both ends of the spline coupling portion. It is characterized by being done.
[0023]
According to this invention, the gear is supported by the rotary shaft via the pair of front and rear spigot portions arranged on both sides of the spline coupling portion. Therefore, a gear having a considerably wide tooth width can be stably and reliably supported, and the radial load applied to the spline joint can be relatively reduced. The present invention is effective for a normal spur gear, but is particularly suitably applicable to a helical gear whose meshing starts at one end of one of the teeth. By supporting both side portions of the spline connection portion with the spigot portion, the helical gear is less likely to fall due to a thrust load. Therefore, by reducing the misalignment of the meshing surface of the helical gear, it is possible to prevent the one-sided contact of the gear, and the durability of the gear is remarkably improved.
[0024]
The invention according to claim 3 is characterized in that at least one of the annular spline machining relief portions formed on both side portions of the spline coupling portion has a spacer interposed therebetween, and an outer peripheral surface of the rotary shaft portion and an inner peripheral surface of the gear. The spigot portion is formed at a portion corresponding to the spacer between the surface and the surface.
[0025]
When a spacer is interposed in at least one of the annular spline processing relief portions of the outer spline formed on the outer peripheral surface of the rotary shaft portion and the inner spline formed on the inner peripheral surface of the gear, even if spline processing is performed. Even if the spigot part cannot be formed directly in the relief part, the spigot part can be arranged in the spline processing relief part via the spacer. For this reason, the hub portion of the gear can be made compact and reduced, and the gear can be used extremely effectively without greatly increasing the installation space of the gear in the axial direction. In particular, when a helical gear is used, since the tooth streaks are inclined with respect to the axis, an axial thrust proportional to the torque occurs, but the spacer is provided with a mechanical retaining structure for the gear. And the displacement of the gear in the thrust direction can be prevented.
[0026]
The invention according to claim 4 has a lubricating oil passage along the axis of the rotating shaft portion and a supply oil passage extending radially from the lubricating oil passage, and the port portion of the supply oil passage has the lubricating oil passage. It is characterized in that it is arranged so as to be open to the spline processing relief portion.
[0027]
The present invention is characterized in that the spline machining relief portion is used as a part of a lubricating oil passage or an oil reservoir. Since the spline processing relief portion is formed between the spigot portion and the spline coupling portion, the flow of the lubricating oil is closed by the spigot portion, and the lubricating oil is smoothly supplied to the spline coupling portion. Will be able to Therefore, for example, by forming an outflow hole in a part of the spacer, the lubricating oil flowing in the spline coupling portion can be smoothly led out to the outside, and new lubricating oil is always supplied to the spline coupling portion in the spline coupling portion. Can be supplied to For this reason, the lubricating property of the spline connection part can be extremely improved, and internal wear and abrasion of the spline connection part can be prevented.
[0028]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings, with regard to a fixed structure of a rotating shaft portion and a gear applied to a gearbox of a wind turbine generator.
In the present embodiment, a description will be given by taking as an example a fixed structure of a rotating shaft portion and a gear applied to a speed increaser of a wind turbine generator. In addition to the above, the present invention can be applied to various power transmission devices such as large civil engineering construction machines such as large bulldozers and hydraulic excavators, and gear transmissions of automobiles.
[0029]
FIG. 1 shows a schematic configuration of a wind power generator to which a structure for fixing a rotating shaft and a gear according to a typical embodiment of the present invention is applied. In FIG. 1, a wind power generator 1 has a nacelle 3 which can be turned around a vertical axis at an upper end of an elongated tower 2. One end of the nacelle 3 is provided with a plurality of blades 5 that rotate about a substantially horizontal rotating shaft 4 by wind force. The nacelle 3 includes a gearbox 6 for increasing the rotation of the rotary shaft 4 and a generator 7 connected to the gearbox 6.
