JP2009092109A - Reduction gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a reduction gear that can sufficiently lubricate oil to bearings of planetary gears always immersed in the lubricating oil irrespective of the rotating direction of a carrier and can improve lives of these parts drastically. <P>SOLUTION: In a planetary gear mechanism immersed in the lubricating oil, a planetary gear 20b is supported via a bearing 20g on a planetary shaft 20c provided vertically on the carrier 20d. A vertical hole 21a and a transverse through-hole 21b which intersects the vertical hole 21a and reaches the bearing 20g are formed in the planetary shaft 20c. A catch plate 26 of a barnacle shape is mounted upside down on an upper retainer 20h for preventing the planetary gear 20b from coming off. An oil intake mouth 27 is formed at the central point of the catch plate 26. When the carrier 20d is rotated forward and backward, the lubricating oil taken in from the oil intake mouth 27 can be pumped to the bearing 20g. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a speed reducer in which a planetary gear mechanism that constitutes a speed reducer is arranged in lubricating oil stored in the speed reducer. In particular, the present invention relates to a reduction gear capable of forcibly supplying lubricating oil to a bearing between a planetary gear and a planetary shaft.

  In the planetary gear mechanism, each of the plurality of planetary gears performs a revolving motion for rotating a carrier that rotatably supports each planetary gear in addition to a rotation motion by meshing with the sun gear. That is, the planetary gear mechanism is configured as a mechanism that revolves each planetary shaft around the sun gear around the sun gear while rotating around each planetary shaft while meshing a plurality of planetary gears with the sun gear. ing.

  And when looking at the bearing interposed between the planetary gear and the planetary shaft of the planetary gear, the rotational torque accompanying the rotation movement of the planetary gear is added to the bearing, and along with the revolution movement that rotates the carrier, The carrier-driven reaction force is always received as a radial load from the planetary shaft.

  For this reason, the lubrication between the bearing and the planetary shaft that supports the inner diameter of the bearing often becomes a problem. In particular, when the planetary gear rotates or revolves at high speed, the risk of seizure or the like increases when the lubrication state between the bearing and the planetary shaft deteriorates.

  In order to solve this, various configurations for forcibly supplying lubricating oil between the bearing and the planetary shaft have been proposed in various modes. For example, in the planetary gear structure of an automatic transmission described in Japanese Patent Laid-Open No. 2006-64117, lubricating oil is supplied between the bearing and the planetary shaft while forcibly rotating the planetary shaft (pinion shaft). It has a configuration. That is, the lubricating oil forcedly pumped from the outside flows into the oil passage formed in the carrier, and the lubricating oil from the oil passage collides with the outer diameter portion of the planetary shaft, thereby rotating the planetary shaft. In this configuration, the lubricating oil can be supplied to the bearing by supplying it to the oil passage formed inside the planetary shaft.

  Further, for example, in a lubricating device for a power transmission device described in Japanese Patent Application Laid-Open No. 2007-120519, an axial center oil passage is formed on an axle to which a sun gear is attached, and the shaft oil passage is discharged from an oil pump. The lubricating oil is supplied. The lubricating oil supplied to the shaft center oil passage is supplied to the annular oil guide through a radial hole formed in the axle.

  The annular oil guide is attached to the inner peripheral surface on one end side of the planetary gear, and the lubricating oil supplied to the annular oil guide passes through an oil passage formed inside the planetary shaft, and the planetary gear and the planetary shaft. It is the structure supplied to the bearing interposed between.

  In this way, the lubricating oil forcibly supplied from the outside is supplied to the oil passage formed on the planetary shaft from the passage formed on the drive shaft of the carrier or the sun gear, and is interposed between the planetary gear and the planetary shaft. Various configurations for supplying lubricating oil to mounted bearings have been proposed. In general, in order to flow the lubricating oil in an oil passage formed on the planetary shaft and supply it to the bearing, the lubricating oil can be discharged efficiently. Lubricating oil must be pumped, and for this reason, forced lubrication is used.

  However, on the other hand, there is a speed reducer that cannot adopt a configuration in which forced lubrication is performed on a bearing interposed between the planetary gear and the planetary shaft for structural reasons. For example, in a swivel device for a construction machine equipped with a speed reducer, it is difficult to configure an oil path for forced lubrication in the speed reducer, and an oil path for forced lubrication in the speed reducer is configured. Even if this is possible, the speed reducer itself will be large and will not be practically used.

