JP5102663B2 - Vertical motor unit with reduction gear - Google Patents

Description

  According to the present invention, a planetary gear mechanism constituting a speed reducer is disposed in lubricating oil stored in the speed reducer, and a sun gear drive shaft and a vertical motor output shaft in the planetary gear mechanism are spline-coupled. The present invention relates to a machine-equipped vertical motor device. In particular, the present invention relates to a vertical motor device with a reduction gear capable of forcibly supplying lubricating oil to a spline coupling portion between a drive shaft of a sun gear and an output shaft of a vertical motor.

  BACKGROUND ART A vertical motor device with a reduction gear is used as a drive source or the like for turning an upper swing body with respect to a lower travel body in a self-propelled construction work machine such as a hydraulic excavator. And the vertical motor apparatus with a reduction gear is normally attached to the upper revolving body side.

  As a vertical motor device with a reduction gear, various types of hydraulic motor devices with a reduction gear for turning (see Patent Document 1) have been proposed. In the hydraulic motor device described in Patent Document 1, as shown in FIG. 7, a hydraulic motor unit 52 having a hydraulic motor 56 and a planetary gear mechanism in which a sun gear 61 is attached to an output shaft 58 of the hydraulic motor 56 are used. And a speed reduction mechanism portion 53.

  The hydraulic motor 56 configured as a swash plate type hydraulic motor is housed in the motor housing 54 of the hydraulic motor section 52, and the speed reduction mechanism section 53 is housed in casings 62 and 63 constituting the speed reduction mechanism section 53. Has been. The rotation of the hydraulic motor 56 is decelerated in the decelerating mechanism 53, and the decelerated rotation is finally transmitted to the output pinion 64.

  The output pinion 64 is meshed with an internal gear (ring gear) 65 of an inner ring fixed to the lower traveling body side (not shown). On the lower traveling body side, rotation is restricted by grounding, and when the output pinion 64 rotates, the output pinion 64 revolves while rotating along the inner peripheral surface of the internal gear (ring gear) 65. The upper swing body provided with the speed reducer-equipped hydraulic motor device 51 can swing relative to the lower traveling body.

  In the hydraulic motor device with a reduction gear 51 shown in Patent Document 1, the sun gear 61 is attached to the output shaft 58 of the hydraulic motor 56, and the driving force of the hydraulic motor 56 is reduced from the sun gear 61 to the planetary gear reduction. The structure is transmitted to the mechanism. Further, a two-stage planetary gear reduction mechanism is employed as the reduction mechanism unit 53.

The speed reduction mechanism portion 53 including the two-stage planetary gear speed reduction mechanism has an outer casing constituted by casings 62 and 63, and one casing 63 is fixed on the turning frame of the upper turning body. With this configuration, the hydraulic motor device 51 with a reduction gear for turning is fixedly provided on the upper turning body side. Then, by the rotational drive of the hydraulic motor 56, the upper swing body can decelerate and swing with respect to the lower traveling body.
JP 2002-357260 A

  In the planetary gear speed reduction mechanism in Patent Document 1, a convex spline formed on the outer peripheral surface of the output shaft 58 of the hydraulic motor 56 is spline-coupled to the concave spline formed in the central portion of the sun gear 61. Incidentally, oil bath lubrication (oil bath system) is generally used in a turning device of a construction machine equipped with a reduction gear, and sun gears, planetary gears, etc. are used in a state of being immersed in lubricating oil. Yes.

  The two-stage planetary gear reduction mechanism in Patent Document 1 also employs oil bath lubrication as described above. Therefore, the two-stage planetary gear reduction mechanism is soaked in the lubricating oil filled in the casings 62 and 63. It has become. The spline coupling portion between the sun gear 61 and the output shaft 58 of the hydraulic motor 56 is immersed in the lubricating oil, and the spline coupling portion can be sufficiently lubricated.

  By the way, in recent years, hybrid construction machines have been studied, and it is considered that the hydraulic motor 56 described in Patent Document 1 is replaced with an electric vertical motor. However, even if the hydraulic motor 56 is replaced with a vertical motor, the size of the vertical motor inevitably depends on the configuration of the hydraulic motor 56 as long as the horsepower can be obtained at the same level as when the hydraulic motor 56 is used. It will be larger than 56. For this reason, when the replacement with the vertical motor is attempted, there is a problem in mounting on the upper swing body.

  Therefore, by setting the lower end surface position of the output shaft in the vertical motor inside the motor case that houses the vertical motor, the length in the longitudinal direction can be shortened, The problem of mounting on the swivel can be solved. However, the spline coupling portion between the output shaft of the vertical motor and the drive shaft of the sun gear is located inside the motor case. For this reason, the spline coupling portion is disposed at a position away from the oil surface of the lubricating oil performing oil bath lubrication, and lubrication with respect to the spline coupling portion becomes difficult.

