JPH10184663A - Bearing device - Google Patents
Bearing deviceInfo
- Publication number
- JPH10184663A JPH10184663A JP34718196A JP34718196A JPH10184663A JP H10184663 A JPH10184663 A JP H10184663A JP 34718196 A JP34718196 A JP 34718196A JP 34718196 A JP34718196 A JP 34718196A JP H10184663 A JPH10184663 A JP H10184663A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- load
- outer diameter
- fitting hole
- circular
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Electrophotography Configuration And Component (AREA)
- Rolls And Other Rotary Bodies (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、回転体の軸受装置
に係り、特に複写機やレーザプリンタ等の事務機におけ
る軸受装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device for a rotating body, and more particularly to a bearing device for an office machine such as a copying machine or a laser printer.
【０００２】[0002]
【従来の技術】従来の軸受装置の一例を図６及び図７を
用いて説明する。図６は駆動モータ101 の回転駆動力を
負荷装置102 に伝達する駆動ユニットＡを示す断面説明
図であり、側板103 に固定された駆動モータ101 の回転
軸に圧入されたギア105 が、側板103 ，104 に軸受106
，107 を介して回転可能に支持された回転軸108 に固
定されたギア109 に噛合する。回転軸108 の一端部には
駆動ユニットＡの出力ギア110 が固定されており、該出
力ギア110 には負荷装置102 の入力ギア111 が噛合して
いる。これにより、駆動モータ101 の回転駆動力はギア
105 ，109 、回転軸108 、出力ギア110 及び入力ギア11
1 を介して負荷装置102 に伝達される。2. Description of the Related Art An example of a conventional bearing device will be described with reference to FIGS. FIG. 6 is a sectional view showing a driving unit A for transmitting the rotational driving force of the driving motor 101 to the load device 102. The gear 105 press-fitted on the rotating shaft of the driving motor 101 fixed to the side plate 103 is connected to the side plate 103. , 104 and bearing 106
, 107 mesh with a gear 109 fixed to a rotating shaft 108 rotatably supported. An output gear 110 of the drive unit A is fixed to one end of the rotating shaft 108, and an input gear 111 of the load device 102 meshes with the output gear 110. As a result, the rotational driving force of the drive motor 101 is reduced by the gear.
105, 109, rotating shaft 108, output gear 110, and input gear 11
1 to the load device 102.
【０００３】ここで、軸受107 の側板104 に対する取付
部の構成について図７を用いて具体的に説明する。図７
（ａ）は軸受107 の構成を示す斜視図、図７（ｂ）は側
板104 に形成された軸受107 の嵌合穴112 を示す図、図
７（ｃ）は軸受107 を嵌合穴112 に取り付けた様子を示
す図である。Here, the structure of the mounting portion of the bearing 107 to the side plate 104 will be specifically described with reference to FIG. FIG.
7A is a perspective view showing the configuration of the bearing 107, FIG. 7B is a diagram showing a fitting hole 112 of the bearing 107 formed in the side plate 104, and FIG. 7C is a diagram showing the bearing 107 in the fitting hole 112. It is a figure showing signs that it was attached.
【０００４】軸受107 は図７（ａ）に示すように、回転
軸108 を回転可能に嵌挿する内径部107aと、図７（ｂ）
に示す側板104 の真円形状で形成された嵌合穴112 に嵌
合する外径部107bと、前記嵌合穴112 よりも大きい外径
を有するフランジ部107cを有しており、図７（ｃ）に示
すように、側板104 に形成された嵌合穴112 に軸受107
の外径部107bが嵌合されて支持され、軸受107 の内径部
107aに回転軸108 を嵌挿して回転可能に支持するように
なっている。As shown in FIG. 7A, a bearing 107 has an inner diameter portion 107a into which a rotary shaft 108 is rotatably inserted, and a bearing 107 shown in FIG.
7 has an outer diameter portion 107b fitted into a perfectly circular fitting hole 112 of the side plate 104, and a flange portion 107c having an outer diameter larger than the fitting hole 112. As shown in c), a bearing 107 is inserted into a fitting hole 112 formed in the side plate 104.
The outer diameter part 107b of the bearing 107 is fitted and supported, and the inner diameter part of the bearing 107 is
The rotating shaft 108 is inserted into the 107a and rotatably supported.
【０００５】事務機においては、負荷装置102 の負荷が
比較的軽く、軸受107 にかかる面圧が小さい場合には、
樹脂軸受を用いることが多く、負荷装置102 の負荷が比
較的重く、軸受107 にかかる面圧が３０kgf/cm2 以上と
大きい場合には、ボールベアリングや燃結軸受を用いる
のが一般的である。In office machines, when the load of the load device 102 is relatively light and the surface pressure applied to the bearing 107 is small,
In many cases, a resin bearing is used, and when the load of the load device 102 is relatively heavy and the surface pressure applied to the bearing 107 is as large as 30 kgf / cm 2 or more, a ball bearing or a fired bearing is generally used. .
【０００６】[0006]
【発明が解決しようとする課題】しかしながら、前述の
従来の技術において、軸受107 にかかる面圧が大きくて
ボールベアリングや燃結軸受を用いた場合、軸受にかか
るコストが樹脂軸受に比べて、ボールベアリングの場合
で約１０倍以上、燃結軸受でも２倍以上になってしまい
コストアップにつながるという問題がある。However, in the prior art described above, when a ball bearing or a fired bearing is used due to a large surface pressure applied to the bearing 107, the cost of the bearing is lower than that of the resin bearing. There is a problem that the cost is increased about 10 times or more in the case of the bearing and twice or more in the case of the fired bearing.
