JP4020574B2 - Free mechanism of reduction gear with motor - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
    The present invention relates to a free mechanism for a speed reducer with a motor that can release the connection between the motor and the speed reducer to temporarily make the speed reducer side free.
[0002]
[Prior art]
    A reduction gear with a motor in which a reduction gear and a motor are integrated is widely used. For example, in Japanese Patent Publication No. 64-5176, rotation by a hydraulic motor is reduced via a planetary differential gear reduction gear, A speed reducer that extracts the output is disclosed. In Japanese Patent Publication No. 64-5176, for example, a crawler vehicle is driven by the extracted output.
[0003]
[Problems to be solved by the invention]
    In such a conventional speed reducer with a motor, if the motor fails for some reason, the output part of the speed reducer cannot be moved because the motor and the speed reducer are integrally connected. End up. In particular, when such a motor-equipped speed reducer is used in a vehicle traveling device or the like, even if the vehicle is connected to a towing vehicle and towed to a predetermined repair station and a failure is repaired at that location, the motor Since the connection between the motor and the speed reducer cannot be disconnected, there is a problem in that extremely large power is required to pull the vehicle, and the vehicle cannot be moved substantially.
[0004]
OBJECT OF THE INVENTION
    In view of the above-described problems, the present invention easily releases the connection between the motor and the speed reducer when the speed reducer with the motor needs to be operated freely for some reason. An object of the present invention is to provide a motor-equipped speed reducer that can easily operate the motor-equipped speed reducer by applying a small force to the output side portion of the speed reducer.
[0005]
[Means for Solving the Problems]
    The purpose is to transmit the rotational driving force from the output shaft of the drive motor to the speed reducer via the first external gear and the second external gear meshing with the first external gear, and to reduce the speed in the speed reducer. Reducer with motorBecauseAnd installed between the output shaft and the first external gear, both on the output shaft and the first external gear.By splineLinked position and outputBy spline on the shaftConcatenatedWhile,1st external gearA connecting member that can move in the axial direction between the free position from which the connection is released, and a movement that moves the connecting member from the free position to the connected position by constantly applying a biasing force to the connecting member. And a pressing means that can apply a pressing force larger than the urging force of the moving means to the connecting member and can move the connecting member from the connecting position to the free position against the moving means.In the free mechanism of the reduction gear with a motor, the first external gear is formed with first spline teeth and second spline teeth, and the first external gear between the first and second spline teeth is scraped off the spline teeth. While forming a diameter part, while forming the 1st spline tooth and the 2nd spline tooth in the connecting member, forming the diameter part by which the spline tooth was scraped off in the connecting member between the first and second spline teeth, And when the said connection member is located in a connection position, the 1st, 2nd spline tooth | gear of a said 1st external gear, a diameter part, and the 1st, 2nd spline tooth | gear of a connection member, and a diameter part of a connection member When the first spline teeth and the second spline teeth mesh with the first spline teeth and the second spline teeth of the first external gear, respectively, while the connecting member moves to the free position Is diameter and the second spline teeth of the coupling member, arranged so as to be located respectively opposite positions on the first spline teeth and the diameter of the first external gearCan be achieved.
[0006]
  In the present invention, the connecting member installed between the output shaft and the first external gear is connected to both the output shaft and the first external gear, and either the output shaft or the first external gear. It is possible to move in the axial direction between the free position connected to one side and the connection released from the other, so that the output shaft and the first external gear are integrated with each other according to the movement of the connecting member. It is possible to selectively switch between a rotating state and a free state in which relative rotation is possible.
[0007]
  Therefore, when it is necessary to release the connection between the drive motor and the reduction gear for some reason and to make the reduction gear with a motor free, the connecting member moved to the connection position by the biasing force of the moving means is set to the free position. Move up like thisNagiriThe changing operation can be performed quickly.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
    Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.