  In the present invention, the lubricating oil in which the output shaft of the electric vertical motor is disposed in the motor housing, and the spline coupling portion between the output shaft of the vertical motor and the drive shaft of the sun gear performs oil bath lubrication. An object of the present invention is to provide a vertical motor device with a reduction gear that can supply lubricating oil to the spline coupling portion even if it is disposed at a position spaced from the oil surface.

The object of the present invention can be achieved by the inventions described in claims 1 to 4.
That is, the vertical motor device with a speed reducer according to the present invention includes a planetary gear mechanism disposed in the lubricating oil stored in the speed reducer, and a drive shaft of the sun gear and an output shaft of the vertical motor in the planetary gear mechanism. Is a vertical motor device with a reduction gear that is spline-coupled,
The position of the lower end surface of the output shaft is located inside the motor case that houses the vertical motor in the axial direction of the output shaft , a convex spline is formed on the outer peripheral surface of the drive shaft, and the lower end of the output shaft A concave spline that engages with the convex spline is formed, and an inner diameter expanding portion formed at the tip of the concave spline is formed above the meshing portion between the sun gear and the planetary gear meshing with the sun gear. The main feature is that it is arranged.

  Further, in the vertical motor device with a reduction gear according to the present invention, the inner diameter expanding portion is formed as a concave portion having an inner peripheral surface having a diameter larger than the root diameter of the concave spline at a tip portion of the concave spline. Is a major feature.

Furthermore, the vertical motor device with a speed reducer according to the present invention is characterized in that the peripheral edge on the inner peripheral surface side of the recess is chamfered.
Furthermore, the vertical motor device with a speed reducer according to the present invention is mainly characterized in that a thread groove is formed on the inner peripheral surface of the recess.

In the present invention, a convex spline is formed on the outer peripheral surface of the drive shaft of the sun gear, and the convex spline is splined with a concave spline formed on the output shaft of the vertical motor. Moreover, the lower end surface position of the output shaft is positioned inside the motor case that houses the vertical motor in the axial direction of the output shaft, and the inner diameter enlarged portion formed at the tip of the concave spline is the same as the sun gear. It is configured so as to be disposed above the meshing portion with the planetary gear meshing with the sun gear.

With this configuration, the position of the lower end surface of the output shaft of the vertical motor can be configured to be positioned inside the motor case that houses the vertical motor in the axial direction of the output shaft . Since the output shaft of the vertical motor is retracted into the motor case, the vertical motor housed in the motor case can be easily conveyed. Even when packing the vertical motor, the output shaft of the vertical motor does not protrude from the motor case, so packing is performed compared to when the output shaft of the vertical motor protrudes from the motor case. The volume can be reduced. Moreover, even if the motor case is placed on a table or the like as it is, the motor case can be placed in a stable state.

  Further, since the length of the output shaft in the vertical motor can be shortened, the driving reaction force transmitted from the sun gear can be received near the bearing supporting the output shaft of the vertical motor. . As a result, the volume of the bearing can be reduced, and the life of the bearing can be extended.

  Furthermore, since the drive shaft of the sun gear protrudes, alignment and the like are facilitated when the vertical motor is coupled to the planetary gear mechanism. In addition, since the sun gear can move somewhat with respect to the planetary gear, the accuracy of alignment when the output shaft of the vertical motor and the drive shaft of the sun gear are spline-coupled should be somewhat rough. Can do.

  For this reason, the operation of coupling the vertical motor to the planetary gear mechanism can be performed in a short time. In particular, when the vertical motor is exchanged outdoors, the operation of coupling the vertical motor to the planetary gear mechanism can be performed in a short time.

  When the lubricating oil performing oil bath lubrication is sandwiched in the meshing portion between the sun gear and the planetary gear, the lubricating oil is pushed out from the meshing portion and ejected from the sides of the sun gear and the planetary gear. . Therefore, in the present invention, by utilizing this phenomenon, the inner diameter widened portion formed at the tip of the concave spline is disposed above the meshing portion of the sun gear and the planetary gear meshing with the sun gear. It is configured. And it is comprised so that the lubricating oil extruded and spouted from the meshing part may be sprayed in the internal diameter expansion part formed in the front-end | tip part of a concave spline.

  The higher the speed of the sun gear, the more intense this blast is. Then, a large amount of lubricating oil is sprayed from one to the next in the inner diameter expanding portion, and the lubricating oil sprayed in the inner diameter expanding portion is pumped back to the back. . For this reason, the lubricating oil sprayed into the inner diameter expanding portion continues to be pumped by the successively sprayed lubricating oil, rather than dropping from the inner diameter expanding portion by gravity. Then, the pumped lubricating oil can move up the spline joint and lubricate the spline joint.

