JP2012140885A - Reduction gear to be used in wind power generating facility - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a reduction gear to be used in a wind power generating facility, which achieves reasonably and safely, i.e. protecting the reduction gear against over-rotation and maintaining a braking force to a certain degree (preventing excessive wobbling of an object to be driven).SOLUTION: In reduction gears G1-G4 to be used in the wind power generating facility 10, a braking mechanism B1 (braking means) is arranged on the power transmitting path of the reduction gears G1-G4. The braking mechanism B1 has a brake shoe 54 (first component piece) installed on the side of a joint shaft 26 (first member) rotating at a higher speed in two members rotating relatively, and a brake drum 56 (second component piece) either rotating at a lower speed than the joint shaft 26 or being fixed (fixed in this case). When the rotating speed of the joint shaft 26 or brake drum 56 reaches or exceeds a predetermined rotating speed, the centrifugal force brings the brake shoe 54 and brake drum 56 in contact with each other, to reduce the rotating speed of the joint shaft 26.

Description

  The present invention relates to a reduction gear used for wind power generation equipment.

  Patent Document 1 discloses a reduction gear used for yaw control of a nacelle (power generation chamber) of a wind power generation facility or pitch control of a wind turbine blade.

  Further, since the wind power generation facility is installed in a natural environment, it sometimes receives a turbulent wind or gust.

  Reduction gears used in wind power generation facilities normally perform yaw control of the nacelle and pitch control of the wind turbine blades by driving a motor. When the huge wind load is applied to the wind turbine blades, the wind turbine blades and nacelle are driven by wind. A phenomenon occurs in which rotation is caused to flow in reverse from the output shaft side of the reduction gear. As a result, the “decelerator” functions as a “accelerator” to which an input is given from the output shaft side, causing each member and motor in the decelerator to rotate at an extremely high speed, sometimes leading to destruction.

  In Patent Document 1, when an excessive torque exceeding a set value is input from the wind turbine blade side, the slip coupling is operated to interrupt the power transmission of the drive system and prevent the drive system from being overloaded. The technology is disclosed.

US2007-0098549A1 (Claim 1, paragraph [0015])

  The slip coupling in Patent Document 1 described above interrupts transmission of power in the reduction gear when a wind load exceeding a preset threshold value is transmitted to the drive system. Therefore, as a practical matter, for example, in a situation where a strong wind load is applied, when yaw control is performed against the wind load (when the nacelle is fixed and maintained in a certain direction), it is more excessive. When a wind force is applied and power transmission in the speed reducer is interrupted, there is a problem that the drive system becomes free. That is, when the power transmission is interrupted, it is impossible to maintain the direction of the nacelle that has been performed so far, and there is a problem that the nacelle leaves the wind and vibrates uncontrollably.

  Similarly, in the event of a power failure, the drive system remains free and the nacelle direction that was previously maintained cannot be maintained, and a strong wind load is applied in that state. There was a problem that a state of shaking violently occurred.

  This situation also applies to the speed reducer for pitch control, "when the power transmission of the speed reducer is interrupted by an overload, the wind turbine blades leave the wind and the state of violent fluctuation occurs in an uncontrolled state." It is the same in that point.

  The present invention has been made to solve such a conventional problem, and is capable of protecting the speed reducer while preventing the drive target of the wind power generation facility from being excessively fluctuated. An object of the present invention is to provide a reduction gear used for a wind power generation facility.

  The present invention relates to a reduction gear including an output pinion that meshes with a gear provided on the wind power generation equipment side, and includes a braking means on a power transmission path of the reduction gear, and the braking means rotates relatively. A first member provided on the first member rotating at a higher speed of the two members, and a second member provided on the second member rotating or fixed at a lower speed than the first member And the first member and the second member are brought into contact with each other by the centrifugal force to reduce the rotation speed of the first member. By being configured, the above-described problems are solved.

