JP2007247857A - Bearing device for gear - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing device for gears capable of absorbing a difference in material property of a bearing and a casing and stably supporting a rotary shaft of a gearing arrangement. <P>SOLUTION: The bearing device for gears includes the casing 12 formed of light alloy such as aluminum alloy, an input shaft 13 extending through the casing 12, an output shaft 14 arranged in parallel with the input shaft 13, a pinion 15 fixedly connected to the input shaft 13, a rack 16 fixedly connected to the output shaft 14 so as to engage with the pinion 15, four bearings 17, 18, 19, 20 through which the input shaft 13 and the output shaft 14 are rotatably supported by the casing 12, bearing retainer members 21, 22 having bearing securing portions 21a, 21b, 22a, 22b for receiving the bearings 17 to 20 and secured to the casing 12 in an unrotatable manner, and vibration isolating members arranged at contact portions between the casing 12 and the bearing retainer members 21, 22. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a gear bearing device, and more particularly to a gear bearing device that supports a rotating shaft of a gear device such as a speed reducer, a speed increaser, a transmission, a four-wheel drive vehicle transfer, and a hydraulic pump.

Referring to FIG. 14, for example, a conventional gear device 101 includes a casing 102, an input shaft 103 inserted through the casing 102, an output shaft 104 arranged in parallel with the input shaft 103 in the casing 102, and an input shaft 103. The small gear 105 having a fixed number of teeth n ₁ , the large gear 106 having a number of teeth n ₂ fixedly connected to the output shaft 104 and meshing with the small gear 105, and the input shaft 103 and the output shaft 104 are rotatable to the casing 102. And four bearings 107 to be supported.

The gear device 101 is a speed reducer that reduces the rotation of the input shaft 103 at a reduction ratio of n ₁ / n ₂ and transmits it to the output shaft 104. For example, Japanese Patent Laid-Open No. 8-196057 (Patent Document 1). It is also described in.

Referring to FIG. 15, casing 102 includes a recess 102b for receiving bearing 107, an opening 102a through which the rotation shaft is inserted into the bottom wall of recess 102b, and a ring for preventing bearing 107 from falling off at the open end side of recess 102b. Member 108. On the other hand, the bearing 107 is a ball bearing having an inner ring 107a, an outer ring 107b, and a plurality of balls 107c arranged between the inner ring 107a and the outer ring 107b. The bearing 107 is fixed by being fitted into the recess 102b.
JP-A-8-196057

  In recent years, a casing 102 made of a light alloy such as an aluminum alloy is sometimes used in accordance with a demand for weight reduction of the gear device 101. Compared with the bearing steel used for the bearing 107, the light alloy used for the casing 102 has low hardness and rigidity and a large linear expansion coefficient.

  Since the bearing 107 is merely fixed by fitting into the recess 102b of the casing 102, a phenomenon occurs in which the outer ring 107b rotates in the recess 102b during rotation of the bearing (hereinafter, this phenomenon is referred to as “creep”). As a result, the inner wall surface of the recess 102b having a lower hardness than the outer ring 107b is worn by friction with the outer ring 107b.

  Further, since the casing 102 having a large linear expansion coefficient has a larger dimensional change rate due to a temperature change than the bearing 107, the position of the bearing 107 in the casing 102 changes according to the temperature change. As a result, the distance between the input shaft 103 and the output shaft 104 also changes, so that proper engagement between the small gear 105 and the large gear 106 cannot be maintained.

  Further, vibration generated by meshing between the small gear 105 and the large gear 106 is transmitted to the casing 102 via the input shaft 103, the output shaft 104, and the bearing 107. This vibration becomes larger when a gap is generated between the casing 102 and the bearing 107 due to wear or thermal expansion of the casing 102.

  Accordingly, an object of the present invention is to provide a gear bearing device capable of absorbing the difference in material characteristics between the bearing and the casing and stably supporting the rotating shaft of the gear device.