【０００７】また、燃結軸受では、回転軸108 の回転初
期には燃結軸受107 のポーラスからのオイルの染み出し
が十分でなく、該回転初期に軸受107 の表面が傷ついて
ポーラスが潰れてしまい、回転軸108 の回転中のオイル
の染み出しが不十分となり、軸受107 が摩耗する虞があ
る。In the case of the combustion bearing, oil does not sufficiently seep out of the porous portion of the combustion bearing 107 at the beginning of rotation of the rotary shaft 108, and the surface of the bearing 107 is damaged at the beginning of rotation and the porous body is crushed. As a result, the oil seeping out during rotation of the rotating shaft 108 becomes insufficient, and the bearing 107 may be worn.
【０００８】また、燃結軸受では、回転軸108 の温度が
高い場合や、回転軸108 と軸受107の内径部107aとのク
リアランスが大きい場合には、燃焼軸受の含浸油が流れ
出て、回転軸108 の回転中のオイルの染み出しが不十分
となり、軸受107 が摩耗してしまう虞がある。In the case of a combustion bearing, when the temperature of the rotating shaft 108 is high, or when the clearance between the rotating shaft 108 and the inner diameter portion 107a of the bearing 107 is large, oil impregnated in the combustion bearing flows out and the rotating shaft 108 During the rotation of the oil 108, the oil does not sufficiently seep out, and the bearing 107 may be worn.
【０００９】また、図６において、軸受107 には出力ギ
ア110 と入力ギア111 との噛み合い、及びギア105 ，10
9 の噛み合いによる回転力の伝達荷重が作用するが、ギ
ア105 ，109 の噛み合いにより軸受107 に作用する荷重
は比較的小さいので、軸受107 にかかる荷重方向は図７
（ｄ）に示すように、出力ギア110 と入力ギア111 との
噛み合いの圧力角方向Ｆと考えることが出来、この圧力
角方向Ｆに約３０kgf/cm2 以上の面圧がかかる。尚、圧
力角方向Ｆは出力ギア110 と入力ギア111 とが噛み合う
接線方向ｌに対してα（≒２０°）の方向である。In FIG. 6, a bearing 107 is engaged with an output gear 110 and an input gear 111, and gears 105, 10 are provided.
9 transmits a rotational force due to the engagement of the gears 9 and 9, but the load applied to the bearing 107 by the engagement of the gears 105 and 109 is relatively small.
As shown in (d), the meshing of the output gear 110 and the input gear 111 can be considered as a pressure angle direction F, and a surface pressure of about 30 kgf / cm 2 or more is applied in the pressure angle direction F. The pressure angle direction F is α (α20 °) with respect to the tangential direction 1 in which the output gear 110 and the input gear 111 mesh.
【００１０】ここで、軸受107 を樹脂軸受で構成した場
合、軸受107 は側板104 の嵌合穴112 から約３０kgf/cm
2 以上の面圧を直接受けるため、摩耗により破断する虞
がある。Here, when the bearing 107 is formed of a resin bearing, the bearing 107 is approximately 30 kgf / cm from the fitting hole 112 of the side plate 104.
Since it is directly subjected to two or more surface pressures, it may be broken by wear.
【００１１】本発明は前記課題を解決するものであり、
その目的とするところは、軸受の破断を防止して該軸受
の寿命を向上し、軸受のコストダウンを可能とする軸受
装置を提供せんとするものである。The present invention has been made to solve the above problems, and
It is an object of the present invention to provide a bearing device that prevents the bearing from being broken, improves the life of the bearing, and reduces the cost of the bearing.
【００１２】[0012]
【課題を解決するための手段】前記目的を達成するため
の本発明に係る代表的な構成は、軸を回転可能に支持す
る軸受を軸受支持部材に対して荷重が作用する方向に弾
性的に支持するように構成したことを特徴とする軸受装
置である。A typical configuration according to the present invention for achieving the above object is to elastically move a bearing rotatably supporting a shaft in a direction in which a load acts on a bearing support member. A bearing device configured to be supported.
【００１３】本発明は、上述の如く構成したので、軸受
が軸受支持部材に対して荷重が作用する方向に弾性的に
支持されることで、該軸受にかかる荷重を吸収すること
が出来る。[0013] Since the present invention is configured as described above, the load applied to the bearing can be absorbed by the bearing being elastically supported in the direction in which the load acts on the bearing support member.
【００１４】また、前記軸受は樹脂を成形して構成さ
れ、前記軸受の荷重が作用する方向下流側外形部に対応
する前記軸受支持部材の部位に該軸受の逃げ部を設けた
ことを特徴とする。Further, the bearing is formed by molding a resin, and a relief portion of the bearing is provided at a portion of the bearing support member corresponding to a downstream external portion in a direction in which a load acts on the bearing. I do.
【００１５】上記構成によれば、軸受にかかる面圧が３
０kgf/cm2 以上となる部位に樹脂軸受を用いる場合に、
樹脂軸受が軸受支持部材の逃げ部に変形して逃げること
が出来、摩耗による破断を防止して軸受の寿命を向上す
ることが出来る。According to the above construction, the surface pressure applied to the bearing is 3
When a resin bearing is used in a part where the weight becomes 0 kgf / cm 2 or more,
The resin bearing can be deformed and escape to the escape portion of the bearing support member, thereby preventing breakage due to wear and improving the life of the bearing.
