WO2006080127A1 - はすば歯車支持構造、風力発電機用増速機および垂直軸支持構造 - Google Patents
はすば歯車支持構造、風力発電機用増速機および垂直軸支持構造 Download PDFInfo
- Publication number
- WO2006080127A1 WO2006080127A1 PCT/JP2005/020742 JP2005020742W WO2006080127A1 WO 2006080127 A1 WO2006080127 A1 WO 2006080127A1 JP 2005020742 W JP2005020742 W JP 2005020742W WO 2006080127 A1 WO2006080127 A1 WO 2006080127A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- row
- double
- support structure
- bearing
- right rows
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/50—Other types of ball or roller bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
- F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
- F03D80/70—Bearing or lubricating arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
- F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
- F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
- F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings in O-arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/50—Other types of ball or roller bearings
- F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/56—Systems consisting of a plurality of bearings with rolling friction in which the rolling bodies of one bearing differ in diameter from those of another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/06—Ball or roller bearings
- F16C23/08—Ball or roller bearings self-adjusting
- F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
- F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/36—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers
- F16C19/364—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/30—Angles, e.g. inclinations
- F16C2240/34—Contact angles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/31—Wind motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/34—Rollers; Needles
- F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/041—Combinations of toothed gearings only for conveying rotary motion with constant gear ratio
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Definitions
- the present invention relates to a helical gear support structure, a wind power generator that includes a helical gear, and a swivel reducer that includes a vertical shaft support structure and a vertical shaft.
- the wind speed booster 1 is supported by an input shaft 2 that rotates together with blades that receive wind power, and a double-row rolling bearing 4, and an output connected to the generator. It comprises a shaft 3 and a planetary gear mechanism 5 that accelerates the rotation of the input shaft 2 and transmits it to the output shaft 3.
- the planetary gear mechanism 5 includes a sun gear 6 connected to the output shaft 3, an internal gear 7 fixed to the housing, and the input shaft 2 via a bearing 9. It consists of 6 gears and 8 planetary gears.
- the sun gear 6, the internal gear 7 and the planetary gear 8 are helical gears that can transmit a large force with extremely smooth transmission and little vibration noise.
- FIG. 2A is a diagram showing a state in which the helical gear 71 and the helical gear 72 are held together.
- the helical gear 71 rotates clockwise as viewed from the right side of the figure, the helical gear 71 is caused by the meshing of the helical gear 71 and the helical gear 72 as shown in FIG.
- the power F which is the resultant force of the radial component force Fr and the axial component force Fa, acts.
- both the radial load and the axial load are applied to one row of the double row rolling bearing 4 while only the radial load is applied to the other row. Therefore, the rolling fatigue life of the high load side row is shortened.
- slip occurs between the rollers and the raceway surfaces of the inner and outer rings, causing problems of surface damage and wear.
- the margin becomes too large on the light load side, which is uneconomical.
- FIG. 3 is a schematic cross-sectional view of the swivel reducer described in the publication.
- a swivel reducer 101 is supported by an input shaft 102 connected to a power generation device such as a hydraulic motor and a double row rolling bearing 105, and rotates the input shaft 102 with a gear 106.
- a power generation device such as a hydraulic motor and a double row rolling bearing 105
- the input shaft 102 and the output shaft 103 are vertically supported vertically.
- the vertical axis includes the case where it is supported at a certain angle from the vertical direction, which is not strictly supported in the vertical direction.
- the planetary gear mechanism 104 is connected to the output shaft 103 via a sun gear 107 connected to the input shaft 102, an internal gear 108 fixed to the housing, and a bearing 110.
- the planetary gear 109 meshes with the tooth gear 108 and also becomes a force.
- the swivel reducer 101 shown in FIG. 3 operates as follows.
- the double-row rolling bearing 105 that supports 103 is required to have a large axial load capacity.
- a double-row self-aligning roller bearing or a double-row tapered roller bearing is used as a bearing that supports a vertical shaft such as the output shaft 103 of the swivel reducer 101.
- An object of the present invention is to provide an appropriate support according to the load condition of each row in an environment where different loads are applied to the left and right rows, to extend the actual life, and to waste materials. It is an object to provide a helical gear support structure provided with an economical double-row rolling bearing, and a wind turbine speed increaser provided with such a helical gear support structure.