  The gear bearing device according to the present invention has a casing having an opening through which a rotating shaft to which a gear is fixed, a bearing holding member that is fitted and fixed in the opening of the casing, and a vibration transmissibility of 1 or less. And a vibration isolating member disposed at a contact portion between the casing and the bearing holding member, and a bearing held by the bearing holding member and rotatably supporting the rotating shaft. Thereby, it is possible to suppress the vibration generated from the gears and the like from being transmitted to the casing through the shaft, the bearing, and the bearing holding member. As a result, a gear bearing device with reduced vibration and noise can be obtained.

  Preferably, the vibration isolating member is attached in a compressed state between the casing and the bearing holding member. Further, the vibration isolating member is fixed to the casing and / or the bearing holding member in a non-detachable manner. This prevents a gap from being generated between the casing and the vibration isolating member and between the bearing holding member and the vibration isolating member due to its own weight or temperature change (including both rising and lowering). can do.

  As one embodiment of the gear bearing device described above, the casing has openings through which a plurality of rotating shafts pass, and the bearing holding member holds a bearing that rotatably supports each of the plurality of rotating shafts.

  According to the present invention, the material characteristics of the bearing and the casing, in particular, the difference in rigidity and linear expansion coefficient can be absorbed to stably support the rotating shaft of the gear device. It is possible to obtain a gear bearing device that suppresses vibrations transmitted through the casing to the casing.

  With reference to FIGS. 1-7, the gear apparatus 11 which concerns on one Embodiment of this invention is demonstrated. FIG. 1 is a view showing a gear device 11 in which the gear bearing device according to the present invention is used.

Referring to FIG. 1, a gear device 11 includes a casing 12 formed of a light alloy such as an aluminum alloy, an input shaft 13 inserted through the casing 12, an output shaft 14 disposed in parallel with the input shaft 13, Casing the small gear 15 with the number of teeth n ₁ fixedly connected to the input shaft 13, the large gear 16 with the number of teeth n ₂ fixedly connected to the output shaft 14 and meshing with the small gear 15, and the input shaft 13 and the output shaft 14. Bearings that have four bearings 17, 18, 19, and 20 that are rotatably supported by 12, and bearing fixing portions 21 a, 21 b, 22 a, and 22 b that receive the bearings 17 to 20, and are fixed to the casing 12 so as not to rotate. Holding members 21 and 22. The gear device 11 is a speed reducer that reduces the rotation of the input shaft 13 with a reduction ratio of n ₁ / n ₂ and transmits the reduced speed to the output shaft 14.

  FIG. 2 is an enlarged view of a fitting portion between the casing 12 of FIG. 1 and the bearing 17 and the bearing holding member 21. Referring to FIG. 2, casing 12 has an opening 12 a through which output shaft 14 passes. The opening 12a includes a recess 12b that protrudes inside the casing 12, and a hole 12c provided in the bottom wall of the recess 12b. The bearing holding member 21 is fixed by being fitted into a recess 12 b provided in the casing 12. At this time, a vibration isolating member 23 that suppresses vibration transmitted from the bearing holding member 21 to the casing 12 is disposed at a contact portion between the casing 12 and the bearing holding member 21. The support portion of the input shaft 13 has the same configuration.

  The bearing 17 includes an inner ring 17a, an outer ring 17b, a plurality of balls 17c disposed between the inner ring 17a and the outer ring 17b, a retainer (not shown) that holds a space between the plurality of balls 17c, an inner ring 17a, It is a ball bearing provided with the sealing member (not shown) which seals the end surface of the outer ring | wheel 17b. The bearing 17 is held by fitting into a bearing fixing portion 21 a provided in the bearing holding member 21. The bearings 18, 19, and 20 have the same configuration.