【００１６】また、前記軸受の荷重が作用する方向下流
側外形部に切り込みを設け、該軸受の肉厚の薄い部分を
設けた場合には、該樹脂軸受の外形部に設けた切り込み
による該軸受の肉厚の薄い部分において該軸受が軸受支
持部材の逃げ部に変形し易くなり、好ましい。In the case where a notch is provided in the outer portion on the downstream side in the direction in which the load of the bearing acts and a thin portion of the bearing is provided, the bearing is formed by the notch provided in the outer portion of the resin bearing. It is preferable that the bearing is easily deformed into a relief portion of the bearing support member in a thin portion of the bearing.
【００１７】また、前記軸受は燃結軸受で構成され、該
軸受を弾性部材を介して前記軸受支持部材に対して支持
するように構成したことを特徴とする。Further, the bearing is constituted by a combustion bearing, and the bearing is supported on the bearing support member via an elastic member.
【００１８】上記構成によれば、軸受は、弾性部材の弾
性力により軸の回転開始時に荷重方向に逃げることが可
能となり、ポーラスからのオイルの染み出しが十分でな
い回転初期に該軸受の内径表面を傷つけることがなく、
回転中のオイルの染み出しが不十分となることがない。
これにより、軸受の耐久性能が向上する。According to the above construction, the bearing can escape in the load direction at the start of rotation of the shaft due to the elastic force of the elastic member, and the inner surface of the bearing can be released at the beginning of rotation when the oil does not sufficiently seep out from the porous body. Without damaging
The leakage of oil during rotation does not become insufficient.
Thereby, the durability performance of the bearing is improved.
【００１９】また、前記燃結軸受を前記軸受支持部材に
対して荷重が作用する方向にスライド可能で、且つ、前
記軸受を弾性部材により前記軸受支持部材に対して所定
方向に付勢して支持するように構成した場合には、軸の
回転開始時に軸受がスライドして荷重方向に逃げること
が可能となり、ポーラスからのオイルの染み出しが十分
でない回転初期に該軸受の内径表面を傷つけることがな
く、回転中のオイルの染み出しが不十分となることがな
い。これにより、軸受の耐久性能が向上する。Further, the fuel bearing can be slid in a direction in which a load acts on the bearing support member, and the bearing is urged by an elastic member in a predetermined direction with respect to the bearing support member to be supported. In such a case, when the rotation of the shaft is started, the bearing can slide and escape in the load direction, and the inner surface of the bearing may be damaged at the beginning of rotation when the oil does not sufficiently seep out from the porous body. In addition, the oil does not leak out during rotation. Thereby, the durability performance of the bearing is improved.
【００２０】[0020]
【発明の実施の形態】図により本発明に係る軸受装置の
一実施形態を具体的に説明する。図１は本発明に係る軸
受装置の全体構成を示す断面説明図、図２（ａ）は本発
明に係る軸受装置の第１実施形態の軸受の構成を示す斜
視図、図２（ｂ）は第１実施形態の軸受の構成を示す平
面図、図２（ｃ）は本発明に係る軸受装置の第１実施形
態の軸受支持部材に形成された軸受の嵌合穴を示す図、
図２（ｄ）は第１実施形態において軸受を嵌合穴に取り
付けた様子を示す図、図３（ａ）は軸受が受ける荷重の
方向を示す図、図３（ｂ）は第１実施形態の軸受が変形
した様子を示す図である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of a bearing device according to the present invention will be specifically described with reference to the drawings. FIG. 1 is a cross-sectional explanatory view showing the overall configuration of a bearing device according to the present invention, FIG. 2A is a perspective view showing the configuration of a bearing according to a first embodiment of the bearing device according to the present invention, and FIG. FIG. 2C is a plan view illustrating the configuration of the bearing according to the first embodiment, and FIG. 2C is a diagram illustrating a fitting hole of a bearing formed in the bearing support member according to the first embodiment of the bearing device according to the present invention;
FIG. 2D is a view showing a state where the bearing is attached to the fitting hole in the first embodiment, FIG. 3A is a view showing the direction of a load received by the bearing, and FIG. 3B is a first embodiment. FIG. 6 is a view showing a state in which the bearing of FIG.
【００２１】先ず、図１を用いて本発明に係る軸受装置
の全体構成について説明する。図１において、駆動モー
タ１の回転駆動力は駆動ユニットＡを介して負荷装置２
に伝達されるようになっている。First, the overall structure of the bearing device according to the present invention will be described with reference to FIG. In FIG. 1, the rotational driving force of a driving motor 1 is transmitted to a load device 2 via a driving unit A.
It is transmitted to.
【００２２】駆動ユニットＡの筐体を構成する軸受支持
部材となる側板３，４の一方である側板３に固定された
駆動モータ１の回転軸にはギア５が圧入されており、該
ギア５は側板３，４に取り付けられた軸受６，７により
回転可能に支持された回転軸８に固定されたギア９に噛
合する。A gear 5 is press-fitted into the rotation shaft of the drive motor 1 fixed to one of the side plates 3 and 4 serving as bearing support members constituting the housing of the drive unit A. Meshes with a gear 9 fixed to a rotating shaft 8 rotatably supported by bearings 6 and 7 attached to the side plates 3 and 4.
【００２３】回転軸８の一端部には駆動ユニットＡの出
力ギア10が固定されており、該出力ギア10には負荷装置
２の入力ギア11が噛合している。これによって、駆動モ
ータ１の回転駆動力はギア５，９、回転軸８、出力ギア
10及び入力ギア11を介して負荷装置２に伝達される。An output gear 10 of the drive unit A is fixed to one end of the rotating shaft 8, and an input gear 11 of the load device 2 meshes with the output gear 10. As a result, the rotational driving force of the driving motor 1 is changed to the gears 5 and 9, the rotating shaft 8 and the output gear.