    1 and 2, reference numeral 11 denotes a swash plate type hydraulic motor as a drive motor attached to a fixed frame of a winch installed in, for example, a crane truck. The hydraulic motor 11 has a storage chamber 12 formed therein. And a side plate 14 that is fixed to the other end of the case body 13 and closes the other end opening of the storage chamber 12 to form a sealed space. The case body 13 and the side plate 14 are casings as a whole. Configure 15
[0009]
  Reference numeral 17 denotes a rotating shaft whose other side portion is inserted into the storage chamber 12, and this rotating shaft 17 is rotatably supported by the side plate 14 and the case body 13 via a bearing 16, and is provided on the outer periphery of one end portion thereof. Spline external teeth 17a are formed. Reference numeral 18 denotes a connecting sleeve having a cylindrical shape coaxial with the rotating shaft 17, and spline inner teeth 18 a are formed on the inner periphery of the connecting sleeve 18 over the entire length. The other end of the connecting sleeve 18 is fitted to one end of the rotating shaft 17 with the spline and the external teeth 18a, 17a meshing with each other. As a result, the connecting sleeve 18 and the rotating shaft 17 Are connected so as to rotate together. The rotary shaft 17 and the connecting sleeve 18 described above constitute an output shaft 19 of the hydraulic motor 11 as a whole.
[0010]
  Reference numeral 21 denotes a cylindrical cylinder block stored in the storage chamber 12, and the rotary shaft 17 is inserted into the cylinder block 21 and connected by a spline. As a result, the cylinder block 21 is connected to the rotary shaft. Can rotate integrally with 17. A plurality of cylinder holes 22 are formed on one end surface of the cylinder block 21 and extend in the axial direction. Plungers 23 are slidably inserted into the cylinder holes 22, respectively. The shoes 25 are connected to each other through the ball joint 24.
[0011]
  Reference numeral 27 denotes a timing plate interposed between the cylinder block 21 and the side plate 14, and two arc-shaped holes 28 separated in the circumferential direction are formed in the timing plate 27. The holes 22 are connected one after another as the cylinder block 21 rotates. These arc-shaped holes 28 are connected to a hydraulic pressure source and a tank via a supply / exhaust passage and a switching valve (not shown), and when the switching valve is switched, one of them becomes a supply side and the rest becomes a discharge side.
[0012]
  31 is a substantially ring-shaped swash plate stored in the storage chamber 12, and the output shaft 19 passes through the swash plate 31. The swash plate 31 has an inclined surface 32 that is inclined with respect to a plane perpendicular to the rotation axis of the output shaft 19 at the other end facing the cylinder block 21, and the shoe 25 is in sliding contact with the inclined surface 32. ing.
[0013]
  33 is a substantially ring-shaped retainer plate that is engaged with all the shoes 25, and 34 is a thrust contact that is spherically contacted with the inner periphery of the retainer plate 33 and that is fitted to the outside of the rotary shaft 17 and connected by spline coupling. A ball 35 is a spring that applies a biasing force directed to one side via the transmission rod 36 to the thrust ball 34. The casing 15, the output shaft 19, the cylinder block 21, the plunger 23, the shoe 25, the timing plate 27, the swash plate 31, and the thrust ball 34 described above constitute the hydraulic motor 11 as a whole.
[0014]
  Reference numeral 38 denotes a negative brake that applies a braking force to the hydraulic motor 11 when the hydraulic motor 11 is stopped. The negative brake 38 includes a plurality of inner friction plates 39 splined to the outer periphery of the cylinder block 21 and a casing 15. A plurality of outer friction plates 40 splined to the inner periphery of the storage chamber 12. When the supply of high-pressure fluid to the brake passage 41 is stopped, the negative brake 38 is pressed against the inner friction plate 39 by the piston 43 biased by the disc spring 42, and the cylinder block When a braking force is applied to 21 and high pressure fluid is supplied to the brake passage 41 and the piston 43 moves to the other side while compressing the disc spring 42, the outer friction plate 40 moves away from the inner friction plate 39 and the cylinder block. Allow 21 rotations. The inner and outer friction plates 39, 40, the disc spring 42, and the piston 43 described above constitute the negative brake 38 as a whole.
[0015]
  47 is an eccentric differential speed reducer attached to one end of the hydraulic motor 11, and this speed reducer 47 has a substantially cylindrical hub at the output end, for example, the hoisting drum of the winch. 48 is provided integrally. Between the pair of flanges 48a of the hoisting drum 48 is a body portion 48b around which a rope is wound, and a spiral guide groove 48c is formed on the outer periphery of the body portion 48b to contribute to smooth winding of the rope. Has been.