  For this reason, oil bath lubrication (oil bath system) is generally used in a turning device of a construction machine equipped with a reduction gear, and the bearing between the planetary gear and the planetary shaft and the planetary shaft are always lubricated. It is used in the state immersed in.

  And as a reduction gear which employ | adopted the oil bath system, for example, the turning machine for construction machines shown as patent document 1 below, the hydraulic motor apparatus with the reduction gear for turning disclosed by Unexamined-Japanese-Patent No. 2002-357260, A swivel device disclosed in Japanese Unexamined Patent Application Publication No. 2003-232448, a reduction gear disclosed in Japanese Patent Application Laid-Open No. 2006-220220, and the like have been proposed.

  FIG. 9 shows a partially cutaway longitudinal sectional view of a construction machine turning device as a conventional example of the invention of the present invention. As shown in FIG. 9, the turning speed reducer 51 for construction machinery includes a first stage carrier assembly 52, a planetary mechanism section 55 including a second stage carrier assembly 53 and an internal gear 54. In the first stage carrier assembly 52, the planetary gear 52b meshes with the sun gear 52a, and the planetary gear 52b is rotatably supported by the carrier 52d via the bearing 56 and the pin 52c.

In the second stage carrier assembly 53, the planetary gear 53b meshes with the sun gear 53a, and the planetary gear 53b is rotatably supported by the carrier 53d via a bearing 57 and a pin 53c. In order to lubricate the bearing 56 and the bearing 57, a flow passage 58 and a flow passage 59 are formed in the pin 52c and the pin 53c, respectively.
JP 2001-227623 A

  Although it is the structure common to the thing of the four conventional examples mentioned above as a reduction gear which employ | adopted the oil bath system, the turning apparatus for construction machines shown in patent document 1 is a reduction using a two-stage planetary gear mechanism. It is configured as a machine. The oil level of the lubricating oil is set at a position higher than the meshing surface between the planetary gear and the sun gear in the first stage. In addition, oil holes are formed in the center of the planetary shaft and in a direction orthogonal to the axial direction of the planetary shaft, and these oil holes apply lubricating oil to a bearing interposed between the planetary gear and the planetary shaft. It is configured as an oil passage for supply.

  When schematically showing this common configuration, and representatively showing one planetary gear in the two-stage planetary gear mechanism, a top view of the planetary gear unit can be shown as in FIG. FIG. 11 shows a partial longitudinal sectional view of the planetary gear unit.

  In the example shown in FIGS. 10 and 11, the planetary gear 60b is supported in a cantilevered state by the carrier 60d. The lower end side of the planetary shaft 60c is supported by a carrier 60d, and a retainer 62 that prevents the planetary gear 60b from coming off from the planetary shaft 60c is attached to the upper end side of the planetary shaft 60c. The planetary gear 60b meshes with a sun gear 60a and a ring gear 60e attached to a motor shaft of a drive motor (not shown), and the planetary gear 60 is connected to the planetary gear 63 via a bearing 63 (the needle bearing is illustrated in the illustrated example). It is rotatably supported with respect to the shaft 60c.

  Since the planetary shaft 60c is configured to be fitted with the carrier 60d, there is no restriction on the planetary shaft 60c itself rotating, but the planetary shaft 60c rotates freely. It is not configured as such. Further, the planetary shaft 60c is shown as a member for preventing the planetary gear 60b from coming off in the axial direction, and has a structure fixed by a snap ring 62a and a washer 62b. However, in this specification, the snap ring 62a and the washer 62b are also shown. In addition, the member that prevents the planetary gear 60b from coming off in the axial direction is described using the term retainer.

  A through hole 64 penetrating in the vertical direction is formed at the center of the planetary shaft 60c. A horizontal hole 65 orthogonal to the through hole 64 is formed in the middle of the through hole 64, and the horizontal hole 65 communicates with the bearing 63. As a result, the lubricating oil that has entered the through hole 64 can be supplied to the bearing 63.

