JP6509090B2 - Planetary gear device and maintenance method of lubricant for planetary gear device - Google Patents

Description

  The present invention relates to a planetary gear device and a lubricant maintenance method for the planetary gear device.

  Patent Document 1 discloses a planetary gear device including a planetary gear, an internal gear meshing with the planetary gear, a casing integrated with the internal gear, and a carrier rotating relative to the casing. ing. A main bearing is disposed between the casing and the carrier.

  A cover member is integrated with the casing. The cover member is axially opposed to the carrier with a space, and the space between the carrier and the cover member constitutes a lubricant reservoir.

Unexamined-Japanese-Patent No. 2006-38108 (FIG. 1)

  In Patent Document 1, there is a problem that the axial length of the entire device is increased in order to secure a larger lubricant accumulation with the carrier.

  The present invention has been made to solve such conventional problems, and a planetary gear device capable of securing a larger lubricant reservoir while suppressing an increase in axial length of the entire device. It is the issue to provide.

  According to the present invention, a planetary gear, an internal gear meshing with the planetary gear, a casing integrated with the internal gear, a carrier rotating relative to the casing, and a space between the casing and the carrier A planetary gear device comprising: a main bearing; and a cover member integrated with the casing and having an axial space opposite to the carrier, the carrier being disposed with the main bearing The above problem is solved by the configuration including the outermost periphery to be formed, and the concave portion provided radially inward of the outermost periphery and recessed in the side opposite to the cover in the axial direction from the outermost periphery. It is a thing.

  According to the invention, the carrier, which rotates relative to the casing, is provided with a recess. The recessed portion is provided radially inward of the outermost periphery where the main bearing is disposed, and is recessed toward the side opposite to the cover member in the axial direction with respect to the outermost periphery. For this reason, while suppressing an increase in the axial length of the entire device, it is possible to secure a larger lubricant accumulation as compared with the configuration in which the conventional carrier (in which the recess is not formed) is incorporated.

  The present invention is integrated with a planetary gear, an internal gear that meshes with the planetary gear, a casing that is integrated with the internal gear, a carrier that rotates relative to the casing, and the casing. A method of maintaining a lubricant of a planetary gear device, comprising: a carrier and a cover member having a space in the axial direction and facing each other, wherein the first internal space of the planetary gear device is contained in the planetary gear device. An initial sealing step of sealing the lubricant in an amount corresponding to a predetermined percentage, and after the planetary gear device is operated for a first predetermined period, a lubricant having an amount corresponding to a second predetermined percentage in the internal space is additionally sealed. And a method of maintaining the lubricant of the planetary gear set, which is characterized by including an additional sealing step.

  According to the present invention, it is possible to secure a larger lubricant accumulation while suppressing an increase in the axial length of the entire planetary gear device.

Sectional drawing which shows the structure of the gear apparatus of the eccentric oscillation type | mold which concerns on an example of embodiment of this invention The right side view which looked at the gear apparatus of FIG. 1 from the axial direction with a cover member removed. Sectional view perpendicular to the axis including the external gear on the first carrier side of the gear unit of FIG. 1 The perspective view of the 1st carrier single-piece | unit of the gear apparatus of FIG. 1

  Hereinafter, a planetary gear according to an example of an embodiment of the present invention will be described in detail based on the drawings.

  FIG. 1 is a cross-sectional view showing a configuration of an eccentrically oscillating gear device according to an example of an embodiment of the present invention, and FIG. 2 is a right side view of the gear device as viewed from the axial direction with a cover member removed. FIG. 3 is a cross-sectional view perpendicular to the axis including the external gear on the first carrier side of the gear device of FIG. In addition, FIG. 1 is corresponded to sectional drawing in alignment with the arrow I-I line of FIG.

  Generally speaking, this eccentrically oscillating gear device (planet gear device) G1 includes an external gear (planet gear) 10, an internal gear 40 meshing with the external gear 10, and the internal gear 40. And a first carrier 61 that rotates relative to the casing 50.

  A first main bearing 71 is disposed between the casing 50 and the first carrier 61. A cover member 80 is integrated with the casing 50. The cover member 80 axially opposes the first carrier 61 with a space P1. A space P1 between the first carrier 61 and the cover member 80 constitutes a lubricant reservoir. The first carrier 61 is provided radially inward of the outermost peripheral portion 61A where the first main bearing 71 is disposed, and the outermost peripheral portion 61A, and is recessed toward the non-cover member side in the axial direction relative to the outermost peripheral portion 61A. And a recess 65 (a first recess 66, a second recess 67).