[0030]
FIG. 2 schematically shows an example of a configuration of a main part of a speed increaser in a wind power generator. In FIG. 1, first to third rotating shaft portions 15 to 17 arranged in parallel via bearings 9 to 14 are rotatably supported on a housing 8 of the speed increasing gear 6. According to the illustrated example, the rotation from the blade 5 is transmitted to the first rotating shaft portion 15, and the rotation of the first rotating shaft portion 15 is transmitted through the first helical gear 18 having a large diameter. The two rotation shaft portions 16 are rotated at an increased speed. The rotation of the second rotary shaft 16 is caused by the rotation of the third rotary shaft 17 via the second helical gear 19 having a smaller diameter than the first helical gear 18, and the third rotary shaft 17 is rotated. The output from 17 is transmitted to the input shaft of the generator 7.
[0031]
A feature of the present invention is that spline coupling portions 20 and 20 and spigot portions 21 and 22 are formed between the outer peripheral surfaces of the rotating shaft portions 15 and 16 and the inner peripheral surfaces of the helical gears 18 and 19. That is, the rotating shaft portions 15 and 16 and the helical gears 18 and 19 are meshed with each other via the spline coupling portions 20 and 20, and are formed on the annular spigot portions 21 and 22 that have been mirror-finished in the circumferential direction. The main configuration is to be supported by fitting.
[0032]
According to the present invention, the rotational force of the rotating shaft portions 15 and 16 acts on the gears 18 and 19 on the spline coupling portions 20 and 20 as in the prior art, but the radial load applied to the spline coupling portions 20 and 20 is reduced by the spigot portion. 21 and 22 directly. Therefore, no excessive radial load is applied to the peaks and valleys of the spline joints 20, 20.
[0033]
FIG. 3 schematically shows an example of a configuration of a rotating shaft portion and a fixed portion of a helical gear according to the first embodiment of the present invention. Insertion end of the second rotating shaft portion 16 disposed in parallel between the first rotating shaft portion 15 as the input shaft and the third rotating shaft portion 17 as the output shaft with respect to the bearing 11 (left side in FIG. 3). Is formed through an annular stepped portion extending in the insertion direction, and a shaft portion having a larger diameter than the insertion end portion has an outer peripheral surface of the second rotary shaft portion 16 and the inside of the second helical gear 19. A part of the mating surface with the peripheral surface is integrally attached by a spline coupling portion 20. First and second spline machining relief portions 23 and 24 are formed on both front and rear sides of the spline coupling portion 20. A spacer 25 is fitted and fixed concentrically in the annular space of the first spline processing relief portion 23.
[0034]
The inner peripheral surface of the open end (left side in FIG. 3) of the hub portion 19a of the helical gear 19 is set to have a size larger than the inner diameter of the center inside having the inner spline via the annular step portion. Between the inner peripheral surface of the opening end of the hub portion 19a and the outer peripheral surface of the rotating shaft portion 16, an annular first spigot portion 21 extending in the circumferential direction with the spacer 25 interposed therebetween is provided. A second spigot portion 22 is also provided adjacent to the second spline machining relief portion 24. The first spigot portion 21 supports the outer peripheral surface of the rotating shaft portion 16 and the inner peripheral surface of the helical gear 19 in contact with the entire surface in the circumferential direction via the spacer 25. The second spigot portion 22 directly supports the outer peripheral surface of the rotating shaft portion 16 and the inner peripheral surface of the helical gear 19.
[0035]
Since the spigot portions 21 and 22 are formed on both front and rear sides of the spline connection portion 20, the spline processing relief portions 23 and 24 can be used as lubricating oil stoppers. According to the illustrated example, the port portion of the supply oil passage 27 extending in the radial direction from the lubricating oil passage 26 along the axis of the rotating shaft portion 16 is provided in the second spline machining relief portion 24 on the opposite side to the spacer 25. Reference numeral 27a is disposed in the rotary shaft portion 16 so as to open to the spline processing escape annular groove.
