JP2009079627A - Reduction gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a reduction gear which can perform sufficient lubrication with respect to a bearing of a planetary gear dipped into lubricating oil, moreover improve the life of the components extremely. <P>SOLUTION: A planetary gear mechanism dipped into the lubricating oil has a planetary gear 20b supported with a planetary shaft 20c perpendicularly arranged in a carrier 20d through a bearing 20g. The planetary shaft 20c has a vertical hole 21a and a through side hole 21b which intersects the vertical hole 21a and reaches the bearing 20g, and a retainer 20h preventing the planetary gear 20b from coming-out has an oil taking-in opening 22 communicating with the vertical hole 21a. The oil taking-in opening 22 is formed as an opening facing toward a rotary direction of the carrier 20d, and when the carrier 20 rotates, the lubricating oil sent from the oil taking-in opening 22 can be supplied 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 Application 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.

  As a reduction gear that employs an oil bath system, for example, a swing device for construction machinery shown as Patent Document 1 below, a hydraulic motor device with a reduction gear for turning disclosed in Japanese Patent Laid-Open 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. 14 is a partially cutaway longitudinal sectional view of a construction machine turning device shown in FIG. As shown in FIG. 14, the turning speed reducer 51 for a construction machine 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 this common configuration is schematically shown, when one planetary gear in a two-stage planetary gear mechanism is shown as a representative, a top view of the planetary gear unit can be shown as in FIG. FIG. 16 shows a partial longitudinal sectional view of the gear portion.
In the example shown in FIGS. 15 and 16, the planetary gear 60b is supported in a cantilevered state by a 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 sufficient lubrication is forcibly applied to the planetary shaft, the planetary gear, and the bearing arranged between the planetary shaft that are always immersed in the lubricating oil. In addition, an object of the present invention is to provide a speed reducer that can dramatically improve the life of these components.

The object of the present invention can be achieved by the inventions described in claims 1 to 5.
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,
The main feature is that the oil intake port communicating with the flow passage is always formed as an opening facing one revolving direction of the planetary gear.

In the present invention, the main feature of the above-described invention is that the member in which the oil intake port is formed is specified by a plurality of members.
Furthermore, in the present invention, in the above-described invention, the main feature is that the position where the oil intake port is formed is specified as the position with respect to the part of the planetary shaft.

  In the present invention, since the oil intake port communicating with the flow passage formed in the planetary shaft is always formed as an opening facing one revolution direction in the planetary gear, the planetary gear in one revolution direction is arranged. With the rotation, that is, the rotation of the carrier in one direction, the lubricating oil in the speed reducer can be taken from the oil intake port.

  Lubricating oil fed into the flow passage from the oil intake port will be pumped to the bearing through the flow passage, and forcibly lubricates the bearing as long as the carrier rotates in one direction. be able to. Even when the rotation of the carrier is stopped, the oil intake port is arranged in the lubricating oil in the speed reducer, so that the flow path is filled with lubricating oil by the action of gravity. I can leave.

  Since the oil intake port is formed as an opening that faces one of the revolving directions of the planetary gear, the planetary gear is a planetary gear that rotates in both forward and reverse revolving directions. When the gear rotates in the other revolution direction, it is difficult to take in the lubricating oil from the oil intake port. However, in such a forward and reverse speed reducer, there is a stop period in which the revolution of the planetary gear is stopped until the revolution direction of the planetary gear is changed. During the stop period, the lubricating oil can be filled in the flow path by the action of gravity.

  Thus, when the planetary gear is rotating in the other revolution direction, the lubricating oil filled in the flow passage can be used during the stop period. Moreover, even when the planetary gear is revolving and rotating in the other direction, the lubricating oil drawn into the flow passage or the bearing when the planetary gear is revolving and rotating in one direction can be used for lubricating the bearing. it can. Therefore, the lubrication state of the bearing can be improved to a lubrication level that causes no problem in practice.

Further, by forming the oil intake port as a large mortar-shaped opening hole, a large amount of lubricating oil can be fed into the flow passage at a time.
Thus, even if the planetary gear rotates and revolves at a high speed, it is possible to prevent the bearing from running out of oil, 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 showing an overall configuration diagram of an electric swing device used in a construction machine according to an embodiment of the present invention. 2 to 4 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.

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.

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.

