JPH0139964Y2 - - Google Patents
Info
- Publication number
- JPH0139964Y2 JPH0139964Y2 JP12035684U JP12035684U JPH0139964Y2 JP H0139964 Y2 JPH0139964 Y2 JP H0139964Y2 JP 12035684 U JP12035684 U JP 12035684U JP 12035684 U JP12035684 U JP 12035684U JP H0139964 Y2 JPH0139964 Y2 JP H0139964Y2
- Authority
- JP
- Japan
- Prior art keywords
- piston
- transmission body
- pressure oil
- oil chamber
- pressure
- 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.)
- Expired
Links
- 230000005540 biological transmission Effects 0.000 claims description 66
- 230000002093 peripheral effect Effects 0.000 claims description 11
- 239000003921 oil Substances 0.000 description 41
- 238000005452 bending Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 239000002184 metal Substances 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
Landscapes
- Friction Gearing (AREA)
Description
【考案の詳細な説明】
(産業上の利用分野)
本考案は、農用運搬車その他に利用する無段変
速装置に係り、特に、摩擦円板による無段変速装
置の改良に関する。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a continuously variable transmission device used for agricultural transport vehicles and the like, and particularly relates to an improvement of a continuously variable transmission device using friction discs.
(従来の技術)
一対の入力円板と出力円板とを同一軸心上に対
向して配置する一方、これら円板に対して径方向
外方から圧接する伝動体をその軸心廻りに回転自
在に設け、入力円板から伝動体を経て出力円板に
動力を伝達するようにした無段変速装置がある。(Prior art) A pair of input disks and output disks are arranged facing each other on the same axis, and a transmission body that presses against these disks from the outside in the radial direction is rotated around its axis. There is a continuously variable transmission device which is arranged freely and transmits power from an input disc to an output disc via a transmission body.
この種の変速装置では、伝動体1を円板2に圧
接させかつ回転自在に支持するための手段とし
て、第7図に示すような構造を採用していた。即
ち、円板2を取囲むハウジング3に円板径方向の
シリンダ孔4が形成され、このシリンダ孔4にピ
ストン5が摺動自在に内嵌されると共に、伝動体
1の中心部の軸部6がピストン5に回転自在に挿
支され、かつピストン5と伝動体1との間にニー
ドル軸受7が介在されている。 In this type of transmission, a structure as shown in FIG. 7 has been adopted as a means for bringing the transmission body 1 into pressure contact with the disc 2 and supporting it rotatably. That is, a cylinder hole 4 in the radial direction of the disk is formed in a housing 3 surrounding the disk 2, and a piston 5 is slidably fitted into the cylinder hole 4, and a shaft portion at the center of the transmission body 1 is inserted into the cylinder hole 4. 6 is rotatably inserted and supported by the piston 5, and a needle bearing 7 is interposed between the piston 5 and the transmission body 1.
(考案が解決しようとする問題点)
この場合、蓋体8の孔9から圧油室10に圧油
を供給して、ピストン5によりニードル軸受7を
介して伝動体1を円板2側に押圧するのである
が、ニードル軸受7に作用するスラスト荷重が1
〜2トンにもなれば、伝動体1の回転が非常に悪
くなり、動力の伝達ロスが増大する欠点があつ
た。これは、ニードル軸受7は一応潤滑されてい
るが、強大な荷重が作用すれば、その表面の潤滑
油膜が破れ、金属面同士が直接接触することにな
り、潤滑の効果が極端に低下するためである。(Problem to be solved by the invention) In this case, pressure oil is supplied from the hole 9 of the lid body 8 to the pressure oil chamber 10, and the piston 5 moves the transmission body 1 to the disk 2 side via the needle bearing 7. However, the thrust load acting on the needle bearing 7 is 1
If the weight exceeded 2 tons, the rotation of the transmission body 1 would become very slow, resulting in an increase in power transmission loss. This is because the needle bearing 7 is lubricated, but if a large load is applied to it, the lubricating oil film on its surface will break, causing the metal surfaces to come into direct contact with each other, and the lubrication effect will be extremely reduced. It is.