  In order to achieve both prevention of excessive wobbling of the driven object and protection of the reduction gear, it is necessary to balance power transmission interruption and braking force application. Such control includes, for example, detecting the rotational speed of a specific member in the motor shaft or the speed reducer, and appropriately releasing the clutch or appropriately applying the braking force according to the detected rotational speed. realizable. However, this method requires some kind of “sensor mechanism” in order to detect the rotation speed of a specific member. However, such stormy weather conditions that cause overspeed and overload are often accompanied by heavy rains and frequent lightning strikes, causing power outages, power systems, and control systems. There is no guarantee that such a sensor mechanism will always function normally due to defects or the like. Therefore, it is not necessarily an appropriate method for “protective control of wind power generation equipment performed in rough weather”.

  Therefore, in the present invention, the trigger (the rotational speed of the motor shaft or the like) for demonstrating the protection function of the reduction gear is not detected as a “numerical value”, but “mechanical movement by centrifugal force ( Specific phenomenon) ”. In addition, the “mechanical movement itself due to centrifugal force” is positively utilized to directly reduce the rotation of the speed reducer and to apply a braking force to the drive system. Thereby, it is possible to simultaneously prevent the bearing and the motor from being damaged or burnt due to over-rotation while preventing a state in which the driven object such as the nacelle is excessively fluctuated.

  The stronger the load that is input from the output side of the speed reducer due to a gust or wind direction change, the stronger the braking force is required to prevent excessive wobbling. According to the present invention, the stronger the wind load input from the output side of the speed reducer, the stronger centrifugal force is generated in the rotating system and the stronger braking force is obtained. Further, according to the present invention, a state in which the centrifugal force is weakened and the rotation can be permitted is formed as the rotational speed of the drive system is lowered by the application of the braking force, not just the strong braking force. . For this reason, a state where the wind torque is completely received in a so-called stop state (in a complete braking state) can be avoided, and each part of the reduction gear can be prevented from being damaged by an overload.

  According to the present invention, it is an object of the present invention to provide a speed reducer used in a wind power generation facility that can protect the speed reducer while preventing a state in which an object to be driven of the wind power generation equipment is excessively fluctuated. Yes.

Whole sectional drawing of the reduction gear device used for the wind power generation equipment which concerns on an example of embodiment of this invention 1 is an enlarged cross-sectional view of the main part of FIG. The top view which shows the structure of the braking mechanism of the reduction gear of FIG. The front view which shows the whole structure of the wind power generation facility to which the said reduction gear device is applied Overall schematic perspective view of a yaw drive device of a wind power generation facility to which the speed reducer is applied Sectional drawing which shows a mode that the said reduction gear is used for a yaw drive device 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. 7 is an enlarged cross-sectional view of the main part of FIG.

  Hereinafter, a reduction gear used in a wind power generation facility according to an example of an embodiment of the present invention will be described in detail.

  First, an outline of a wind power generation facility to which the speed reducer is applied will be described.

  With reference to FIGS. 4 and 5, the wind power generation facility 10 includes a nacelle (power generation chamber) 12 at the uppermost portion 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 a motor 22, four reduction gears G <b> 1 to G <b> 4 with an output pinion 24, and one turning internal gear 28 that meshes with each output pinion 24. Each reduction gear G1-G4 is being fixed to the predetermined position by the side of the main body of nacelle 12, respectively. Referring also to FIG. 6, the turning internal gear 28 with which the output pinions 24 of the reduction gears G <b> 1 to G <b> 4 are meshed is fixed to the cylindrical column 11, and the inner ring of the yaw bearing 30 is It is composed. The outer ring 30 </ b> A of the yaw bearing 30 is fixed to the main body 12 </ b> A side of the nacelle 12. In addition, the code | symbol 25 of FIG. This brake mechanism is provided for intentionally braking the yaw drive device, but may be omitted.

  With this configuration, when the output pinions 24 are simultaneously rotated by the motors 22 of the reduction gears G1 to G4, the output pinion 24 is engaged with the internal gear for rotation 28 and the center 36 of the internal gear for rotation 28 (see FIG. 5)). As a result, the entire nacelle 12 can be turned around the center 36 of the turning internal gear 28 fixed to the cylindrical column 11. 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 reduction gears G1 to G4 have the same configuration, the reduction gear G1 will be described here with reference to FIG.