The power is transmitted to the load device 2 via the input gear 10 and the input gear 11.
【００２４】ここで、軸受７の側板４に対する取付部の
構成について図２及び図３を用いて具体的に説明する。
図において、軸受７は荷重を受けて変形可能なポリアセ
タール樹脂を成形して構成され、図２（ａ），（ｂ）に
示すように、回転軸８が摺動して該回転軸８を回転可能
に嵌挿する内径部７ａと、図２（ｃ）に示す側板４の嵌
合穴12の円形部12ａに嵌合する外径部７ｂと、前記嵌合
穴12の円形部12ａよりも大きい外径を有するフランジ部
７ｃを有している。Here, the structure of the mounting portion of the bearing 7 to the side plate 4 will be specifically described with reference to FIGS.
In the figure, a bearing 7 is formed by molding a polyacetal resin which can be deformed under a load, and as shown in FIGS. 2 (a) and 2 (b), the rotating shaft 8 slides to rotate the rotating shaft 8. An inner diameter portion 7a to be inserted as much as possible, an outer diameter portion 7b to be fitted to the circular portion 12a of the fitting hole 12 of the side plate 4 shown in FIG. It has a flange portion 7c having an outer diameter.
【００２５】また、前記外径部７ｂの一部には該外径部
７ｂから突出すると共に、該軸受７の軸方向に形成され
た回り止め部７ｄが設けてあり、図２（ｄ）に示すよう
に、軸受７を嵌合穴12に嵌合した状態で、該回り止め部
７ｄが図２（ｃ）に示す側板４の嵌合穴12の円形部12ａ
の一部を切り欠いて形成された逃げ部12ｂの当接辺12ｃ
に当接して該軸受７の回転を規制して係止し得るように
なっている。A part of the outer diameter part 7b is provided with a rotation preventing part 7d which protrudes from the outer diameter part 7b and is formed in the axial direction of the bearing 7, as shown in FIG. As shown in the drawing, in a state where the bearing 7 is fitted in the fitting hole 12, the rotation preventing portion 7d is formed into a circular portion 12a of the fitting hole 12 of the side plate 4 shown in FIG.
Abutment side 12c of escape portion 12b formed by cutting out a part of
, So that the rotation of the bearing 7 can be restricted and locked.
【００２６】前述の側板４に形成された嵌合穴12は、図
２（ｃ）に示すように、軸受７の外径部７ｂの外径に対
応する内径を有する円形部12ａと、該円形部12ａの一部
を所定の幅を有して略９０°の円弧状に切り欠いた逃げ
部12ｂを有しており、この逃げ部12ｂは図２（ｃ）に示
すように、円形部12ａの軸受７が荷重を受ける圧力角方
向Ｆの下流側に形成され、軸受７が荷重方向である圧力
角方向Ｆの下流側に変形できるように設けられている。As shown in FIG. 2C, the fitting hole 12 formed in the side plate 4 has a circular portion 12a having an inner diameter corresponding to the outer diameter of the outer diameter portion 7b of the bearing 7, and the circular portion 12a. A part of the part 12a has a relief part 12b having a predetermined width and being cut out in an arc shape of about 90 °, and as shown in FIG. 2C, the relief part 12b has a circular part 12a. The bearing 7 is formed on the downstream side in the pressure angular direction F that receives a load, and is provided so as to be deformable downstream in the pressure angular direction F that is the load direction.
【００２７】そして、図２（ｄ）に示すように、側板４
に形成された嵌合穴12の円形部12ａに軸受７の外径部７
ｂを嵌合すると共に、逃げ部12ｂに回り止め部７ｄを合
わせて嵌入して軸受７が側板４に支持され、同じく軸受
６も側板３の嵌合穴13に嵌入して支持され、軸受６，７
の内径部６ａ，７ａに回転軸８を嵌挿して回転可能に支
持するようになっている。Then, as shown in FIG.
The circular portion 12a of the fitting hole 12 formed in the
b, the bearing 7 is supported by the side plate 4 by fitting the rotation preventing portion 7d to the escape portion 12b, and the bearing 6 is also supported by fitting into the fitting hole 13 of the side plate 3. , 7
The rotary shaft 8 is inserted into the inner diameter portions 6a and 7a of the first and second rotatable supports.
【００２８】また、図１において、軸受７には出力ギア
10と入力ギア11との噛み合い、及びギア５，９の噛み合
いによる回転力の伝達荷重が作用するが、ギア５，９の
噛み合いにより軸受７に作用する荷重は比較的小さいの
で、軸受７にかかる荷重方向は図３（ａ）に示すよう
に、出力ギア10と入力ギア11との噛み合いの圧力角方向
Ｆと考えることが出来、この圧力角方向Ｆに約３０kgf/
cm2 以上の面圧がかかる。尚、圧力角方向Ｆは出力ギア
10と入力ギア11とが噛み合う接線方向ｌに対してα（≒
２０°）の方向である。In FIG. 1, the bearing 7 has an output gear.
A transmission load of rotational force due to the meshing of the input gear 11 with the input gear 11 and the meshing of the gears 5 and 9 acts. However, the load applied to the bearing 7 by the meshing of the gears 5 and 9 is relatively small. As shown in FIG. 3 (a), the load direction can be considered as the pressure angle direction F of the engagement between the output gear 10 and the input gear 11, and the pressure angle direction F is about 30 kgf /
Surface pressure of 2 cm2 or more is applied. The pressure angle direction F is the output gear.