[0016]
  In the inner periphery of the winding drum (hub) 48, a large number of cylindrical internal teeth pins 49 are inserted in the center in the axial direction, and these internal teeth pins 49 extend in the axial direction and They are arranged equidistantly in the direction. In the hoist drum 48, two disk-shaped pinions 50 are accommodated, and the outer periphery of each pinion 50 meshes with the inner tooth pins 49 and has a slightly smaller number of teeth than the number of the inner tooth pins 49. External teeth 51 are formed. Each pinion 50 is formed with a plurality of penetrating loose-fitting holes 52 and a plurality of penetrating shaft holes 53, respectively.
[0017]
  Reference numeral 55 denotes a plurality of columnar columns integrally formed with the case main body 13. The column 55 protrudes from one end surface of the case main body 13 toward one side, and enters the loose fitting hole 52. Each is loosely fitted. A disk-shaped end plate 56 and a storage block 57 are attached to one end of these column bodies 55 by bolts 58 so as to be detachable. The column body 55 and the end plate 56 described above constitute a carrier 59 of the speed reducer 47 as a whole.
[0018]
  Reference numeral 61 denotes a plurality of crankshafts parallel to the output shaft 19. Both ends of the crankshaft 61 are rotatably supported by the case body 13 and the end plate 56 via bearings 62, respectively. Each crankshaft 61 has two eccentric parts 63 which are eccentric in the opposite direction from the central axis of the crankshaft 61 at the center part in the axial direction, and these eccentric parts 63 are needle roller bearings in the shaft hole 53 of the pinion 50. Each is inserted with 64 in between.
[0019]
  67 is a first external gear installed on one side of the output shaft 19 so as to maintain a coaxial relationship therewith, and one end portion of the first external gear 67 is in a state in which a needle roller bearing 68 is interposed in the storage block 57. On the other hand, external teeth 69 are formed on the outer periphery of the other end. Reference numeral 70 denotes a second external gear fixed to one end of each crankshaft 61. These second external gears 70 surround the first external gear 67 from the outside. Outer teeth 71 that mesh with the outer teeth 69 of the first external gear 67 are formed on the outer periphery of the second external gear 70.
[0020]
  74 is a connecting member installed between the output shaft 19 and the first external gear 67. The connecting member 74 is coaxial with the output shaft 19 and the first external gear 67 and can move in the axial direction, and has one end thereof. On the outer peripheryAs second spline teethSpline external teeth 74a are formed. On the other side of this spline external tooth 74aAs the diameterA small-diameter portion 74b is formed, and the aforementioned spline external teeth are cut off in the small-diameter portion 74b. The outer periphery of the connecting member 74 on the other side of the small diameter portion 74b is similar to the spline external teeth 74a.As the first spline teethSpline external teeth 74c are formed.
[0021]
  The other end of the connecting member 74 is fitted to one end of the connecting sleeve 18 with the splines outside and the inner teeth 74c, 18a engaged with each other. As a result, the connecting member 74 and the connecting sleeve 18, That is, the output shaft 19 is connected to the output shaft 19 so as to be integrally rotatable and movable in the axial direction. Here, the connecting member 74 is movable in the axial direction as described above. However, even if the connecting member 74 moves to one end in the axial direction or the other end in the axial direction, it does not come out of the connecting sleeve 18. For this reason, the connecting member 74 and the output shaft 19 are always connected.
[0022]
  76 is a through hole formed in the first external gear 67 extending in the axial direction. The through hole 76 is formed on the inner periphery of one end and the inner periphery of the other end, respectively.As second and first spline teethSpline inner teeth 76a and 76b were formed, and the central portion located between the spline inner teeth 76a and 76b was scraped off.As the diameterIt is a large diameter portion 76c. One end portion of the connecting member 74 is inserted into the through hole 76 so as to be movable in the axial direction. Reference numerals 77 and 78 denote through-holes respectively formed on the central axes of the pinion 50 and the end plate 56, and the above-described connecting sleeve 18 and connecting member 74 are loosely fitted in these through-holes 77 and 78.
[0023]
  When the connecting member 74 moves to one axial limit, the spline external teeth 74a of the connecting member 74 mesh with the spline internal teeth 76a of the first external gear 67, and the spline external teeth 74c mesh with the spline internal teeth 76b. Therefore, the connecting member 74 and the first external gear 67 are connected to each other so as to be able to rotate integrally and move in the axial direction. Here, since the connecting member 74 is always connected to the output shaft 19 as described above, this one axial limit shown in FIG. 2 is connected to both the output shaft 19 and the first external gear 67. It becomes the connection position R. When the connecting member 74 is located at the connecting position R, the rotational driving force from the output shaft 19 of the hydraulic motor 11 is transmitted to the speed reducer 47 via the first external gear 67 and the second external gear 70. The speed reducer 47 decelerates.
