JP2012180809A - Reduction gear of wind power generation equipment and reduction gear having output pinion - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compact reduction gear capable of effectively preventing any breakage or failure of the reduction gear and a motor at low cost, even in a situation in which excessive wind power load is applied.SOLUTION: The reduction gear G1 has an output pinion 24 to be engaged with a gear provided on a body side of a wind power generation equipment, and includes: a planetary gear reduction gear mechanism 44 having an external-tooth gear (planetary gear) 76, an output flange (carrier) 82, and a plurality of inner pins (planetary pins) 80; and a constraint ring 88 for bundling ends on each counter-carrier side of the inner pins 80. A counter-load side cover body (casing) 48C and the constraint ring 88 have a very small spacing δ1 when they are assembled, and are arranged opposite to each other so as to be brought into contact with each other when the load L to be transmitted exceeds a predetermined value Lo, and the predetermined value Lo is set within a range of Le<Lo<Lm, wherein Le denotes a fatigue equivalent load, and Lm denotes an extreme value load.

Description

  The present invention relates to a reduction gear used particularly for wind power generation equipment and a reduction gear provided with an output pinion.

  Patent Document 1 discloses a reduction gear used for a wind power generation facility. As control of wind power generation equipment, yaw control for controlling the direction (rotation) of the nacelle (power generation chamber) in the horizontal plane with respect to the wind, pitch control for controlling the direction (tilt) of the windmill blade with respect to the wind, etc. However, both are realized by a speed reducer driven by a motor or a hydraulic cylinder.

  In many cases, a planetary gear reduction mechanism is used as a reduction gear used in a wind power generation facility, including the reduction gear of Patent Document 1, for a part or all of the reduction gear. The planetary gear speed reduction mechanism includes a planetary gear, a carrier, and a plurality of planetary pins protruding from the carrier and penetrating through the planetary gear, and the planetary gear from the carrier via the plurality of planetary pins (inner pins). The rotation or revolution component is taken out. The carrier is connected to the output shaft of the speed reducer, and an output pinion is provided on the output shaft. For example, in the case of a yaw drive device, the output pinion meshes with an internal gear (or external gear) provided on the cylindrical support column side of the wind power generation facility, and the nacelle (with a speed reducer attached) is driven by its reaction. It has come to be.

  Since wind power generation equipment is installed in a natural environment, it sometimes receives strong turbulent winds and gusts. When such a strong wind is applied to the wind turbine blade, the wind turbine blade itself rotates or the wind turbine blade rotates the nacelle. Thereby, each reduction gear will be in the state where the huge load was applied from the output side. As a result, the speed reducer exhibits the motion of the speed increasing device with the original output shaft as the input shaft, and each member or motor in the speed reducing device is forced to rotate with an excessively strong torque (or rotational speed). Will occur.

  This Patent Document 1 discloses a configuration that is devised to disperse and reduce the weight of the load acting on the planetary pins by incorporating a constraining ring that bundles the opposite carrier sides of the plurality of planetary pins. According to this configuration, it is possible to prevent only some planetary pins from being greatly deformed.

JP 2010-236357 A (paragraph [0024], FIG. 1)

  However, even a structure having a “restraint ring that bundles the opposite carrier sides of a plurality of planetary pins” as in Patent Document 1 is still sufficient in strength as a structure of a natural counterpart wind power generation facility. There was a face that could not be said.

  For example, if the thickness of the inner pin is increased in order to increase the strength of the planetary pin, a margin for strength can be obtained. However, the increase in the thickness of the inner pin increases the size of the entire speed reducer. This is a major disadvantage for equipment installed in a narrow nacelle. In addition, the cost increases, the weight increases, and the power loss increases.

  The present invention has been made to solve such a conventional problem, and is small in size and low in cost, and can reduce transmission loss during normal operation and increase support rigidity at high load. Therefore, it is an object of the present invention to effectively prevent breakage or failure of each element of the reduction gear even in a situation where an excessive load is applied from the output pinion side.

  The present invention relates to a reduction gear including an output pinion that meshes with a gear provided on a main body side of a wind turbine generator, and includes a planetary gear, a carrier, and a plurality of planetary pins protruding from the carrier and penetrating through the planetary gear. And a planetary gear speed reduction mechanism for extracting the rotation or revolution component of the planetary gear from the carrier via the plurality of planetary pins, and a restraining ring for bundling the ends on the opposite carrier side of the plurality of planetary pins. Provided, the casing of the speed reducer and the restraining ring have a minute gap at the time of assembly, but are arranged to face each other so that the load L transmitted in a specific part of the speed reducer exceeds a predetermined value Lo And the predetermined value Lo is defined as Le for the fatigue equivalent load to be transmitted in the specific portion, and Lm for the extreme load that is the limit of transmission. Occasionally, by adopting the configuration that is set in the range of Le <Lo <Lm, it is obtained by solving the above problems.