また、伝動体1は軸部6がピストン5に挿支さ
れ、ブシユで示す軸受6Aを介してピストン5に
回転自在に支持されており、円板2の外周面との
距離が長いために、円板2の一方を摺動させたと
きの偏荷重を軸受6Aで受けるものであるから、
該軸受6Aに作用する曲げモーメントが大となつ
て負担が大きく、耐久性の点が今一歩であつた。 In addition, the shaft portion 6 of the transmission body 1 is inserted into and supported by the piston 5, and is rotatably supported by the piston 5 via a bearing 6A indicated by a bush, and the distance from the outer peripheral surface of the disc 2 is long. Since the unbalanced load when one side of the disc 2 is slid is received by the bearing 6A,
The bending moment acting on the bearing 6A was large, resulting in a heavy burden, and the durability was poor.
更に、軸部6は伝動体1から一体に突出されて
いるから、ニードル軸受7を受ける伝動体1の面
が精密に加工することが困難であつた。 Furthermore, since the shaft portion 6 projects integrally from the transmission body 1, it has been difficult to precisely machine the surface of the transmission body 1 that receives the needle bearing 7.
本考案は、斯る従来の技術の問題点を解消する
ために案出されたものである。 The present invention was devised to solve the problems of the conventional technology.
(問題を解決するための手段)
前述の問題点を解消するために本考案が講じた
処の技術的手段は同一軸心上で対向して配置され
た入力円板11と出力円板20とに対して径方向
外方から接当する伝動体27が設けられ、固定側
に前記各円板11,20の軸心と直交方向に摺動
自在なピストン29が設けられ、このピストン2
9により前記伝動体27が該ピストン29の軸心
回りに回転自在に軸受32を介して支持され、油
圧により前記伝動体27を各円板11,20側に
押圧するようにした無段変速装置において、ピス
トン29の軸心方向両側に各円板11,20の径
方向外方に位置する第1圧油室34と径方向内方
に位置する第2圧油室35とが形成され、該圧油
室34,35のそれぞれを互いに連通する通孔3
3が形成され、ピストン29と伝動体27との外
周側の摺接部間に油膜ができるように、第2圧油
室35におけるピストン29の受圧面積が第1圧
油室34の受圧面積よりも小さくされており、更
に、ピストン29の軸心より径方向内方に突出さ
れた軸部31に軸受32を介して伝動体27が回
転自在に支持されている点にある。(Means for Solving the Problem) The technical means taken by the present invention to solve the above-mentioned problems is that the input disk 11 and the output disk 20 are arranged facing each other on the same axis. A transmission body 27 is provided which contacts from the outside in the radial direction, and a piston 29 that is slidable in a direction perpendicular to the axis of each of the disks 11 and 20 is provided on the fixed side.
9, the transmission body 27 is rotatably supported via a bearing 32 around the axis of the piston 29, and the transmission body 27 is pressed toward each disc 11, 20 by hydraulic pressure. A first pressure oil chamber 34 located radially outward of each disc 11, 20 and a second pressure oil chamber 35 located radially inward are formed on both sides of the piston 29 in the axial direction. A through hole 3 that communicates the pressure oil chambers 34 and 35 with each other
3 is formed, and the pressure receiving area of the piston 29 in the second pressure oil chamber 35 is larger than the pressure receiving area of the first pressure oil chamber 34 so that an oil film is formed between the sliding contact portion of the piston 29 and the transmission body 27 on the outer peripheral side. Furthermore, the transmission body 27 is rotatably supported via a bearing 32 on a shaft portion 31 that projects radially inward from the axis of the piston 29.
(作用)
圧油室34,35に圧油を供給すれば、その圧
油で伝動体27が各円板11,20側に押圧され
る。(Function) When pressure oil is supplied to the pressure oil chambers 34 and 35, the transmission body 27 is pressed toward the respective disks 11 and 20 by the pressure oil.