- Another object of the present invention is to provide an appropriate support according to the load condition of each row in an environment where different loads are applied to the left and right rows, thereby extending the substantial life, and It is to provide a vertical shaft support structure with an economical double row rolling bearing that is free of material.
- a helical gear support structure includes a helical gear having a central axis, and a double-row rolling bearing incorporated in a fixed member and rotatably supporting the central axis.
- This is a Subaru gear support structure. Focusing on double row rolling bearings, the load capacity of the left and right rows is different from each other, and the load capacity of the row that receives a large axial load is increased.
- the double row rolling bearing includes, for example, an inner ring having raceway surfaces in the left and right rows, an outer ring having a raceway surface of a spherical recess, and spherical rollers arranged in a double row between the inner ring and the outer ring. It is preferable to provide a double row spherical roller bearing. As a result, a double-row rolling bearing having alignment with respect to misalignment due to shaft sag or the like can be obtained.
- the roller lengths in the left and right rows are different from each other, and the roller length on the side receiving a large axial load is increased.
- the load capacity of the row having the spherical roller having a long roller length can be increased.
- the roller diameters in the left and right rows are different from each other, and the roller diameter in the row on the side receiving a large axial load is increased.
- the load capacity of the row having the spherical roller having a large roller diameter is increased.
- the contact angles of the left and right rows are the same.
- a symmetrical standard product can be used for the outer ring, so that the manufacturing cost can be reduced. Furthermore, since the right and left columns can be measured under the same measurement conditions when measuring the accuracy of the outer ring, the measurement work can be performed efficiently.
- the double-row rolling bearing includes, for example, a double-row tapered roller bearing including an inner ring having raceways in the left and right rows, an outer ring, and a tapered roller disposed in a double row between the inner ring and the outer ring. It is preferable to do.
- the double row tapered roller bearing is preferably, for example, a back combination bearing in which the small diameter side ends of the tapered rollers in the left and right rows face each other.
- This configuration increases the distance between the rotation center line of the bearing and the contact line between the tapered rollers in the left and right rows and the inner and outer rings (hereinafter referred to as the “distance between the operating points”). Capacity and moment load capacity are improved.
- the double-row tapered roller bearing is preferably a front combination bearing in which the large-diameter end portions of the left and right rows of tapered rollers face each other.
- the left and right rows have different roller lengths, and the length of the row on the side receiving a large axial load is increased.
- a wind turbine speed increaser is fixed to one end of a blade that receives wind power, and rotates with the blade, an output shaft connected to the generator, an input shaft, and an output shaft. It is a speed increasing device for wind power generators provided with a speed increasing mechanism that is disposed between the speed increasing rotation of the input shaft and transmitting it to the output shaft.
- the speed increasing mechanism includes a helical gear as one element of the power transmission means and a double-row rolling bearing that rotatably supports the shaft of the helical gear.
- the present invention uses negative bearings in each row by using bearings having different load capacities in the left and right rows. Proper support according to the load situation can be performed, and a long-life helical gear support structure with high reliability can be obtained.
- the vertical shaft support structure according to the present invention is a vertical shaft support structure including a vertical shaft and a double row rolling bearing that is incorporated in a fixed member and rotatably supports the vertical shaft.
- double row rolling bearings When paying attention to double row rolling bearings, the load capacity of the left and right rows is different from each other, and the load capacity of the row receiving the large axial load is increased.
- the double row rolling bearing includes, for example, an inner ring having a raceway surface in the left and right rows, an outer ring having a spherical concave raceway surface, and spherical rollers arranged in a double row between the inner ring and the outer ring. It is preferable that it is a double row self-aligning roller bearing provided. As a result, a double row rolling bearing having alignment with respect to misalignment due to shaft sag or the like can be obtained.
- the roller lengths in the left and right rows are different from each other, and the roller length on the side receiving a large axial load is increased.
- the load capacity of the row having the spherical roller having a long roller length can be increased.
- the roller diameters of the left and right rows are different from each other, and the roller diameter of the row on the side receiving a large axial load is increased.
- the load capacity of the row having the spherical roller having a large roller diameter is increased.
- the contact angles of the left and right rows are the same.
- a symmetrical standard product can be used for the outer ring, so that the manufacturing cost can be reduced.
- the right and left columns can be measured under the same measurement conditions when measuring the raceway diameter, surface roughness, roundness, etc. (hereinafter referred to as “dimensions etc.”) of the outer ring raceway surface. Can be performed efficiently.