  The reduction gear G1 includes a motor 22, a two-stage swinging inscribed first-stage and rear-stage reduction mechanisms G11 and G12. The motor 22 is detachably provided on the joint case 23 on the side opposite to the load of the speed reducer G1, and the braking mechanism (braking means) B1 according to the present invention is provided in the sealed space P1 formed by the motor 22 being attached. It has been incorporated. The structure of the braking mechanism B1 and its periphery will be described in detail later.

  Hereinafter, the power transmission path will be described in order.

  A joint shaft 26 is assembled to the motor shaft 25 of the motor 22 via a key 27 so as to be integrally rotatable. The joint shaft 26 is integrated with the input shaft 30 of the first-stage reduction mechanism G11 of the reduction gear G1. The first-stage reduction mechanism G11 includes the input shaft 30, two eccentric bodies 34 provided on the input shaft 30, two external gears 36 that swing eccentrically via the eccentric body 34, and the external gear 36. Is provided with an internal gear 38 that is inscribed in mesh. The two external gears 36 have an eccentric phase that is exactly 180 degrees away from each other, and rotate and rotate while maintaining an eccentric state in directions away from each other. In this embodiment, the internal teeth of the internal gear 38 are constituted by pins and rollers, and the internal gear main body is integrated with the high-speed side casing body 39. The number of internal teeth (the number of pins and rollers) of the internal gear 38 is slightly larger (for example, by 1) than the number of external teeth of the external gear 36. An inner pin 40 is loosely fitted to the external gear 36. The inner pin 40 is integrated with the first stage output flange 42, and the first stage output flange 42 is integrated with the first stage output shaft 44.

  In this embodiment, since the internal gear 38 is integrated with the high-speed casing body 39, when the input shaft 30 of the first stage reduction mechanism G11 rotates, the external gear 36 swings via the eccentric body 34, The relative rotation (autorotation) of the external gear 36 with respect to the internal gear 38 is extracted from the first stage output shaft 44 (as the output of the first stage reduction mechanism G11) via the inner pin 40 and the first stage output flange 42.

  The first-stage output shaft 44 is a hollow shaft, and the input shaft 130 of the rear-stage reduction mechanism G12 is press-fitted and connected to the hollow portion 44A together with an adhesive. The rear stage reduction mechanism G12 is slightly different in detail, but the basic structure of the power transmission system is substantially the same as that of the first stage reduction mechanism G11. Therefore, the same or corresponding parts are only given the same reference numerals in the last two digits in FIG. 1, and the detailed description of the rear-stage reduction mechanism G12 is omitted. The output shaft 144 of the post-stage speed reduction mechanism G12 is fixed and connected to the output pinion 24 through a spline 146, and the output pinion 24 has already been described for the turning internal gear 28 (FIGS. 5 and 6). It is set as the structure meshed with.

  Next, a configuration in the vicinity of the braking mechanism (braking means) B1 incorporated in the reduction gear will be described in detail with reference to FIGS.

  As described above, the motor 22 is detachably provided on the joint case 23 of the reduction gear G1. The front cover 22A of the motor 22 is connected to the flange portion 23A of the joint case 23 via a bolt (only the center line is shown in FIG. 1) in close contact with a seal member such as an O-ring (not shown). . The bearing 50 that rotatably supports the joint shaft 26 fitted to the motor shaft 25 on the joint case 23 is a sealed bearing having a sealing function. For this reason, the motor 22 is attached to the joint case 23, so that the sealed space P <b> 1 can be formed by the front cover 22 </ b> A of the motor 22 and the joint case 23.