  However, the through hole 64 formed at the center of the planetary shaft 60c is arranged in the direction perpendicular to the rotation direction of the carrier 60d, that is, the revolution direction of the planetary gear 60b. For this reason, the force for feeding the lubricating oil into the through hole 64 during the rotation of the carrier 60d cannot be obtained from the rotation of the carrier 60d. Instead, the surrounding lubricating oil can be fed into the through-hole 64 by the action of gravity only when the carrier 60d is stopped.

  When the carrier 60d starts rotating from the stopped state, a part of the lubricating oil accumulated in the through hole 64 can move to the bearing 63 by the action of the centrifugal force. As a result, the bearing 63 can be lubricated by the lubricating oil that has moved to the bearing 63. However, after a part of the lubricating oil stored in the through hole 64 is supplied to the bearing 63, new lubricating oil is not continuously supplied to the bearing 63.

  This is a method of using a turning device mounted on a construction machine. After turning in a certain direction, turn in the opposite direction to return to the original position, and repeat this intermittently. A turning operation is being performed. Using this turning operation, lubricating oil is stored in the through hole 64 in a stopped state after the turning work is performed, and a part of the lubricating oil stored in the through hole is supplied to the bearing during turning. It seems to be the composition.

  In recent years, there has been a demand for a turning device that can perform turning work at a higher speed, and there is a demand to manufacture the turning device at a low cost by reducing the size of the turning motor by decelerating at a high stage. For this reason, the rotation of the sun gear attached to the drive shaft that rotates at high speed is decelerated through the planetary gear that meshes with the sun gear by using a turning motor that rotates at high speed.

  At this time, as the rotation of the planetary gear and the rotation of the carrier during the turning operation in a certain direction, the rotation is performed at a high rotational speed, and more rotational torque and carrier are generated in the bearing and the planetary shaft. Driving reaction force is generated.

  For this reason, in the lubrication method using only the lubricating oil that has entered the through-hole formed in the central portion of the planetary shaft when the carrier is stopped, the occurrence of running out of oil or insufficient lubrication during the turning operation cannot be avoided. As a result, when the rotation of the sun gear rotating at a high speed is decelerated at a high stage, the service life of the bearing and the planetary shaft is significantly reduced.

  In the present invention, these problems can be solved, and the planetary shaft, which is always immersed in the lubricating oil, and the bearing disposed between the planetary gear and the planetary shaft, is related to the direction of the revolution rotation in the planetary gear. Accordingly, it is an object of the present invention to provide a reduction gear which can forcibly perform sufficient lubrication and can dramatically improve the service life of these components.

The object of the present invention can be achieved by the inventions described in claims 1 to 4.
That is, in the speed reducer of the present invention, a planetary gear mechanism is disposed in the lubricating oil stored in the speed reducer, and a flow passage for supplying the lubricating oil to a bearing between the planetary gear and the planetary shaft includes the planetary gear. A speed reducer formed on a shaft,
A retainer for preventing the removal of the planetary gear from the planetary shaft, wherein a catch plate that covers the end of the flow passage that opens at the shaft end of the planetary shaft through a gap has a spire portion protruding toward the center. A surface of the spire portion that generates a flow of lubricating oil along the surface during the revolution movement of the planetary gear is formed as an inclined surface inclined with respect to the axial direction of the planetary shaft, The most important feature is that an oil intake port that communicates with the spier is formed at the top of the spire portion.

In the present invention, in the above-described invention, the main feature is that the shape of the catch plate and the shape of the oil intake port are specified.
Further, in the present invention, in the above-described invention, a configuration in which the catch plates are attached to both end portions of the planetary shaft is a main feature.

  In the present invention, a catch plate having a steeple protruding toward the center is attached to a retainer that prevents the planetary gear from coming off from the planetary shaft. In addition, an oil intake port is formed at the top of the spire portion and communicates with the flow passage formed in the planetary shaft. Further, the surface of the spire portion that generates a flow of lubricating oil along the surface during the revolution movement of the planetary gear is formed as an inclined surface that is inclined with respect to the axial direction of the planetary shaft.

  With this configuration, the lubricant can be taken in from the oil intake port formed in the spire portion of the catch plate regardless of the direction of rotation of the carrier, that is, the revolving motion of the planetary gear in any direction. .