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 FIGS. 2 to 4, a description will be given of a flow path configuration for supplying lubricating oil to a bearing disposed between a planetary gear and a planetary shaft, which is a characteristic configuration of the present invention. In FIGS. 2 to 4, the configurations of the bearings, the flow passages, and the like 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 FIGS. 2 to 4, member codes such as 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 are 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 FIGS. 2 to 4.

  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. FIG. 4 shows a side 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 are attached to the upper and lower ends of the planetary shaft 20c.

  Each planetary shaft 20c is formed with a vertical hole 21a in the vertical direction, a through horizontal hole 21b that intersects the vertical hole 21a and reaches the bearing 20g, and a horizontal hole 21c that connects the oil intake port 22 and the vertical hole 21a. The vertical hole 21a, the through horizontal hole 21b, and the horizontal hole 21c formed in each planetary shaft 20c constitute a flow passage 21 for supplying lubricating oil to the bearing 20g.

As shown in FIG. 4, the oil intake port 22 is formed in a side surface portion of the upper retainer 20h, and is formed as an opening facing the revolution direction of the planetary gear 20b indicated by an arrow in FIG.
When the revolution direction of the planetary gear 20b is opposite to the arrow shown in FIG. 2, the oil intake port 22 can be formed as an opening facing the opposite direction to the arrow shown in FIG.

  The shape of the oil intake port 22 can be formed as a large mortar-shaped opening hole. With this configuration, a large amount of lubricating oil can be fed into the flow passage 21 from the oil intake port 22 at a time. Therefore, even when the speed reducer according to the present invention is used for a revolving device that frequently rotates forward and backward, a large amount of lubricating oil is fed into the flow passage 21 from the oil intake port 22 during normal rotation, and lubricated to the bearing 20g. Oil can be supplied.

  In addition, it becomes difficult to feed the lubricating oil from the oil intake port 22 when rotating in the reverse direction, but it flows when the lubricating oil that has been fed into the flow passage 21 or the bearing 20g during rotation in the forward direction or when the swiveling device stops turning. Lubricating oil drawn into the passage 21 by the action of gravity can be used for lubricating the bearing 20g. Therefore, even in a revolving device that rotates forward and reverse, it is possible to maintain a lubrication level that is not problematic in practice.

  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. A part of the lubricating oil fed from the oil intake port 22 escapes from the opening of the vertical hole 21a, but moves downward in the vertical hole 21a, and the lubricating oil moves from the through hole 21b to the bearing 20g. Can be supplied. 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.

By arranging the oil intake port 22 so as to be fixed at a phase that matches the notch portion provided in the upper retainer 20h, it is possible to have an arrangement configuration that does not hinder the inflow of the lubricating oil.
At this time, since each planetary shaft 20c is supported in a state of 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.

  FIG. 5 shows a longitudinal sectional view of the flow passage configuration and the like in the second embodiment according to the present invention. Similar to the configuration of FIG. 3 in the first embodiment, FIG. 5 also shows the configuration of the bearings and flow passages in the first reduction gear 11 to the third reduction gear 13 shown in FIG. 1 as a common configuration. It is shown in a schematic diagram deformed so that the characteristic configuration becomes clear. As in the description in FIG. 3, the alphabet added at the end of the member code of each constituent member is attached to each member corresponding to the member described above in the first reduction gear 11 to the third reduction gear 13. The same alphabet is used.

  As shown in FIG. 5, in the second embodiment, the vertical hole 27a of the flow passage 21 is configured to penetrate in the vertical direction of the planetary shaft 20c. An oil intake port 28 is also formed in the lower retainer 20h. The oil intake port 28 communicates with the vertical hole 27a through the horizontal hole 27c. The oil intake port 28 is formed in the lower retainer 20h as an opening facing one revolving direction of the planetary gear 20b. The configuration of the oil intake port 28 formed in the lower retainer 20h can be the same as the configuration of the oil intake port 22 formed in the upper retainer 20h.

  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.

  With the configuration of the second embodiment, the lubricating oil can be fed from both the upper and lower sides of the planetary shaft 20c, and the flow rate of the lubricating oil flowing through the flow passage 21 can be increased. 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.

  FIG. 6 shows a longitudinal sectional view of the flow passage configuration and the like in the third embodiment according to the present invention. Similar to the configuration of FIG. 3 in the first embodiment, FIG. 6 also shows the configuration of the bearings and flow passages in the first reduction gear 11 to the third reduction gear 13 shown in FIG. 1 as a common configuration. It is shown in a schematic diagram deformed so that the characteristic configuration becomes clear. As in the description in FIG. 3, the alphabet added at the end of the member code of each constituent member is attached to each member corresponding to the member described above in the first reduction gear 11 to the third reduction gear 13. The same alphabet is used.