ピストン29には、その両側の受圧面積差に応
じた力が作用し、これによつて、ピストン29が
伝動体27側に押圧されているので、ピストン2
9と伝動体27との外周側の摺接部間には油膜が
でき、この油膜を介して伝動体27がピストン2
9により支持され、伝動体27の回転を円滑にす
る。 A force corresponding to the difference in pressure receiving areas on both sides acts on the piston 29, and as a result, the piston 29 is pressed toward the transmission body 27, so that the piston 29
An oil film is formed between the sliding contact portion of the outer peripheral side of the transmission body 27 and the transmission body 27, and the transmission body 27 is connected to the piston 2 through this oil film.
9 to make the rotation of the transmission body 27 smooth.
そして、伝動体27を支持する軸部31はピス
トン29より径方向内方へ突出され、軸受32を
介して伝動体27を回転自在に支持しており、該
軸受32は円板11,20側に非常に近く、円板
20を摺動させたときの曲げモーメントは軸受3
2が摺動面に近いから小さく、ここに、軸受32
の負担は小さくなる。 A shaft portion 31 supporting the transmission body 27 projects radially inward from the piston 29 and rotatably supports the transmission body 27 via a bearing 32, which is located on the side of the discs 11, 20. The bending moment when the disc 20 slides is very close to the bearing 3.
Bearing 32 is small because it is close to the sliding surface.
The burden will be smaller.
(実施例) 図面を参照して本考案の実施例を詳述する。(Example) Embodiments of the present invention will be described in detail with reference to the drawings.
第2図、第3図において、10はエンジンのフ
ライホイールで、その外周に入力円板11が取付
けられる。12はPTO軸、13は円板取付軸で、
軸受14,15を介してフライホイール10とハ
ウジング16とに支持され、かつギヤー17,1
8を介してパワーシフト式変速装置19に連動連
結されている。20は出力円板で、シフター21
の外周に取付けられており、この出力円板20は
入力円板11と同径でかつ同一軸心上に対向して
配置されている。シフター21は円板取付軸13
に軸心方向に摺動自在にスプライン嵌合され、か
つ、操作レバー22により、レバー軸23、アー
ム24、及びフオーク軸25上のシフトフオーク
26を介してシフト操作可能である。27は伝動
体で、各円板11,20に対して径方向外方から
接当するように、円板11,20を取囲んでハウ
ジング16側に放射状に配置されている。即ち、
ハウジング16側には、第1図に示すように伝動
体27に対応する部位に円板軸心と直交方向のシ
リンダ孔28が形成され、このシリンダ孔28に
ピストン29が軸心方向に摺動自在に内嵌される
と共に、蓋体30が嵌着されている。 In FIGS. 2 and 3, 10 is an engine flywheel, and an input disk 11 is attached to the outer periphery of the flywheel. 12 is the PTO shaft, 13 is the disc mounting shaft,
It is supported by the flywheel 10 and the housing 16 via bearings 14 and 15, and gears 17 and 1.
It is interlocked and connected to a power shift type transmission 19 via 8. 20 is the output disc, shifter 21
The output disc 20 has the same diameter as the input disc 11 and is disposed facing the input disc 11 on the same axis. The shifter 21 is a disc mounting shaft 13
It is spline-fitted to be slidable in the axial direction, and can be shifted by the operating lever 22 via the lever shaft 23, the arm 24, and the shift fork 26 on the fork shaft 25. Reference numeral 27 denotes a transmission body that is arranged radially toward the housing 16, surrounding the discs 11 and 20, so as to contact each disc 11 and 20 from the outside in the radial direction. That is,
As shown in FIG. 1, on the housing 16 side, a cylinder hole 28 is formed at a portion corresponding to the transmission body 27 in a direction perpendicular to the disc axis, and a piston 29 slides into this cylinder hole 28 in the axial direction. It is freely fitted inside, and a lid body 30 is also fitted.
伝動体27は第1図で示す如く、第1伝動体2
7Aと第2伝動体27Bとからなり、両者はボル
ト27Cと平行ピン27Dを介して組合されてお
り、第1伝動体27Aは中心部にボス部27Eを
有し、これに第2伝動体27Bが外嵌され、本例
では第1伝動体27AはFC材で作成され、第2
伝動体27BはSCM415で作成されている。 The transmission body 27 is the first transmission body 2 as shown in FIG.