Α (≒) with respect to the tangential direction 1 where the input gear 10 and the input gear 11 mesh.
20 °).
【００２９】上記の構成により、軸受７に作用する面圧
が大きい場合には、軸受７は図３（ｂ）に示すように、
嵌合穴12の逃げ部12ｂの方向に変形するので、樹脂軸受
７であっても該軸受７が摩耗して破断する虞がない。With the above configuration, when the surface pressure acting on the bearing 7 is large, the bearing 7 is moved as shown in FIG.
Since the bearing 7 is deformed in the direction of the escape portion 12b of the fitting hole 12, there is no possibility that the resin bearing 7 is worn and broken.
【００３０】次に図４（ａ）〜（ｃ）を用いて本発明に
係る軸受装置の第２実施形態について説明する。図４
（ａ）は本発明に係る軸受装置の第２実施形態の軸受の
構成を示す斜視図、図４（ｂ）は第２実施形態の軸受の
構成を示す平面図、図４（ｃ）は第２実施形態において
軸受を嵌合穴に取り付けた様子を示す図である。尚、前
記第１実施形態と同様に構成したものは同一の符号を付
して説明を省略する。Next, a second embodiment of the bearing device according to the present invention will be described with reference to FIGS. FIG.
(A) is a perspective view showing a configuration of a bearing of a second embodiment of the bearing device according to the present invention, FIG. 4 (b) is a plan view showing a configuration of the bearing of the second embodiment, and FIG. It is a figure showing signs that a bearing was attached to a fitting hole in a 2nd embodiment. The same components as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
【００３１】本実施形態では、前記第１実施形態の軸受
７の荷重が作用する圧力角方向Ｆの下流側（嵌合穴12の
逃げ部12ｂに対応する側）の外径部７ｂに、逃げ部12ｂ
の長さに対応する寸法だけ離間して配置され、該軸受７
の軸方向に形成された２本の切り込み７ｅ，７ｆが設け
てあり、該切り込み７ｅ，７ｆの間の部位ではフランジ
部７ｃが削除されている。In the present embodiment, the outer diameter portion 7b on the downstream side (the side corresponding to the relief portion 12b of the fitting hole 12) in the pressure angular direction F where the load of the bearing 7 of the first embodiment is applied acts as a relief. Part 12b
Are spaced apart by a dimension corresponding to the length of the bearing 7.
Are provided in the axial direction, and two cuts 7e and 7f are provided, and a flange portion 7c is deleted at a portion between the cuts 7e and 7f.
【００３２】上記構成により、前記第１実施形態と同様
にポリアセタール樹脂を成形して構成された軸受７の切
り込み７ｅ，７ｆによる内径部７ａと外径部７ｂとの間
の肉厚の薄い部分が出来るために、軸受７に作用する面
圧が大きい場合には、軸受７は切り込み７ｅ，７ｆの部
分から逃げ部12ｂの方向に変形し易くなるので、軸受７
が摩耗して破断してしまうことがない。With the above configuration, the thin portion between the inner diameter portion 7a and the outer diameter portion 7b due to the cuts 7e and 7f of the bearing 7 formed by molding a polyacetal resin as in the first embodiment is formed. For this reason, when the surface pressure acting on the bearing 7 is large, the bearing 7 is easily deformed from the cuts 7e and 7f toward the escape portion 12b.
Does not wear and break.
【００３３】次に図５（ａ）〜（ｄ）を用いて本発明に
係る軸受装置の第３実施形態について説明する。図５
（ａ）は本発明に係る軸受装置の第３実施形態の軸受の
構成を示す斜視図、図５（ｂ）は本発明に係る軸受装置
の第３実施形態の軸受支持部材に形成された軸受の嵌合
穴を示す図、図５（ｃ）は第３実施形態において軸受を
嵌合穴に取り付けた様子を示す図である。尚、前記第１
実施形態と同様に構成したものは同一の符号を付して説
明を省略する。Next, a third embodiment of the bearing device according to the present invention will be described with reference to FIGS. 5 (a) to 5 (d). FIG.
FIG. 5A is a perspective view showing the configuration of a bearing according to a third embodiment of the bearing device according to the present invention, and FIG. 5B is a bearing formed on a bearing support member according to the third embodiment of the bearing device according to the present invention. FIG. 5C is a diagram showing a state where the bearing is attached to the fitting hole in the third embodiment. In addition, the first
Components configured in the same manner as in the embodiment are denoted by the same reference numerals and description thereof is omitted.
【００３４】図５（ａ）において、本実施形態の軸受21
は燃結含油軸受であり、回転軸８が摺動して該回転軸８
を回転可能に嵌挿する内径部21ａと、図５（ｂ）に示す
側板４に形成された長穴22に嵌合する外径部21ｂと、前
記長穴22よりも大きい外形を有するフランジ部21ｃを有
している。In FIG. 5A, the bearing 21 of the present embodiment is shown.
Is a fired oil-impregnated bearing, in which the rotating shaft 8 slides,
5B, an outer diameter portion 21b fitted into a long hole 22 formed in the side plate 4 shown in FIG. 5B, and a flange portion having an outer shape larger than the long hole 22. 21c.
【００３５】前記外形部21ｂは回り止め部を兼ねるよう
に、前記長穴22の外形に対応して互いに対向する両側に
カット面21b1が形成されており、フランジ部21ｃの前記
カット面21b1に対応する部位にもカット面21c1が形成さ
れている。The outer surface portion 21b is formed with cut surfaces 21b1 on both sides facing each other corresponding to the outer shape of the elongated hole 22 so as to also serve as a rotation preventing portion, and corresponds to the cut surface 21b1 of the flange portion 21c. The cut surface 21c1 is also formed at the portion where the cutting is performed.