  In the first embodiment, as shown in FIG. 3, the vertical hole 21a remains open at the top, whereas in the third embodiment, the upper portion of the vertical hole 21a is sealed with a plug 31 as shown in FIG. It becomes the composition. 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.

  With the configuration in which the upper portion of the vertical hole 21a is sealed with the plug 31, the lubricating oil fed from the oil intake port 22 can be efficiently supplied to the bearing 20g. Moreover, as a structure which provides the plug 31, it can also comprise with respect to the opening in the both ends of the vertical hole 27a in Example 2, and the both ends of the vertical hole 27a can be made into a sealing state.

  With this configuration, the lubricating oil fed from the oil intake port 22 and the oil intake port 28 can be supplied to the bearing 20g without leaking. 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.

  FIG. 7 shows a top view of the flow passage configuration and the like in the fourth embodiment according to the present invention, and FIG. 8 shows a longitudinal sectional view of the flow passage configuration and the like in the fourth embodiment. 2 and FIG. 3 in the first embodiment, FIG. 7 and FIG. 8 also have common configurations such as bearings and flow paths in the first reduction gear 11 to the third reduction gear 13 shown in FIG. It is shown as a schematic diagram deformed so that the characteristic configuration becomes clear. Similarly to the description in FIGS. 2 and 3, the alphabet added at the end of the member code of each constituent member is attached to each member corresponding to the above-described member in the first reduction gear 11 to the third reduction gear 13. The same alphabet is used.

  In the first to third embodiments, the oil intake ports 22 and 28 are formed in the retainer 20h. However, in the fourth embodiment, the oil intake port 33 is formed on the side surface of the carrier 20d. Further, a vertical hole 34a connected to the through horizontal hole 21b communicating with the bearing 20g is formed in the lower part of the planetary shaft 20c, and the horizontal hole 34c connecting the vertical hole 34a and the oil intake port 33 is formed with the carrier 20d and the planetary shaft 20c. It is formed in the lower part. The lower end opening of the vertical hole 34a is sealed with a plug 31.

  In addition, by forming the opening of the oil intake port 33 in a direction substantially orthogonal to the tangential direction of the carrier 20d in a plan view, the lubricating oil is removed from the oil intake port 33 when the carrier 20d rotates. A large amount can be sent.

  Other configurations are the same as those in the first embodiment. Therefore, about the structure similar to Example 1- Example 3, the description is abbreviate | omitted by using the same member code | symbol as the member code | symbol used in Example 1- Example 3. FIG.

  In the fourth embodiment, the lubricating oil fed from the oil intake port 33 formed on the side surface portion of the carrier 20d moves upward in the vertical hole 34a provided at the center of the planetary shaft 20c, and the center of the planetary shaft 20c. It is configured to reach the bearing 20g through the through horizontal hole 21b formed in the portion. For this reason, unlike the case of the first embodiment, the lubricating oil fed from the oil intake port 33 is once moved upward, so that the opening on the lower end side is the shape of the vertical hole 34a. It is desirable that the structure sealed with the plug 31 shown in FIG.

  Further, in this configuration, when the planetary gear 20b revolves in one direction, the lubricating oil is taken in from the oil take-in port 33. However, since the oil take-in port 33 is formed on the side surface of the carrier 20d, the oil take-in The mouth 33 can be configured as a large mortar-shaped opening. In addition, in order to increase the amount of lubricating oil fed from the oil intake port 33, the portion where the oil intake port 33 is formed in the carrier 20d is cut out in the radial direction. By configuring in this way, the oil intake port 33 can be configured as a larger mortar-shaped opening compared to the case where the oil intake port is formed in the retainer 20h in the first to third embodiments.

  Therefore, it becomes possible to feed a large amount of lubricating oil from the oil intake port 33 at a time, and the planetary gear 20b in the direction opposite to the opening direction of the oil intake port 33 even in the use of a swiveling device that frequently rotates forward and reverse. Even if the planetary gear 20b is revolved in the opening direction of the oil intake port 33, the bearing 20g can be lubricated with the remaining oil stored in the flow passage 21 and the bearing 20g. . For this reason, the lubrication state of the bearing 20g can be improved to a lubrication level that causes no problem in practice.