  Note that the “main body” on the main body side of the wind power generation facility refers to a “member or device that moves relative to a member in which the speed reducer is incorporated”. For example, in the case of a yaw drive device of a wind power generation facility, a cylindrical column that moves relative to the structural member of the nacelle in which the speed reducer is incorporated corresponds to the “main body”, and in the case of a pitch drive device, The wind turbine blade that moves relative to the structural member of the nacelle in which the speed reducer is incorporated corresponds to the “main body”.

  The constraining ring according to the present invention not only simply bundles the ends of the plurality of planetary pins on the side opposite to the carrier, but under the “predetermined condition”, the outer periphery abuts against the inner periphery of the casing. Can receive support reaction force from.

  More specifically, in the restraining ring according to the present invention, the load L (which can also be regarded as torque) L transmitted in a specific part of the reduction gear (for example, output shaft: details will be described later) exceeds a predetermined value Lo. At that time, it receives support reaction force from the casing side. In the present invention, the predetermined value Lo is defined as follows.

  In this type of wind power generation equipment, each device including the speed reducer is designed to ensure a service life of at least 20 years. However, a load that does not break even if given for 20 years is a “fatigue equivalent load”. Called. Moreover, the limit load of transmission which does not break even if it is applied only once in 20 years is called “extreme load”.

  In the present invention, when the speed reducer is assembled and when the load L transmitted in a specific portion of the speed reducer is lower than the fatigue equivalent load Le, a minute gap is maintained between the casing and the restraining ring, and the casing And the restraining ring will not contact. However, when the load L transmitted in a specific part of the reduction gear exceeds the fatigue equivalent load Le and reaches a predetermined value Lo, the rotation of the carrier and the planetary pin is caused by the radial load and the rotational torque input from the output pinion side. The shaft center is displaced from the shaft center of the casing, and the restraining ring comes into contact with the casing. In the present invention, the predetermined value Lo is set to a value larger than the fatigue equivalent load Le and smaller than the extreme value load Lm. If expressed by an equation, the range Le <Lo <Lm is set.

  According to the present invention, it is small in size and low in cost, can reduce transmission loss during normal operation, can increase support rigidity at high load, and is in a situation where an excessive load is applied from the output pinion side. It is possible to effectively prevent breakage or failure of each element of the speed reducer.

Whole sectional drawing of the reduction gear used for the wind power generation equipment which concerns on an example of embodiment of this invention Enlarged view of the relevant parts of the speed reducer (A) Front view and (B) IIIB-IIIB sectional view of the restraining ring of the speed reducer (A) Front view and (B) IVB-IVB sectional view of the casing cover body of the speed reducer The graph which shows the deformation | transformation aspect of each inner pin (planetary pin) in the said embodiment. The graph which shows the tensile stress of each inner pin (planetary pin) in the said embodiment Front view of wind power generation equipment to which the speed reducer is applied The perspective view which shows typically a mode that the said speed reducer is integrated in the nacelle of the said wind power generation equipment. Cross-sectional view of the main part showing the structure of the yaw drive device of the wind power generation facility Whole sectional drawing of the reduction gear device used for the wind power generation equipment which concerns on an example of other embodiment of this invention.

  Hereinafter, a reduction device for a wind power generation facility according to an example of an embodiment of the present invention will be described in detail with reference to the drawings.

  First, an outline of a yaw drive device for wind power generation equipment to which the speed reducer is applied will be described.

  With reference to FIGS. 7 to 9, the wind power generation facility 10 includes a nacelle (power generation chamber) 12 at the top of the cylindrical support 11. The nacelle 12 includes a yaw driving device 14 and a pitch driving device 16. The yaw driving device 14 is for controlling the turning angle of the entire nacelle 12 with respect to the cylindrical column 11, and the pitch driving device 16 is for controlling the pitch angle of the three windmill blades 20 attached to the nose cone 18. belongs to.

  In this embodiment, since the present invention is applied to the yaw driving device 14, the yaw driving device 14 will be described here.

  The yaw drive device 14 includes four reduction gears G1 to G4 with a motor 22 and an output pinion 24, and one internal gear 28 for turning meshing with each output pinion 24 (internal teeth for turning). The gear 28 may be an external gear). Each of the reduction gears G1 to G4 is fixed at a predetermined position of the nacelle 12 on the structure 12A side.

  As shown in FIGS. 8 and 9, the internal gear 28 for turning, in which the respective output pinions 24 of the reduction gears G1 to G4 are engaged, is fixed to the cylindrical column 11 (the main body of the wind power generation equipment). And constitutes the inner ring of the yaw bearing 30. The outer ring 30 </ b> A of the yaw bearing 30 is fixed to the structure 12 </ b> A side of the nacelle 12. In addition, the code | symbol 25 of FIG. 9 is a brake mechanism of the yaw drive device 14, and is used when fixing the nacelle 12 with respect to the cylindrical support | pillar 11. FIG.