  A gear bearing device according to an embodiment of the present invention will be described with reference to FIGS. 3 and 4. 3 is a front view of the bearing holding member 21 shown in FIG. 1, and FIG. 4 is a cross-sectional view taken along line IV-IV in FIG.

  Referring to FIG. 3, the gear bearing device according to one embodiment of the present invention includes a casing 12 (not shown), bearings 17 and 18, and a bearing holding member 21. The bearing holding member 21 has bearing fixing portions 21 a and 21 b that receive the bearings 17 and 18 in a non-circular shape whose outer contour line includes an arc portion and a straight portion. Referring to FIG. 4, the bearing holding member 21 is plate-shaped along the recess 12 b on the outer wall surface of the casing 12, and the bearing fixing portions 21 a and 21 b are recesses that can accommodate the bearings 17 and 18 therein. It is. Further, holes 21c and 21d through which the input shaft 13 and the output shaft 14 are inserted are formed in the bottom walls of the bearing fixing portions 21a and 21b.

  In the present specification, “non-circular” means that the outer contour line includes all of the first part having a relatively long distance from the center of gravity and the second part having a relatively short distance from the center of gravity. It shall refer to the shape of Specifically, it is an ellipse or a polygon. The bearing holding member 22 has the same configuration.

  The vibration isolating member 23 is an annular member having an L-shaped cross section including a cylindrical cylindrical portion 23 a and a disc-shaped flange portion 23 b, and is a contact portion between the casing 12 and the bearing holding member 21. It is provided all around.

  The vibration isolator 23 is preferably attached in a compressed state by the casing 12 and the bearing holding member 21. Accordingly, a gap is generated between the casing 12 and the vibration isolating member 23 and between the bearing holding member 21 and the vibration isolating member 23 due to the weight of the gear unit 11 or a temperature change (including both rising and lowering). Can be prevented. Further, the vibration isolating member 23 may be fixed to the casing 12 and / or the bearing holding member 21 in a non-detachable manner by adhesion, welding, or the like.

  The vibration isolation member 23 is formed using a metal spring, a natural resin, a synthetic resin (plastic) such as a thermoplastic resin or a thermosetting resin, or an elastomer. Specifically, for example, general-purpose plastics such as polyethylene (PE) such as high-density polyethylene (HDPE), polypropylene (PP), polystyrene (PS), polyvinyl chloride (PVC), acrylic resin (PMMA), and 11 nylon Polyamides such as polyamide (PA) such as nylon 6, polycarbonate (PC), polyesters such as polybutylene terephthalate (PBT), polyarylene sulfides such as polyacetal (POM), cyclic polyolefin (COP), fluororesin and polyphenylene sulfide (PPS) (PAS), engineering plastics including super engineering plastics such as polyether ether ketones (PEEK) and polyether ketones (PEK), or silicone rubbers, Acrylic rubber, nitrile rubber, butyl rubber, chloroprene rubber, elastomers such as natural rubber - Tsu containing rubbers, butadiene rubber, isoprene rubber, styrene-butadiene rubber, acrylic rubber, ethylene propylene rubber, ethylene.

  In addition, a polymer alloy obtained by mixing two or more kinds of materials as described above may be used, and there is no particular problem as a composite composition containing additives such as other reinforcing materials and plasticizers as necessary. . Further, these foam materials may be used. A low elastic modulus of the vibration-proof member is preferable because it has a high degree of freedom in designing the gear device and is excellent in manufacturability.

  As the gear device 11 shown in FIG. 1, the bearing holding members 21 and 22 are arranged between the casing 12 and the bearings 17 to 20, so that the casing 12 is not worn by creep of the bearings 17 to 20. Further, since the outer contour lines of the bearing holding members 21 and 22 are non-circular, there is no fear that the bearing holding members 21 and 22 rotate inside the recess 12 b of the casing 12. Furthermore, since the bearing holding members 21 and 22 are made of a material having the same hardness as the bearings 17 to 20, there is little fear of wear due to creep of the bearings 17 to 20.