  As the oil level of the lubricating oil performing the oil bath lubrication, for example, when the sun gear is stationary, even if the sun gear is set on the upper surface of the gear at the meshing portion of the sun gear and the planetary gear, A centrifugal force acts on the lubricating oil with the rotation of the oil, and the oil surface of the lubricating oil has a mortar shape. For this reason, a state in which the oil level does not exist near the center of the drive shaft of the sun gear or the upper surface portion of the meshing portion between the sun gear and the planetary gear occurs.

  However, by adjusting the degree of meshing at the meshing part between the sun gear and the planetary gear, a part of the meshing part can be kept in a state of being always immersed in the lubricating oil. And the lubricating oil which has immersed a part of said meshing part can be extruded from a meshing part, and can be spouted up. The lubricating oil is extruded upward and downward from the meshing portion, but the lubricating oil extruded downward is returned to the lubricating oil stored in the speed reducer. Then, as described above, the lubricating oil pushed upward is sprayed onto the inner diameter enlarged portion formed at the tip of the concave spline.

  In the present invention, an inner diameter expanding portion may be configured as a concave portion having an inner peripheral surface larger in diameter than the root diameter of the concave spline at the tip end portion of the concave spline formed on the output shaft of the vertical motor. it can. By configuring the inner diameter expanding portion in this way, the lubricating oil sprayed from the meshing portion between the sun gear and the planetary gear can be easily taken into the inner diameter expanding portion. Further, it is possible to satisfactorily lubricate the spline connection between the output shaft of the vertical motor and the drive shaft of the sun gear.

  In this invention, the chamfering process can be given with respect to the peripheral edge in the inner peripheral surface side of the said recessed part. By configuring in this way, it is possible to more easily take in the lubricant sprayed from the meshing portion of the sun gear and the planetary gear, and to take in a large amount of lubricant into the inner diameter expanding portion. Can do.

  Moreover, in this invention, a thread groove can be formed in the internal peripheral surface of the said recessed part. By configuring in this way, as the output shaft of the vertical motor rotates, the lubricating oil taken into the inner diameter enlarged portion is forcedly splined by the screw groove feed action. Can be supplied to.

Preferred embodiments of the present invention will be specifically described below with reference to the accompanying drawings. As the configuration of the vertical motor device with a speed reducer of the present invention, in addition to the configuration using an electric motor as a vertical motor described below, for example, a configuration using a hydraulic motor as a vertical motor, The present invention can be effectively applied to vertical motor devices with various reduction gears that employ an oil bath system. For this reason, this invention is not limited to the Example demonstrated below, A various change is possible.

  FIG. 1 is a longitudinal sectional view of a vertical motor device with a reduction gear used in a construction machine according to an embodiment of the present invention. FIG. 2 is a diagram schematically showing a main configuration of the spline coupling portion, which is a characteristic configuration of the present invention. Further, FIG. 6 shows the main configuration of the spline coupling portion in the case where the inner diameter expanding portion is not formed at the tip end portion of the concave spline formed on the output shaft of the vertical motor for comparison with the present invention. It is the figure shown typically.

  As shown in FIG. 1, the vertical motor device 4 with a speed reducer has a configuration including an electric motor 5 and a speed reducer 10 used as a vertical motor. The electric motor 5 is rotated by being supplied with a predetermined electric power under the control of a turning control device (not shown). The electric motor 5 has a size substantially the same as that of a conventional hydraulic motor, but a size different from that of a conventional hydraulic motor can also be used. Further, the electric motor 5 uses a high-speed rotation type motor as compared with the hydraulic motor in order to generate an output torque corresponding to the conventional hydraulic motor.

  In the following, the configuration using the electric motor 5 as the vertical motor will be described, but a hydraulic motor may be used as the vertical motor. Therefore, the present invention is not limited to the configuration using the electric motor 5 as the vertical motor.

  On the lower side of the electric motor 5, a speed reducer 10 that decelerates the rotation of the motor output shaft 5a is provided. The speed reducer 10 is configured as a three-stage speed reducer. The three-stage reducer includes a first reducer 11 that first decelerates rotation from the electric motor 5, a second reducer 12 that further decelerates the rotation decelerated by the first reducer 11, and a second reducer. The third speed reducer 13 rotates the output pinion 14 by further decelerating the rotation decelerated at 12.

  A mechanical brake 15 is disposed between the first speed reducer 11 and the second speed reducer 12. Further, the lubricating oil is stored in the lubricating oil chamber 9 in the speed reducer 10, and the first speed reducer 11, the second speed reducer 12, the third speed reducer 13 and the mechanical brake 15 are arranged in the lubricating oil. It becomes the composition.

  The electric turning device 4 is fixed to the upper turning body 2, and the swing circle 3 is fixed to the lower traveling body 1. In addition, a concentric outer ring 8 (illustration of the left cross section is omitted) is fixed to the upper swing body 2 so as to be circumscribed and relative to the swing circle 3. A bearing 8 a is interposed between the outer ring 8 and the swing circle 3 so that relative rotation can be performed between the outer ring 8 and the swing circle 3.