  The braking mechanism B1 is accommodated in the sealed space P1. Cooling oil is enclosed in the sealed space P1. That is, the braking mechanism B1 of this embodiment is a “wet” braking mechanism that operates in the cooling oil. An oil seal 52 with a so-called swing-off mechanism is incorporated adjacent to the bearing 50 having the sealing function. The oil seal 52 includes a rubber first seal body 52C and a second seal opposed to the first seal body 52C in a space formed by a metal base body 52A and a metal cover body 52B. The seal body 52D is incorporated. A lip surface 52C1 is formed on the first seal body 52C, and a narrow maze (labyrinth) is formed between the first seal body 52C and the second seal body 52D. As a result, wear powder or the like generated on the side of the braking mechanism B1 described below is prevented from entering the first-stage reduction mechanism G11.

  The braking mechanism according to the present invention includes a first member provided on the first member side and a second member provided on the second member side.

  Here, the first member is a member that rotates at a higher speed among the two members that rotate relatively. The second member is a member rotating at a lower rotational speed than the first member. The concept of “rotation at a slower rotation speed” includes the concept of “rotation at zero speed”, that is, the “fixed state”. In the present embodiment, the joint shaft 26 fitted to the motor shaft 25 and rotating at the same speed as the input shaft 30 of the reduction gear G1 corresponds to the first member. Further, the joint case 23 in the fixed state corresponds to the second member.

  Details will be described below.

  The joint shaft 26 as the first member is provided with three brake shoes 54 corresponding to the first member. The brake shoe 54 includes a first friction portion 54A having an arc-shaped cross section perpendicular to the radial direction. A brake drum 56 corresponding to the second member is fixed to the joint case 23 as the second member via a drum fixing bolt 57. The brake drum 56 is formed of a material harder than the joint case 23, and includes a second friction portion 56A that is opposed to the first friction portion 54A of the brake shoe 54 with substantially the same inner diameter.

  In this braking mechanism B1, when the joint shaft (first member) 26 reaches or exceeds a predetermined rotational speed, the brake shoe (first member) 54 and the brake drum (second member) 56 come into contact with each other by centrifugal force. The rotational speed of the joint shaft 26 is reduced. And in order to exhibit this braking function, in this embodiment, the guide mechanism 58 and the spring mechanism 60 are provided.

  The guide mechanism 58 will be described. The guide mechanism 58 fixes the brake shoe 54 in the circumferential direction with respect to the joint shaft 26 and enables displacement in the radial direction. In this embodiment, a brake boss 64 is fitted to the outer periphery of the joint shaft 26 via a spline 62. The brake boss 64 is positioned in the axial direction with respect to the joint shaft 26 via a retaining ring 59. The brake boss 64 has three guide portions 64A protruding and extending in the radial direction from the axis O1 of the joint shaft 26. Each guide portion 64A includes a pair of guide surfaces 64A1 perpendicular to the axis O1 of the joint shaft 26 (perpendicular to the paper surface of FIG. 3). On the other hand, the brake shoe 54 is formed with a guided surface 54B slidable in the radial direction along the guide surface 64A1 on the radially inner side. The guided surface 54B has a U-shaped cross section perpendicular to the axis, and covers the pair of guide surfaces 64A1 so as to be slidable from the outside in the radial direction. With this configuration, the guide mechanism 58 fixes the brake shoe (first member) 54 with respect to the joint shaft (first member) 26 in the circumferential direction and can be displaced in the radial direction.

  On the other hand, the spring mechanism 60 applies a radially inward biasing force to the brake shoe 54. In this embodiment, the spring mechanism 60 includes a coil spring 66 that connects the adjacent brake shoes 54, 54 to each other. ing. Each coil spring 66 is assembled in the assembly hole 54 </ b> C of each brake shoe 54 in a state of being pulled beyond its free length, and the radial component of the tensile force of each coil spring 66 is relative to the brake shoe 54. A biasing force inward in the radial direction is given.