[0036]
The lubricating oil passage 26 and the second spline machining relief portion 24 communicate with each other via the supply oil passage 27. The lubricating oil stored in the annular space of the spline machining relief portion 24 is guided to the spline coupling portion 20 with the rotation of the rotating shaft portion 16, and a thin lubricating film is formed between the spline meshing surfaces. An outflow hole 25a communicating with the spline connection portion 20 is formed inside the spacer 25, and the lubricating oil from the spline connection portion 20 is led out. The lubricating oil passage 26 is sealed by a sealing plug 28 for lubricating oil as shown in FIG.
[0037]
In such a lubricating structure, since the outflow hole 25a communicating with the spline coupling portion 20 is formed inside the spacer 25, the lubricating oil flowing in the spline coupling portion 20 is smoothly led out to the outside, and always, New lubricating oil can be supplied into the spline connection 20. For this reason, the lubricity in the spline connection part 20 can be extremely improved, and the internal abrasion and abrasion of the spline connection part 20 can be prevented.
[0038]
Each of the spigot portions 21 and 22 has a function of centering the center of the rotary shaft portion 16 and the center of the helical gear 19. When the inner peripheral surface of the helical gear 19 is inserted into the outer peripheral surface of the rotating shaft 16, the center position of the helical gear 19 automatically coincides with the center of the rotating shaft 16. The centering of the rotating shaft portion 16 and the helical gear 19 is smoothly and smoothly performed.
[0039]
The fixing structure of the rotating shaft portion 16 and the helical gear 19 according to the illustrated example transmits the torque of the rotating shaft portion 16 directly to the helical gear 19 via the spline coupling portion 20. Each of the spigot portions 21 and 22 makes the outer peripheral surface of the rotating shaft portion 16 and the inner peripheral surface of the helical gear 19 contact the entire surface in the circumferential direction, so that the spline coupling portions 20 and 20 extend in the radial direction. The load is directly received.
[0040]
As described above, since the rotating shaft portion 16 and the helical gear 19 can be supported by the respective spigot portions 21 and 22, the support of the helical gear 19 is stabilized, and the radial force applied to the spline coupling portions 20 and 20. The load can be reduced. In addition, it is possible to reduce the inclination of the helical gear 19 due to the thrust load, to reduce the misalignment of the meshing surface of the helical gear 19, thereby preventing the helical gear 19 from coming into contact with one side. Can be extremely improved in durability. Furthermore, there is no need to strictly perform the finishing processing of the spline connection part 20 and to improve the processing accuracy per tooth. Therefore, by performing quenching and tempering by carburizing, high frequency, or the like, the surface hardness of the spline connection portion 20 can be significantly increased.
[0041]
FIG. 4 shows a main part of a rotary shaft part and a gear fixing part according to a second embodiment. The difference between the second embodiment and the first embodiment is that both the first and second spigot portions 21 and 22 are connected to the outer peripheral surface of the second rotating shaft portion 16 and the second helical gear. The second rotation shaft portion 16 and the second helical gear 19 are arranged in contact with the spacers 25 and 29 between the inner peripheral surfaces of the rotation shaft 19 and are in contact with and supported by the entire surface.
[0042]
In the second embodiment, the front side (left side in FIG. 4) of the open end of the hub portion 19a of the second helical gear 19 has the same structure as the second helical gear 19 according to the first embodiment. However, an annular step having a diameter larger than the outer diameter of the outer spline of the second rotary shaft 16 is formed on the rear side (the right side in FIG. 4) of the open end of the hub 19a. A second spline machining relief 24 is formed between the opening end and the second rotation shaft 16. A spacer 29 is interposed concentrically in the annular space of the second spline machining relief portion 24. A port portion 27 a of a supply oil passage 27 extending in a radial direction from a lubrication oil passage 26 along the axis of the second rotation shaft portion 16 is arranged so as to open in a direction facing the spacer 29.