【００３６】また、前記フランジ部21ｃの長手方向（カ
ット面21c1が形成されていない側）の両側には図５
（ｃ）に示す弾性部材となる引っ張りバネ23の一端を係
止するための穴21ｄが形成されている。FIG. 5 shows two sides of the flange 21c in the longitudinal direction (the side where the cut surface 21c1 is not formed).
A hole 21d for locking one end of a tension spring 23 serving as an elastic member shown in (c) is formed.
【００３７】前記長穴22は、図５（ｂ）に示すように、
互いに対向する直線部と、該直線部の両側に接続される
円弧部とからなり、その長手方向が、前記第１実施形態
において、図３（ａ）に示した圧力角方向Ｆに一致して
配置されている。また、長穴22の長手方向（図５（ｂ）
の左右方向）の寸法は、軸受21の外径部21ｂの長手方向
（図５（ａ）の左右方向）の寸法よりも所定長さだけ長
くなるように構成されている。As shown in FIG. 5 (b),
It consists of straight portions facing each other, and arc portions connected to both sides of the straight portions, and the longitudinal direction thereof coincides with the pressure angular direction F shown in FIG. 3A in the first embodiment. Are located. The longitudinal direction of the elongated hole 22 (FIG. 5B)
(Horizontal direction of the bearing 21) is configured to be longer by a predetermined length than the dimension of the outer diameter portion 21b of the bearing 21 in the longitudinal direction (horizontal direction in FIG. 5A).
【００３８】従って、軸受21の外径部21ｂを軸受支持部
材である側板４の長穴22に嵌入した状態で軸受21が長穴
22に沿って荷重が作用する方向にスライド可能に支持さ
れるようになっている。Therefore, when the outer diameter portion 21b of the bearing 21 is fitted into the elongated hole 22 of the side plate 4 as a bearing support member, the bearing 21 is
It is supported so as to be slidable in the direction in which a load acts along 22.
【００３９】図５（ｃ）に示すように、軸受21のフラン
ジ部21ｃに形成された穴21ｄに係止された引っ張りバネ
23の他端は側板４に係止されており、軸受21が側板４の
長穴22に嵌入して取り付けられた際に軸受21は引っ張り
バネ23の引っ張り力により長穴22の圧力角方向Ｆ（図３
（ａ）参照）の上流側に引き寄せられている。As shown in FIG. 5C, a tension spring locked in a hole 21d formed in the flange portion 21c of the bearing 21.
The other end of the lock 23 is locked to the side plate 4, and when the bearing 21 is fitted and mounted in the elongated hole 22 of the side plate 4, the bearing 21 is pulled by the tension force of the extension spring 23 in the pressure angular direction F of the elongated hole 22. (FIG. 3
(See (a)).
【００４０】上記構成により、軸受21は回転軸８の回転
初期の起動時に軸受21が引っ張りバネ23の引っ張り力に
抗して長穴22に沿って荷重方向である図３（ａ）に示し
た圧力角方向Ｆの下流側へ逃げることが可能となり、こ
れによって、燃結軸受21のポーラスからのオイルの染み
出しが十分でない回転初期に該軸受21の表面を傷つけて
回転軸８の回転中のオイルの染み出しが不十分となるこ
とがなくなり、軸受21の耐久性を向上することが出来
る。With the above configuration, the bearing 21 is in the load direction along the elongated hole 22 against the pulling force of the tension spring 23 when the bearing 21 is started at the beginning of rotation of the rotating shaft 8 as shown in FIG. It is possible to escape to the downstream side in the pressure angle direction F, thereby damaging the surface of the bearing 21 at the initial stage of rotation when the oil does not seep out sufficiently from the porous portion of the combustion bearing 21 and rotating the rotary shaft 8 during rotation. Insufficient oil seepage can be prevented, and the durability of the bearing 21 can be improved.
【００４１】また、図５（ｄ）は燃結含油軸受21の他の
構成を示す図であり、引っ張りバネ23の代わりに、軸受
21の外径部21ｂの外周に弾性部材となるゴム層24を設
け、該ゴム層24の外形に対応する形状の長穴22を側板４
に形成して構成したものである。FIG. 5D is a view showing another configuration of the fired oil-impregnated bearing 21. Instead of the tension spring 23, a bearing is used.
A rubber layer 24 serving as an elastic member is provided on the outer periphery of an outer diameter portion 21b of the side plate 21. An elongated hole 22 corresponding to the outer shape of the rubber layer 24 is
It is formed and formed.
【００４２】上記構成によれば、軸受21は回転軸８の回
転初期の起動時に軸受21がゴム層24の弾性力により長穴
22に沿って荷重方向である図３（ａ）に示した圧力角方
向Ｆの下流側へ逃げることが可能となり、前述と同様
に、燃結軸受21のポーラスからのオイルの染み出しが十
分でない回転初期に該軸受21の表面を傷つけて回転軸８
の回転中のオイルの染み出しが不十分となることがなく
なり、軸受21の耐久性を向上することが出来る。According to the above configuration, the bearing 21 is driven by the elastic force of the rubber layer 24 when the rotating shaft 8 starts rotating at the beginning of rotation.
It is possible to escape to the downstream side in the pressure angular direction F shown in FIG. 3A which is the load direction along the direction 22, and the seepage of oil from the porous of the combustion bearing 21 is not sufficient as described above. At the beginning of rotation, the surface of the bearing 21 is damaged to
It is possible to prevent the oil seeping out during rotation of the roller from becoming insufficient, and to improve the durability of the bearing 21.