7A and a second transmission body 27B, both are combined via a bolt 27C and a parallel pin 27D, and the first transmission body 27A has a boss portion 27E in the center, and the second transmission body 27B In this example, the first transmission body 27A is made of FC material, and the second
The transmission body 27B is made of SCM415.
そして、ピストン29の軸心にナツト31Aを
介して取付けられた軸部31が径方向内方に突出
されており、この軸部31にニードル軸受32を
介して伝動体27、本例では第1伝動体27Aの
ボス部27Eが回転自在に支持されている。 A shaft portion 31 attached to the axis of the piston 29 via a nut 31A projects inward in the radial direction, and the transmission body 27, in this example, the first A boss portion 27E of the transmission body 27A is rotatably supported.
ピストン29の軸心方向両側には通孔33を介
して互いに連通する第1圧油室34,35が形成
され、第1圧油室34は径方向外方に位置し、第
2圧油室35は径方向内方に位置している。 First pressure oil chambers 34 and 35 are formed on both sides of the piston 29 in the axial direction and communicate with each other via a through hole 33, the first pressure oil chamber 34 is located radially outward, and the second pressure oil chamber 35 is located radially inward.
更に、第1伝動体27Aのピストン29側には
周壁36が第2圧油室35を取囲むように形成さ
れている。 Further, a peripheral wall 36 is formed on the piston 29 side of the first transmission body 27A so as to surround the second pressure oil chamber 35.
そして、ピストン29の第2圧油室35の受圧
面積は、周壁36と伝動体27との摺接部間に油
膜が形成できるように、第1圧油室34の受圧面
積に比較して周壁36相当分だけは少なくとも小
さくなつている。 The pressure receiving area of the second pressure oil chamber 35 of the piston 29 is larger than the pressure receiving area of the first pressure oil chamber 34 so that an oil film can be formed between the sliding contact portion of the peripheral wall 36 and the transmission body 27. At least it has become smaller by an amount equivalent to 36.
更に、第1図において、30Aは平行ピンであ
り、蓋体30とピストン29とを位置決めしてい
る。 Furthermore, in FIG. 1, 30A is a parallel pin, which positions the lid 30 and the piston 29.
なお、周壁36は第6図で示す如く、ピストン
29側に形成して、第2圧油室35を取囲むよう
にしてもよい。 Note that the peripheral wall 36 may be formed on the piston 29 side to surround the second pressure oil chamber 35, as shown in FIG.
又、第5図は、本考案の第2実施例であり、ピ
ストン29を第1ピストン29Aと第2ピストン
29Bとして分割したもので、ボルト29Cと位
置決めピン29Dで組合されており、この場合、
第2ピストン29Bは砲金製である。 FIG. 5 shows a second embodiment of the present invention, in which the piston 29 is divided into a first piston 29A and a second piston 29B, which are combined with a bolt 29C and a positioning pin 29D.
The second piston 29B is made of gun metal.
なお、この第5図の例では伝動体27は
SCM415で一体構造とされており、図示省略して
いるが通孔を介して第1圧油室34と第2圧油室
35は互いに連通されている点は、第1図の例と
同じである。 In the example shown in FIG. 5, the transmission body 27 is
SCM415 has an integral structure, and although not shown, the first pressure oil chamber 34 and the second pressure oil chamber 35 are communicated with each other via a through hole, which is the same as the example shown in Figure 1. be.
上記構成において、図外のバルブより蓋体30
の孔37より圧油を供給すると、その圧油は圧油
室34に入ると共に、通孔33を経て圧油室35
へと入り、その油圧でもつて伝動体27を円板1
1,20側に強力に押圧する。一方、ピストン2
9の両圧油室34,35側の受圧面積は、第2圧
油室35側が小となつているため、その面積差に
応じた力でピストン29が伝動体27側に付勢さ
れている。従つて、ピストン29の周壁36と伝
動体27との接触圧は、伝動体27が円板11,
20に押圧する押圧力に比較して極端に低く、周
壁36と伝動体27との間に摺接部間に第4図及
び第6図の如く間隙A部分の油膜が形成される。
これによつて伝動体27はその油膜上を軸部31
廻りに回転することになり、伝動体27の円板1
1,20に対する押圧力が如何に強大であろうと
も、伝動体27の回転を円滑にし、動力ロスを低
減できる。 In the above configuration, the lid body 30 is
When pressure oil is supplied from the hole 37, the pressure oil enters the pressure oil chamber 34 and passes through the through hole 33 to the pressure oil chamber 35.