  Next, with reference to FIGS. 5-7, the manufacturing method of the bearing holding member 21 is demonstrated. First, referring to FIG. 5, as a starting material for the bearing holding member 21, steel plates such as bearing steel, carbon steel, and rolled steel, steel strips, polished special strip steels, and the like are used.

  Referring to FIG. 6, as a first step, concave bearing fixing portions 21a and 21b are formed on a steel plate by drawing. The diameters of the inner wall surfaces of the bearing fixing portions 21a and 21b are adjusted to the outer diameter dimensions of the bearings 17 and 18. Further, the distance between the centers of the bearing fixing portions 21 a and 21 b is adjusted to the distance between the shaft centers of the input shaft 13 and the output shaft 14. 6 shows an example in which the outer edge portion 21e and the central portion 21f have the same height. However, when the distance between the bearing fixing portions 21a and 21b is small, the central portion 21f is lower than the outer edge portion 21e. Sometimes.

  Referring to FIG. 7, as a second step, holes 21c and 21d through which input shaft 13 and output shaft 14 are inserted are formed in the bottom walls of bearing fixing portions 21a and 21b by punching. At this time, the diameters of the holes 21c and 21d are set such that the bottom wall does not interfere with the end faces of the inner rings 17a and 18a in order not to prevent smooth rotation of the bearings 17 and 18.

  The process of processing the outer contour of the bearing holding member 21 into a non-circular shape as shown in FIG. 3 may be after the first process shown in FIG. 6 or the second process shown in FIG. It may be after the process. In addition, after the shape processing of the bearing holding member 21, heat treatment such as quenching, carburizing, and nitriding is performed in order to obtain predetermined mechanical properties.

  In the method for manufacturing the bearing holding member 21 shown in FIGS. 5 to 7, an example of a manufacturing method for pressing a steel plate from the viewpoint of manufacturing cost and production efficiency has been shown. You may manufacture by a drawing process.

  The bearing holding member 21 configured as described above is attached to the casing 12 with the bearings 17 and 18 incorporated therein. At this time, since the interval between the bearing fixing portions 21a and 21b is already coincident with the interval between the input shaft 13 and the output shaft 14, it is not necessary to position the bearings 17 and 18 when the gear device 11 is assembled. Assembly man-hours can be reduced.

  In the gear device 11 shown in FIG. 1, the casing 12 and the bearing holding members 21 and 22 may be formed of the same material, but the dimensional change due to temperature, the rigidity of the gear device, the weight reduction of the gear device, and the like. From this point of view, it is desirable to form with different materials.

For example, the linear expansion coefficient of bearing steel used for the bearings 17 to 20 is α ₁ , the linear expansion coefficient of bearing steel or carbon steel used for the bearing holding members 21 and 22 is α ₂ , an aluminum alloy used for the casing 12, etc. When the linear expansion coefficient of the light alloy is α ₃ and the linear expansion coefficient of the vibration isolation member 23 is α ₄ , at least α ₁ ≦ α ₂ <α ₃ , more preferably α ₁ ≦ α ₂ <α ₃ <α ₄ . Select materials that satisfy the relationship.

  When such a material is selected, the difference in expansion amount between the bearings 17 to 20 and the bearing holding members 21 and 22 due to the temperature change is small. Therefore, the position of the bearings 17 to 20 in the bearing holding members 21 and 22 is changed. Is extremely small. As a result, since the inter-axis dimension of the input shaft 13 and the output shaft 14 hardly changes, an appropriate meshing amount between the small gear 15 and the large gear 16 can be maintained.

Also, when made different from the linear expansion coefficient alpha ₃ of the linear expansion coefficient alpha ₂ and the casing 12 of the bearing holding member 21, a gap between the casing 12 and the bearing holding member 21 along with the temperature change, the driving force The vibration of the conversion mechanism or the like is easily amplified through the bearing holding member 21 and transmitted to the casing 12.