  Then, the output pinion 14 rotated by the output from the third reduction gear 13 meshes with the internal teeth formed in the swing circle 3 provided in the lower traveling body 1, and the output pinion 14 rotates, The upper swing body 2 can swing with respect to the lower traveling body 1.

  Next, the structure of the speed reducer 10 and the structure of the mechanical brake 15 will be described. However, the speed reducer 10 is not limited to a three-stage speed reducer, and has a suitable number of stages including a one-stage speed reducer. It can be configured as a machine.

  In the illustrated example, the planetary gears 11b, 12b, and 13b in the first speed reducer 11 to the third speed reducer 13 are supported in a cantilever state by the respective carriers 11d, 12d, and 13d. However, as the support structure of each planetary gear 11b, 12b, 13b, the both ends of the planetary shafts 11c, 12c, 13c of each planetary gear 11b, 12b, 13b are supported by the respective carriers 11d, 12d, 13d. It can also be left. The support structure for both-end support is not particularly illustrated because it is a known support structure. For example, Japanese Patent Application Laid-Open No. 2006-220220 discloses a support structure for both-end support.

  Further, the configuration of the mechanical brake 15 is not limited to the brake mechanism described below, and a known brake mechanism can be used. The part where the brake mechanism is disposed is not limited to the part between the first reduction gear 11 and the second reduction gear 12.

  The reduction gear 10 and the mechanical brake 15 are accommodated in a cylindrical casing 7 fixed to the upper swing body 2. The casing 7 includes, in order from the top, a first casing 7a in which a first speed reducer 11 is disposed, a brake casing 7b in which a mechanical brake 15 is disposed, and a second speed reducer 12 and a second inside. A third casing 7c in which a part of the three reduction gears 13 is disposed and a third casing 7d in which the remaining part of the third reduction gear 13 is disposed. Adjacent casings 7a to 7d are fixed by fixing means such as bolts.

  The electric motor 5 is fixed to the upper end portion of the first casing 7a, and the lower end portion of the third casing 7d is fixed to the upper swing body 2. In the illustrated example, the electric motor 5 is disposed in the motor case 19.

The first speed reducer 11 is configured to decelerate the rotation of the first sun gear 11a provided on the drive shaft 20 , increase the drive torque, and output from the first drive shaft 11f. The rotation of the first sun gear 11a is transmitted to the first planetary gear 11b meshed with the first sun gear 11a and the first ring gear 11e formed on the inner peripheral surface of the first casing 7a.

  The first planetary gear 11b is rotatably supported between the first planetary gear 11b and the first planetary shaft 11c supported by the first carrier 11d. Further, in order to prevent the first planetary gear 11b from coming off from the first planetary shaft 11c, a first retainer 11h is attached to the upper end portion side of the first planetary shaft 11c.

  By the rotation from the first sun gear 11a, the first planetary gear 11b rotates and revolves around the outer periphery of the first sun gear 11a. The revolving motion of the first planetary gear 11b can be taken out as the rotation of the first carrier 11d that rotatably supports the first planetary gear 11b. The rotational speed of the first carrier 11d is the revolution speed of the first planetary gear 11b that revolves around the outer periphery of the first sun gear 11a, and is decelerated from the rotational speed of the first sun gear 11a. The rotation of the first carrier 11d is transmitted to the first drive shaft 11f that is splined with the first carrier 11d.

  The second speed reducer 12 is configured to decelerate the rotation of the second sun gear 12a provided on the first drive shaft 11f, increase the drive torque, and output from the second drive shaft 12f. The rotation of the second sun gear 12a is transmitted to the second planetary gear 12b meshed with the second sun gear 12a and the second ring gear 12e formed on the inner peripheral surface of the second casing 7c.

  The second planetary gear 12b is rotatably supported between the second planetary shaft 12c supported by the second carrier 12d. Further, in order to prevent the second planetary gear 12b from coming off from the second planetary shaft 12c, a second retainer 12h is attached to the upper end portion side of the second planetary shaft 12c.

  Due to the rotation from the second sun gear 12a, the second planetary gear 12b rotates and revolves around the outer periphery of the second sun gear 12a. The revolving motion of the second planetary gear 12b can be taken out as the rotation of the second carrier 12d that rotatably supports the second planetary gear 12b. The rotation speed of the second carrier 12d is the revolution speed of the second planetary gear 12b that revolves around the outer periphery of the second sun gear 12a, and is decelerated from the rotation speed of the second sun gear 12a. The rotation of the second carrier 12d is transmitted to the second drive shaft 12f that is splined to the second carrier 12d.