[0024]
  On the other hand, when the connecting member 74 moves to the other end in the axial direction, the small diameter portion 74b faces the spline inner teeth 76b, and the spline outer teeth 74a disengages from the spline inner teeth 76a and faces the large diameter portion 76c. The spline external teeth 74c come out from the first external gear 67 to the other side. As a result, the connection between the connecting member 74 and the first external gear 67 is released. Here, since the connecting member 74 is always connected to the output shaft 19 as described above, the other end in the axial direction shown in FIG. 3 is connected to the output shaft 19, but the first external gear 67 and The free position F is released. Since the connecting member 74 can move in the axial direction between the connecting position R and the free position F, the output shaft 19 and the first external gear 67 are connected in accordance with the movement of the connecting member 74. Thus, it is possible to selectively switch between a state of rotating integrally and a free state of relative rotation.
[0025]
  As shown in FIG. 4, the spline outer teeth 74a of the connecting member 74 are constituted by a large number of teeth 79 that extend in the axial direction and are equidistant from each other in the circumferential direction. The tooth thickness t at the adjacent proximity end (on the side where engagement with the spline inner teeth 76a starts, one end here) is made thinner as the proximity end (here one end) is approached. In this embodiment, the tooth depth h at the proximal end of each tooth 79 is lowered as it approaches the proximal end. As a result, when the connecting member 74 moves from the free position F toward the connecting position R and the spline outer teeth 74a start to engage with the spline inner teeth 76a, the meshing of the spline outer teeth 74a and the spline inner teeth 76a proceeds. Can be made smooth. In this embodiment, the reduction in the tooth thickness t and the tooth depth h as described above is also performed on the spline outer teeth 74c.
[0026]
  Reference numeral 81 denotes a snap ring attached to the outer periphery of the central portion of the connecting member 74, and a spring 82 as a moving means is interposed between the snap ring 81 and one end of the connecting sleeve 18. The spring 82 constantly applies a biasing force toward one side to the connecting member 74, thereby moving the connecting member 74 from the free position F to the connecting position R.
[0027]
  85 is a cylinder chamber formed inside the storage block 57, and a communication hole 86 as a fluid passage is formed between the cylinder chamber 85 and one end surface of the storage block 57. A hydraulic pressure source is connected through a supply / discharge passage and a switching valve (not shown). A piston 87 is housed in the cylinder chamber 85 so as to be movable in the axial direction, and a rod 88 of the piston 87 penetrates the housing block 57 and extends toward one end of the connecting member 74. 89 is a ball rotatably supported on one end surface of the connecting member 74, and the tip (the other end) of the rod 88 is in contact with the ball 89.
[0028]
  As a result, high pressure fluid is supplied to and discharged from the cylinder chamber 85 through the communication hole 86. Here, when high pressure fluid is supplied to the cylinder chamber 85 and the piston 87, the piston 87 is driven by the biasing force of the spring 82. A large pressing force (fluid force) is applied to the connecting member 74, the connecting member 74 is moved from the connecting position R to the free position F against the spring 82, and conversely, when the high-pressure fluid is discharged, the connecting member 74 moves together with the piston 87 from the free position F to the connecting position R by the biasing force of the spring 82. As a whole, the communication hole 86 and the piston 87 described above can apply a pressing force larger than the urging force of the spring 82 to the connecting member 74, and the connecting member 74 is opposed to the spring 82 to move from the connecting position R to the free position. The pressing means 90 that can be moved to F is configured.
[0029]
  Incidentally, 91 is interposed between the hoisting drum 48 and the casing 15 and the storage block 57, and a bearing for rotatably supporting the hoisting drum 48 on the casing 15 and the storage block 57, and 92 is the hoisting drum 48. The seal member is interposed between the casing 15 and the storage block 57 and seals between them.
[0030]
    Next, the operation of the first embodiment of the present invention will be described.