In order to solve this problem, the linear expansion coefficient α ₄ of the vibration isolation member 23 is set to be higher than the linear expansion coefficients α ₂ and α ₃ of the casing 12 and the bearing holding member 21. Thereby, the difference of the dimensional change between the casing 12 and the bearing holding member 21 caused by thermal expansion can be filled. Thereby, even when the temperature of the gear apparatus 11 changes, the bearing holding member 21 can be appropriately supported by the casing 12.

  In addition, when attaching this bearing apparatus to the casing 12, this problem can also be solved by attaching the vibration isolating member 23 in a compressed state. In this case, not only when the temperature rises but also when the temperature falls, a gap or the like due to a large linear expansion coefficient of the vibration isolation member 23 is not generated, which is preferable.

Further, the vibration transmission rate τ from the gear unit 11 to the casing 12 is set to 1 or less (τ ≦ 1) by arranging the vibration isolation member 23. Note that the vibration transmissibility τ is F ₀ (N) at the vibration generating source such as the meshing portion of the small gear 15 and the large gear 16, and the casing 12 through the bearing holding member 21 and the vibration isolating member 23. Assuming that the force transmitted to F is F, the vibration frequency at the vibration source is f (Hz), and the natural frequency of the gear unit 11 with the vibration isolation member 23 incorporated is f ₀ (Hz), expressed.

Here, f / f _{0 is referred} to as a frequency ratio, and in order to satisfy τ ≦ 1, f / f ₀ needs to be within the range of Formula 2.

However, if the frequency ratio is too large, the weight of the speed reducer 11 may not be supported. Therefore, it is usually desirable to set it within the range of 2 ≦ f / f ₀ ≦ 3. Substituting this into Equation 1, 1/8 ≦ τ ≦ 1/3.

  Further, the bearing holding members 21 and 22 are made of a material having higher rigidity than the casing 12. Thereby, the rigidity of the casing 12 can be supplemented. As a result, a material that is lighter than the light alloy, such as an engineering plastic, can be used as the material of the casing 12.

  A gear bearing device according to another embodiment of the present invention will be described with reference to FIGS. 8 and 9. 8 is a view showing a gear bearing device according to another embodiment of the present invention, and FIG. 9 is a cross-sectional view taken along line IX-IX in FIG.

  The gear bearing device shown in FIGS. 8 and 9 includes a casing 12 (not shown), bearings 32 and 33, and a bearing holding member 31. The bearing holding member 31 has the same basic configuration as the bearing holding member 21 shown in FIGS. Moreover, since the bearings 32 and 33 are the same as the bearing 17, description is abbreviate | omitted.

  Ribs 31e as reinforcing portions are formed on the entire circumference of the outer edge portion of the bearing holding member 31 by bending about 90 ° in the same direction as the protruding direction of the bearing fixing portions 31a and 31b. Thereby, the rigidity of the bearing holding member 31 is further improved. Further, the rib 31e and the outer wall surfaces of the recesses 31a and 31b function as a vibration isolating member holding portion that prevents the vibration isolating member 34 from falling off. When the bearing holding member 31 is manufactured by pressing as shown in FIGS. 5 to 7, the rib 31e may be formed before or after the first step shown in FIG. It may be after the second step shown in FIG.

  In the embodiment shown in FIGS. 8 and 9, an example is shown in which the outer edge portion of the bearing holding member 31 is bent in the same direction as the protruding direction of the bearing fixing portions 31 a and 31 b to form the rib 31 e. Without limitation, it may be formed by bending in the direction opposite to the protruding direction. However, in this case, the rib does not function as a vibration isolating member holding portion. Moreover, although the rib 31e showed the example provided in the perimeter of an outer edge part, it is effective even if it provides in part, without restricting to this. For example, you may provide only in a circular arc part and may provide only in a linear part.