  The third speed reducer 13 is configured to decelerate the rotation of the third sun gear 13a provided on the second drive shaft 12f, increase the drive torque, and output from the third drive shaft 13f. The rotation of the third sun gear 13a is transmitted to the third planetary gear 13b meshed with the third sun gear 13a and a third ring gear 13e formed on the inner peripheral surface of the second casing 7c.

  The third planetary gear 13b is rotatably supported between the third planetary shaft 13c supported by the third carrier 13d. In order to prevent the third planetary gear 13b from coming off from the third planetary shaft 13c, a third retainer 13h is attached to the upper end side of the third planetary shaft 13c.

  By rotation from the third sun gear 13a, the third planetary gear 13b rotates and revolves around the outer periphery of the third sun gear 13a. The revolution movement of the third planetary gear 13b can be taken out as the rotation of the third carrier 13d that rotatably supports the third planetary gear 13b. The rotational speed of the third carrier 13d is the revolution speed of the third planetary gear 13b that revolves around the outer periphery of the third sun gear 13a, and is decelerated from the rotational speed of the third sun gear 13a. The rotation of the third carrier 13d is transmitted to the third drive shaft 13f that is splined to the third carrier 13d. The rotation of the third drive shaft 13f is used as a rotational force for rotating the output pinion 14.

  Thus, the rotation of the electric motor 5 that has been rotating at a high speed is decelerated by the speed reducer 10 to be in a high output torque state, and the output pinion 14 can be rotated. Further, as the configuration of the first sun gear 11a to the third sun gear 13a and the configuration of the output pinion 14, respectively, one end of the drive shaft 20, the tip of the first drive shaft 11f, the tip of the second drive shaft 12f, The tip of the third drive shaft 13f may be processed into a gear shape and formed integrally with the respective shafts 20, 11f, 12f, 13f. Moreover, it can also be set as the structure fitted with each shaft 20, 11f, 12f, 13f in the non-rotatable state.

  The mechanical brake 15 is disposed between the first speed reducer 11 and the second speed reducer 12, and is configured to brake the rotation of the first drive shaft 11f that is the output shaft of the first speed reducer 11. In other words, the mechanical brake 15 is a brake piston 16 that is controlled to move up and down the brake disc 15b joined to the first drive shaft 11f via the brake pad 15c, and holds or releases the holding pressure. It is the structure which can do. With this configuration, braking can be applied to the rotation of the first drive shaft 11f and braking can be released.

  The brake disc 15b is provided on the outer peripheral portion of the brake connecting portion 15a joined to the first drive shaft 11f by spline joining, serration joining, or the like. A pair of brake pads 15c are provided at positions facing the upper and lower surfaces of the brake disc 15b. Of the pair of brake pads 15c, the brake pad 15c provided facing the lower surface of the brake disc 15b is fixed to the pad fixing portion of the brake casing 7b, and is opposed to the upper surface of the brake disc 15b. The brake pad 15c provided is attached to the lower end of the brake piston 16.

  The brake piston 16 is formed in a substantially annular shape, and includes a step portion having a shape facing the step portion of the brake casing 7b. A hydraulic chamber 17 is formed by the stepped portion of the brake casing 7b and the stepped portion of the brake piston 16. The brake piston 16 is given a downward biasing force by a spring 18 provided at the upper part.

  By supplying / discharging pressure oil to / from the hydraulic chamber 17, sliding of the brake piston 16 in the vertical direction can be controlled. Supply and discharge of pressure oil to and from the hydraulic chamber 17 can be performed from a hydraulic port 17a formed in the brake casing 7b. When pressure oil is supplied to the hydraulic chamber 17, the brake piston 16 is pushed upward while compressing the spring 18. As a result, the holding state of the brake disc 15b held by the brake piston 16 is released, and the rotation of the first drive shaft 11f is not braked.

  When the pressure oil is discharged from the hydraulic chamber 17, the brake piston 16 is pushed downward by the urging force of the spring 18. As a result, the brake disk 15b is held and held by the brake piston 16, and the rotation of the first drive shaft 11f is braked.

  In this embodiment, an example using one brake disk 15b has been described. However, the present invention is not limited to this configuration, and a brake mechanism using a configuration using a plurality of brake discs or other well-known configuration is used. May be adopted. Further, when the brake disk 15b is used, the brake pad 15c may be provided on the brake disk 15b side.

  Next, the configuration of the spline coupling portion 22 that couples the drive shaft 20 of the first sun gear 11a and the motor output shaft 5a of the electric motor 5, which is a characteristic configuration of the present invention, will be described with reference to FIG. The drive shaft 20 is erected from the first sun gear 11a, and a convex spline 24 is formed on the outer peripheral surface of the drive shaft 20 on the upper end side.

  Further, the lower end portion of the motor output shaft 5a is configured to be located in the motor case 19. A concave spline 23 that engages with the convex spline 24 formed on the drive shaft 20 is formed at the end of the motor output shaft 5a. Further, an inner diameter expanding portion 30 is formed at the tip of the concave spline 23, and a gap is formed between the inner diameter expanding portion 30 and the convex spline 24 at the time of spline coupling.