  As a flow of the lubricating oil generated when the carrier rotates, a flow along the surface of the surface forming the spire portion is generated. And as a flow of lubricating oil, it will change from the state of a substantially straight flow along the surface of an inclined surface to the flow which turns an angle in the top part of a spire part. Due to the vortex generated by the flow around the corner, the lubricating oil is introduced into the oil intake port formed at the top of the spire, and the lubricating oil can be taken into the internal space of the catch plate.

  Then, the flow around the corner at the top of the spire portion is a flow obtained regardless of whether the carrier rotates in the forward or reverse direction. Therefore, the lubricating oil can always be taken into the catch plate from the oil intake port regardless of which direction the carrier rotates, that is, the revolution direction of the planetary gear. The lubricating oil taken into the catch plate is pumped through the flow passage formed in the planetary shaft, and can lubricate the bearing between the planetary gear and the planetary shaft.

  By forming the shape of the end of the flow passage opened at the shaft end of the planetary shaft into a mortar shape that expands toward the oil intake port side, the lubricating oil taken into the catch plate can be efficiently flowed. Can be pumped in. Accordingly, the lubricating oil can be forcibly supplied to the bearing between the planetary gear and the planetary shaft regardless of the rotation direction of the carrier.

The catch plate can be configured, for example, by drawing a sheet metal member into a barnacle shape and providing an opening at the top. The catch plate can be attached to the retainer by fixing means such as welding or bolt fixing.
Alternatively, two pairs of sheet metal members are prepared, each set of sheet metal members is bent, and the bent side surface portion and the other set of bent side surface portions are welded and fixed to each other so that a space is formed inside. It can also be configured in an obelisk shape having a portion. The shape at the top of the obelisk shape can be configured as a rectangular opening. The obelisk-shaped catch plate can also be attached to the retainer by fixing means such as welding or bolt fixing.

  In this way, the structure for supplying the lubricating oil to the bearing is configured as a speed reducer using a planetary gear mechanism, so even if the planetary gear rotates and revolves at high speed, it can revolve in either direction. Even if this is done, it is possible to prevent running out of oil in the bearing, and the bearing and the planetary shaft can always be used in good condition. Therefore, the reliability of the bearing and the planetary shaft can be greatly improved, and the life of these members can be greatly improved.

  Preferred embodiments of the present invention will be specifically described below with reference to the accompanying drawings. As the configuration of the speed reducer of the present invention, in addition to the configuration of the speed reducer used in the electric swivel device described below, for example, even if the speed reducer is combined with a hydraulic motor, an oil bath system is adopted. The present invention can be effectively applied to various reduction gears. 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 an electric swing device used for a construction machine according to an embodiment of the present invention. FIG. 2 and FIG. 3 are schematic views showing the main configuration of a flow passage that supplies lubricating oil to a bearing disposed between a planetary gear and a planetary shaft, which is a characteristic configuration of the present invention. As shown in FIG. 1, the electric turning device 4 includes an electric motor 5 and a speed reducer 10.

  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.

  On the lower side of the electric motor 5, a speed reducer 10 that decelerates the rotation of the motor drive 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 running 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.

  And the output pinion 14 rotated by the output from the third reduction gear 13 is meshed 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 turning body 2 can turn 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, but Japanese Patent Laid-Open No. 2006-220220 exemplified in the background art as an oil bath type speed reducer discloses a support structure for both-end support. ing.

  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 water cooling jacket 19.

  The first speed reducer 11 is configured to decelerate the rotation of the first sun gear 11a provided on the motor drive shaft 5a, 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 via a first bearing 11g 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. The detailed configuration will be described later with reference to FIGS. 2 and 3. The first retainer 11h has a catch plate (not shown) for supplying the lubricating oil in the lubricating oil chamber 9 to the first bearing 11g. Installed.

Since the first retainer 11h is attached to the first planetary shaft 11c, the upper first retainer 11h is also restricted from rotating in the rotation direction with respect to 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 obstructs the rotation of 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 via a second bearing 12g between the second planetary gear 12b and 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. The detailed structure will be described later with reference to FIGS. 2 and 3. The second retainer 12h has a catch plate (not shown) for supplying the lubricating oil in the lubricating oil chamber 9 to the second bearing 12g. Installed.