  With this configuration, when the output pinions 24 are simultaneously rotated by the motors 22 of the reduction gears G1 to G4, the output pinions 24 mesh with the internal gears 28 while being centered on the internal gear 28 (see FIG. 8). Revolve against. As a result, the structure 12A of the nacelle 12 can be moved relative to the cylindrical support 11 (the internal gear 28 fixed to the cylindrical support 11), and the entire nacelle 12 is fixed to the cylindrical support 11. It can be swiveled around a center 36 of 28. Thereby, the nose cone 18 can be directed in a desired direction (for example, the windward direction), and the wind pressure can be efficiently received.

  Since the speed reducers G1 to G4 have the same configuration, the speed reducer G1 will be described here.

  Referring to FIG. 1, a reduction gear G1 includes a motor 22, an orthogonal gear reduction mechanism 40, first and second parallel shaft reduction mechanisms 41 and 42, and an eccentric oscillating planetary gear reduction mechanism 44 on a power transmission path. Arranged in order.

  Hereinafter, description will be made in the order on the power transmission path. The motor shaft 46 of the motor 22 also serves as the input shaft of the orthogonal gear reduction mechanism 40, and a hypoid pinion 47 is formed by straight cutting at the load side end of the motor shaft 46 of the motor 22. A brake device 49 and a cooling fan 51 are provided at the end of the motor shaft 46 on the side opposite to the load (see FIG. 9).

  The orthogonal gear reduction mechanism 40 includes the hypoid pinion 47 formed by cutting directly at the tip of the motor 22 and the hypoid gear 50 that meshes with the hypoid pinion 47, and changes the rotation direction of the motor shaft 46 to a right angle direction. . The hypoid gear 50 is fixed to the first intermediate shaft 52.

  The first intermediate shaft 52 is directly formed with a spar pinion 54 of the first parallel shaft speed reduction mechanism 41. The first parallel shaft reduction mechanism 41 includes the spar pinion 54 and a spar gear 56 that meshes with the spar pinion 54. The spur gear 56 is fixed to the second intermediate shaft 58. A spar pinion 60 of the second parallel axis reduction mechanism 42 is directly formed on the second intermediate shaft 58. The second parallel shaft reduction mechanism 42 includes the spar pinion 60 and a spar gear 64 that meshes with the spar pinion 60. The spur gear 64 is fixed to a hollow shaft 66 (an output shaft of the second parallel shaft reduction mechanism 42). The hollow shaft 66 is connected to the joint shaft 70 via a key 67 and a bolt 68. A joint coupling 70 </ b> A is press-fitted on the load side of the joint shaft 70. The load side of the joint coupling 70A is a hollow portion, and a spline 71 formed inside the hollow portion and an input shaft 72 of the planetary gear speed reduction mechanism 44 are connected. As a result, the hollow shaft 66 is connected to the input shaft 72 via the joint shaft 70 and the joint coupling 70A. On the other hand, if a large torque is input from the output shaft 84 side to the motor 22 via the reduction gear G1, a failure of the motor 22 may be caused. Therefore, the joint shaft 70 and the joint coupling 70A have such an input. In this case, a torque limiter that blocks the input to the motor 22 by sliding the press-fitting portions of the joint shaft 70 and the joint coupling 70A.

  Referring also to FIG. 2, the planetary gear speed reduction mechanism 44 includes the input shaft 72, an eccentric body 74 having two eccentric portions key-coupled to the input shaft 72, and an eccentric swing through the eccentric body 74. Two external gears 76, and an internal gear 78 in which the external gears 76 are internally meshed. The two external gears 76 have an eccentric phase shifted by exactly 180 degrees, and rotate and rotate while maintaining an eccentric state in directions away from each other. The casing 48 of the planetary gear speed reduction mechanism 44 is mainly composed of first and second casing bodies 48A and 48B and anti-load side and load side cover bodies 48C and 48D, and the nacelle 12 is connected via bolts 79. It is fixed to the structure 12A.

  The internal gear 78 includes an internal gear main body 78B integrated with the first casing body 48A, and a cylindrical external gear that is rotatably held by the internal gear main body 78B and functions as internal teeth. A pin 78A is used. The number of internal teeth of the internal gear 78 (the number of external pins 78A) is slightly larger (only 1 in this example) than the number of external teeth of the external gear 76. A plurality (12 in this example) of inner pins (planetary pins) 80 pass through the external gear 76. The inner pin 80 is integrated with an output flange (carrier) 82, and the output flange 82 is integrated with the output shaft 84 of the reduction gear G1. The configuration near the inner pin 80 will be described in detail later.

  The output shaft 84 is supported by a self-aligning roller bearing 85 incorporated in the inner periphery of the second casing body 48B and rollers 86 disposed on the inner periphery of the first casing body 48A. The roller 86 is disposed coaxially with the outer pin 78A constituting the internal teeth of the internal gear 78, and supports an output flange 82 integrated with the output shaft 84, so that one end of the output shaft 84 is rotatable. I support it.