[0043]
Due to this structural change, in addition to having the same operation and effect as the first embodiment, even if the spigot portion cannot be formed directly in the second spline machining relief portion 24, the second spline machining relief portion can be formed. The second spigot portion 22 can be formed in the inside 24 via the spacer 29, and the axial length of the hub portion 19a of the helical gear 19 is larger than that of the gear hub portion of the first embodiment. Can be set shorter. Therefore, the helical gear 19 can be made compact, and its installation space can be used very effectively. The helical gear 19 has an axial thrust proportional to the torque because the tooth streaks are inclined with respect to the axis. However, the spacer 29 is used as a mechanical retaining structure for the helical gear 19. The second helical gear 19 can be prevented from being displaced in the thrust direction.
[0044]
FIG. 5 shows a main part of a rotating shaft part and a gear fixing part according to a third embodiment. The third embodiment is different from the above-described embodiments in that both the first and second spigot portions 21 and 22 eliminate the spacers 25 and 29 and make contact with the outer peripheral surface of the second rotary shaft portion 16. The second point is that the inner peripheral surface of the helical gear 19 is directly supported. Therefore, the axial length of the hub portion 19a of the helical gear 19 is set to be longer than the gear hub portion of each of the above embodiments.
[0045]
In the illustrated example, the rear side (the right side in FIG. 5) of the hub portion 19a of the helical gear 19 has the same structure as the first embodiment, but the front side of the open end portion of the hub portion 19a. Is set smaller than the inner diameter of the center inside having the inner spline via the annular step. The end surface of the opening end is in contact with the outer peripheral surface of the second rotating shaft 16, and a first spline processing relief portion 23 is formed between the opening end and the second rotating shaft 16. . The spline machining relief portion 23 and the lubricating oil passage 26 communicate with each other via the spline coupling portion 20. The lubricating oil supplied into the annular space of the spline machining escape portion 23 is led out.
[0046]
By this structural change, the number of parts can be reduced, and each of the spigot portions 21 and 22 directly supports the outer peripheral surface of the rotary shaft portion 16 and the inner peripheral surface of the helical gear 19. Therefore, a gear having a considerably wide tooth width can be stably and reliably supported. As for the gear, the radial load applied to the helical gear can be relatively reduced, with the meshing starting at one end of one of the teeth and ending with the point contact at the other end. In addition, it is similarly effective not only for a helical gear but also for a normal spur gear.
[0047]
FIG. 6 schematically shows a configuration example of a rotating shaft portion which is an input shaft of the blade and a fixed portion of the gear. In the figure, members that are substantially the same as those in the above embodiments are given the same member names and reference numerals. The first spigot portion 21 according to the illustrated example directly removes the spacer 25 and directly supports the outer peripheral surface of the first rotary shaft portion 15 and the inner peripheral surface of the first helical gear 18 as in the above-described embodiments. ing. The second spigot portion 22 supports the outer peripheral surface of the first rotating shaft portion 15 and the inner peripheral surface of the first helical gear 18 in the entire circumferential direction via a spacer 29 and supports the same.
[0048]
An outlet hole 18b is formed on the front side of the opening end of the hub portion 18a of the first helical gear 18 (left side in FIG. 6). The rear side of the open end of the hub portion 18a is set to have a size larger than the center inside having an inner diameter larger than the outer diameter of the outer spline of the first rotary shaft portion 15. A second spline machining relief portion 24 is formed between the rear end of the opening end and the first rotary shaft portion 15, and a spacer 29 is concentrically interposed in the annular space of the spline machining relief portion 24. ing.
[0049]
A port portion 27a of a supply oil passage 27 extending in a radial direction from an annular lubricating oil passage 26 along the axis of the first rotary shaft portion 15 is arranged to be open to the second spline machining relief portion 24. The lubricating oil passage 26 and the second spline machining relief portion 24 communicate with each other via the supply oil passage 27. The lubricating oil stored in the annular space of the spline processing relief portion 24 is guided to the spline coupling portion 20 with the rotation of the first rotation shaft portion 15, and a thin lubricating film is formed between the spline engagement surfaces. Is done. The lubricating oil supplied to the spline coupling portion 20 is led out of the first spline machining relief portion 23 through the outflow hole 18b. Even in the fourth embodiment, it is needless to say that the same operation and effect as the above embodiments can be obtained.