  Alternatively, the oil intake port 33 may be formed in the side surface portion of the carrier 20d, and the horizontal hole 34c formed in the carrier 20d may be formed as a horizontal hole inclined obliquely downward as indicated by a solid line in FIG. Furthermore, as shown by the dotted line in FIG. 9, the oil intake port 33 can be formed on the bottom surface of the carrier 20d. 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.

  FIG. 10 shows a longitudinal sectional view of the flow passage configuration and the like in the fifth embodiment according to the present invention. In the fourth embodiment, the oil intake port 33 is provided in the carrier 20d, but in the fifth embodiment, the oil intake port 22 is also formed in the upper retainer 20h. Since the oil retainer 22 is also formed in the upper retainer 20h, the amount of lubricating oil fed into the flow passage 21 can be increased.

  Other configurations are the same as those in the fourth embodiment. Therefore, about the structure similar to Example 4, the description is abbreviate | omitted by using the same member code | symbol as the member code | symbol used in Example 4. FIG.

  The vertical hole 34a can be formed as a hole penetrating in the vertical direction of the planetary shaft 20c, or can be formed as a hole formed from one end of the planetary shaft 20c. Regardless of the configuration in which the vertical hole 34a is formed, it is desirable that the opening at the axial end of the vertical hole 34a be sealed with a plug 31 or the like.

  Further, 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. Will be.

  When the flow rate of the lubricating oil fed from the oil intake port 33 provided in the carrier 20d is larger than the flow rate of the lubricating oil sent from the oil intake port 22 provided in the upper retainer 20h, the oil intake port 33 The hole diameter from the through hole 21b to the through hole 21b may be larger than the hole diameter from the oil inlet 22 to the through hole 21b.

  As a result, the lubricating oil fed from the oil intake port 33 can be prevented from being discharged to the outside from the oil intake port 22, and the lubricating oil taken in from the oil intake port 33 and the oil intake port 22 can be removed. Each of them can be fed to the bearing 20g in a combined state.

  FIG. 11 shows a top view of the flow path configuration and the like in the sixth embodiment according to the present invention, and FIG. 12 shows a longitudinal sectional view of the flow path configuration and the like in the sixth embodiment. Similar to the configurations of FIGS. 2 and 3 in the first embodiment, the configurations of the bearings and flow passages in the first reduction gear 11 to the third reduction gear 13 shown in FIG. It is shown as, and shows a deformed state so that the characteristic configuration becomes clear. Similarly to the description in FIGS. 2 and 3, the alphabet added at the end of the member code of each constituent member is attached to each member corresponding to the above-described member in the first reduction gear 11 to the third reduction gear 13. The same alphabet is used.

  In the first to fifth embodiments, the oil intake ports 22 and 30 are formed in the retainer 20h or the carrier 20d. However, in the sixth embodiment, the oil intake port 36 is provided on the catch plate 35 attached to the retainer 20h. Is forming. The vertical hole 38 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 35 is an opening portion of the vertical hole 38 opened at the shaft end of the planetary shaft 20c. Is configured to cover the entire surface through a gap.

Further, the oil intake port 36 for taking in the lubricating oil when the carrier 20d rotates is formed at a portion of the catch plate 35 that always faces the rotation direction of the carrier 20d.
Other configurations have the same configurations as those in the first to fifth embodiments. 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- Example 5. FIG.

  As shown in FIGS. 11 and 12, the catch plate 35 attached to the retainer 20h is attached to the retainer 20h via bolts 39 so as to cover the opening 38 of the vertical hole 37 via a gap. The catch plate 35 can be made of sheet metal or the like, and as a method of attaching the catch plate 35 to the retainer 20h, an appropriate fixing method such as welding or a fixing method using a bolt 39 can be used. Further, in order to make the opening 38 of the vertical hole 37 large at the head of the planetary shaft 20c, the planetary shaft 20c is formed in a shape that is wide open in a mortar shape.

  In this manner, the opening area of the oil intake port 36 can be configured to be large, and the lubricating oil can be stored between the catch plate 35 and the retainer 20h. When the carrier 20d shown in FIG. 12 rotates, the lubricating oil can be taken into the catch plate 35 from the oil take-in port 36 and flow into the vertical hole 37 through the opening 38 of the vertical hole 37 as shown by the arrow in FIG. The lubricating oil that has flowed into the vertical hole 37 can be supplied to the bearing 20g from the through horizontal hole 21b.

  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.