- the double-row rolling bearing is, for example, a double-row tapered roller bearing including an inner ring having raceways in the left and right rows, an outer ring, and tapered rollers arranged in a double row between the inner ring and the outer ring. It is preferable to have it.
- the double row tapered roller bearing is preferably, for example, a back combination bearing in which the small diameter side ends of the tapered rollers in the left and right rows face each other.
- the double row tapered roller bearing is preferably, for example, a back combination bearing in which the large diameter side ends of the tapered rollers in the left and right rows face each other.
- the roller lengths of the left and right rows are different from each other, and the roller length of the row on the side receiving a large axial load is increased.
- the roller diameters in the left and right rows are different from each other, and the roller diameter in the row on the side receiving a large axial load is increased.
- the present invention uses the bearings in which the load capacities of the left and right rows are different from each other, thereby responding to the load condition of each row. Therefore, it is possible to obtain a reliable and long-life vertical shaft support structure.
- FIG. 1 is a schematic view of a conventional wind speed booster.
- FIG. 2A A view showing a pair of helical gears.
- FIG. 2B is a diagram showing the direction of a load acting during rotation.
- FIG. 3 is a schematic cross-sectional view of a conventional turning speed reducer.
- FIG. 2 is a view showing a double-row self-aligning roller bearing in which the roller lengths in the left and right rows are different from each other.
- FIG. 5 is a bearing used in the helical gear support structure and the vertical shaft support structure according to the present invention, wherein the roller lengths are different from each other in the left and right rows, and the contact angles of the left and right rows of the bearings are the same. It is a figure showing a double row self-aligning roller bearing.
- FIG. 6 shows a front row double row tapered roller bearing that is used in the helical gear support structure and the vertical shaft support structure according to the present invention and that has different roller lengths in the left and right rows.
- FIG. 7 A bearing used in the helical gear support structure and the vertical shaft support structure according to the present invention, showing a double-row conical roller bearing with a back surface combination in which the roller lengths are different from each other in the left and right rows.
- FIG. 8 is a schematic view showing a wind power speed increaser according to another embodiment of the present invention.
- the double row rolling bearing shown in FIG. 4 holds the inner ring 12, the outer ring 13, and the spherical rollers 14, 15 and the spherical rollers 14, 15 arranged in a double row between the inner ring 12 and the outer ring 13.
- This is a double row spherical roller bearing 11 provided with a cage 16.
- the inner ring 12 has a raceway surface along the outer diameter surface of each of the spherical rollers 14 and 15, and an intermediate flange 17.
- the outer ring 13 is a common raceway surface along the outer diameter surface of the spherical rollers 14 and 15.
- roller length L of spherical roller 15 is the same as the roller length L of spherical roller 14.
- the contact angle ⁇ of the bearing l ib in the row is larger than the contact angle ⁇ of the bearing 11a in the left row.
- the double-row self-aligning roller bearing 11 having the above-described configuration has a spherical bearing 15 on the side of the spherical roller 15 having a longer roller length by making the roller lengths different between the left and right rows.
- Roller 14 It can be made larger than the bearing 11a on the side.
- the axial load capacity of the bearings ib in the right row with the increased contact angles can be made larger than that in the bearings 11a in the left row.
- the double-row rolling bearing shown in FIG. 5 is arranged in a double row between the inner ring 22 having a center collar 27, the outer ring 23 having a spherical concave raceway surface, and the inner ring 22 and the outer ring 23. It is equipped with spherical rollers 24 and 25 with different roller lengths in a row, L, and a cage 26 that holds the spherical rollers 24 and 25.
- the force using a symmetric roller as the spherical roller is not limited to this.
- the maximum radial position force of the roller The center in the length direction of the roller Asymmetrical rollers that do not exist in may be used.
- an induced thrust load is generated when the double row spherical roller bearing receives a load, and the spherical roller is pressed against the center. Can be suppressed.
- the inner ring has a center collar
- the inner ring has a guide collar guided by the inner ring or the outer ring. As good as that.
- the double-row rolling bearing shown in FIG. 6 includes an inner ring 32 that abuts the large-diameter side ends of two inner ring members, an outer ring 33 that abuts two outer ring members across a spacer 37, an inner ring 32, and A double-row tapered roller bearing 31 having tapered rollers 34 and 35 having different roller lengths in the left and right rows between outer rings 33 and a retainer 36 that holds the tapered rollers 34 and 35 in each row. .