    When the winch is operated to rotate the hoisting drum 48 at a low speed and the rope is wound or unwound on the body 48b of the hoisting drum 48, first, the supply of the high-pressure fluid to the communication hole 86 is cut off and connected. The member 74 is moved to the connecting position R by the urging force of the spring 82, whereby the spline outer teeth 74a and the spline inner teeth 76a and the spline outer teeth 74c and the spline inner teeth 76b are meshed with each other, and the output shaft 19 The 1 external gear 67 is connected through a connecting member 74. At this time, by supplying a high pressure fluid to the piston 43 through the brake passage 41, the piston 43 is moved to the other side so as to be separated from the outer friction plate 40 against the disc spring 42, and the cylinder block 21 is moved to the negative brake 38. Free from braking.
[0031]
  In this state, when pressure oil is supplied to the cylinder hole 22 of the cylinder block 21 through one of the supply / discharge passages and the arc-shaped hole 28, the plunger 23 in the cylinder hole 22 protrudes toward the swash plate 31 and presses the inclined surface 32. However, at this time, since the tip of the plunger 23 is engaged with the inclined surface 32 via the shoe 25, the circumferential component of the pressing force acts on the plunger 23. As a result, the plunger 23 and the shoe 25 slide on the inclined surface 32, and the plunger 23, the cylinder block 21, and the output shaft 19 are integrally driven and rotated.
[0032]
  Due to the rotation of the cylinder block 21, the plunger 23 in the cylinder hole 22 communicating with the other arcuate hole 28 moves on the inclined surface 32 of the swash plate 31, so that the inclined surface 32 causes the plunger 23 to enter the cylinder hole 22. It is gradually pushed in and discharges the low pressure oil in the cylinder hole 22 through the other arcuate hole 28 and the supply / discharge passage.
[0033]
  At this time, the rotation of the output shaft 19 is input to the crankshaft 61 through the connecting member 74 and the first and second external gears 67 and 70 because the connecting member 74 is located at the connecting position R. Each crankshaft 61 is rotated around the central axis. As a result, the eccentric parts 63 of the crankshaft 61 are eccentrically rotated in the shaft hole 53 of the pinion 50 to cause the pinion 50 to undergo eccentric revolving motion, but as described above, the number of external teeth 51 is greater than the number of internal tooth pins 49. Since the winding drum 48 is slightly less, the hoisting drum 48 is greatly decelerated by the eccentric revolving motion of the pinion 50 and rotates at a low speed. As a result, the rope is wound around the body 48b of the hoisting drum 48 one after another or unwound.
[0034]
  Here, for example, when pulling the load by winding the rope in a place where the crane vehicle cannot enter, the rope tied to the load must be unwound from the winch. At this time, the hydraulic motor 11 is rotated. Thus, it is conceivable that the rope is unwound from the hoisting drum 48 and the operator guides the unwound rope while dragging it to the luggage. However, in this case, when the unwinding speed of the rope is higher than the guide speed of the operator, the rope may be tangled in the middle or may be loosened and caught on surrounding objects.
[0035]
  For this reason, in this embodiment, by releasing the connection between the hydraulic motor 11 and the speed reducer 47, the speed reducer 47, here, the hoisting drum 48 is made free, so that the operator guides the rope while pulling it to the load. Thus, the rope can be easily unwound by hand without being entangled or loosened from the hoisting drum 48. Here, such release of the connection is performed as follows.
[0036]
  That is, when the rotation of the hydraulic motor 11 is stopped, the switching valve is switched to supply high-pressure fluid from the hydraulic source to the cylinder chamber 85 through the communication hole 86, and the connecting member 74 (the other side) is larger than the urging force of the spring 82 to the piston 87. ) To generate fluid force (pressing force). As a result, the connecting member 74 located at the connecting position R is moved to the free position F while compressing the spring 82 by applying a fluid force from the piston 87. As a result, the spline external teeth 74a of the connecting member 74 are disengaged from the spline internal teeth 76a of the first external gear 67 and face the large diameter portion 76c, and the spline external teeth 74c are disengaged from the spline internal teeth 76b. 1 Pull out from the external gear 67 to the other side.
[0037]
  Here, in order to move the connecting member 74 in this way, it is only necessary to apply a pressing force larger than the urging force of the spring 82 to the connecting member 74 by the pressing means 90 as described above. In addition, the switching operation can be performed quickly. If the pressing means 90 is constituted by the communication hole 86 and the piston 87 as described above, the position can be switched powerfully and instantaneously by remote operation.