  A more detailed description will be given below.

  The eccentrically oscillating gear device G1 includes an input shaft 12 at the center in the radial direction. The input shaft 12 has a large diameter hollow portion 12S penetrating in the axial direction. A tap hole 12T is formed at an axial end 12E of the input shaft 12. A power input member (not shown) for inputting power from the motor side (not shown) is connected to the input shaft 12 via the tap hole 12T.

  The input shaft 12 is integrally provided at its outer periphery with two eccentric portions 14 for swinging the external gear 10. That is, the input shaft 12 constitutes a crankshaft provided with an eccentric portion 14 for swinging the external gear 10. The axial centers C14 of the two eccentric portions 14 are each eccentric with respect to the axial center C12 of the input shaft 12 by an eccentricity e. In order to balance the oscillation of the external gear 10, the two eccentric portions 14 are eccentric to each other with a phase difference of 180 degrees.

  An eccentric part bearing 16 is disposed between the eccentric part 14 and the external gear 10. The eccentric portion bearing 16 has a retainer 18 and is configured by a needle bearing without a dedicated inner ring and an outer ring. The needle bearing in the present specification includes the concept of a roller bearing.

  The external gear 10 is incorporated in the outer periphery of the eccentric portion 14 via the eccentric portion bearing 16. Therefore, the axial center C <b> 10 of the external gear 10 swings with respect to the axial center C <b> 12 of the input shaft (crankshaft) 12.

  The external gear 10, which is a planetary gear, meshes internally with the internal gear 40. The axial center C40 of the internal gear 40 coincides with the axial center C12 of the input shaft 12. The internal gear 40 has an internal gear main body 41 integrated with the casing 50, a pin groove 42 formed along the axial direction on the inner periphery of the internal gear main body 41, and is rotatable in the pin groove 42. And a cylindrical internal tooth pin 43 which is incorporated in the internal gear and constitutes the internal tooth of the internal gear 40.

  As shown in FIG. 3, in the present gear device G1, the internal tooth pins 43 are not evenly arranged in the circumferential direction, but “two-piece arrangement” and “two-piece thinning” are alternately repeated. It is arranged in an aspect. In this example, the number of internal tooth pins 43 actually arranged is thirty.

  Even if the internal tooth pins 43 are arranged in this manner, the number of substantial internal teeth of the internal gear 40 is equivalent to the number including the number of internal tooth pins thinned out (60 in this example) Become. The number of substantial internal teeth of the internal gear 40 is only slightly (two in this example) greater than the number of external teeth of the external gear 10 (58 in this example).

  A plurality of (only one is shown in FIG. 1) inner pins 22 pass through the external gear 10 at a position offset from the axial center C10. The external gear 10 is formed with a plurality of inner pin holes 10A through which the inner pin 22 passes. Since the inner pin 22 penetrates the external gear 10, it moves in synchronization with the rotation of the external gear 10.

  Carriers 60 (a first carrier 61 and a second carrier 62) are disposed on both axial sides of the external gear 10, and the inner pin 22 is supported by the carrier 60.

  More specifically, the inner pin 22 is fitted into the first inner pin insertion hole 61Q of the first carrier 61 with a clearance fit, and an interference fit (the second inner pin insertion hole 62Q of the second carrier 62) Press fit). That is, although grease can enter between the first inner pin insertion hole 61Q of the first carrier 61 and the inner pin 22, grease can be inserted between the second inner pin insertion hole 62Q of the second carrier 62 and the inner pin 22. I can not enter.

  An inner roller 24 is externally fitted to the inner pin 22 as a sliding acceleration member. Needle bearings 26 are arranged in two rows in the axial direction between the inner pin 22 and the inner roller 24. With this configuration, relative rotation between the inner pin 22 and the inner roller 24 can be performed extremely smoothly, and as a result, the external gear 10 can be smoothly rocked around the eccentric portion 14.

  A part of the inner roller 24 is in contact with the inner pin hole 10 A of the external gear 10. The outer diameter of the inner roller 24 is smaller than the inner diameter of the inner pin hole 10A, and a gap 30 equivalent to twice the eccentricity e of the eccentric portion 14 is secured between the inner roller 24 and the inner pin hole 10A. There is. The oscillating component of the external gear 10 is absorbed by the gap 30 secured between the inner roller 24 and the inner pin hole 10A.

  A main bearing 70 (a first main bearing 71 and a second main bearing 72) is disposed between the carrier 60 and the casing 50. The carrier 60 rotates relative to the casing 50 via the main bearing 70.