Since the second retainer 12h is configured to be attached to the second planetary shaft 12c, the upper second retainer 12h is also restricted from rotating in the rotation direction with respect to 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 obstructs the second planetary gear 12b in a freely rotating manner. 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 via a third bearing 13g between the third planetary gear 13b and 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. The detailed configuration will be described later with reference to FIGS. 2 and 3. The third retainer 13h has a catch plate (not shown) for supplying the lubricating oil in the lubricating oil chamber 9 to the third bearing 13g. Installed.

Since the third retainer 13h is configured to be attached to the third planetary shaft 13c, the upper third retainer 13h is also restricted from rotating in the rotation direction with respect to 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 revolving motion of the third planetary gear 13b can be taken out as the rotation of the third carrier 13d that obstructs the rotation of 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, the tip portion of the motor drive shaft 5a, the tip portion of the first drive shaft 11f, and the tip portion of the second drive shaft 12f, respectively. Alternatively, the tip of the third drive shaft 13f can be processed into a gear shape and formed integrally with the respective shafts 5a, 11f, 12f, 13f. Moreover, it can also be set as the structure fitted with each shaft 5a, 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. That is, the mechanical brake 15 is a brake piston 16 that is controlled to move up and down the brake disk 15b joined to the first drive shaft 11f via the brake pad 15, 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, with reference to FIG. 2 and FIG. 3, a description will be given of a flow path configuration for supplying lubricating oil to a bearing disposed between the planetary gear and the planetary shaft, which is a characteristic configuration of the present invention. 2 and 3, the configurations of the bearings and the flow passages in the first reduction gear 11 to the third reduction gear 13 are shown as common configurations, and deformed so that the characteristic configuration becomes clear. This is shown in the configuration.

In FIG. 2 and FIG. 3, the member code | symbol which used the sun gear 20a, the planetary gear 20b, the planetary shaft 20c, the carrier 20d, the ring gear 20e, the bearing 20g, and the retainer 20h is used. Regarding the alphabets attached to these member codes, the same alphabets as the alphabets attached to the members corresponding to the members described above in the first reduction gear 11 to the third reduction gear 13 are used. By using a common alphabet, the members of the first speed reducer 11 to the third speed reducer 13 are representatively shown in FIG. 2 and FIG.
FIG. 2 shows a top view of the main part centering on the planetary gear 20b, and FIG. 3 shows a longitudinal sectional view of the main part centering on the planetary gear 20b.

  As shown in FIGS. 2 and 3, three planetary shafts 20c that support the three planetary gears 20b rotatably via bearings 20g are supported on the carrier 20d. As the bearing 20g, a known radial bearing such as a needle bearing can be used. A thrust washer 23 is interposed between the lower end side of each planetary gear 20b and the carrier 20d, and a pair of retainers 20h for preventing the planetary gear 20b from being detached are attached to the upper and lower ends of the planetary shaft 20c. Yes.

  A catch plate 26 is attached to the upper retainer 20h, and the catch plate 26 having a barnacle shape is attached to the upper retainer 20h via bolts 30 in a face-down state. An oil intake port 27 is formed at the top of the spire portion 26a at the center of the catch plate 26 having a barnacle shape. As a method of attaching the catch plate 26 to the retainer 20h, an appropriate fixing method such as welding or a fixing method using a bolt 30 can be used.

  As the catch plate 26, for example, a sheet metal member may be drawn into a barnacle shape to form a spire portion 26a, and a circular oil intake port 27 may be provided at the top of the spire portion 26a. In addition, a disc-shaped flange portion 26b can be formed around the spire portion 26a. In the disc-shaped sheet metal member, the steeple portion 26a and the flange portion 26b can be formed simultaneously by performing a barnacle-shaped drawing process on the central portion side excluding the outer peripheral edge side. Bolt insertion holes for inserting the bolts 30 are formed in the flange portion 26b.

  Each planetary shaft 20c is formed with a vertical hole 21a in the vertical direction and a through horizontal hole 21b that intersects the vertical hole 21a and reaches the bearing 20g. A flow passage 21 for supplying lubricating oil to the bearings 20g is formed by the vertical holes 21a and the through horizontal holes 21b formed in each planetary shaft 20c.