- each of the tapered rollers 34, 35 in the left and right rows is provided.
- This is a front combination bearing with large diameter side ends facing each other.
- the roller length L of the tapered roller 35 is set to the length of the tapered roller 34.
- roller length is longer than L, the axial load carrying capacity is higher in the row of tapered rollers 35 having a longer roller length.
- the inner ring 32 may be integrally formed.
- the double-row rolling bearing shown in FIG. Different tapered rollers 44, 45 are arranged.
- the tapered rollers 44 and 45 are double row tapered roller bearings 41 each having a retainer 46 that holds the tapered rollers 44 and 45 in each row.
- the double row tapered roller bearing 41 is a rear combination bearing in which the small diameter side ends of the tapered rollers 44 and 45 of the left and right rows are aligned! /.
- the roller length L of the tapered roller 44 is longer than the roller length L of the tapered roller 45.
- FIG. 4 to 7 an example has been shown in which the load capacity is changed between the left and right rows of the bearing by making the roller lengths different between the left and right rows.
- the left and right rows may have different roller diameters, or one roller may be a solid roller and the other roller may be a hollow roller having a through hole penetrating both end faces. Furthermore, by combining these, it is also effective to vary the load capacity between the left and right rows of the bearing.
- the load capacity of the bearing on the larger roller diameter side can be increased.
- the load capacity of the bearing on the side where the solid roller is disposed can be increased by using one of the left and right rows of the bearing as a solid roller and the other as a hollow roller.
- the inner ring and the outer ring can be used as standard products, and the manufacturing cost can be reduced.
- the speed increaser 50 for a wind power generator includes an input shaft 51 that rotates together with a blade that receives wind power, an intermediate shaft 52, and a planetary gear mechanism 55 that accelerates the rotation of the input shaft 51 and transmits the rotation to the intermediate shaft 52.
- a first speed increasing device comprising: intermediate shafts 52 and 53; an output shaft 54 connected to the generator; and parallel shafts connecting the intermediate shafts 52 and 53 and the output shaft 54 with helical gears 56 to 59.
- a second speed increasing device of the gear mechanism is a first speed increasing device comprising: intermediate shafts 52 and 53; an output shaft 54 connected to the generator; and parallel shafts connecting the intermediate shafts 52 and 53 and the output shaft 54 with helical gears 56 to 59.
- the planetary gear mechanism 55 is connected to the input shaft 51 via the sun gear 60 connected to the intermediate shaft 52, the internal gear 61 fixed to the housing, and the bearing 63. It consists of a planetary gear 62 that meshes with the toothed gear 61. Helical gears are used for the sun gear 60, the internal gear 61 and the planetary gear 62.
- the intermediate shafts 52 and 53 and the output shaft 54 are supported by double-row rolling bearings 64 to 69 fixed to the housing, respectively.
- the first speed increasing device rotates by meshing with the internal gear 61 when the planetary gear 62 revolves around the sun gear 60 as the input shaft 51 rotates.
- the sun gear 60 transmits rotation of the input shaft 51 to the intermediate shaft 52 by meshing with the planetary gear 62 that rotates.
- the greater the difference in the number of teeth between the sun gear 60 and the internal gear 61 the faster the rotation of the input shaft 51 is transmitted to the intermediate shaft 52.
- the second speed increasing device transmits the rotation of the intermediate shaft 52 to the output shaft 54 via the intermediate shaft 53 by means of helical gears 56 to 59.
- the rotation of the intermediate shaft 52 is accelerated and the output shaft is increased. Is transmitted to 54.
- Spur gears may be used for some or all of the various gears used in the wind turbine speed increaser 50. However, by using helical gears, transmission is extremely smooth and vibration is achieved. It is possible to obtain a gearbox capable of transmitting a large force with less dynamic noise.
- the input shaft 51, the intermediate shafts 52 and 53, and the output shaft 54 each receive an axial load due to the meshing of the helical gears. Therefore, by using the double-row rolling bearing shown in Figs. 4 to 7 as the double-row rolling bearing that supports each shaft, appropriate support according to the load condition of each row can be performed, so the reliability is high. A long-life wind generator gearbox can be obtained.
- the double row rolling bearing 68 has a row closer to the helical gear 59. It is preferable to arrange the row on the side with the higher load capacity of the bearing in the row farther from the helical gear 59 of the double row rolling bearing S 69.