[0038]
  Next, when the connecting member 74 is moved from the free position F to the connecting position R, the supply of the high-pressure fluid to the communication hole 86 is stopped. As a result, the connecting member 74 moves to one side together with the piston 87 by the biasing force of the spring 82, the spline outer teeth 74a mesh with the spline inner teeth 76a, and the spline outer teeth 74c mesh with the spline inner teeth 76b, respectively. 74 and the first external gear 67 are connected. At this time, as described above, the tooth thickness t at the proximal end of each tooth 79 constituting the spline outer teeth 74a and 74c is reduced as it approaches the proximal end, and the tooth depth h is lowered. When the outer teeth 74a and c start to mesh with the spline inner teeth 76a and b, the meshing between the spline outer teeth 74a and c and the spline inner teeth 76a and b becomes smooth.
[0039]
    FIG. 5 is a diagram showing a second embodiment of the present invention. In this embodiment, one end opening of the communication hole 86 is closed by a cap 95, and one end is on the outer peripheral surface of the side plate 14 in the side plate 14, the case main body 13, the column body 55, the end plate 56, and the storage block 57. A communication passage 96 that is open and has the other end communicating with the communication hole 86 is formed. The communication hole 86 and the communication passage 96 constitute a fluid passage 97. In this way, the hose connected to the communication passage 96 can be provided closer to the center of the vehicle body than the hydraulic motor 11 or the like, thereby effectively preventing the hose from being damaged. Other configurations and operations are the same as those in the first embodiment.
[0040]
    6 and 7Example of reduction gear with motorFIG. thisExampleIn the inner circumference of the connecting sleeve 100, spline inner teeth 100a that are always meshed with the spline outer teeth 17a of the rotary shaft 17 are formed at the center and the other side, and the inner spline teeth are scraped off at the inner circumference of one end. The large diameter portion 100b. On the other hand, in the connecting member 101, a spline external tooth 101a is formed on the outer periphery of the other end portion, and a small-diameter portion 101b configured by scraping the spline external tooth on one side from the spline external tooth 101a is formed. Spline external teeth 101c are formed on the outer periphery of the connecting member 101 on one side of the small diameter portion 101b. Further, spline inner teeth 103a are formed over the entire inner circumference of the through hole 103 of the first external gear 102, and one end portion of the spline outer teeth 101c of the connecting member 101 is formed on the spline inner teeth 103a. Always engaged.
[0041]
  The connecting member 101 includes a connecting position R (see FIG. 6) where the spline outer teeth 101a mesh with the spline inner teeth 100a of the connecting sleeve 100, and the spline outer teeth 101a disengaged from the spline inner teeth 100a. It can move in the axial direction between a free position F (see FIG. 7) facing 100b.
[0042]
  Here, the axial movement of the connecting member 101 is performed by a spring 105 as a moving means interposed between the snap ring 104 attached to the connecting member 101 and the first external gear 102 and the tip of the rotary shaft 17. A piston 107 accommodated in a cylinder chamber 106 formed in the inner portion (one end portion) so as to be movable in the axial direction, and formed in the side plate 14 and the rotating shaft 17, and a high-pressure fluid is applied to the piston 107 in the cylinder chamber 106. This is performed using the fluid passage 108 to be guided. That is, when the high-pressure fluid is not supplied to the fluid passage 108, the connecting member 101 is moved to the connecting position R toward the other side by the biasing force of the spring 105, whereby the connecting member 101 is connected to the output shaft 19 and the first shaft. When the high pressure fluid is supplied to the fluid passage 108 while being connected to both the external gear 102, the connecting member 101 moves to the free position F toward one side while compressing the spring 105 by the piston 107. The member 101 releases the connection with the output shaft 19 while maintaining the connection with the first external gear 102.
[0043]
  Also thisExample, The tooth thickness at the proximal side end (other end) of each tooth constituting the spline external tooth 101a is made thinner as it approaches the proximal end, and the tooth depth is lowered. As a result, when the spline outer teeth 101a start to mesh with the spline inner teeth 100a, the meshing between the spline outer teeth 101a and the spline inner teeth 100a becomes smooth..
[0044]
    8 and 9 show the first aspect of the present invention.3It is a figure which shows embodiment. In this embodiment, a stepped through-hole 110 having a large-diameter portion 110a on one side and a small-diameter portion 110b on the other side is formed in the storage block 57 described above, and a circle is formed on the small-diameter portion 110b of the through-hole 110. A columnar pressing body 111 is slidably inserted, and the other end of the pressing body 111 is brought into contact with one end of the connecting member 74. Here, at one end of the pressing body 111, a stopper 111a for defining a movement limit of the pressing body 111 to the other side is formed. A cap 112 is detachably fixed to one end of the storage block 57 and closes one end opening of the through hole 110. The cap 112 and the storage block 57 constitute a fixing member 113 as a whole.