  The vertical hole 21a formed in the shaft portion of the planetary shaft 20c is formed as a vertical hole opened at the shaft end of the planetary shaft 20c, and the catch plate 26 is opened at the shaft end of the planetary shaft 20c on the inner surface side of the spire portion 26a. The opening 21c of the vertical hole 21a can be entirely covered with a gap. The opening 21c of the vertical hole 21a is formed in a mortar shape that expands toward the oil intake port 27 side, and is configured to easily introduce the lubricating oil taken into the catch plate 26 into the vertical hole 21a.

  The vertical hole 21a is preferably not formed as a through hole penetrating in the vertical direction of the planetary shaft 20c but deeper than the formation position of the through horizontal hole 21b and formed at the lower end side as a stop hole. The lubricating oil supplied to the bearing 20g is discharged to the outside of the planetary shaft 20c from a radial groove formed in advance in the thrust washer 23 that supports the lower portion of the planetary gear 20b.

  Since each planetary shaft 20c is supported while being engaged with the carrier 20d, the rotation of each planetary shaft 20c in the rotation direction is restricted. The upper retainer 20h is composed of a snap ring 25a and a washer 25b. However, the retainer 20h is configured as a retainer that can be attached to the planetary shaft 20c by other configurations such as screw fixing to the planetary shaft 20c. You can also

  Since the washer 25b is sandwiched and attached between the snap ring 25a and the planetary shaft 20c, the upper retainer 20h is also restricted from rotating in the rotation direction. If the upper retainer 20h is worried about slippage due to relative rotation with the planetary shaft 20c, the upper retainer 20h slips by adopting a configuration such as a key connection so that no phase shift occurs between the planetary shafts 20c. Can also be prevented.

  In this way, since the steeple portion 26a is formed in the center of the barnacle-shaped catch plate 26 in which the oil intake port 27 is turned down, the oil intake port 27 is lubricated regardless of the revolution direction of the planetary gear 20b. Oil can be taken in, and lubricating oil can be forcibly taken into the catch plate 26.

  That is, when the carrier 20d rotates, the lubricating oil flows substantially linearly along the surface of the spire portion 26a, and changes to a flow around the corner at the top of the spire portion 26a. Due to the vortex generated by the flow around the corner, the lubricating oil is introduced into the oil intake port 27 formed at the top of the spire portion 26a, and the lubricating oil can be taken into the internal space of the catch plate 26. .

  Therefore, while the planetary gear 20b is rotating in the revolution direction, the lubricating oil taken in from the oil take-in port 27 can be forcibly supplied to the bearing 20g. Further, when the revolution of the planetary gear 20b is stopped, the lubricating oil in the lubricating oil chamber 9 shown in FIG. 1 can be caused to flow into the flow passage 21 from the oil intake port 27 by the action of gravity. .

  FIG. 4 shows a longitudinal sectional view of a flow passage configuration and the like in another embodiment according to the present invention. In the first embodiment, the catch plate 26 is attached to the upper retainer 20h. In the second embodiment, the catch plate 28 is attached to the lower retainer 20h. The configuration of the catch plate 28 is the same as that of the catch plate 26, and an oil intake port 29 is formed in the barnacle-shaped spire portion 28a.

  The catch plate 28 is configured to be attached to the lower retainer 20h via a bolt 30 inserted into a bolt insertion hole (not shown) formed in the flange portion 28b of the catch plate 28. The vertical hole 22 formed in the planetary shaft 20c is formed as a vertical hole 22 penetrating in the vertical direction of the planetary shaft 20c. In addition, the lower end portion of the planetary shaft 20c is also configured in a mortar shape that expands toward the oil intake port 29 side in order to make the opening portion of the vertical hole 22 large.

  Other configurations are the same as those in the first embodiment. Therefore, about the structure similar to Example 1, the description is abbreviate | omitted by using the same member code | symbol as the member code | symbol used in Example 1. FIG.

  According to the second embodiment, not only the upper retainer 20h but also the lower retainer 20h is provided with the catch plate 28 having the same structure as the catch plate 26 provided on the upper retainer 20h. As a result, the lubricating oil can be taken in from the oil intake port 29 provided in the catch plate 28, and the oil intake effect of the first embodiment can be doubled. As described in the first embodiment, the lubricating oil supplied to the bearing 20g is discharged to the outside of the planetary shaft 20c from a radial groove formed in advance in the thrust washer 23 that supports the lower portion of the planetary gear 20b. It will be.