  In this embodiment, since the internal gear 78 is fixed to the first casing body 48A, when the input shaft 72 of the planetary gear reduction mechanism 44 rotates, the external gear 76 swings via the eccentric body 74, The relative rotation (autorotation component) of the external gear 76 with respect to the internal gear 78 is extracted from the output shaft 84 via the internal pin 80 and the output flange 82. The output pinion 24 is connected to the output shaft 84 through a spline 87, and the output pinion 24 is configured to mesh with the turning internal gear 28 (FIGS. 8 and 9) already described. Yes.

  Here, the configuration near the inner pin (planetary pin) 80 will be described in detail.

  In the present embodiment, twelve inner pins 80 are provided. Each inner pin 80 is integrated with the output flange 82 by being press-fitted into the output flange (carrier) 82, and protrudes in a cantilever state from the output flange 82 toward the non-load side (vertical upper side).

  A constraining ring 88 is incorporated at the end of each inner pin 80 on the side opposite to the carrier, and the end on the side opposite to the load of the inner pin 80 is bundled. As shown in detail in FIG. 3, the restraining ring 88 is composed of a ring-shaped plate having 12 through holes 90 into which the inner pins 80 are inserted. The material of the restraining ring 88 is bearing steel.

  A contact surface 92 is formed on the outer periphery of the restraining ring 88. The contact surface 92 faces a receiving surface 100 of an anti-load side cover body (casing) 48C described later. The contact surface 92 is formed with three recesses 93 for allowing the lubricant to pass along the axial direction. As shown in FIG. 3, the concave portion 93 is formed so as not to be positioned outside the through hole 90 in the radial direction in order to keep the strength of the restraining ring 88 high. 3A is a screw hole for fixing a jig used when disassembling the restraining ring 88 once assembled from the inner pin 80.

  On the other hand, the anti-load side cover body 48C (formed with the receiving surface 100) is formed of a casting. That is, the restraint ring 88 is made of bearing steel so that high strength can be obtained even if it is thin, and the anti-load side cover body 48C is designed to prevent seizure by changing the material of the restraint ring 88. As shown in FIGS. 2 and 4, the anti-load side cover body 48 </ b> C has a through-hole through which the input shaft 72 of the planetary gear reduction mechanism 44 penetrates at the center in the radial direction, that is, an oil seal hole 97 into which the oil seal 96 is incorporated. And a bearing hole 99 into which a bearing 98 for supporting the input shaft 72 is incorporated. Further, a receiving surface 100 capable of providing a reaction force when the corresponding contact surface 92 contacts is provided at a position facing the contact surface 92 of the restraining ring 88 on the inner periphery of the anti-load side cover body 48C.

  In this embodiment, an inner roller 81 that is a sliding acceleration member for accelerating the sliding between the inner pin 80 and the external gear 76 is disposed on the outer periphery of the inner pin 80. The inner roller 81 is not disposed at the end of the inner pin 80, and the restraining ring 88 is configured to directly bundle the outer periphery of the end of the inner pin 80 where the inner roller 81 does not exist. With this configuration, while the inner roller 81 is configured to be incorporated on the outer periphery of the inner pin 80, the restraining ring 88 can be directly incorporated into the inner pin 80 (without relative rotation with the restraining ring 88). Reference numeral 102 denotes a lubricant supply port (grease), 104 denotes a bolt hole into which the bolt 79 is inserted, and 105 denotes a bolt 77 for connection to the first and second casing bodies 48A and 48B. It is a bolt hole to be inserted.

  Here, the receiving surface 100 of the anti-load side cover body 48C and the contact surface 92 of the restraining ring 88 are arranged to face each other with a minute gap δ1 when the speed reducer G1 is assembled. , Not touching. Specifically, the size of the minute gap δ1 is about 50 μm in a wind power generation facility of 1.5 to 3.0 MW (1500 to 3000 kW) class. On the other hand, when the load (or torque) L transmitted in a specific portion (for example, the output shaft 84) of the reduction gear G1 exceeds a predetermined value Lo, the receiving surface 100 and the contact surface 92 are subjected to the transmitted load. The output shaft 84 and the inner pin 80 are designed and arranged so as to be in contact with each other by elastic deformation generated by L. In other words, the restraining ring 88 receives the support reaction force from the receiving surface 100 of the anti-load side cover body 48C when the load L transmitted in the specific portion of the reduction gear G1 exceeds the predetermined value Lo.

  In the present embodiment, the predetermined value Lo is defined as follows.

  That is, as described above, in this type of wind power generation facility 10, each device including the reduction gear G1 is designed so as to ensure a useful life of at least 20 years. A load that does not break even if it is given for 20 years in the reduction gear G1 is called “fatigue equivalent load” and is one of the design indices. In addition, the limit load of transmission that does not break even if it is applied once in 20 years (during the service life) is called “extreme load”, which is also an index of design of equipment used in wind power generation equipment. It has become one. In the present embodiment, if the predetermined value Lo, which is the transmission load when the receiving surface 100 and the contact surface 92 start to contact, is expressed by a value or expression that is larger than the fatigue equivalent load Le and smaller than the extreme load Lm. For example, the range Le <Lo <Lm is set. The fatigue equivalent load Le depends on the number of speed reducers (2 to 6 units) used in the wind power generation facility. For example, in the case of 4 units as in this example, the wind power generation facility of 2 MW class is approximately 5 kNm. The extreme load is approximately 25 to 100 kNm (although the width is large).