[0045]
   Reference numeral 114 denotes a push-pull cable. The push-pull cable 114 is composed of a core wire 115 and an outer tube 116 in which the core wire 115 is movably inserted. Has been inserted from. The outer tube 116 of the push-pull cable 114 is fixed to the fixing member 113, specifically, the cap 112 by sandwiching the cap 112 with a pair of nuts 117, 118 screwed to the outside thereof. On the other hand, the tip of the core wire 115 is connected to one end of the pressing body 111. The aforementioned pressing body 111 and push-pull cable 114 constitute the pressing means 119 as a whole. If the pressing means 119 is constituted by the pressing body 111 and the push-pull cable 114 as described above, the hydraulic power source and the valve required in the first embodiment are not necessary, and the position can be switched reliably and quickly by remote operation. It can be performed.
[0046]
  When the core wire 115 of the push-pull cable 114 is pushed by a large external force and moved to the other side as shown in FIG. 8, the biasing force of the spring 82 is applied from the core wire 115 to the connecting member 74 via the pressing body 111. A larger pressing force is applied, whereby the connecting member 74 moves from the connecting position R to the free position F against the spring 82. Here, in order to stop the connecting member 74 at the free position F, the large external force described above is continuously applied to the core wire 115. On the other hand, when the application of the external force to the core wire 115 is finished, the connecting member 74 is returned from the free position F to the connecting position R by the urging force of the spring 82 as shown in FIG. The core 115 is pushed back. Other configurations and operations are the same as those in the first embodiment.
[0047]
    10 and 11 show the first aspect of the present invention.4It is a figure which shows embodiment. Also in this embodiment, a stepped through hole 110 is formed in the storage block 57 as in the fourth embodiment, and a cylindrical pressing body 111 is slidable in the small diameter portion 110b of the through hole 110. The other end of the pressing body 111 is brought into contact with one end of the connecting member 74. A cap 112 that is substantially the same as that of the fourth embodiment is detachably fixed to one end of the storage block 57.
[0048]
   Reference numeral 121 denotes a spring as an urging member interposed between the stopper 111a of the pressing body 111 and the cap 112. The spring 121 presses the pressing body 111 and the connecting member 74 with a pressing force larger than the urging force of the spring 82 ( Energizing force). As a result, when no other external force is applied to the pressing body 111, the connecting member 74 moves from the connecting position R to the free position F and stops, while compressing the spring 82, as shown in FIG.
[0049]
  122 is a wire, and the tip of the wire 122 is connected to one end of the pressing body 111 via an intermediate rod 124. The aforementioned pressing body 111, spring 121, and wire 122 constitute the pressing means 123 as a whole. If the pressing means 123 is constituted by the pressing body 111, the spring 121, and the wire 122 in this way, the hydraulic power source and the valve that are necessary in the first embodiment are not necessary, and the position can be reliably and quickly set by remote operation. Switching can be performed.
[0050]
  When the wire 122 is pulled to one side, the pressing member 111 moves away from the connecting member 74 while facing the spring 121 as shown in FIG. The urging force toward the other side disappears. As a result, the connecting member 74 is pushed by the urging force of the spring 82 and returns from the free position F to the connecting position R. Other configurations and operations are the same as those in the first embodiment.
[0051]
    In the above-described embodiment, the hydraulic motor 11 is used as the drive motor. However, in the present invention, an electric motor may be used. In the above-described embodiment, the springs 82 and 105 are used as the moving means. However, in the present invention, a piston that always generates a fluid force smaller than the pistons 87 and 107 may be used. Furthermore, in the above-described embodiment, the present invention is applied to a winch of a crane vehicle. However, in the present invention, the present invention may be used to drive a crawler vehicle as described in the prior art.