  When there is a difference between the amount of lubricating oil taken in from the oil intake port 27 on the upper retainer 20h side and the amount of lubricating oil taken in from the oil intake port 29 on the lower retainer 20h side, the oil intake By adjusting the opening diameter of the port 27 or the opening diameter of the oil intake port 29, it is also possible to adjust the intake amount in each of them to be substantially the same. Alternatively, the lubricating oil intake amount from the oil intake port 29 may be configured to be slightly larger than the lubricating oil intake amount from the oil intake port 27.

  5 to 8 show the structure of the catch plate in another embodiment according to the present invention. FIG. 5 shows an overall perspective view of the catch plate 32 in the third embodiment, and FIG. 6 shows a top view of the catch plate 32. 7 shows a side view from the I direction in FIG. 5, and FIG. 8 shows a side view from the II direction in FIG.

  In Examples 1 and 2, the catch plates 26 and 28 were configured in a barnacle shape with the inner side cut out. On the other hand, in Example 3, the catch plate 32 is configured in an obelisk shape that is hollowed out inside. For this reason, in Examples 1 and 2, the shape of the oil intake ports 27 and 28 is formed in a circular shape, whereas in Example 3, the shape of the oil intake port 35 is formed in a rectangular shape. .

  Other configurations are the same as those in the first and second embodiments. Therefore, about the structure similar to Example 1, 2, the description is abbreviate | omitted by using the same member code | symbol as the member code | symbol used in Example 1,2. Further, the longitudinal sectional view of the catch plate 32 of the third embodiment attached to the retainer 20h is the same as the configuration shown in FIG.

  As shown in FIGS. 5 and 6, the catch plate 32 has a first member 33 made of a pair of sheet metal members and a second member 34 made of a pair of sheet metal members. The sheet metal member is bent, and the side surface portion of the bent first member 33 and the side surface portion of the bent second member 34 are fixed to each other by fillet welding from the inside, and an obelisk shape having a space portion inside is configured. .

  The first member 33 includes a rectangular first spire portion 33a (see FIG. 8) by bending a sheet metal member and a first flange portion 33b having an outer peripheral shape that matches the outer peripheral shape of the retainer 20h. Yes. The pair of first spire portions 33a constitute opposite side surfaces of the spire portion of the catch plate 32, and a bolt insertion hole 36 into which the bolt 30 for fixing the catch plate 32 to the retainer 20h is inserted into the first flange portion 33b. Is formed.

  The second member 34 includes a trapezoidal second spire portion 34a (see FIG. 7) by bending a sheet metal member and a second flange portion 34b having an outer peripheral shape that matches the outer peripheral shape of the retainer 20h. Yes. The pair of second spire portions 34a constitutes the remaining both side surfaces constituted by the first flange portion 33b of the spire portion of the catch plate 32, and the bolts that fix the catch plate 32 to the retainer 20h are formed on the second flange portion 34b. A bolt insertion hole 36 for inserting 30 is formed.

  An obelisk shape can be formed by performing fillet welding from both sides of both side surface portions of the first spire portion 33a and both side surface portions of the second spire portion 34a. An oil intake port 35 having a rectangular shape is formed at the top of the obelisk shape surrounded by the first spire portion 33a and the second spire portion 34a. The side surface portion of the first flange portion 33b and the side surface portion of the second flange portion 34b can be kept in contact with each other. Further, as required, the side surface portion of the first flange portion 33b and the side surface portion of the second flange portion 34b can be bonded with an adhesive or can be bonded with an adhesive tape.

  Each of the pair of first spire portions 33a is arranged and configured as a surface that generates a flow of lubricating oil along the surface when the carrier 20d rotates. That is, when the carrier 20d rotates, the lubricating oil flows substantially linearly along the surface of one of the first spire portions 33a, and changes to a flow around the corner at the top of the first spire portion 33a. Due to the vortex generated by the flow around the corner, the lubricating oil is introduced into the oil intake port 35 formed at the top of the spire, and the lubricating oil can be taken into the internal space of the catch plate 32.