  Specifically, the first main bearing 71 disposed between the casing 50 and the first carrier 61 is a first rolling surface 71A formed on the outer periphery of the first carrier 61 which also has the function of the inner ring, the casing A first outer ring 71B disposed on the inner circumference of 50, and a first ball 71C rolling between the first rolling surface 71A and the first outer ring 71B. The second main bearing 72 disposed between the casing 50 and the second carrier 62 is also configured similarly.

  In the present gear device G1, the input shaft (crankshaft) 12 is relatively rotated with respect to the carrier 60 on the inner side in the radial direction of the carrier 60. A first input shaft bearing 31 is disposed between the input shaft 12 and the first carrier 61. The first input shaft bearing 31 has a retainer 33 and is configured by a needle bearing having no dedicated inner ring and no outer ring.

  In addition, a second input shaft bearing 32 is disposed between the input shaft 12 and the second carrier 62. The second input shaft bearing 32 is a ball bearing having a dedicated second inner ring 32A, a second outer ring 32B, and a second ball 32C.

  The first carrier 61 and the second carrier 62 are connected via a carrier pin 63 integrally projected from the second carrier 62 side and a carrier bolt 64 inserted from the first carrier 61 side. Carrier pin 63 penetrates carrier pin hole 10B formed in external gear 10 with a gap. That is, the external gear 10 and the carrier pin 63 do not contact even when the external gear 10 swings. The second carrier 62 is formed with a connecting bolt hole 62S for connecting a mating machine (a driven shaft) (not shown).

  Next, with reference to FIG. 1 to FIG. 3 together with FIG. 4, the configuration relating to the lubricant reservoir of the eccentrically oscillating gear device G1 will be described in detail. FIG. 4 is a perspective view of the first carrier 61 of the present gear device G1.

  The present gear device G1 includes a cover member 80 that is integrated with the casing 50 and that faces the first carrier 61 with a space P1 in the axial direction. The space P1 constitutes a lubricant reservoir described later. Hereinafter, this space P1 is appropriately referred to as a lubricant reservoir P1.

  The casing 50 of the present gear device G1 includes a casing cylindrical portion 55, and a casing flange portion 56 projecting radially outward at the cover member side end of the casing cylindrical portion 55.

  The shape of the axial cover member side end face 50E of the casing 50 is based on a square having four sides 54, and the four corners of the square are the axial center C50 of the casing 50 (= the axis of the internal gear 40). It is made into the shape rounded by the circular arc 52 of radius R52 concentric with the center C40). The shape of the axial casing side end face 80E of the cover member 80 matches the shape of the axial cover member side end face 50E of the casing 50.

  The casing 50 and the cover member 80 are connected by a connection bolt (attachment member) 87 via a connection hole 56S formed in the casing flange portion 56 and a connection hole 86S formed in the cover member 80 corresponding to the connection hole 56S. It is detachably connected and integrated.

  The cover member 80 of the present gear device G1 includes a cover member cylindrical portion 82, a cover member flange portion 86 projecting radially outward at an axial carrier side end of the cover member cylindrical portion 82, and a cover member cylindrical And a collar wall portion 84 extending radially inward from the axially opposite carrier side end of the portion 82.

  The wedge wall portion 84 of the cover member 80 is formed at an axial position receded from the axial direction casing side end face 80E of the cover member 80 to the side opposite to the axial direction by the axial length L82 of the cover member cylindrical portion 82. ing. That is, the lubricant reservoir P1 formed between the cover member 80 and the first carrier 61 is a portion where the wedge wall portion 84 recedes to the side opposite to the carrier in the axial direction with respect to the cover member flange portion 86. It is secured larger than the flat cover member.

  In the present invention, the cover member 80 may not necessarily have such a configuration for securing the lubricant reservoir P1 large as described above. For example, it may be configured by a member formed in a simple flat plate shape (a member in which there is no cylindrical portion, and the cover member flange portion 86 and the wall portion 84 are formed on the same plane). Thereby, the axial length of the entire gear device G1 can be further shortened.

  The collar wall portion 84 of the cover member 80 of the present gear device G1 has a through hole 84S through which the input shaft 12 passes at the center in the radial direction. A first oil seal 88 is disposed between the through hole 84 </ b> S of the wedge wall portion 84 and the input shaft 12. The vicinity of the through hole 84S of the wedge wall portion 84 slightly protrudes and extends toward the first carrier 61 side, and the arrangement surface of the first oil seal 88 is formed wide. The wall portion 84 radially includes reinforcing ribs 87.