  By the way, as shown in FIG. 6, the meshing length of the concave spline 23 and the convex spline 24 is the meshing length of both when there is an error in the length direction when both are relatively positioned. Is set with a margin so as not to be shortened. That is, the gap t is set between the meshing end of the concave spline 23 and the effective end of the convex spline 24 when the concave spline 23 and the convex spline 24 are engaged.

  Further, a rounded end exists further below the concave spline 23 by the length of the rounded convex spline 24. Even if it is a structure as shown in FIG. 6, if the position of the meshing part 25 of the 1st sun gear 11a and the 1st planetary gear 11b can be arrange | positioned near the spline coupling part 22, the 1st sun gear During the rotation of 11a, oil can be repelled on the portion of the gap t.

However, the cut upper ends of the convex splines 24 serving as the portions of the gap t are configured to be scattered as depressions corresponding to the tooth width of the convex splines 24 at equal intervals in the circumferential direction of the drive shaft 20.
Therefore, the lubricating oil hardly accumulates in the portion of the gap t, and the oil splashed on the portion of the gap t by the centrifugal force due to the rotation of the motor output shaft 5a is outside the shaft of the motor output shaft 5a. Will be skipped. For this reason, the oil cannot be spread over the spline coupling portion 22.

  Therefore, in the present invention, the splashed oil is configured not to be blown off by the centrifugal force in the gap t between the concave spline 23 and the convex spline 24 and the length-up length portion of the convex spline 24. As shown in FIG. 2, an inner diameter expanding portion 30 having a diameter larger than the root diameter of the spline teeth of the concave spline 23 is provided at the tip of the concave spline 23.

  That is, the oil once splashed on the portion of the raised length of the convex spline 24 is likely to be ejected to the outside by the action of the centrifugal force, but can be received by the inner diameter expanding portion 30. Then, the remaining oil that moves upward moves further to the upper spline coupling portion 22.

  The inner diameter expanding portion 30 is configured such that the inner diameter expanding portion 30 is located at a position above the meshing portion 25 of the first sun gear 11a and the first planetary gear 11b. With this configuration, when the lubricating oil performing oil bath lubrication is pushed out from the meshing portion 25 of the first sun gear 11a and the first planetary gear 11b and spouted above the meshing portion 25, the spouted lubrication The oil is sprayed into the inner diameter expanding portion 30 disposed above the meshing portion 25 and is captured in the inner diameter expanding portion 30.

  The lubricating oil trapped in the inner diameter expanding portion 30 continues to be pumped to the back of the spline coupling portion 22 by the lubricating oil sprayed from one to the next rather than dropping due to gravity. . Then, the lubricating oil ascends from the inside of the inner diameter expanding portion 30 to the spline coupling portion 22, and can lubricate the spline coupling portion 22.

  The portion in the inner diameter expanding portion 30 to which the lubricating oil is sprayed moves little by little within the circumference of the inner diameter expanding portion 30 by the revolving motion of the first planetary gear 11b. Therefore, the lubricating oil that has risen up the spline coupling portion 22 returns to the inner diameter expansion portion 30 through the spline coupling portion 22 where the lubricating oil is not sprayed in the inner diameter expansion portion 30. The expanded portion 30 returns to the location of the lubricating oil stored in the first casing 7a.

  In addition, by forming a drill hole that penetrates in the radial direction of the motor output shaft 5a in the vicinity of the bottom of the hole in which the concave spline 23 is formed at the end of the motor output shaft 5a, the motor output shaft 5a is pumped to the bottom of the hole. The lubricating oil can also be discharged to the bearing 26 side. The lubricating oil discharged to the bearing 26 side can return to the lubricating oil in the first casing 7a by lubricating and cooling the bearing 26.

  The higher the rotational speed of the first sun gear 11a, the more intense the lubricant sprayed from the meshing portion 25. Then, a large amount of lubricating oil is sprayed into the inner diameter expanding portion 30 from one to the next, and the lubricating oil sprayed into the inner diameter expanding portion 30 is pumped back to the back. Will be.

  For example, when the rotation of the first sun gear 11a is stationary, the gear at the meshing portion 25 of the first sun gear 11a and the first planetary gear 11b is used as the oil level of the lubricating oil performing oil bath lubrication. Even if the upper surface is set, the centrifugal force acts on the lubricating oil as the first sun gear 11a rotates, so that the oil surface of the lubricating oil has a mortar shape. For this reason, there is a state in which no oil surface exists in the vicinity of the center of the drive shaft 20 of the first sun gear 11a or the upper surface portion of the meshing portion 25 between the first sun gear 11a and the first planetary gear 11b.