  In the embodiment shown in FIG. 2 to FIG. 9, the vibration isolation members 23 and 34 are annular members, and the structure covering the entire circumference of the contact portion between the casing 12 and the bearing holding members 21 and 31 is shown. However, the present invention is not limited to this, and a plurality of arc-shaped vibration-proof members may be arranged at a predetermined interval.

  Moreover, although the vibration isolator members 23 and 34 showed the example with the same thickness dimension of cylindrical part 23a, 34a and flange part 23b, 34b, it is not restricted to this, A cylindrical part by the magnitude | size, direction, etc. of a vibration The thickness dimension of 23a, 34a and the flange parts 23b, 34b may be arbitrarily changed, and the cylindrical part and the flange part may be formed separately. For example, it is conceivable to increase the thickness dimension in the direction of large vibration and decrease the thickness dimension in the direction of small vibration.

  Further, in each of the above-described embodiments, the example of the vibration isolating members 23 and 34 having the L-shaped cross section including the cylindrical portions 23a and 34a and the flange portions 23b and 34b has been shown, but the present invention is not limited thereto. , Can be any shape. For example, only the cylindrical portions 23a and 34a or the vibration isolation members having only the flange portions 23b and 34b may be used. Furthermore, a vibration isolating member having a shape as shown in FIGS. 10 and 11 may be used.

  A gear bearing device according to another embodiment of the present invention will be described with reference to FIGS. 10 and 11. 10 is a view showing a gear bearing device according to another embodiment of the present invention, and FIG. 11 is a cross-sectional view taken along line XI-XI in FIG.

  The gear bearing device shown in FIGS. 10 and 11 includes a casing 12 (not shown), bearings 42 and 43, and a bearing holding member 41. Since the bearing holding member 41 has the same basic configuration as the bearing holding member 21 shown in FIGS. 3 and 4, the description will focus on the differences. Moreover, since the bearings 42 and 43 are the same as the bearing 17, description is abbreviate | omitted.

  On the surface of the bearing holding member 41, an uneven portion 41e as a reinforcing portion protruding in a direction opposite to the protruding direction of the bearing fixing portions 41a and 41b is continuously provided so as to surround the bearing fixing portions 41a and 41b. An anti-vibration member 44 having an annular shape and a circular cross section is disposed at a part of the contact portion between the casing 12 and the bearing holding member 41. Thereby, the rigidity of the bearing holding member 41 is further improved. Further, the concave portion side of the concavo-convex portion 41 e also functions as a vibration isolating member holding portion that prevents the vibration isolating member 44 from falling off. When the bearing holding member 41 is manufactured by pressing as shown in FIGS. 5 to 7, the uneven portion 41 e may be formed before or after the first step shown in FIG. It may be after the second step shown in FIG.

  In the embodiment shown in FIGS. 10 and 11, the concave and convex portion 41e is structured to project in the direction opposite to the projecting direction of the bearing fixing portions 41a and 41b. However, the present invention is not limited thereto, and the bearing fixing portions 41a and 41b are not limited thereto. It is good also as a structure protruding in the same direction. Moreover, although the uneven | corrugated | grooved part 41e showed the example formed continuously on the surface of the bearing holding member 41, it is effective even if it provides partially, without restricting to this. Furthermore, you may provide both the rib shown in FIG. 8 and FIG. 9, and an uneven | corrugated | grooved part.

  Further, in the above embodiment, the vibration isolating member 44 is disposed only at a part of the contact portion between the casing 12 and the bearing holding member 41, and the portion where the casing 12 and the bearing holding member 41 are in direct contact with each other is provided. is there. However, even in such an embodiment, a certain vibration isolation effect can be expected.

  A gear bearing device according to another embodiment of the present invention will be described with reference to FIG. FIG. 12 is a partial cross-sectional view of a gear bearing device according to another embodiment of the present invention. This gear bearing device includes a casing 12 (not shown), a vibration isolating member (not shown), a bearing 52, and a bearing holding member 51. The bearing holding member 51 has the same basic configuration as the bearing holding member 21 shown in FIGS. Further, since the bearing 52 is the same as the bearing 17, the description thereof is omitted.