  An O-ring 90 is disposed between the casing 50 and the cover member 80. A second oil seal 91 is disposed between the casing 50 and the second carrier 62. A third oil seal 92 is disposed between the second carrier 62 and the input shaft 12. As a result, the internal space (the space sealed by the first oil seal 88, the O-ring 90, and the second and third oil seals 91 and 92) P2 of the gear device G1 is sealed.

  In the present gear device G1, grease is enclosed in the internal space P2 as a lubricant for lubricating the power transmission mechanism of the gear device G1. In the present gear device G1, since channeling type lubrication (described later) is intended, a relatively hard grease having a consistency number of about 1 to 2 is used as a lubricant.

  On the other hand, the first carrier 61 of the present gear device G1 is provided radially inward of the outermost peripheral portion 61A where the first main bearing 71 is disposed and the outermost peripheral portion 61A, and axially relative to the outermost peripheral portion 61A. And a recessed portion 65 recessed on the side opposite to the cover member.

  Specifically, the first carrier 61 includes, as the recess 65, one large first recess 66 and nine small second recesses 67.

  The first recess 66 is formed in a flat plate shape having a bottom surface 66B slightly smaller than the opening on the inner side in the radial direction of the outermost periphery 61A of the first carrier 61. The first concave portion 66 is formed in a ring shape which is connected in a circumferential direction. The bottom surface 66 B of the first recess 66 is flush with the bearing surface of the carrier bolt 64. The bottom surface 66B of the first recess 66 is flush with the inner peripheral edge 61B of the first carrier 61. That is, in the present gear device G1, the inner peripheral edge 61B of the carrier 60 is also recessed more toward the side opposite to the cover member in the axial direction than the outermost peripheral portion 61A.

  In other words, the first recess 66 is formed by expanding the bearing surface of the carrier bolt 64 into a ring shape that is connected circumferentially in a circumferential direction, including the inner peripheral edge 61B of the first carrier 61.

  The first concave portion 66 is a bottom surface which is recessed on the side opposite to the cover member in the axial direction from the axial end face 61A1 of the outermost periphery 61A by an axial depth δ66 on the inner side in the radial direction of the outermost periphery 61A of the first carrier 61 Including 66B. Therefore, in the present embodiment, the first concave portion 66 constitutes “a concave portion which is concaved to the side opposite to the cover member in the axial direction with respect to the outermost peripheral portion 61A”. The first recess 66 enlarges the space (lubricant reservoir) P1 between the first carrier 61 and the cover member 80 (compared to the configuration without the first recess 66).

  On the other hand, the second recess 67 is constituted by nine through holes 61P and an axial end face 22E of the inner pin 22 integrated with the first carrier 61. That is, the through hole 61P is formed coaxially with the axial center C22 of the inner pin 22 inward of the outermost periphery 61A of the first carrier 61 in the radial direction. The inner pin 22 is inserted into the through hole 61P from the side opposite to the cover member in the axial direction. Since the inner pin 22 is integrated with the first carrier 61, it can be grasped that the axial end face 22E constitutes the bottom of the through hole 61P.

  That is, the axial end face 22E of the through hole 61P and the inner pin 22 is on the side opposite to the cover member in the axial direction from the axial end face 61A1 of the outermost periphery 61A inside the radial direction of the outermost periphery 61A of the first carrier 61. It can be said that the concave second concave portion 67 is configured.

  The through hole 61S of the carrier bolt 64 of the first carrier 61 is closed by the carrier bolt 64 and can not be referred to as "a recessed portion recessed to the side opposite to the cover member in the axial direction". It does not correspond to

  Further, since the end surface 64E on the cover member 80 side of the head of the carrier bolt 64 is located on the “axial direction cover member 80 side” with respect to the axial direction end surface 61A1 of the outermost peripheral portion 61A, Is not equivalent.

  However, if the end surface 64E on the cover member 80 side of the head of the carrier bolt 64 is located on the “axially opposite cover member side” than the axial direction end surface 61A1 of the outermost peripheral portion 61A, The end face 64E of the head of the carrier bolt 64 also corresponds to the recess of this embodiment.

  The bottom surface of the recess does not necessarily have to be configured in a plane perpendicular to the axis. For example, it may consist of a plane that is at an angle to a plane perpendicular to the axis. Furthermore, the bottom of the recess does not necessarily have to be flat. For example, it may be configured by a curved surface.