  As is apparent from this configuration, the structure according to the present embodiment is not simply a “bearing support function” that is always provided to the receiving surface 100 of the anti-load side cover body 48C. In other words, the receiving surface 100 and the restraining ring 88 of the cover 48C on the non-load side of the casing 48 are “small gaps” at least during assembly and when the load (or torque) L transmitted on the output shaft 84 is a predetermined value Lo or less. "have.

  In this embodiment, attention is focused on the output shaft 84 as a “specific part”. However, in the present invention, a member focused on as a “specific part” is not limited to the output shaft 84. For example, the joint shaft 70, the motor shaft 46, and the like may be focused on as “specific portions”. In this case, since the speed reduction ratio differs depending on the place of interest, the predetermined value Lo differs by an amount corresponding to the speed reduction ratio (compared to when the output shaft 84 is a specific part). Incidentally, since the length of the arm of the specific part is determined when the part to be focused on is determined, the predetermined value Lo can also be regarded as a concept of torque.

  Next, the operation of the reduction gear G1 will be described.

  The rotation of the motor shaft 46 of the motor 22 is decelerated at the first stage by meshing of the hypoid pinion 47 and the hypoid gear 50 of the orthogonal gear reduction mechanism 40, and simultaneously the direction of the rotation axis is changed by 90 degrees to change the first of the first parallel axis reduction mechanism 41. It is transmitted to the intermediate shaft 52.

  The rotation of the first intermediate shaft 52 is transmitted to the second intermediate shaft 58 by the engagement of the spur pinion 54 and the spur gear 56 of the first parallel shaft speed reduction mechanism 41, and further the spur pinion 60 of the second parallel shaft speed reduction mechanism 42 and It is transmitted to a hollow shaft (output shaft of the second parallel shaft reduction mechanism 42) 66 through a spur gear 64. The rotation of the hollow shaft 66 is transmitted to the joint shaft 70 via the key 67 (and the bolt 68), and is transmitted to the input shaft 72 of the planetary gear speed reduction mechanism 44 via the spline 71.

  When the input shaft 72 of the planetary gear speed reduction mechanism 44 is rotated, the external gear 76 is oscillated and rotated via the eccentric body 74 (while inscribed in the internal gear 78), so that the external gear 76 and the internal gear 78 are This causes a phenomenon in which the meshing positions are sequentially shifted. As a result, every time the input shaft 72 of the planetary gear speed reduction mechanism 44 rotates once, the external gear 76 swings once, and is one tooth relative to the internal gear 78 (in a fixed state with the nacelle 12). The phase gradually shifts (rotation component is generated). By taking out the rotation component to the output shaft 84 side through the inner pin (planetary pin) 80 and the output flange (carrier) 82, the planetary gear reduction mechanism 44 achieves deceleration.

  The rotation of the output shaft 84 is transmitted to the output pinion 24 through the spline 87. Since the output pinion 24 is meshed with the internal gear 28 for turning, and the internal gear 28 is fixed to the cylindrical column 11, the output pinion 24 eventually rotates while being rotated. It revolves around the center 36 of the toothed gear 28 (see FIG. 8). Since the reduction gear G1 is fixed to the nacelle 12, the nacelle 12 rotates (turns) in the horizontal direction with respect to the axis 36 of the internal gear 28 on the cylindrical column 11 side.

  Here, while the load L transmitted on the output shaft 84 of the reduction gear G1 is lower than the fatigue equivalent load Le, the receiving surface 100 of the anti-load side cover body 48C and the contact surface 92 of the outer periphery of the restraining ring 88 are in contact. A minute gap δ1 is maintained between them, and the receiving surface 100 of the anti-load side cover body 48C and the contact surface 92 on the outer periphery of the restraining ring 88 are basically not in contact with each other. As a result, in most of the normal yaw drive in which the output shaft 84 is driven by the motor 22, no sliding resistance occurs and no transmission loss occurs during the power transmission.

  However, for example, when a huge torque for forcibly turning the nacelle 12 due to a gust of wind acting on the windmill blade 20 when the motor 22 is stopped is input from the output pinion 24 side of the reduction gear G1. The huge “wind load” drives the yaw drive device 14 from the reverse side and tries to rotate the output shaft 84 of the reduction gear G1. At this time, the load L transmitted on the output shaft 84 of the reduction gear G1 easily exceeds the fatigue equivalent load Le. However, in this embodiment, when the torque L transmitted in the reduction gear G1 exceeds the predetermined value Lo, the rotational center (or the inner pin 80) of the output flange (carrier) 82 is generated by the radial torque input from the output pinion 24 side. The center of revolution) O1 is displaced from the axis Oc of the casing 48, and the contact surface 92 on the outer periphery of the restraining ring 88 comes into contact with the receiving surface 100 of the anti-load side cover body 48C.