- the double row rolling bearing shown in Fig. 7 is used for the double row rolling bearings 68 and 69, the double row rolling bearing 68 has a row farther from the helical gear 59 and a double row rolling bearing. Place the row with the higher load capacity of the bearing in the row closer to the helical gear 59 of the bearing 69.
- Each of the embodiments shown in FIGS. 4 to 7 has a force applicable to the double row rolling bearing 105 that supports the output shaft 102 of the swivel reducer shown in FIG. It can also be applied to a vertical shaft support structure to be loaded.
- the present invention is advantageously used in a helical gear support structure and a vertical shaft support structure.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Rolling Contact Bearings (AREA)
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/795,752 US20080118344A1 (en) | 2005-01-25 | 2005-11-11 | Helical Gear Supporting Structure, Speed Increaser for Wind Power Generator, and Vertical Shaft Supporting Structure |
DE112005003424T DE112005003424T5 (de) | 2005-01-25 | 2005-11-11 | Tragkonstruktion für ein Schrägzahnrad, Drehzahlerhöhungsgetriebe für einen Windkraftgenerator, und Tragkonstruktion für eine vertikale Welle |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005017112A JP2006207622A (ja) | 2005-01-25 | 2005-01-25 | はすば歯車支持構造および風力発電機用増速機 |
JP2005-017113 | 2005-01-25 | ||
JP2005-017112 | 2005-01-25 | ||
JP2005017113A JP2006207623A (ja) | 2005-01-25 | 2005-01-25 | 垂直軸支持構造 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006080127A1 true WO2006080127A1 (ja) | 2006-08-03 |
Family
ID=36740161
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/020742 WO2006080127A1 (ja) | 2005-01-25 | 2005-11-11 | はすば歯車支持構造、風力発電機用増速機および垂直軸支持構造 |
Country Status (3)
Country | Link |
---|---|
US (1) | US20080118344A1 (ja) |
DE (1) | DE112005003424T5 (ja) |
WO (1) | WO2006080127A1 (ja) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8137234B2 (en) | 2007-10-23 | 2012-03-20 | Vestas Wind Systems A/S | Gearbox for a wind turbine, a method of converting wind energy and use of a gearbox |
CN105378308A (zh) * | 2013-07-30 | 2016-03-02 | 舍弗勒技术股份两合公司 | 用于将变速器轮支承在变速器轴上的不对称的锥形滚子轴承 |
CN109424726A (zh) * | 2017-08-30 | 2019-03-05 | 上海旭恒精工机械制造有限公司 | 一种转向传动支撑装置 |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
BE1016856A5 (nl) * | 2005-11-21 | 2007-08-07 | Hansen Transmissions Int | Een tandwielkast voor een windturbine. |
GB201104917D0 (en) * | 2011-03-24 | 2011-05-04 | Qinetiq Ltd | Gear reduction mechanism |
WO2012130305A1 (en) * | 2011-03-30 | 2012-10-04 | Amsc Windtec Gmbh | Bearing arrangement and wind energy converter |
CN102619875B (zh) * | 2012-04-10 | 2014-05-07 | 济南轨道交通装备有限责任公司 | 一种风力发电机主轴调心滚子轴承及其设计方法 |
EP2669541B1 (en) * | 2012-05-31 | 2015-06-24 | Siemens Aktiengesellschaft | Tapered roller bearing arrangement for a direct drive generator of a wind turbine |
DE102014104862A1 (de) * | 2014-04-04 | 2015-10-08 | Thyssenkrupp Ag | Wälzlageranordnung und Windkraftanlage |
JP6459370B2 (ja) * | 2014-04-10 | 2019-01-30 | 株式会社ジェイテクト | 駆動ユニット及び駆動モジュール |
DE102014213789A1 (de) * | 2014-07-16 | 2016-01-21 | Schaeffler Technologies AG & Co. KG | Zweireihiges Pendelrollenlager |