  The bearing holding member 51 has a ring member 53 as a bearing fixing means for preventing the bearing 52 from dropping off from the bearing fixing portion 51a. The ring member 53 is disposed at a position where it abuts against the end surface of the outer ring 52 b on the opening end side of the bearing fixing portion 51 a incorporating the bearing 52, and the outer edge thereof is fixed by welding to the bearing holding member 51. The ring member 53 has a hole 53a through which the rotation shaft is inserted at the center. The diameter of the hole 53a is set so as not to contact the inner ring 52a so as not to prevent smooth rotation of the bearing 52. With the above configuration, even when the dimensional tolerance between the inner wall surface of the bearing fixing portion 51a and the outer diameter surface of the outer ring 52b is large, there is no fear that the bearing 52 will drop off from the bearing fixing portion 51a during the rotation of the bearing.

  A gear bearing device according to another embodiment of the present invention will be described with reference to FIG. FIG. 13 is a partial cross-sectional view of a gear bearing device according to another embodiment of the present invention. The gear bearing device includes a casing 12 (not shown), a vibration isolating member (not shown), a bearing 62, and a bearing holding member 61. Since the bearing holding member 61 has the same basic configuration as the bearing holding member 21 shown in FIGS. 3 and 4, the description will focus on the differences. Further, since the bearing 62 is the same as the bearing 17, the description thereof is omitted.

  The bearing holding member 61 has a caulking portion 61c as a bearing fixing means for preventing the bearing 62 from dropping off from the bearing fixing portion 61a. In this embodiment, since a special member like the ring member 53 shown in FIG. 12 is not required, the number of parts can be reduced. Further, there is no fear that the structure of the bearing holding member 61 or the bearing 62 is altered by welding.

  The embodiments shown in FIGS. 12 and 13 can be applied to any of the embodiments shown in FIGS.

  In the embodiment shown in FIG. 1, the example in which the bearing holding member 21 is arranged along the outer wall surface of the casing 12 is shown. However, the present invention is not limited to this, and the bearing holding member 21 is arranged along the inner wall surface of the casing 12. May be. In this case, as long as the bearing holding member 21 has a shape that does not hinder the smooth rotation of the bearings 17 and 18, the holes 21c and 21d may not be provided. Further, the casing 12 may not have the hole 12c as long as the bearing holding member 21 can be fixed.

  In the embodiment shown in FIG. 1, an example in which the gear bearing device according to the present invention is adopted as a speed reducer has been shown. However, the present invention is not limited thereto, and a speed increaser, a transmission, a four-wheel drive vehicle transfer, It can be used for any gear device in which a plurality of rotation shafts are provided in parallel, such as a hydraulic pump.

  In each of the above embodiments, the bearing holding member has an example having two bearing fixing portions. However, the present invention is not limited to this, and the bearing holding member has one bearing fixing portion in accordance with the number of rotating shafts. It may be a thing, and may have two or more bearing fixing parts.

  In each of the above embodiments, an example in which a single-row ball bearing is used as a bearing for supporting the input shaft 13 and the output shaft 14 is shown. However, the present invention is not limited to this, and a double-row or multi-row ball bearing is used. May be adopted. Also, it is not limited to ball bearings, but can be applied to all types of rolling bearings regardless of whether the rolling elements are balls or rollers, cylindrical roller bearings, tapered roller bearings, needle roller bearings, self-aligning roller bearings. Can do. Furthermore, it is applicable not only to a rolling bearing having rolling elements but also to a sliding bearing.

  As mentioned above, although embodiment of this invention was described with reference to drawings, this invention is not limited to the thing of embodiment shown in figure. Various modifications and variations can be made to the illustrated embodiment within the same range or equivalent range as the present invention.