[0052]
  In the above-described embodiment, the spline inner teeth 18a, 76a, b are formed on the output shaft 19 and the first external gear 67, and the spline outer teeth 74a, c are formed on the connecting member 74. Spline external teeth may be formed on the shaft and the first external gear, and spline internal teeth may be formed on the connecting member. Furthermore, in the above-described embodiment, the tooth thickness and the depth of the teeth of the spline external teeth 74a, c, 101a are made thinner and lower as they approach the proximal end. The tooth thickness and the depth of the teeth may be made thinner and lower as they approach the proximal end, or both the teeth inside and outside the spline may be made thinner and lower as well.
[0053]
【The invention's effect】
    As described above, according to the present invention, the connection between the motor and the speed reducer can be quickly released by a simple operation as necessary.
[Brief description of the drawings]
FIG. 1 is a front sectional view showing a first embodiment of the present invention.
FIG. 2 is an enlarged cross-sectional view in the vicinity of a connecting portion between an output shaft and a first external gear, showing a state in which the output shaft and the first external gear are connected.
FIG. 3 is an enlarged cross-sectional view in the vicinity of a connection portion between an output shaft and a first external gear, showing a state in which the connection between the output shaft and the first external gear is released and becomes free.
FIG. 4 is an enlarged perspective view showing the vicinity of one end of a connecting member.
FIG. 5 is a front sectional view showing a second embodiment of the present invention.
[Fig. 6]Example of reduction gear with motorFIG.
FIG. 7 is an enlarged cross-sectional view of the vicinity of the connecting portion between the output shaft and the first external gear, showing a state in which the connection between the output shaft and the first external gear is released and becomes free.
FIG. 8 shows the first aspect of the present invention.3It is an expanded sectional view near the connection part which shows an embodiment, and shows the state where connection with an output axis and the 1st external gear was canceled and it became free.
FIG. 9 is an enlarged cross-sectional view of the vicinity of the connecting portion similar to FIG. 8, showing a state where the output shaft and the first external gear are connected.
FIG. 10 shows the first of the present invention.4It is an expanded sectional view near the connection part which shows an embodiment, and shows the state where connection with an output axis and the 1st external gear was canceled and it became free.
FIG. 11 is an enlarged cross-sectional view of the vicinity of the connecting portion similar to FIG. 10, showing a state where the output shaft and the first external gear are connected.
[Explanation of symbols]
    11 ... Drive motor 19 ... Output shaft
    47 ... Reducer 48 ... Hoisting drum
    67 ... First external gear 70 ... Second external gear
    74 ... Connecting members 74a, 74c ... Spline external teeth
    76a, b ... Spline internal teeth 79 ... Teeth
    82 ... Movement means 86 ... Fluid passage
    87 ... Piston 90, 119, 123 ... Pressing means
   111 ... Pressing body 113 ... Fixing member
   114 ... Push-pull cable 115 ... Core
   116 ... outer cylinder 121 ... biasing member
   122 ... Wire R ... Connection position
    F ... Free position t ... Tooth thickness
    h ... Toothpaste

Claims (1)

Via a second external gear which meshes a rotational driving force from the output shaft of the drive motor to the first external gear and the first external gear transmitted to the reduction gear, a motor with reduction gear so as to decelerate the speed reducer there it is installed between the output shaft and the first external gear, an output shaft and a coupling position which is connected by splines to both the first external gear, while that will be connected by a spline to an output shaft, a first outer A connecting member that can move in the axial direction between a free position where the connection is released from the gear , and a biasing force is constantly applied to the connecting member, thereby moving the connecting member from the free position to the connected position. A moving means; and a pressing means that can apply a pressing force larger than the urging force of the moving means to the connecting member, and can move the connecting member from the connecting position to the free position against the moving means. In free mechanism of motorized speed reducer, to form a first spline teeth and second spline teeth on the first external gear, these first, shaved off splined teeth on the first external gear between second spline teeth While forming a diameter part, while forming the 1st spline tooth and the 2nd spline tooth in the connecting member, forming the diameter part by which the spline tooth was scraped off in the connecting member between the first and second spline teeth, And when the said connection member is located in a connection position, the 1st, 2nd spline tooth | gear of a said 1st external gear, a diameter part, and the 1st, 2nd spline tooth | gear of a connection member, and a diameter part of a connection member The first spline teeth and the second spline teeth mesh with the first spline teeth and the second spline teeth of the first external gear, respectively, and the connecting member moves to the free position. The coupling diameter and the second spline teeth of the members, a first external gear of the first spline teeth and motor with reduction gear free mechanism, characterized in that arranged so that each positioned in a position facing the diameter .

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