DE102017103332A1 (de) | 2017-02-17 | 2018-08-23 | Thyssenkrupp Ag | Magnetlager und Verfahren zum Betrieb eines Magnetlagers |
USD877783S1 (en) * | 2018-04-17 | 2020-03-10 | Justin Smith | Helical gear |
WO2022015791A1 (en) * | 2020-07-17 | 2022-01-20 | The Timken Company | Bearing assembly with stainless steel race |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61171917A (ja) * | 1985-01-25 | 1986-08-02 | Nippon Seiko Kk | 圧延機ロールネック用多列ころ軸受 |
JP2002031148A (ja) * | 2000-07-14 | 2002-01-31 | Nsk Ltd | 転がり軸受装置 |
JP2003172345A (ja) * | 2001-12-07 | 2003-06-20 | Koyo Seiko Co Ltd | 車軸ピニオン用軸受装置および車両用終減速装置 |
JP2004245251A (ja) * | 2003-02-10 | 2004-09-02 | Nsk Ltd | 自動調心ころ軸受 |
JP2004339953A (ja) * | 2003-05-13 | 2004-12-02 | Kanzaki Kokyukoki Mfg Co Ltd | 風力発電装置 |
JP2005147330A (ja) * | 2003-11-18 | 2005-06-09 | Ntn Corp | 複列自動調心ころ軸受および風力発電機主軸支持装置 |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US931924A (en) * | 1907-06-26 | 1909-08-24 | Henry Hess | Journal-bearing. |
US1928114A (en) * | 1932-03-18 | 1933-09-26 | Scheffler Frederick William | Antifriction bearing |
US2130379A (en) * | 1937-06-02 | 1938-09-20 | Chilton Roland | Antifriction bearing |
US3556618A (en) * | 1968-12-11 | 1971-01-19 | Torrington Co | Double race screwdown thrust bearing |
NL7710564A (nl) * | 1977-09-28 | 1979-03-30 | Skf Ind Trading & Dev | Wentellager. |
US4557613A (en) * | 1978-09-01 | 1985-12-10 | Skf Industries, Inc. | Spherical roller bearing having reciprocal crowning for skew control |
DE8615458U1 (de) * | 1986-06-07 | 1986-07-24 | SKF GmbH, 8720 Schweinfurt | Abgedichtete Lagerung |
DE3733495A1 (de) * | 1987-10-03 | 1989-04-13 | Skf Gmbh | Eine winkelcodierung aufweisendes lager |
JP4023860B2 (ja) * | 1996-02-28 | 2007-12-19 | Ntn株式会社 | 自動車の変速機における主軸歯車機構 |
DE19612589B4 (de) * | 1996-03-29 | 2005-12-22 | Skf Gmbh | Lagerung |
US5975762A (en) * | 1997-10-14 | 1999-11-02 | The Timken Company | Tapered roller bearing with true rolling contacts |
US6814494B2 (en) * | 2002-04-23 | 2004-11-09 | The Timken Company | Sealed spherical roller bearing for dragline swing shaft |
US6293704B1 (en) * | 2000-03-21 | 2001-09-25 | The Timken Company | Shaft mounting with enhanced stability |
US6851863B2 (en) * | 2001-12-07 | 2005-02-08 | Koyo Seiko Co., Ltd. | Double row tapered rolier bearing apparatus |
JP4031747B2 (ja) * | 2003-09-30 | 2008-01-09 | 三菱重工業株式会社 | 風力発電用風車 |
US7918649B2 (en) * | 2003-11-18 | 2011-04-05 | Ntn Corporation | Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft |
DE102004013542A1 (de) * | 2004-03-19 | 2005-10-06 | Fag Kugelfischer Ag | Bolzenkäfig für ein zweireihiges Pendelrollenlager |
US7922396B2 (en) * | 2004-09-21 | 2011-04-12 | Ntn Corporation | Double row self-aligning roller bearing and main shaft support structure of wind power generator |
WO2006035836A1 (ja) * | 2004-09-30 | 2006-04-06 | Jtekt Corporation | ハブユニットと転がり軸受装置及びその製造方法並びに転がり軸受装置の組み付け装置及びその組み付け方法 |
WO2007111316A1 (ja) * | 2006-03-28 | 2007-10-04 | Jtekt Corporation | 車輪用軸受装置 |
-
2005
- 2005-11-11 US US11/795,752 patent/US20080118344A1/en not_active Abandoned
- 2005-11-11 DE DE112005003424T patent/DE112005003424T5/de not_active Withdrawn
- 2005-11-11 WO PCT/JP2005/020742 patent/WO2006080127A1/ja not_active Application Discontinuation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61171917A (ja) * | 1985-01-25 | 1986-08-02 | Nippon Seiko Kk | 圧延機ロールネック用多列ころ軸受 |