The oil pressure moves the transmission body 27 towards the disk 1.
Press firmly on the 1 and 20 sides. On the other hand, piston 2
Since the pressure receiving area of the dual pressure oil chambers 34 and 35 of 9 is smaller on the second pressure oil chamber 35 side, the piston 29 is urged toward the transmission body 27 side with a force corresponding to the area difference. . Therefore, the contact pressure between the peripheral wall 36 of the piston 29 and the transmission body 27 is such that the transmission body 27 is
20, an oil film is formed in the gap A between the sliding contact portion between the peripheral wall 36 and the transmission body 27 as shown in FIGS. 4 and 6.
As a result, the transmission body 27 moves over the oil film onto the shaft portion 31.
The disc 1 of the transmission body 27 rotates around the
No matter how strong the pressing force on 1 and 20 is, the transmission body 27 can rotate smoothly and power loss can be reduced.
そして、変速時には、操作レバー22で出力円
板20を摺動させれば良いが、この出力円板20
の摺動で軸受32には偏心荷重が生じることにな
るが、摺動面、つまり、摩擦面に軸受32は近い
ので、偏心荷重による曲げモーメントは軸受32
には差程作用せず、軸受32の寿命はあまり短命
となることはない。 When changing gears, the output disc 20 may be slid using the operating lever 22;
An eccentric load will be generated on the bearing 32 due to the sliding, but since the bearing 32 is close to the sliding surface, that is, the friction surface, the bending moment due to the eccentric load will be
This does not affect the bearing 32 much, and the life of the bearing 32 is not shortened very much.
なお、第2圧油室35を形成するための周壁3
6はピストン29と伝動体27との双方に形成し
ても良い。又、第2圧油室35の圧油は、油膜を
形成するように少しづつ外部に逃げるので、常に
補充できるような油圧回路に構成しておくことが
望ましい。 Note that the peripheral wall 3 for forming the second pressure oil chamber 35
6 may be formed on both the piston 29 and the transmission body 27. Moreover, since the pressure oil in the second pressure oil chamber 35 escapes to the outside little by little to form an oil film, it is desirable to configure the hydraulic circuit so that it can be constantly replenished.
(考案の効果)
本考案によれば、圧油室に供給された圧油の油
圧力でもつて伝動体を強力に円板側に押圧できる
と共に、ピストン両側に面積差を持たせて、ピス
トンと伝動体との外周側の摺接部に油膜を形成
し、その油膜を介して伝動体を受けているので、
伝動体の回転が円滑になり、動力のロスを防止で
き、また耐久性も向上する。(Effects of the invention) According to the invention, the transmission body can be strongly pressed toward the disc side by the hydraulic pressure of the pressure oil supplied to the pressure oil chamber, and the area difference between both sides of the piston is created. An oil film is formed on the sliding contact part on the outer circumferential side with the transmission body, and the transmission body is received through the oil film, so
The transmission body rotates smoothly, prevents loss of power, and improves durability.
また、伝動体を回転自在に支持する軸受はピス
トンより径方向内方に突出の軸部に備えられてい
るから、円板に近くなり、ここに、偏荷重に伴う
軸受にかかる負担も小さくでき、伝動体の回転を
円滑にしながら、耐久性を向上できる。 In addition, since the bearing that rotatably supports the transmission body is installed on the shaft that protrudes radially inward from the piston, it becomes close to a disc, which reduces the burden placed on the bearing due to unbalanced loads. , the durability can be improved while making the rotation of the transmission body smooth.