  The larger the axial depth (the size of the recess) from the axial end face 61A1 of the outermost periphery 61A of the carrier 60, the larger the amount of lubricant accumulated between the first carrier 61 and the cover member 80. P1 can be secured. Therefore, the first recess 66 of the first carrier 61 is formed to overlap the first outer ring 71B of the first main bearing 71 by δ (66B-71B1) as viewed in the radial direction. In other words, the bottom surface 66B of the first recess 66 is positioned on the side opposite to the cover member in the axial direction by δ (66B-71B1) than the end face 71B1 of the first outer ring 71B of the first main bearing 71 on the cover cover side. doing.

  Further, the second recess 67 of the first carrier 61 overlaps the first rolling surface 71A of the first main bearing 71, the first outer ring 71B, and the first ball 71C as viewed in the radial direction.

  Thus, the axial position of the bottom surface of each recess does not have to be uniform (uniform).

  Further, the larger the area of the bottom surface of the recess 65, the larger the lubricant reservoir P1 can be secured between the first carrier 61 and the cover member 80. In this respect, the area of the recess 65 is preferably large.

  Here, "the area of the recess" means the sum of the area of the bottom surface or the opening of each recess. If the area of the bottom of a specific recess and the area of the opening are different, it is defined as the larger area. According to this definition, for example, in the case of a recess having a bottom surface smaller than the opening, such as the first recess 66 of the gear device G1, the area of the opening is the area of the recess. On the other hand, when the area of the bottom (the axial end face 22E of the inner pin 22) is larger than the area of the opening (the cross section perpendicular to the axis of the through hole 61P) like the second recess 67 of the present gear device G1. The area of the bottom surface 22E of the inner pin 22 means "the area of the recess".

  In addition to the case where the recess is divided into a plurality of parts, as in the case of the present gear device G1, even if there is a small recess overlapping in one large recess, the total sum of the areas of the recesses is the gear device The area of the recess is This is because each of the large recess and the small recess has the function of expanding the lubricant pool synergistically (for example, having only the first recess 66 and not having the second recess 67). As compared with the configuration, the lubricant recess can be further expanded if the second recess 67 is provided).

  The area of the recess is 50% or more of the area of the end face in the axial direction of the first carrier 61 (the sum of the area of the recess and the area of the end face in the axial direction other than the recess) in order to make the present invention function effectively. More preferably, 60% or more is secured. In the present gear device G1, the area of the recess 65 (the area of the opening of the first recess 66 + the area of the end face 22E of the inner pin 22 of the second recess 67) is the axis of the first carrier 61. It reaches about 65% of the area of the direction end face.

  In addition, the code | symbol 93 of FIG. 3 has shown the grease supply port (injection port of grease). The code | symbol 95 is a cover body of this oil supply port 93. As shown in FIG. The oil supply port 93 penetrates the casing 50 in the radial direction, and opens at a portion other than the lubricant reservoir P1 secured between the first carrier 61 and the cover member 80. Specifically, the oil supply port 93 opens at a meshing portion of the internal gear 40 and the external gear 10 (between the pin groove 42 of the internal gear 40 and the internal pin 43). Moreover, the code | symbol 94 has shown the grease removal port (discharge port of grease). Reference numeral 96 denotes a lid of the grease outlet 94. The oil discharge port 94 is provided on the opposite side of the oil supply port 93 to the axial center C40 of the internal gear 40. That is, the oil drainage port 94 also opens at a portion other than the lubricant reservoir P1 secured between the first carrier 61 and the cover member 80.

  Next, the operation of the eccentrically oscillating gear device G1 will be described.

  First, the operation of the power transmission system will be described. The input shaft 12 receives power from the motor side via a power input member (not shown) and rotates. When the input shaft 12 rotates, the eccentric portion 14 integrally formed with the input shaft 12 rotates. When the eccentric portion 14 rotates, the axial center C10 of the external gear 10 installed on the outer periphery of the eccentric portion 14 via the eccentric portion bearing 16 swings. The external gear 10 internally meshes with the internal gear 40. Further, the number of teeth 58 of the external gear of the external gear 10 is smaller than the number 60 of the substantially internal teeth of the internal gear 40 by two.

  Thereby, in the external gear 10, the axial center C10 swings once each time the input shaft 12 rotates once, and the number of teeth difference (two teeth) with respect to the meshing internal gear 40 It is out of phase and rotates. The rotation component is transmitted to the inner pin 22 through the inner roller 24 and the needle bearing 26 penetrating the external gear 10, and the inner pin 22 revolves around the axial center C40 of the internal gear 40.