[0050]
As is clear from the above description, the fixed structure of the rotating shaft portion and the gear according to the present invention can prevent rattling due to internal wear on the spline connection portion, and the gear having a wide tooth width can be prevented. Can be completely prevented. Therefore, it is possible to secure the initially set good tooth contact over a long period of time, and to extremely increase the allowable stress. As a result, the durability between the rotating shaft portion and the gear can be significantly improved without generating vibration or noise.
[0051]
Further, since the rotating shaft portion and the gear can be supported by each spigot portion, the spline connecting portion can be fitted and fixed with an appropriate amount of clearance which is normally allowed. The disassembly and assembly of the rotating shaft portion and the gear can be easily performed at low cost. The above-described embodiments and examples are merely examples of the curved shape of the present invention, and the applicable range is also applicable to, for example, transmissions of general machinery in addition to the speed increaser of the wind power generator. The configuration can be variously modified within the scope of the technical matters described in the claims.
[Brief description of the drawings]
FIG. 1 is a schematic configuration diagram of a wind power generator as a typical embodiment to which a structure for fixing a rotating shaft portion and a gear according to the present invention is applied.
FIG. 2 is a cross-sectional view of a main part schematically showing an example of a speed increaser of the wind turbine generator.
FIG. 3 is a partially enlarged cross-sectional view schematically illustrating a configuration example of a rotating shaft portion and a fixing portion of the helical gear according to the first embodiment of the present invention.
FIG. 4 is a partially enlarged cross-sectional view schematically illustrating a configuration example of a rotating shaft portion and a fixing portion of a helical gear according to a second embodiment of the present invention.
FIG. 5 is a partially enlarged cross-sectional view schematically showing a configuration example of a rotating shaft portion and a fixing portion of a helical gear according to a third embodiment of the present invention.
FIG. 6 is a partially enlarged cross-sectional view schematically illustrating a configuration example of a rotating shaft portion and a fixed portion of a gear according to a fourth embodiment of the present invention.
[Explanation of symbols]
1 Wind power generator
Two towers
3 Nasser
4 Rotation axis
5 blade
6 Gearbox
7 Generator
8 Housing
9-14 bearing
15-17 First to third rotating shafts
18, 19 First and second helical gears
18a, 19a hub
20 spline joint
21, 22 First and second spigot parts
23, 24 First and second spline machining relief
25, 29 spacer
25a, 18b Outflow hole
26 Lubricating oil passage
27 Supply oil passage
27a Port section
28 Sealing stopper for lubricating oil

Claims (4)

A fixed structure of the rotating shaft and the gear,
A spline coupling portion (20) and a spigot portion (21, 22) between the outer peripheral surface of the rotary shaft portion (15, 16) and the inner peripheral surface of the gear (18, 19). Characteristic fixed structure of rotating shaft and gear. The spline coupling portion (20) is disposed at an intermediate portion between the outer peripheral surface of the rotating shaft portion (15, 16) and the inner peripheral surface of the gear (18, 19), and the spigot portion (21, 22) is provided. 2. The fixing structure according to claim 1, wherein the first and second splines are arranged at both ends of the spline connection part. A spacer (25, 29) is interposed in at least one of the annular spline processing relief portions (23, 24) formed on both sides of the spline coupling portion (20),
The spigot portions (21, 22) are formed at positions corresponding to the spacers (25, 29) between the outer peripheral surface of the rotary shaft portions (15, 16) and the inner peripheral surface of the gears (18, 19). The fixing structure according to claim 2, wherein the fixing structure is formed. A lubricating oil passage (26) extending along the axis of the rotating shaft portions (15, 16); and a supply oil passage (27) extending radially from the lubricating oil passage (26).
The fixing structure according to any one of claims 1 to 3, wherein a port portion (27a) of the supply oil passage (27) is arranged so as to open to the spline machining relief portion (23, 24). .

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