  However, by adjusting the degree of meshing in the meshing portion 25 between the first sun gear 11a and the first planetary gear 11b, a part of the first sun gear 11a and the first planetary gear 11b in the meshing portion 25. Can always be immersed in the lubricating oil. Then, the lubricating oil soaking part of the meshing portion 25 is pushed out of the meshing portion 25 and sprayed up. Lubricating oil is extruded upward and downward from the meshing portion 25, but the lubricating oil pushed downward is returned to the lubricating oil in the first casing 7a. Then, the lubricating oil pushed upward is sprayed into the inner diameter enlarged portion 30 formed at the tip of the concave spline 23 as described above.

  In the present invention, the lower end surface position of the motor output shaft 5a of the electric motor 5 can be configured to be located inside the motor case 19 that houses the electric motor 5. That is, since the motor output shaft 5a is retracted and accommodated in the motor case 19, the electric motor 5 accommodated in the motor case 19 can be easily conveyed. Even when packing the motor case 19, since the motor output shaft 5a does not protrude from the motor case 19, the packing volume can be kept smaller than when the motor output shaft protrudes from the motor case. it can. Furthermore, the motor case 19 that houses the electric motor 5 can be placed in a stable state on a flat table or the like.

  Furthermore, since the length of the motor output shaft 5a can be shortened, the driving reaction force transmitted from the first sun gear 11a is received near the bearing 26 supporting the motor output shaft 5a. Can be configured. As a result, the volume of the bearing 26 can be reduced, and the driving reaction force acting on the bearing 26 is reduced, so that the life of the bearing 26 can be extended.

  Further, since the drive shaft 20 of the first sun tooth 11a car protrudes, when the motor shaft 5a of the electric motor 5 and the drive shaft 20 of the first sun tooth 11a car are splined together, alignment and the like are performed. It becomes easy. In addition, since the first sun gear 11a can move somewhat with respect to the first planetary gear 11b, the accuracy of centering when the motor output shaft 5a and the drive shaft 20 are spline-coupled is somewhat rough. I can leave.

  For this reason, the operation | work which connects the electric motor 5 to the 1st reduction gear 11 can be performed in a short time. In particular, when the electric motor 5 is exchanged outdoors, the operation of connecting the electric motor 5 to the first speed reducer 11 can be performed in a short time.

  By the way, if the lower end surface position of the motor output shaft 5a of the electric motor 5 is set inside the motor case 19, the spline coupling portion 22 between the motor output shaft 5a and the drive shaft 20 is connected to the motor case 19. Will be located inside. The spline connecting portion 22 is disposed at a position away from the oil surface of the lubricating oil that is subjected to oil bath lubrication, which makes it difficult to lubricate the spline connecting portion.

  However, in the present invention, as described above, the inner diameter enlarged portion 30 is formed in the upper portion of the meshing portion 25 between the first sun gear 11a and the first planetary gear 11b. With this configuration, the lubricating oil spouted from the meshing portion 25 can be captured in the inner diameter expanding portion 30, and the spline coupling portion 22 can be lubricated.

  FIG. 3 schematically shows a main configuration of the spline coupling portion in the vicinity of the spline coupling portion in the second embodiment according to the present invention. In FIG. 2 in the first embodiment, the raised portion of the convex spline 24 is covered with the inner diameter expanding portion 30. For this reason, the opening area into which the lubricant sprayed from the meshing part 25 is sprayed becomes a small opening area.

  Therefore, in Example 2, the opening area is configured to be large. That is, as shown in FIG. 3, the rounded end of the concave spline 23 formed on the motor output shaft 5a is arranged below the tip of the inner diameter expanding portion 31. Other configurations are the same as those in the first embodiment. Therefore, the same members are denoted by the same reference numerals as those used in the first embodiment, and the description thereof is omitted.

  In the second embodiment, as shown in FIG. 3, since the positional relationship between the tip end position of the inner diameter expanding portion 31 and the rounded end of the concave spline 23 is configured, the lubricating oil is taken in by the inner diameter expanding portion 31. The opening area that can be increased can be increased.

  Then, a large amount of lubricating oil can be taken into the inner diameter expanded portion 31, and the lubrication of the spline coupling portion 22 between the motor output shaft 5a and the drive shaft 20 of the first sun gear 11a is further improved. can do.

  FIG. 4 schematically shows the main configuration of the spline coupling portion in the vicinity of the spline coupling portion in the third embodiment according to the present invention. The third embodiment has a configuration in which a chamfering process is performed on the peripheral edge on the inner peripheral surface side at the distal end portion of the inner diameter enlarged portion 31 in the second embodiment. Other configurations are the same as those in the second embodiment. Therefore, regarding the same member, the same reference numerals as those used in the first and second embodiments are used, and the description thereof is omitted.