  The revolution of the inner pin 22 causes the carrier 60 (the first carrier 61 and the second carrier 62) with which the inner pin 22 is integrated to rotate (rotation) around the axial center C40 of the internal gear 40. As a result, it is possible to rotate and drive the other machine integrated with the second carrier 62 via the bolt (only the connecting bolt hole 62S is shown).

  Subsequently, an operation regarding holding and maintenance of the lubricant of the present gear device G1 will be described.

  Generally, there are so-called "charing type lubrication" and "channeling type lubrication" as a method of lubrication of a planetary gear device. Although the two do not have clear boundaries, qualitatively, the charing-type lubrication uses a soft grease (high consistency grease, low consistency number grease) that is fluid, and a lubrication point Perform lubrication in a manner that causes Therefore, in the churning type lubrication, the amount of grease necessary for the lubrication tends to be large. Further, in the charring type lubrication, the movable member moves in such a manner as to push off the grease, so the power loss tends to be large. However, charring type lubrication is easy to replace (maintenance) when the lubricant deteriorates due to use. Specifically, it is possible to adopt a so-called grease-up replacement method in which a used lubricant is discharged so as to be pushed out from the drainage port 94 by injecting a new lubricant from the oil supply port 93. .

  On the other hand, with channeling type lubrication, lubrication is performed in a mode in which a proper amount of grease is attached to the lubrication site using hard grease with a low flowability (grease with low consistency, grease with high consistency number). Therefore, in the channeling type lubrication, the amount of grease required for the lubrication tends to be small. The channeling type lubrication can further reduce the power loss because the movable member can reduce the resistance to displace the grease. However, since channeling type lubrication can not adopt so-called grease-up replacement methods such as charring type lubrication, when the lubricant deteriorates due to use, the apparatus is disassembled and grease is repainted. . For this reason, a worker is required to have appropriate knowledge about the structure of the apparatus, and it takes time and effort (maintenance is expensive).

  Therefore, in the present gear device G1, it was intended to design so that maintenance can be performed more easily while adopting channeling type lubrication with small power loss.

  Specifically, the present gear device G1 is provided with a cover member 80 integrated with the casing 50 and facing the first carrier 61 with a space P1 in the axial direction, and on top of that, in the gear device G1, A lubricant is sealed in an amount corresponding to the first predetermined percentage of the internal space P2 of the gear device G1 (initial sealing step). The first predetermined% means an amount (% by volume) with respect to the volume of the internal space P2 of the grease to be initially enclosed when the present gear device G1 is newly manufactured. Specifically, for example, about 30%. As the channeling type lubrication is intended, as described above, a hard grease, specifically a grease having a consistency number of about 1 to 2 or more in consistency number is used as the grease. It is enclosed.

  This initial sealing is performed in such a manner that an appropriate amount of grease is attached to the necessary lubrication site when the gear device G1 is assembled. As a result, the grease is properly sealed in the necessary part of the lubrication between the first carrier 61 and the second carrier 62. Also for the initial sealing, it is not prohibited to seal the oil supply port 93 after assembling the gear device G1.

  Then, after the gear unit G1 is operated for a first predetermined period (for example, after two to three years), a lubricant corresponding to a second predetermined percentage (for example, 10%) of the inner space P2 is additionally Seal (additional sealing step). This additional sealing is performed without disassembling the gear device G1 and with the lid 96 of the grease outlet 94 closed (or with the lid 96 slightly loosened), the internal gear 40 and the external gear It is performed from the oil supply port 93 opened to the meshing part of the gear 10. The additional encapsulation amount (second predetermined percentage) may often be less than (or more than) the first predetermined percentage.

  Since the existing grease already adheres to the lubrication site, and the drainage port 94 is in a closed or nearly closed state, the additionally filled grease is subjected to an appropriate pressure. Therefore, the additionally enclosed grease pushes out most of the existing (used) grease to the lubricant reservoir P1 side through the first main bearing 71, the first input shaft bearing 31, or the through hole 61P, etc. , Combine with some existing grease, familiar, improve the quality. The grease is not discharged out of the gear unit G1.

  As described above, the lubricant maintenance method in the present gear device G1 completes the maintenance of the lubricant without disassembling the gear device G1 and without discharging the existing grease to the outside of the gear device G1. Is a major feature of

  Then, after the maintenance by the additional sealing is performed, when the gear unit G1 is operated for a second predetermined period, the lubricant corresponding to the third predetermined percentage of the internal space P2 of the gear unit G1 is further Add and seal (increasing process). The second predetermined period may be the same as, shorter than, or longer than the first predetermined period. The third predetermined percentage may be the same as, less than, or more than the second predetermined percentage.