  FIG. 13: has shown longitudinal cross-sectional views, such as a flow path structure in 7th Example concerning this invention. In the sixth embodiment, the catch plate 35 is attached to the upper retainer 20h. In the sixth embodiment, the catch plate 40 is also attached to the lower retainer 20h.

  Since the catch plate 40 is also attached to the lower retainer 20h via the bolt 39, the vertical hole 41 formed in the planetary shaft 20c is formed as a vertical hole 41 penetrating in the vertical direction of the planetary shaft 20c. . In addition, the lower end portion of the planetary shaft 20c is also formed in a shape that is wide open in a mortar shape in order to make the opening 42 of the vertical hole 41 large.

  Other configurations are the same as those in the sixth embodiment. Therefore, about the structure similar to Example 6, the description is abbreviate | omitted by using the same member code | symbol as the member code | symbol used in Example 6. FIG.

  According to the seventh embodiment, not only the upper retainer 20h but also the lower retainer 20h is provided with the catch plate 40 having the same structure as the catch plate 35 provided on the upper retainer 20h. Thereby, since the lubricating oil can be taken in from the oil intake port 43 provided in the catch plate 40, the effect of taking in the oil according to the sixth 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 36 on the upper retainer 20h side and the amount of lubricating oil taken in from the oil intake port 43 on the lower retainer 20h side, the oil intake It is also possible to adjust the opening diameter of the opening 36 or the opening diameter of the oil intake opening 43 so that the intake amount is substantially the same.

  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 FIG. 3 is a cross-sectional view taken along the line BB in FIG. Example 1 It is a side 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 longitudinal cross-sectional view of the principal part centering on a planetary gear. (Example 3) It is a top view of the principal part centering on a planetary gear. (Example 4) It is EE sectional drawing of FIG. 7, and is a longitudinal cross-sectional view of the principal part centering on the planetary gear. (Example 4) It is another longitudinal cross-sectional view of the principal part centering on the planetary gear. (Example 4) It is a longitudinal cross-sectional view of the principal part centering on a planetary gear. (Example 5) It is a top view of the principal part centering on a planetary gear. (Example 6) It is DD sectional drawing of FIG. 11, and is a longitudinal cross-sectional view of the principal part centering on the planetary gear. (Example 6) It is another longitudinal cross-sectional view of the principal part centering on the planetary gear. (Example 7) 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 AA sectional drawing of FIG. 15, and is a longitudinal cross-sectional view of the principal part centering on the planetary gear. (Explanation of conventional example)

Explanation of symbols

4 ... Electric swivel device,
5 ... Electric motor,
9: Lubricating oil chamber,
10 ... reducer,
11: First reduction gear,
12 ... second reducer,
13: Third reduction gear,
14 ... Output pinion,
15 ... mechanical brake,
20a ... sun gear,
20b planetary gear,
20c ... Planetary axis,
20d ... carrier,
20e ... ring gear,
20g ... bearing,
20h ... Retainer,
21 ... Flow path,
21a ... vertical hole,
21b ... through hole,
21c ... side hole,
22 ... Oil intake port,
25a ... snap ring,
25b ... washer,
28 ... Oil intake port,
31 ... Plug,
33 ... Oil intake port,
35 ... catch plate,
36: Oil intake port,
40 ... Catch plate,
43 ... Mouth for oil intake,
51 ... Swivel reducer for construction machinery,
52... First stage carrier assembly,
53 ... Second stage carrier assembly,
54 ... Internal gear,
55 ... Planetary mechanism,
56, 57 ... bearings,
58, 59 ... flow passage,
60a ... sun gear,
60b ... planetary gear,
60c ... Planetary axis,
60d ... carrier,
60e ... ring gear,
62 ... Retainer,
63 ... bearing,
64 ... through hole,
65: Horizontal hole.

Claims (5)

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,
The speed reducer, wherein an oil intake port communicating with the flow passage is always formed as an opening facing one revolution direction of the planetary gear.   The speed reducer according to claim 1, wherein the oil intake port is formed in a retainer that prevents the planetary gear from coming off from the planetary shaft.   The speed reducer according to claim 1, wherein the oil intake port is formed in a carrier that supports the planetary shaft. A catch plate that covers the end of the flow passage that opens at the shaft end of the planetary shaft via a gap is attached to the retainer,
The speed reducer according to claim 1, wherein the oil intake port is formed in the catch plate.   The speed reducer according to any one of claims 1 to 4, wherein the oil intake ports are respectively formed on both end sides of the planetary shaft.

Images