JP2002031148A (ja) * | 2000-07-14 | 2002-01-31 | Nsk Ltd | 転がり軸受装置 |
JP2003172345A (ja) * | 2001-12-07 | 2003-06-20 | Koyo Seiko Co Ltd | 車軸ピニオン用軸受装置および車両用終減速装置 |
JP2004245251A (ja) * | 2003-02-10 | 2004-09-02 | Nsk Ltd | 自動調心ころ軸受 |
JP2004339953A (ja) * | 2003-05-13 | 2004-12-02 | Kanzaki Kokyukoki Mfg Co Ltd | 風力発電装置 |
JP2005147330A (ja) * | 2003-11-18 | 2005-06-09 | Ntn Corp | 複列自動調心ころ軸受および風力発電機主軸支持装置 |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8137234B2 (en) | 2007-10-23 | 2012-03-20 | Vestas Wind Systems A/S | Gearbox for a wind turbine, a method of converting wind energy and use of a gearbox |
US8393994B2 (en) | 2007-10-23 | 2013-03-12 | Vestas Wind Systems A/S | Gearbox for a wind turbine, a method of converting wind energy and use of a gearbox |
CN105378308A (zh) * | 2013-07-30 | 2016-03-02 | 舍弗勒技术股份两合公司 | 用于将变速器轮支承在变速器轴上的不对称的锥形滚子轴承 |
CN105378308B (zh) * | 2013-07-30 | 2018-05-25 | 舍弗勒技术股份两合公司 | 用于将变速器轮支承在变速器轴上的不对称的锥形滚子轴承 |
CN109424726A (zh) * | 2017-08-30 | 2019-03-05 | 上海旭恒精工机械制造有限公司 | 一种转向传动支撑装置 |
CN109424726B (zh) * | 2017-08-30 | 2024-04-30 | 上海旭恒精工机械制造有限公司 | 一种转向传动支撑装置 |
Also Published As
Publication number | Publication date |
---|---|
US20080118344A1 (en) | 2008-05-22 |
DE112005003424T5 (de) | 2007-12-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2006080127A1 (ja) | はすば歯車支持構造、風力発電機用増速機および垂直軸支持構造 | |
US8192323B2 (en) | Epicyclic gear system with flexpins | |
JP5156961B2 (ja) | 減速装置 | |
US9435399B2 (en) | Reduction gear | |
US7988583B2 (en) | Final reduction gear device | |
US20050148425A1 (en) | Cylindrical roller bearing and planetary gear assembly utilizing the same | |
EP2426355A1 (en) | Step-up gear for a wind-powered electrical generator, and wind-powered electrical generator | |
KR101248306B1 (ko) | 증감속 장치 | |
TW201305464A (zh) | 附有複合滾動軸承的內齒輪單元及諧波齒輪裝置 | |
JP2013231448A (ja) | 一方向クラッチ及び発電装置 | |
US10233906B2 (en) | Joint member for wind power generation apparatus, and wind power generation apparatus | |
KR20110034660A (ko) | 유성 증속기 | |
CN108843746A (zh) | 一种用于机械人的精密减速器 | |
JP2013053713A (ja) | ころ軸受及び風力発電用増速機 | |
JP2006177447A (ja) | 複列転がり軸受 | |
JP2006207623A (ja) | 垂直軸支持構造 | |
JP6233805B2 (ja) | トラクション動力伝達装置 | |
JP5232763B2 (ja) | マイクロトラクションドライブ | |
JP2006207622A (ja) | はすば歯車支持構造および風力発電機用増速機 | |
JP2007085559A (ja) | 撓み噛み合い式減速機 | |
JP3692330B2 (ja) | マイクロトラクションドライブ | |
JP2007024086A (ja) | 軸受装置 | |
JP3617645B2 (ja) | マイクロトラクションドライブ | |
JP2020200850A (ja) | 組合せ円錐ころ軸受及びギヤボックス | |
JP2003021212A (ja) | 摩擦式無段変速機 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 11795752 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120050034240 Country of ref document: DE |
|
RET | De translation (de og part 6b) |
Ref document number: 112005003424 Country of ref document: DE Date of ref document: 20071213 Kind code of ref document: P |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 05806268 Country of ref document: EP Kind code of ref document: A1 |
|
WWW | Wipo information: withdrawn in national office |
Ref document number: 5806268 Country of ref document: EP |
|
WWP | Wipo information: published in national office |
Ref document number: 11795752 Country of ref document: US |