  In the illustrated example, in particular, as shown in FIGS. 7 and 8, the first spire portion 33a is configured as an inclined surface and the second spire portion 34a is configured as a vertical surface, but with respect to the second spire portion 34a. It can also be configured with a slight inclination. Further, when the carrier 20d rotates, the first spire portion 33a is arranged so that the surface of the first spire portion 33a is orthogonal to the rotation direction of the carrier 20d. It can also be configured to be narrower than the lateral width of the second spire portion 34a on the gear 20e side.

  The obelisk-shaped catch plate 32 can be provided not only on the upper retainer 20h but also on the lower retainer 20h as in the second embodiment. In this case, as described in the second embodiment, it is necessary to form the flow passage 21 penetrating in the vertical direction of the planetary shaft 20c.

  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 block diagram of an electric swivel device. (Example) It is a top view of the principal part centering on a planetary gear. (Example 1) It is a longitudinal cross-sectional view of the principal part centering on a planetary gear. (Example 1) It is a longitudinal cross-sectional view of the principal part centering on a planetary gear. (Example 2) It is a perspective view of a catch plate. (Example 3) It is a top view of a catch plate. (Example 3) It is a side view from the I direction in FIG. (Example 3) It is a side view from the II direction in FIG. (Example 3) It is a partial notch longitudinal cross-sectional view of the turning machine for construction machines. (Conventional example) It is a top view of the principal part centering on a planetary gear. (Explanation of conventional example) It is a longitudinal cross-sectional view of the principal part centering on a planetary gear. (Explanation of conventional example)

Explanation of symbols

DESCRIPTION OF SYMBOLS 4 ... Electric turning apparatus, 5 ... Electric motor, 9 ... Lubricating oil chamber, 10 ... Reduction gear, 11 ... First reduction gear, 12 ... Second reduction gear, 13. .. Third reduction gear, 14 ... Output pinion, 15 ... Mechanical brake, 20a ... Sun gear, 20b ... Planet gear, 20c ... Planet shaft, 20d ... Carrier, 20e .... Ring gear, 20g ... bearing, 20h ... retainer, 21 ... flow passage, 21a ... vertical hole, 21b ... through hole, 21c ... opening, 22 ... vertical Hole, 22a, 22b ... opening, 25a ... snap ring, 25b ... washer, 26 ... catch plate, 27 ... oil intake port, 28 ... catch plate, 29 ... Oil intake port, 32 ... catch plate, 33 ... One member 34 ... Second member 35 ... Oil intake port 51 ... Swivel speed reducer for construction machine 52 ... First stage carrier assembly 53 ... Second stage carrier Assembly, 54 ... Internal gear, 55 ... Planetary mechanism, 56, 57 ... Bearing, 58, 59 ... Flow passage, 60a ... Sun gear, 60b ... Planetary gear, 60c -Planetary shaft, 60d ... carrier, 60e ... ring gear, 62 ... retainer, 63 ... bearing, 64 ... through hole, 65 ... side hole.

Claims (4)

A planetary gear mechanism is disposed in the lubricating oil stored in the speed reducer,
A flow passage for supplying the lubricating oil to a bearing between the planetary gear and the planetary shaft is a speed reducer formed on the planetary shaft,
A retainer for preventing the removal of the planetary gear from the planetary shaft, wherein a catch plate that covers the end of the flow passage that opens at the shaft end of the planetary shaft through a gap has a spire portion protruding toward the center. Mounted on and
During the revolving motion of the planetary gear, the surface of the spire portion that generates a flow of lubricating oil along the surface is formed as an inclined surface inclined with respect to the axial direction of the planetary shaft,
The speed reducer, wherein an oil intake port formed in communication with the flow passage is formed at a top portion of the spire portion. The catch plate is formed in a barnacle shape hollowed out inside,
The catch plate is attached to the retainer in a state where the barnacle-shaped spire portion is projected,
The speed reducer according to claim 1, wherein the oil intake port is formed in a circular shape at the top of the barnacle shape. The catch plate is formed into an obelisk shape with a hollow inside,
The catch plate is attached to the retainer in a state in which the obelisk-shaped spire is projected,
The speed reducer according to claim 1, wherein the oil intake port is formed in a rectangular shape at the top of the obelisk shape.   The speed reducer according to any one of claims 1 to 3, wherein the catch plates are attached to retainers respectively disposed at both ends of the planetary shaft.

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