【００４３】[0043]
【発明の効果】本発明は、上述の如き構成と作用とを有
するので、軸受にかかる面圧が大きな場所に樹脂軸受を
用いる際に、樹脂軸受が荷重方向に変形できるように軸
受支持部材に逃げ部を設け、更にその逃げ部方向に樹脂
軸受が変形しやすいように、該樹脂軸受の外形に切り込
みを設けて樹脂の肉厚の薄い部分を設けたことで、該樹
脂軸受は軸受支持部材に設けた逃げ部に容易に変形して
逃げることが出来、摩耗により破断することがなく、軸
受寿命が延び、樹脂軸受を使用することが可能であるた
めボールベアリングや燃結軸受を用いる必要がなくなる
ので軸受のコストダウンが可能になる。Since the present invention has the above-described structure and operation, when the resin bearing is used in a place where the surface pressure applied to the bearing is large, the bearing support member is formed so that the resin bearing can be deformed in the load direction. A relief portion is provided, and a cutout is provided in the outer shape of the resin bearing so that the resin bearing is easily deformed in the direction of the relief portion to provide a thin portion of the resin. It can be easily deformed and escaped to the relief part provided in the car, it does not break due to wear, the bearing life is extended, and it is necessary to use a ball bearing or a fired bearing because it is possible to use a resin bearing Since it is eliminated, the cost of the bearing can be reduced.
【００４４】また、軸受にかかる面圧が大きな場所に燃
結軸受を用いる場合には、該燃結軸受を弾性部材を介し
て軸受支持部材に支持することで、燃結軸受は軸の回転
開始時に弾性部材の弾性力に抗して荷重方向に逃げるこ
とが可能となるので、燃結軸受のポーラスからのオイル
の染み出しが十分でない回転初期に軸受の表面を傷つけ
ることが無くなり、軸受の耐久性を向上させることが出
来る。When the combustion bearing is used in a place where the surface pressure applied to the bearing is large, the combustion bearing is supported by a bearing support member via an elastic member so that the combustion bearing starts rotating. Sometimes it is possible to escape in the load direction against the elastic force of the elastic member, so that the oil does not seep out from the porous of the fired bearing and the surface of the bearing is not damaged at the beginning of rotation and the durability of the bearing Properties can be improved.
【図１】図１は本発明に係る軸受装置の全体構成を示す
断面説明図である。FIG. 1 is an explanatory cross-sectional view showing the overall configuration of a bearing device according to the present invention.
【図２】（ａ）は本発明に係る軸受装置の第１実施形態
の軸受の構成を示す斜視図、（ｂ）は第１実施形態の軸
受の構成を示す平面図、（ｃ）は本発明に係る軸受装置
の第１実施形態の軸受支持部材に形成された軸受の嵌合
穴を示す図、（ｄ）は第１実施形態において軸受を嵌合
穴に取り付けた様子を示す図である。2A is a perspective view showing a configuration of a bearing according to a first embodiment of the bearing device according to the present invention, FIG. 2B is a plan view showing a configuration of the bearing according to the first embodiment, and FIG. FIG. 4 is a view showing a fitting hole of a bearing formed in a bearing support member of the first embodiment of the bearing device according to the present invention, and FIG. 4D is a view showing a state where the bearing is attached to the fitting hole in the first embodiment. .
【図３】（ａ）は軸受が受ける荷重の方向を示す図、
（ｂ）は第１実施形態の軸受が変形した様子を示す図で
ある。FIG. 3A is a diagram showing a direction of a load received by a bearing;
(B) is a figure which shows a mode that the bearing of 1st Embodiment deformed.
【図４】（ａ）は本発明に係る軸受装置の第２実施形態
の軸受の構成を示す斜視図、（ｂ）は第２実施形態の軸
受の構成を示す平面図、（ｃ）は第２実施形態において
軸受を嵌合穴に取り付けた様子を示す図である。4A is a perspective view showing a configuration of a bearing according to a second embodiment of the bearing device according to the present invention, FIG. 4B is a plan view showing a configuration of the bearing according to the second embodiment, and FIG. It is a figure showing signs that a bearing was attached to a fitting hole in a 2nd embodiment.
【図５】（ａ）は本発明に係る軸受装置の第３実施形態
の軸受の構成を示す斜視図、（ｂ）は本発明に係る軸受
装置の第３実施形態の軸受支持部材に形成された軸受の
嵌合穴を示す図、（ｃ）は第３実施形態において軸受を
嵌合穴に取り付けた様子を示す図、（ｄ）は他の軸受の
構成を示す図である。5A is a perspective view showing a configuration of a bearing according to a third embodiment of the bearing device according to the present invention, and FIG. 5B is formed on a bearing support member according to the third embodiment of the bearing device according to the present invention; FIG. 7C is a diagram illustrating a fitting hole of the bearing, FIG. 7C is a diagram illustrating a state where the bearing is attached to the fitting hole in the third embodiment, and FIG. 7D is a diagram illustrating a configuration of another bearing.
【図６】従来例を説明する図である。FIG. 6 is a diagram illustrating a conventional example.
【図７】従来例を説明する図である。FIG. 7 is a diagram illustrating a conventional example.