  The braking mechanism B1 has such a basic configuration, and in a state where the coil spring 66 is incorporated, a predetermined gap δ1 is provided between the brake shoe (first member) 54 and the brake drum (second member) 56. (See FIG. 2) is secured. Due to the presence of this gap δ1, when the rotational speed of the joint shaft (first member) 26 is low, the brake shoe 54 maintains a state of not contacting the brake drum 56. On the other hand, when the rotational speed of the joint shaft 26 exceeds a predetermined rotational speed, the centrifugal force generated in the brake shoe 54 overcomes the urging force of the coil spring 66, and the brake shoe 54 moves (slids) radially outward. As a result, the brake shoe 54 and the brake drum 56 are brought into frictional contact with each other to reduce the rotational speed of the joint shaft 26. The gap δ1 is set to “size” so that this action can be performed satisfactorily.

  That is, as can be understood from this configuration, the phrase “when the rotation speed of the first member exceeds a predetermined rotation speed” according to the present invention is “the rotation speed of the first member is It is used for the purpose of “when a mechanical predetermined movement (specific phenomenon)” occurs due to centrifugal force. In other words, the “predetermined rotational speed” is determined by setting the mass of the brake shoe 54, the gap δ1, etc. (the value itself is uncertainly analog), and is a specific numerical value. (Rpm) is not digitally determined. Qualitatively, when the rotation speed of the joint shaft 26 as the first member becomes a rotation speed that clearly exceeds the rotation speed when the motor 22 rotates at the rated rotation speed, the gap δ1 is filled. A setting that starts braking is preferable.

  Further, even if the rotational speed exceeds the rated rotational speed of the motor 22, if the rotational speed is such that the motor 22 or the like is hardly damaged, it is preferable that the brake shoe 54 and the brake drum 56 are not brought into contact with each other. It is preferable from a viewpoint of reducing. In other words, it is preferable to set the brake shoe 54 and the brake drum 56 in contact with each other at a rotational speed that is higher than the rated rotational speed of the motor 22 and at which there is a possibility of damage to some extent. Specifically, the brake shoe 54 and the brake drum 56 should be set to contact each other at 110% or more, preferably about 130 to 150% of the rated rotation speed (synchronous rotation speed) of the motor.

  For example, in the case of a four-pole motor, the rated rotational speed is about 1500 to 1800 rpm, so it is preferable to set it to 1650 rpm or more, preferably about 1950 to 2700 rpm. In the case of a 6-pole motor, since the synchronous rotation speed is about 1000 to 1200 rpm, it should be set to 1100 rpm or more, preferably about 1300 to 1800 rpm.

  The second member may be a fixed member (as in this embodiment) or a rotating member as long as the rotational speed is slower than that of the first member. When friction braking is applied between the first and second members by the braking mechanism when the second member is a rotating member, the first member (which has a high rotational speed and a small torque) is more smoothly operated. A phenomenon occurs in which the rotational speed of the two members approaches (the rotational speed of the first member decreases first). Then, since the rotation speed of the second member cannot destroy the “proportional relationship with the first member”, the rotation speed of the second member must be decreased to a rotation speed corresponding to the decreased rotation speed of the first member. As a result, both the rotation speeds of the first and second members change so as to approach zero (while maintaining a proportional relationship), and the rotation speed of the first member (and the second member). Can be reduced. For example, in a reduction gear that employs a swinging intermeshing planetary gear mechanism or a simple planetary gear mechanism, it rotates at the same (slow) rotational speed as the output shaft adjacent to the input shaft. Since there are many carriers that exist, the configuration in which the input shaft is the first member and the carrier is the second member is effective.

  Next, the operation of the speed reducer used in this wind power generation facility will be described mainly focusing on the operation of the braking mechanism.

  When the motor shaft 25 of the motor 22 rotates, the joint shaft 26 fitted to the motor shaft 25 rotates. When the joint shaft 26 rotates, the brake shoe 54 of the braking mechanism B1 receives a centrifugal force, overcomes the urging force of the coil spring 66, and slides radially outward along the guide surface 64A1 of the brake boss 64.