  Here, in this embodiment, the predetermined value Lo (the contact surface 92 of the restraining ring 88 contacts the receiving surface 100 of the anti-load side cover body 48C) is “fatigue equivalent load Le <predetermined value Lo <extreme value”. The range is set to “load Lm”. For this reason, before the load L transmitted on the output shaft 84 of the reduction gear G1 reaches the extreme load Lm, the restraining ring 88 always comes into contact with the anti-load side cover body 48C. A reaction force can be received from the cover body 48C. As a result, further deformation of the inner pin 80 is suppressed, the support rigidity of the inner pin 80 is increased, and damage to the inner pin 80 is prevented. Further, since the concave portion 93 for the lubricant is formed on the outer periphery (contact surface 92) of the restraining ring 88, seizure during contact and sliding can be prevented.

  In short, according to the present embodiment, the displacement (Oc → O1) of the rotational axis of the output flange 82 and the inner pin 80 due to the radial torque input from the output pinion 24 side by the wind load is actively used, By reducing the slip loss between the receiving surface 100 and the restraining ring 88 during normal operation and automatically increasing the support rigidity of the inner pin 80 at high load, each part of the reduction gear G1 (and the reduction gear) The motor 22 (connected to G1) can be protected.

  The reaction force that the restraining ring 88 receives from the anti-load side cover body 48C increases as the wind load increases (because the radial load and rotational torque generated on the output shaft 84 increase as the wind load increases). . Therefore, the supporting force of the restraining ring 88 by the anti-load side cover body 48C also increases as the wind load increases. Also, the transmission loss caused by sliding between the receiving surface 100 and the restraining ring 88 is substantially zero during normal operation, but functions as a “braking action” at extremely high loads. The effect which has a tendency is obtained. These effects are not obtained by electrical control using, for example, a sensor, and can be reliably obtained even in an environment where a power failure occurs due to a typhoon or a severe thunderstorm.

  Further, for example, in order to protect the speed reducer and the motor, the power from the output pinion 24 side is “cut off” to make the nacelle 12 free to rotate, and the nacelle 12 fluctuates in an uncontrolled state. There is nothing. This is an extremely important function from the viewpoint of protecting the entire wind power generation facility.

  5 and 6 are graphs simulating the movement (displacement) of each inner pin when a wind load is applied from the output pinion 24 side.

  FIG. 5A corresponds to a structure in which there is a restraining ring but no support from the anti-load side cover body (casing), that is, the structure of the conventional Patent Document 1. (B) is a configuration according to the present embodiment.

  This graph shows that in the plane perpendicular to the axis of each of the twelve inner pins 80 at a certain moment (in the XY plane) when the output pinion 24 portion is driven by simultaneously applying a circumferential torque and a radial load. ) In FIG. In addition, the code | symbol of A-L of a figure attaches | subjects the number to the inner pin 80 in order in the circumferential direction, and respond | corresponds with the circumferential direction position of A-L of FIG. The solid line 82F in FIG. 5 corresponds to the axial end position of the output flange 82, the broken line 76C corresponds to the axial center position of the external gear 76, and the Δ fulcrum corresponds to the support position of the restraining ring 88.

  In the structure of the conventional patent document 1 of FIG. 5A, that is, a structure in which there is a support ring but no support from the anti-load side cover body (casing) 48C, the added circumferential torque and radial direction. Because the inner pins 80 of A to L are freely displaced “as a whole” due to the load, the variation δp1 of the displacement δp is large depending on the circumferential position of each inner pin 80. In particular, the displacement amount δp at the position of the restraining ring 88 of the inner pins I to L is large. Further, the displacement amount δf in the output flange 82 has a maximum variation of δf1, and the absolute value of the displacement amount δf at the inner pin end position (the position of the solid line 82F) in the output flange 82 is also large.

  On the other hand, in the configuration of FIG. 5B according to the present embodiment, each inner pin 80 is deformed as a whole until the fatigue equivalent load Le is exceeded and reaches a predetermined value Lo. Since support from the side opposite to the load side cover body 48C is obtained, it can be confirmed that no further deformation has occurred, that is, the absolute value of the deformation amount δp of each inner pin 80 and the variation δp2 are small (δp2 <δp1). In addition, the absolute value and variation δf2 of the displacement amount δf in the output flange 82 are small (δf2 <δf1), so that the stress reducing effect can be obtained not only in the inner pins 80 but also in the output flange 82 itself. In addition, the load reduction effect with respect to the external gear 76 can be obtained, and the external gear 76 can be made thinner than the conventional one.

Furthermore, FIG. 6 shows the distribution of the tensile stress (N / mm ² ) of each of the inner pins 80 of A to L, for example, by simulation in the state where the extreme load Lm is applied. The ▲ mark in FIG. 6 is a characteristic of the structure without any restraint ring, the rhombus mark is a characteristic of the structure of Patent Document 1 (a structure without any support from the casing), and the square mark is a characteristic of the structure of the present embodiment. is there.