１…駆動モータ、２…負荷装置、３，４…側板、５…ギ
ア、６，７…軸受、７ａ…内径部、７ｂ…外径部、７ｃ
…フランジ部、７ｄ…回り止め部、７ｅ，７ｆ…切り込
み、８…回転軸、９…ギア、10…出力ギア、11…入力ギ
ア、12，13…嵌合穴、12ａ…円形部、12ｂ…逃げ部、12
ｃ…当接辺、21…軸受、21ａ…内径部、21ｂ…外径部、
21b1…カット面、21ｃ…フランジ部、21c1…カット面、
21ｄ…穴、22…長穴、23…引っ張りバネ、Ａ…駆動ユニ
ットDESCRIPTION OF SYMBOLS 1 ... Drive motor, 2 ... Load device, 3, 4 ... Side plate, 5 ... Gear, 6, 7 ... Bearing, 7a ... Inside diameter part, 7b ... Outside diameter part, 7c
... Flange part, 7d ... detent part, 7e, 7f ... notch, 8 ... rotary shaft, 9 ... gear, 10 ... output gear, 11 ... input gear, 12, 13 ... fitting hole, 12a ... circular part, 12b ... Escape, 12
c: contact side, 21: bearing, 21a: inner diameter part, 21b: outer diameter part,
21b1 ... cut surface, 21c ... flange portion, 21c1 ... cut surface,
21d: Hole, 22: Slot, 23: Tension spring, A: Drive unit
Claims (6)
部材に対して荷重が作用する方向に弾性的に支持するよ
うに構成したことを特徴とする軸受装置。1. A bearing device, wherein a bearing for rotatably supporting a shaft is elastically supported in a direction in which a load acts on a bearing support member.
記軸受の荷重が作用する方向下流側外形部に対応する前
記軸受支持部材の部位に該軸受の逃げ部を設けたことを
特徴とする請求項１に記載の軸受装置。2. The bearing according to claim 1, wherein the bearing is formed by molding a resin, and a relief portion of the bearing is provided at a portion of the bearing support member corresponding to a downstream external portion in a direction in which a load of the bearing acts. The bearing device according to claim 1.
形部に切り込みを設け、該軸受の肉厚の薄い部分を設け
たことを特徴とする請求項２に記載の軸受装置。3. The bearing device according to claim 2, wherein a notch is provided in a downstream external portion in a direction in which a load of the bearing acts, and a thin portion of the bearing is provided.
を弾性部材を介して前記軸受支持部材に対して支持する
ように構成したことを特徴とする請求項１に記載の軸受
装置。4. The bearing device according to claim 1, wherein the bearing is constituted by a fired bearing, and the bearing is configured to be supported by the bearing support member via an elastic member.
を前記軸受支持部材に対して荷重が作用する方向にスラ
イド可能で、且つ、前記軸受を弾性部材により前記軸受
支持部材に対して所定方向に付勢して支持するように構
成したことを特徴とする請求項１に記載の軸受装置。5. The bearing according to claim 1, wherein the bearing is a fired bearing, the bearing is slidable in a direction in which a load is applied to the bearing support member, and the bearing is moved relative to the bearing support member by an elastic member. The bearing device according to claim 1, wherein the bearing device is configured to be urged and supported in a predetermined direction.
f/cm2 以上であることを特徴とする請求項１〜５のいず
れか１項に記載の軸受装置。6. A bearing having a surface pressure of 30 kg applied to the bearing.
The bearing device according to claim 1, wherein f / cm 2 or more.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP34718196A JPH10184663A (en) | 1996-12-26 | 1996-12-26 | Bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP34718196A JPH10184663A (en) | 1996-12-26 | 1996-12-26 | Bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH10184663A true JPH10184663A (en) | 1998-07-14 |
Family
ID=18388477
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP34718196A Pending JPH10184663A (en) | 1996-12-26 | 1996-12-26 | Bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH10184663A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008299121A (en) * | 2007-05-31 | 2008-12-11 | Fuji Xerox Co Ltd | Driving force transmission device and image forming apparatus |
| JP2009217017A (en) * | 2008-03-11 | 2009-09-24 | Brother Ind Ltd | Image forming apparatus |
| US7597321B2 (en) | 2004-10-14 | 2009-10-06 | Funai Electric Co., Ltd. | Image forming apparatus |
| US8200122B2 (en) | 2009-09-16 | 2012-06-12 | Brother Kogkyo Kabushiki Kaishi | Bearing device, drum unit, and image forming apparatus |
| JP2017072753A (en) * | 2015-10-08 | 2017-04-13 | 京セラドキュメントソリューションズ株式会社 | Image forming apparatus |
-
1996
- 1996-12-26 JP JP34718196A patent/JPH10184663A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7597321B2 (en) | 2004-10-14 | 2009-10-06 | Funai Electric Co., Ltd. | Image forming apparatus |
| JP2008299121A (en) * | 2007-05-31 | 2008-12-11 | Fuji Xerox Co Ltd | Driving force transmission device and image forming apparatus |
| JP2009217017A (en) * | 2008-03-11 | 2009-09-24 | Brother Ind Ltd | Image forming apparatus |
| JP4596022B2 (en) * | 2008-03-11 | 2010-12-08 | ブラザー工業株式会社 | Image forming apparatus |
| US8027626B2 (en) | 2008-03-11 | 2011-09-27 | Brother Kogyo Kabushiki Kaisha | Image forming apparatus |
| US8200122B2 (en) | 2009-09-16 | 2012-06-12 | Brother Kogkyo Kabushiki Kaishi | Bearing device, drum unit, and image forming apparatus |
| US8442417B2 (en) | 2009-09-16 | 2013-05-14 | Brother Kogyo Kabushiki Kaisha | Bearing device, drum unit, and image forming apparatus |
| JP2017072753A (en) * | 2015-10-08 | 2017-04-13 | 京セラドキュメントソリューションズ株式会社 | Image forming apparatus |
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