  When the total enclosed amount of the lubricant reaches the fourth predetermined percentage (for example, 80%) of the internal space P2 by passing through the increase step one or more times, it is detachably integrated with the casing 50. The cover member 80 being removed is removed from the casing 50, and the lubricant accumulated in the lubricant reservoir P1 is discharged. Thereby, it is possible to repeat the additional sealing process or the increasing process again without disassembling members other than the cover member 80 of the gear device G1.

  According to such a procedure, it is possible to realize simple and low-cost maintenance in the gear unit G1 that adopts channeling type lubrication, which is said to be disadvantageous because it has many merits but the cost of maintenance is high. Become.

  In addition, the said maintenance method is that it is not necessary to decompose | disassemble components other than the cover member 80, and it is not said to "prohibit" the said decomposition | disassembly at all. Maintenance for disassembling part or all of the components of the gear unit G1 including the cover member 80 may be appropriately performed, for example, before the total enclosed amount of the lubricant reaches a fourth predetermined percentage of the internal space P2. Is free.

  Here, in the present gear device G1, a cover member 80 integrated with the casing 50 and facing the first carrier 61 with the space P1 in the axial direction and facing the first carrier 61 is provided, and the first carrier 61 A recess 65 (a first recess 66 and a first recess 66 provided on the radially outer side of the outermost peripheral portion 61A where the bearing 71 is disposed and the innermost peripheral portion 61A and recessed in the axial direction against the cover member side) 2) having a recess 67).

  Therefore, due to the presence of the recess 65 of the first carrier 61, the lubricant reservoir P1 between the first carrier 61 and the cover member 80 is incorporated with a carrier whose end surface on the cover member side is flush (without the recess). Compared to the case, it is more expanded. Then, even if the lubricant reservoir P1 is enlarged due to the presence of the recess 65, the axial length of the entire gear device G1 is not particularly increased. Therefore, it is possible to secure a larger lubricant reservoir P1 while suppressing an increase in the axial length of the entire gear device G1.

  In particular, in the gear device G1, the first concave portion 66 is formed in a ring shape which is connected in a circumferential direction. Further, the first concave portion 66 is formed to the inner peripheral edge 61B of the first carrier 61, and the inner peripheral edge 61B of the first carrier 61 is also recessed on the side opposite to the outermost cover 61A in the axial direction. Further, the bottom surface 66B of the first recess 66 overlaps the first main bearing 71 (the first outer ring 71B) by δ (66B-71B1) as viewed from the radial direction, and the second recess 67 is the first main bearing The first rolling surface 71A, the first outer ring 71B, and the first ball 71C overlap with each other as viewed in the radial direction. From these configurations, as a result, the first recess 66 and the second recess 67 have an area of 50% or more (specifically, 65%) of the area of the axial end surface of the first carrier 61. For this reason, it is possible to secure a larger lubricant reservoir P1 while suppressing an increase in axial length.

  Furthermore, the present gear device G1 is disposed between the input shaft 12 and the first carrier 61, and the input shaft 12 that rotates relative to the first carrier 61 at the radially inner side of the first carrier 61. An input shaft bearing 31 is provided, and the first input shaft bearing 31 is configured by a needle bearing that does not have a dedicated inner and outer ring. Therefore, although the axial length near the inner peripheral edge 61B of the first carrier 61 is reduced because the first recess 66 is formed, the first input shaft bearing 31 having a large capacity is disposed. Is ready. In other words, it is possible to form the large first recess 66 without reducing the capacity of the first input shaft bearing 31.

  Further, in the present gear device G1, a configuration is employed in which the lubricant reservoir P1 is secured larger on the side of the cover member 80 as well. These synergetic effects make it possible to secure a larger lubricant reservoir P1 while suppressing an increase in axial length. Therefore, it is more effective that the grease pushed out by the lubricant pool P1 reaches the limit amount in a short period of time even if the grease is added slightly more frequently or the amount of grease is increased more or less frequently. Can be prevented.

  In the above embodiment, only one crankshaft (the input shaft 12 in the above example) is provided on the axial center C40 of the internal gear 40, a so-called eccentric crank type gear device called a so-called center crank type. The present invention has been applied to (planet gear). However, a so-called distribution type in which a plurality of crankshafts having an eccentric portion for oscillating the external gear is provided at a position offset from the axial center of the external gear is provided in the eccentric oscillation type planetary gear device. The one that adopts the following configuration is also known.