In the case of a structure without a restraining ring (marked with ▲), a large tensile stress is generated on the inner pin of B, and conversely, the tensile stress of the inner pins of E, F, G and K is small. It can be seen that there is a large variation in the stress (the difference is about 400 N / mm ² ).

In the case of the structure of Patent Document 1 (diamond mark), although the variation is relatively small compared to the ▲ mark, the variation is still large (the tensile stress of the inner pin 80 of E and I is 360 N / mm ² different. ) That is, since the inner pins 80 of A to L are freely displaced “as a whole”, the distribution of the tensile stress is also a distribution that is biased in one direction as a whole. That is, although the inner pin 80 on the D to F side has a small tensile stress, the entire inner pin side of H to L, particularly the I inner pin side, has a high tensile stress, and as a result, the variation is large.

On the other hand, in the case of the structure of this embodiment (square mark), the variation in the tensile stress generated in the inner pin is further reduced (the difference in tensile stress between the inner pin 80 of D and K is 150 N / mm ² ). In addition, it can be seen that the absolute value of the tensile stress generated in each inner pin is also small.

  In the above-described embodiment, the predetermined value Lo is set in the range of “fatigue equivalent load Le <predetermined value Lo <extreme load Lm”. Among these, the motor 22 that drives the reduction gear G1 is also included. More preferably, the range is set to “Le <Lo <Lr” where Lr is the load transmitted through the output shaft 84 at the rated output.

  According to this setting, the motor 22 can drive the nacelle 12 with a relatively light driving torque, and power can be transmitted without transmission loss during most yaw driving. On the other hand, the motor 22 (rated output) is against the slightly strong wind. When the nacelle 12 is turned by driving at a high output (below), each inner pin 80 causes a slight reaction force to be applied to the anti-load side cover body 48C (casing) by the restraining ring 88 coming into contact with the anti-load side cover body 48C. 48) It can be received from the side. Since the absolute value of the rotational speed of the restraining ring 88 of the reduction gear G1 of the wind power generation facility 10 is low (very slow) due to large deceleration, contact starts from a level lower than the load Lr transmitted at the rated output of the motor 22. Even if it sets in this way, it does not become a big problem from a viewpoint of transmission loss. Rather, it is excellent in that a corresponding braking effect can be expected when a sudden wind load close to the extreme load Lm is applied.

  In the above-described embodiment, the reduction gear is shown in which the motor 22, the orthogonal gear reduction mechanism 40, the first and second parallel shaft reduction mechanisms 41 and 42, and the planetary gear reduction mechanism 44 are arranged in this order on the power transmission path. However, in the present invention, the specific configuration of the reduction mechanism of the reduction gear is not particularly limited to the above configuration as long as it includes the planetary gear reduction mechanism.

  For example, as shown in FIG. 10, the present invention can be similarly applied to a reduction gear G2 including a simple planetary gear reduction mechanism. In the embodiment of FIG. 10, first to fourth simple planetary gear reduction mechanisms 111 to 114 connected to the motor 106 via a coupling 108 are provided. The first to fourth simple planetary gear speed reduction mechanisms 111 to 114 respectively include planetary gears 111A to 114A, carriers 111B to 114B, and a plurality of planetary pins 111C protruding from the carriers 111B to 114B and penetrating the planetary gears 111A to 114A. To 114C, and the “revolution component” of the planetary gears 111A to 114A is extracted from the carriers 111B to 114B via the plurality of planetary pins 111C to 114C.

  In the present embodiment, the last fourth simple planetary gear speed reduction mechanism 114 is provided with a restraining ring 114F that binds the ends of the plurality of planetary pins 114C on the side opposite to the carriers 111B to 114B. The present invention is applied between the load side cover body (casing) 114K.

  That is, the anti-load side cover body 114K of the reduction gear G2 and the restraining ring 114F have a minute gap (not shown) at the time of assembly, but the load (L) transmitted at the (output shaft 116) of the reduction gear G2. If it exceeds a predetermined value (Lo), they are arranged to face each other. Further, when the predetermined value (Lo) is defined as (Le) as the fatigue equivalent load to be transmitted by the reduction gear G2, and (Lm) as the extreme load that is the limit of transmission, the relationship of Le <Lo <Lm Set to range. This point is common to the previous embodiment. Of the bearings 118 and 120 of the output shaft 116 in FIG. 10, the bearing 120 on the anti-load side may not be required depending on the load condition.

  The present invention can also be applied to, for example, such a simple planetary gear type planetary gear reduction mechanism, and similar effects can be obtained.

  In the above embodiment, the restraining ring is brought into contact with the casing itself. However, the term “casing” in the present invention is fixed and integrated with the casing by press-fitting or bolts, and as a result, a part of the casing is obtained. This includes the concept of “additional member” constituting For example, if the receiving surface of the restraining ring is formed on an additional member integrated with such a casing (not directly on the casing itself), the degree of freedom in design can be increased. In other words, since the additional member has a high degree of freedom in material selection and curing treatment, it has hardness characteristics that prioritize durability during contact, friction characteristics that prioritize prevention of seizure, or more smoothly. It is easy to design such that the friction characteristics give priority to reducing transmission loss by supporting.