  This sliding amount is smaller than the gap δ1 between the brake shoe (first member) 54 and the brake drum (second member) 56 when a driving force is provided from the normal motor 22, and therefore braking is performed. The mechanism B1 does not give any resistance to the rotating system. However, when a large torque is applied by wind power from the windmill blade 20 side and the reduction gear G1 is forcibly “speed-up driven” from the output side, each member of the reduction gear G1 (˜G4) and the motor 22 are It is rotated at a very high rotation speed, causing danger such as breakage.

  In this embodiment, when the rotational speed of the joint shaft 26 exceeds a predetermined rotational speed, the brake shoe 54 slides greatly along the guide surface 64A1 of the brake boss 64 due to the centrifugal force applied to the brake shoe 54, The first friction part 54A of the brake shoe 54 and the second friction part 56A of the brake drum 56 come into frictional contact.

  Since the contact pressure of the first and second friction portions 54A and 56A increases as the rotational speed of the joint shaft 26 increases, the contact pressure between the first friction member 54A and the second friction portion 54A increases. A larger braking force can be obtained by the first and second friction portions 54A and 56A. Since this action is a mechanical action (using centrifugal force) in the braking mechanism B1 housed in the sealed sealed space P1, no power source, sensor, control circuit, or the like is required. In other words, a highly reliable braking function can be obtained even under bad weather conditions such as storms, heavy rains, or frequent lightning strikes.

  Further, unlike the control in which the power transmission system of the reduction gear is released by slip coupling or clutch release, it is possible to prevent the windmill blade 20 and the nacelle 12 from being vibrated violently (in an uncontrolled state) by the wind. That is, during the yaw control for turning the nacelle 12 or when the brake 25 shown in FIG. 6 is released and the nacelle 12 is in a free state with respect to the cylindrical column 11, the output pinion is caused by a gust wind or a sudden change in the wind direction. Even when an excessive torque is input from the 24th side, braking is performed by the braking mechanism B1, so that each part can be prevented from being damaged due to excessive rotation and the nacelle 12 itself can be prevented from being excessively fluctuated. .

  The kinetic energy of the rotating system of the reduction gear G1 whose rotational speed has been reduced by the function of the braking mechanism B1 is released as large heat energy from the first and second friction portions 54A and 56A. Such a braking mechanism is “wet”, has a large heat capacity, and can absorb the released heat energy by abundant lubricant having a cooling function. In particular, when the wind is so strong that excessive rotation of the rotation system of the reduction gear becomes a problem, the cooling effect of the casing by the wind can be expected.

  Further, in this embodiment, the motor 22 is removable, and the sealed space P1 that houses the braking mechanism B1 is formed by the motor 22 being attached, so there is no waste in the casing configuration. , Weight reduction and downsizing can be realized.

  Furthermore, in this embodiment, since the brake drum 56 is formed of a material harder than the joint case (casing) 23, the brake drum 56 is durable, and even if the brake shoe 54 and the brake drum 56 are consumed, Since the brake drum 56 can be replaced simply by removing the motor 22 and loosening the drum fixing bolt 57, maintenance is also easy.

  Further, even when the brake shoe 54 and the brake drum 56 are replaced, for example, the “set” in which the coil spring 66 is attached to the brake shoe 54 and the brake boss 64 is removed, and the retaining ring 59 is removed and the spline 26 is splined. Since it only needs to engage through 62, it can be easily replaced on site.

  Further, even if the first and second friction portions 54A and 56A slide due to the function of the braking mechanism B1 and wear powder or the like is generated, a swing-off mechanism is provided adjacent to the seal bearing 50 in this embodiment. Therefore, the wear powder is effectively prevented from entering the speed reduction mechanism.

  FIG. 7 shows a modification of the above embodiment. FIG. 8 is an enlarged cross-sectional view of the main part of FIG. In this modification, the cost is reduced by omitting the arrangement of the oil seal with the swing-off mechanism as compared with the above embodiment. The main difference is that the oil supply port 70 and the oil discharge port 72 are arranged so that the cooling oil can be easily replaced. Since the other configuration is the same as that of the previous embodiment, the same reference numerals are given to the same or similar parts as those of the previous embodiment in FIGS.