  The present invention is similarly applicable to such a distribution type of eccentric oscillation type planetary gear apparatus. Furthermore, the present invention is applicable not only to the eccentric rocking type planetary gear set, but also to, for example, a simple planetary type planetary gear set, and the same function and effect can be obtained.

  Further, in the above embodiment, the channeling type lubrication is adopted in the configuration of "retaining a larger lubricant reservoir while suppressing an increase in the axial length of the entire planetary gear device due to the presence of the recess provided in the carrier". Applied to the planetary gear system. However, the present invention is not only effective for a planetary gear system adopting channeling type lubrication, but can be applied to a planetary gear system adopting charring type lubrication.

  For example, in patent document 1, in the planetary gear apparatus which employ | adopts the lubrication of a churning type | mold, the lifetime improvement and the efficiency improvement accompanying lubricity improvement are achieved by ensuring a lubricant reservoir larger. In the case where the present invention is applied to a planetary gear device adopting churning type lubrication, "a larger lubricant reservoir is secured while suppressing an increase in the axial length of the entire planetary gear device, and the quality of the lubricant is reduced. It is possible to obtain a beneficial action and effect of "maintaining well over a long period of time".

  In the above embodiment, the cover member 80 is configured of a single member, but the configuration of the cover member is not limited to this. For example, the cover member 80 is divided into a plurality (for example, two) in the circumferential direction You may combine and comprise the member which was carried out.

  With such a configuration, even when a wire or the like is inserted into the hollow portion 12S of the input shaft 12, the cover member 80 can be removed without removing the wire or the like.

  In addition, when making a cover member into a division structure in this way, it is preferable not to arrange an oil seal (88 in the said example) but to employ | adopt a labyrinth structure, for example.

G1 ... Eccentric rocking gear (planet gear)
10: External gear (planet gear)
40: Internal gear 50: Casing 61: First carrier 61A: Outermost circumferential portion 71: First main bearing 80: Cover member 65: Recess 66: First recess 67: Second recess P1: Space (lubricant reservoir)

Claims (9)

A planetary gear, an internal gear meshing with the planetary gear, a casing integrated with the internal gear, a carrier rotating relative to the casing, and a main bearing disposed between the casing and the carrier And a crankshaft having an eccentric portion for swinging the planetary gear,
The axial center of the crankshaft coincides with the axial center of the internal gear,
A cover member integrated with the casing and having an axial space facing the carrier;
The carrier has an outermost peripheral portion on which the main bearing is disposed, and a recess provided radially inward of the outermost peripheral portion and recessed toward the cover opposite to the axial direction from the outermost peripheral portion. A planetary gear device that features. In claim 1,
The planetary gear device according to claim 1, wherein the recess is in a ring shape that is connected in a circumferential direction. In claim 1 or 2,
The planetary gear set according to claim 1, wherein the recess is provided up to the inner peripheral edge of the carrier, and the inner peripheral edge of the carrier is also recessed toward the cover opposite to the axial direction with respect to the outermost periphery. In any one of claims 1 to 3,
The bottom surface of the said recessed part overlaps with the said main bearing seeing from radial direction. The planetary gear apparatus characterized by the above-mentioned. In any one of claims 1 to 4,
A planetary gear device, wherein the recess has an area of 50% or more of the area of the axial end face of the carrier. In any one of claims 1 to 5,
The planetary gear device further includes a shaft receiving disposed between said carrier and said crankshaft,
A planetary gear device characterized in that the bearing is a needle bearing having no dedicated inner and outer rings. In any one of claims 1 to 6,
A planetary gear device comprising an oil seal disposed between the cover member and the crankshaft . A lubricant maintenance method for a planetary gear device according to any one of claims 1 to 7 ,
An initial sealing step of sealing a lubricant in an amount corresponding to a first predetermined percentage of the internal space of the planetary gear set in the planetary gear set;
An additional sealing step of additionally sealing an amount of a lubricant corresponding to a second predetermined percentage of the internal space after the planetary gear device has been operated for a first predetermined period;
A method of maintaining a lubricant for a planetary gear device, comprising: In claim 8,
The planetary gear device is a planetary gear device in which the cover member is detachably integrated with the casing, and further,
After the additional sealing step, after the planetary gear device is operated for a second predetermined period, an increasing step of additionally sealing a lubricant in an amount corresponding to a third predetermined percentage of the internal space;
The cover member is removed when the total enclosed amount of the lubricant reaches a fourth predetermined percentage of the internal space by passing the increasing step one or more times, and the carrier and the cover member are removed. Discharging the lubricant accumulated in the space between
A method of maintaining a lubricant for a planetary gear device, comprising:

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