  As shown in FIG. 4, since the peripheral edge on the inner peripheral surface side at the distal end portion of the inner diameter expanding portion 32 is chamfered, the shape at the distal end portion of the inner diameter expanding portion 32 is upward from the lower side. An inclined surface is provided so that the inner diameter becomes smaller toward the side.

  With this configuration, a larger amount of the lubricating oil sprayed upward from the meshing portion 25 is captured in the inner diameter expanding portion 32. That is, in addition to the function of receiving the lubricating oil splashed and bounced from the meshing portion 25 to the drive shaft 20, it can also have a function of directly capturing the lubricating oil sprayed upward from the meshing portion 25. For this reason, even when the first sun gear 11a is rotating at a low speed, the lubricating effect on the spline coupling portion 22 can be maintained well.

  FIG. 5 schematically shows the main configuration of the spline coupling portion in the vicinity of the spline coupling portion in the fourth embodiment according to the present invention. In the fourth embodiment, a thread groove is formed on the inner peripheral surface of the distal end portion of the inner diameter enlarged portion 31 in the second embodiment. Other configurations are the same as those in the second embodiment. Therefore, the description of the same member is omitted by using the same reference numerals as those used in the first to third embodiments.

  As shown in FIG. 5, a screw groove 27 is formed on the inner peripheral surface at the tip of the inner diameter expanding portion 32. With this configuration, the screw groove 27 also rotates with the rotation of the motor output shaft 5a, and the lubricating oil trapped in the inner diameter expanding portion 33 is more reliably moved upward by the conveying action of the screw groove 27. Can do.

  When the direction of rotation of the screw groove 27 is reversed, the lubricating oil trapped in the inner diameter expanding portion 33 is guided downward, and the function of the screw groove 27 is as follows. This acts as a force for releasing the lubricating oil trapped inside. However, from the viewpoint of spline lubrication, if either the forward or reverse rotation frequency occurs at the same level, lubrication to the spline joint 29 will be promoted at any rotation, This is not a problem as lubrication for the spline joint 29.

  The configurations in Examples 1 to 4 can be used as a single configuration, or can be used as a configuration appropriately combined.

  The present invention can apply the technical idea of the present invention to an apparatus or the like to which the technical idea of the present invention can be applied.

It is a whole lineblock diagram of a vertical motor device with a reduction gear. (Example) It is the schematic sectional drawing which showed the principal part of the spline coupling | bond part. Example 1 It is another schematic sectional drawing which showed the principal part of the spline coupling | bond part. (Example 2) It is another schematic sectional drawing which showed the principal part of the spline coupling | bond part. (Example 3) It is another schematic sectional drawing which showed the principal part of the spline coupling | bond part. Example 4 It is the schematic sectional drawing which showed the principal part of the spline coupling | bond part. (Explanation of conventional example) It is a whole lineblock diagram of a vertical motor device with a reduction gear. (Conventional example)

Explanation of symbols

DESCRIPTION OF SYMBOLS 4 ... Vertical motor apparatus with a reduction gear, 5 ... Electric motor, 9 ... Lubricating oil chamber, 10 ... Reduction gear, 11 ... First reduction gear, 12 ... Second reduction gear 13 ... Third reduction gear, 19 ... Motor case, 20 ... Drive shaft, 22 ... Spline coupling, 23 ... Concave spline, 24 ... Convex spline, 25 ... Meshing part, 26 ... bearing, 27 ... thread groove, 30 to 33 ... inner diameter expanding part, 51 ... hydraulic motor device with reduction gear, 52 ... hydraulic motor part, 53 ... Reduction gear mechanism, 54 ... motor housing, 56 ... hydraulic motor, 58 ... motor output shaft, 60 ... bearing, 61 ... sun gear, 62, 63 ... casing, 64 ... Output pinion, 65 ... Ring gear

Claims (4)

A planetary gear mechanism is disposed in the lubricating oil stored in the speed reducer,
A vertical motor device with a speed reducer in which the drive shaft of the sun gear and the output shaft of the vertical motor in the planetary gear mechanism are spline-coupled,
The position of the lower end surface of the output shaft is located inside the motor case that houses the vertical motor in the axial direction of the output shaft ,
Convex splines are formed on the outer peripheral surface of the drive shaft,
A concave spline that engages with the convex spline is formed at the lower end of the output shaft,
An internal diameter expanding portion formed at the tip end portion of the concave spline is disposed above the meshing portion of the sun gear and the planetary gear meshing with the sun gear. Type motor device.   The speed reducer according to claim 1, wherein the inner diameter expanding portion is formed as a concave portion having an inner peripheral surface larger in diameter than a root diameter of the concave spline at a tip end portion of the concave spline. With vertical motor device.   The vertical motor device with a reduction gear according to claim 2, wherein a peripheral edge on the inner peripheral surface side of the recess is chamfered.   4. A vertical motor device with a reduction gear according to claim 2, wherein a thread groove is formed on an inner peripheral surface of the recess.

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