  In the above-described embodiment, the sealed space P1 in which the braking mechanism (braking means) B1 is accommodated is formed for the first time when the motor 22 is attached. In the present invention, however, the braking mechanism is accommodated. There is no particular limitation on the configuration of the sealed space to be formed. In the first place, the braking means does not need to be wet, and in this case, the sealed space itself is not required. Further, the first member and the second member do not necessarily have to be attached at positions where they can be replaced when the motor is removed.

  Moreover, in the said embodiment, although the 2nd member was detachably fixed to the casing (in the fixed state which is a 2nd member), in this invention, including the structure of a guide mechanism or a spring mechanism, it is the brake mechanism. A specific configuration is not particularly limited. In short, the first member and the second member may be brought into contact with each other by centrifugal force, and the rotational speed of the first member may be reduced.

  In the above embodiment, the speed reduction mechanism constituting the speed reduction device is an eccentric oscillating type speed reduction mechanism, but the speed reduction mechanism applied to the speed reduction device of the present invention is not particularly limited, for example, a simple planetary planet It may be a mold speed reduction mechanism or a worm speed reduction mechanism.

  In the above-described embodiment, the braking mechanism B1 is arranged on the motor side with respect to the speed reduction mechanism. Such a configuration causes a large change in friction loss with respect to a speed change, and a braking torque is small. Although it is preferable because B1 can be reduced in size, in the present invention, the arrangement position of the braking mechanism is not limited, and it may be arranged in any part of the power transmission system from the motor to the output pinion.

  In the above embodiment, the cooling oil is sealed in the sealed space P1, but the sealed space P1 is not limited to the oil and may be a liquid that can be cooled without impairing the braking performance of the braking mechanism B1. Any liquid may be used.

DESCRIPTION OF SYMBOLS 10 ... Wind power generation equipment 12 ... Nacelle 14 ... Yaw drive device 22 ... Motor 23 ... Joint case (2nd member)
24 ... Output pinion 26 ... Joint shaft (first member)
28 ... Turning internal gear 54 ... Brake shoe 56 ... Brake drum 58 ... Guide mechanism 60 ... Spring mechanism 66 ... Coil spring G1-G4 ... Deceleration device B1 ... Braking mechanism (braking means)

Claims (8)

A reduction gear having an output pinion that meshes with a gear provided on the wind power generation equipment side,
Braking means is provided on the power transmission path of the speed reducer,
The braking means is
A first member provided on the first member rotating at a higher speed among the two members rotating relatively, and a second member rotating or fixed at a lower speed than the first member. And when the rotation speed of the first member is equal to or higher than a predetermined rotation speed, the first member and the second member come into contact with each other by centrifugal force, and the rotation of the first member A reduction gear used for wind power generation equipment, characterized in that the speed is reduced. In claim 1,
The speed reducer comprises a removable motor on its anti-load side;
At least one of the first member and the second member is attached at a position where the motor can be replaced when the motor is removed. A reduction gear used for a wind power generation facility. In claim 1 or 2,
The speed reducing device used in wind power generation equipment, wherein the braking means is wet type braking means that operates in a sealed space filled with a coolant. In claim 3,
The speed reducer comprises a removable motor on its anti-load side;
The speed reduction device used for wind power generation equipment, wherein the sealed space is formed by mounting the motor. In any one of Claims 1-4,
The braking mechanism further comprises:
A guide mechanism for fixing the first member in the circumferential direction with respect to the first member and displaceable in the radial direction;
And a spring mechanism for applying a radially inward biasing force to the first member. In claim 5,
A plurality of the first members are provided in the circumferential direction,
The said spring mechanism is comprised by the coil spring which connects adjacent 1st members mutually. The speed reducer used for the wind power generation facility characterized by the above-mentioned. In any one of Claims 1-6,
The second member is a casing of the speed reducer;
The speed reducer used for wind power generation equipment, wherein the second member is detachably fixed to the casing. In claim 7,
The said 2nd member is formed with the raw material harder than the said casing. The speed reducer used for the wind power generation facility characterized by the above-mentioned.

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