  In the above embodiment, the output shaft provided with the output pinion and the output flange (carrier) are integrally formed. This configuration is excellent in that the radial load applied to the output pinion is more directly reflected in the displacement of the inner pin (planetary pin), so that the increase in wind load and the performance of the support function are more accurately linked. . However, in the present invention, the output shaft and the carrier are not necessarily integrated. For example, the output shaft and the carrier may be connected by a spline (not integrated). In this case, the absolute value of the radial load applied to each part of the reduction gear tends to be further reduced as the transmission of the radial load is cut off at the spline portion.

  In the above-described embodiment, the present invention is applied to the speed reducer of the yaw drive device of the wind power generation facility. However, as described above, the present invention is, for example, the speed reduction of the pitch drive device of the wind power generation facility. The same applies to the device. In addition, for example, the invention can be applied to applications such as turning a deck crane, driving a drill of a shield excavator, turning a shovel for construction, etc. That is, even in these applications, the work is suddenly large from the work object side due to the influence of wind, the influence of the inertial force of heavy objects, or the collision with obstacles or underground rocks. This is because a situation in which the pinion provided on the output shaft is forcibly rotated from the load side by receiving a reaction force can be formed. In the present invention, it can be applied to such applications, and the same effects can be obtained. In addition, when the present invention is applied to uses other than wind power generation facilities, a load that does not break even if it is continuously applied to a specific part of the reduction gear during the service life of each device on which the reduction gear is mounted is `` fatigue equivalent The predetermined load Lo may be set by replacing “load Le” and the limit load of transmission that does not break even if applied once during the service life with “extreme load Lm”.

10 ... wind power generation equipment 11 ... cylindrical support 12 ... nacelle (power generation room)
DESCRIPTION OF SYMBOLS 14 ... Yaw drive device 16 ... Pitch drive device 18 ... Nose cone 20 ... Windmill blade 22 ... Motor 24 ... Output pinion 44 ... Planetary gear reduction mechanism 76 ... External gear (planetary gear)
78 ... Internal gear 80 ... Inner pin (planetary pin)
82 ... Output flange (carrier)
84 ... Output shaft 88 ... Restraining ring

Claims (6)

A reduction gear having an output pinion that meshes with a gear provided on the main body side of the wind power generation facility,
A planetary gear reduction mechanism comprising a planetary gear, a carrier, and a plurality of planetary pins protruding from the carrier and penetrating through the planetary gear, and taking out a rotation or revolution component of the planetary gear from the carrier via the plurality of planetary pins;
A constraining ring for bundling the opposite carrier-side ends of each of the plurality of planetary pins,
The casing of the speed reducer and the restraining ring have a minute gap during assembly, but are arranged to face each other so that the load L transmitted in a specific part of the speed reducer exceeds a predetermined value Lo. And
The predetermined value Lo is set in the range of Le <Lo <Lm, where Le is the fatigue equivalent load to be transmitted in the specific portion and Lm is the extreme load that is the limit of transmission. A reduction device for a wind power generation facility. In claim 1,
The predetermined value Lo is set in a range of Le <Lo <Lr, where Lr is a load transmitted at the rated output of the motor that drives the speed reducer in the specific portion. Reduction device for wind power generation equipment. In claim 1 or 2,
A recess for a lubricant is formed on the outer periphery of the restraining ring. In any one of Claims 1-3,
A sliding promotion member for promoting sliding between the planetary pin and the planetary gear is arranged on the outer periphery of the planetary pin,
The sliding promotion member is not arranged at the end of the planetary pin, and the restraining ring is configured to directly bundle the end of the planetary pin without the sliding promotion member. A reduction device for a wind power generation facility. In any one of Claims 1-4,
Deceleration stage of the wind power generation facility, characterized in that the reduction gear stage of the reduction gear device is composed of multiple stages, and the planetary gear speed reduction mechanism provided with the restraining ring is incorporated in the final stage of the reduction gear stage that is the multiple stages. apparatus. A speed reducer with an output pinion,
A planetary gear reduction mechanism comprising a planetary gear, a carrier, and a plurality of planetary pins protruding from the carrier and penetrating through the planetary gear, and taking out a rotation or revolution component of the planetary gear from the carrier via the plurality of planetary pins;
A constraining ring for bundling the opposite carrier-side ends of each of the plurality of planetary pins,
The casing of the speed reducer and the restraining ring have a minute gap during assembly, but are arranged to face each other so that the load L transmitted in a specific part of the speed reducer exceeds a predetermined value Lo. And
The predetermined value Lo is set in the range of Le <Lo <Lm, where Le is the fatigue equivalent load to be transmitted in the specific portion and Lm is the extreme load that is the limit of transmission. A speed reducer with a featured output pinion.

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