  INDUSTRIAL APPLICABILITY The present invention is advantageously used for a gear bearing device, particularly a gear bearing device that supports a rotating shaft of a gear device such as a speed reducer, a speed increaser, a transmission, a four-wheel drive vehicle transfer, and a hydraulic pump. The

It is a figure which shows the gear apparatus which employ | adopted the gear bearing apparatus which concerns on this invention. It is an enlarged view of the fitting part of the casing of FIG. 1 and the gear bearing apparatus. 1 is a front view of a gear bearing device according to an embodiment of the present invention. It is sectional drawing in IV-IV of FIG. It is a figure which shows the manufacturing method of the gear bearing apparatus shown in FIG. 3 and FIG. 4, Comprising: It is a figure which shows the steel plate which is a starting material. It is a figure which shows the manufacturing method of the gear bearing apparatus shown in FIG.3 and FIG.4, Comprising: It is a figure which shows the process of forming a bearing fixing | fixed part by drawing. It is a figure which shows the manufacturing method of the gear bearing apparatus shown in FIG. 3 and FIG. 4, Comprising: It is a figure which shows the process of forming a hole by stamping. It is a front view of the gear bearing device according to another embodiment of the present invention, and is a view showing the gear bearing device having a rib on the outer edge. It is sectional drawing in IX-IX of FIG. It is a front view of the bearing device for gears concerning other embodiments of this invention, and is a figure showing the bearing device for gears which has an uneven part on the surface. It is sectional drawing in XI-XI of FIG. It is a fragmentary sectional view of the gear bearing device concerning other embodiments of this invention, and is a figure showing the gear bearing device which has a ring part as bearing fixing means. It is a fragmentary sectional view of the gear bearing device concerning other embodiments of this invention, and is a figure showing the gear bearing device which has a caulking part as bearing fixing means. It is a figure which shows the conventional gear apparatus. It is an enlarged view of the fitting part of the casing and bearing of FIG.

Explanation of symbols

11, 101 gear device, 12, 102 casing, 12a, 102a opening, 12c, 21c, 21d, 31c, 31d, 41c, 41d, 51b, 53a, 61b hole, 12b, 102b recess, 13, 103 input shaft, 14, 104 output shaft, 15, 105 small gear, 16, 106 large gear, 17, 18, 19, 20, 32, 42, 52, 62, 107 bearing, 17a, 32a, 42a, 52a, 62a, 107a inner ring, 17b, 32b, 42b, 52b, 62b, 107b Outer ring, 17c, 32c, 42c, 52c, 62c, 107c Ball, 21, 22, 31, 41, 51, 61 Bearing holding member, 21a, 21b, 22a, 22b, 31a, 31b 41a, 41b, 51a, 61a Bearing fixing part, 21e Outer edge part, 21f Center part, 31e Rib, 41 Uneven portion, 53,108 ring member, 61c caulked portion, 23,34,44 vibration isolating member, 23a, 34a cylindrical portion, 23b, 34b flange portion.

Claims (4)

A casing having an opening through which a rotating shaft to which a gear is fixed is passed;
A bearing holding member fixed by being fitted into the opening of the casing;
An anti-vibration member disposed at a contact portion between the casing and the bearing holding member so that a vibration transmissibility is 1 or less;
A gear bearing device comprising: a bearing held by the bearing holding member and rotatably supporting the rotating shaft.   The gear vibration bearing device according to claim 1, wherein the vibration isolation member is attached in a compressed state between the casing and the bearing holding member.   3. The gear bearing device according to claim 1, wherein the vibration isolation member is fixed to the casing and / or the bearing holding member in a non-detachable manner. The casing has a plurality of openings through which the rotating shafts pass.
The gear bearing device according to claim 1, wherein the bearing holding member holds a bearing that rotatably supports each of the plurality of rotating shafts.

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