第1図は本考案の第1実施例を示す要部の断面
図、、第2図は同断面側面図、第3図は第2図の
−矢視拡大図、第4図は作用説明図、第5図
は第2実施例を示す要部の断面図、第6図は他の
例の作用説明図、第7図は従来例を示す断面図で
ある。
11……入力円板、16……ハウジング、20
……出力円板、27……伝動体、28……シリン
ダ室、29……ピストン、31……軸部、32…
…軸受、34……第1、第2圧油室、36……周
壁。
Fig. 1 is a cross-sectional view of the main parts showing the first embodiment of the present invention, Fig. 2 is a side view of the same cross-section, Fig. 3 is an enlarged view taken in the - arrow direction of Fig. 2, and Fig. 4 is an explanatory diagram of the operation. , FIG. 5 is a sectional view of essential parts showing the second embodiment, FIG. 6 is an explanatory view of the operation of another example, and FIG. 7 is a sectional view showing a conventional example. 11...Input disk, 16...Housing, 20
... Output disk, 27 ... Transmission body, 28 ... Cylinder chamber, 29 ... Piston, 31 ... Shaft, 32 ...
...bearing, 34...first and second pressure oil chambers, 36...peripheral wall.
Claims (1)
と出力円板20とに対して径方向外方から接当す
る伝動体27が設けられ、固定側に前記各円板1
1,20の軸心と直交方向に摺動自在なピストン
29が設けられ、このピストン29により前記伝
動体27が該ピストン29の軸心回りに回転自在
に軸受32を介して支持され、油圧により前記伝
動体27を各円板11,20側に押圧するように
した無段変速装置において、 ピストン29の軸心方向両側に各円板11,2
0の径方向外方に位置する第1圧油室34と径方
向内方に位置する第2圧油室35とが形成され、
該圧油室34,35のそれぞれを互いに連通する
通孔33が形成され、 ピストン29と伝動体27との外周側の摺接部
間に油膜ができるように、第2圧油室35におけ
るピストン29の受圧面積が第1圧油室34の受
圧面積よりも小さくされており、 更に、ピストン29の軸心より径方向内方に突
出された軸部31に軸受32を介して伝動体27
が回転自在に支持されていることを特徴とする無
段変速装置。[Claims for Utility Model Registration] Input disks 11 arranged facing each other on the same axis
A power transmission body 27 is provided which contacts the output disc 20 from the outside in the radial direction, and each of the discs 1 on the fixed side.
A piston 29 is provided which is slidable in a direction perpendicular to the axes of the pistons 1 and 20, and the transmission body 27 is supported by the piston 29 via a bearing 32 so as to be rotatable around the axes of the piston 29. In the continuously variable transmission device in which the transmission body 27 is pressed toward the discs 11 and 20, the discs 11 and 2 are located on both sides of the piston 29 in the axial direction.
A first pressure oil chamber 34 located radially outward of 0 and a second pressure oil chamber 35 located radially inward are formed,
A through hole 33 is formed to communicate the pressure oil chambers 34 and 35 with each other, and the piston in the second pressure oil chamber 35 is formed so that an oil film is formed between the sliding contact portion of the piston 29 and the transmission body 27 on the outer peripheral side. The pressure-receiving area of the piston 29 is smaller than the pressure-receiving area of the first pressure oil chamber 34 , and the transmission body 27 is connected to the shaft portion 31 that projects radially inward from the axis of the piston 29 via a bearing 32 .
A continuously variable transmission characterized by being rotatably supported.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12035684U JPS6135259U (en) | 1984-08-03 | 1984-08-03 | Continuously variable transmission |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12035684U JPS6135259U (en) | 1984-08-03 | 1984-08-03 | Continuously variable transmission |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6135259U JPS6135259U (en) | 1986-03-04 |
JPH0139964Y2 true JPH0139964Y2 (en) | 1989-11-30 |
Family
ID=30679180
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP12035684U Granted JPS6135259U (en) | 1984-08-03 | 1984-08-03 | Continuously variable transmission |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6135259U (en) |
-
1984
- 1984-08-03 JP JP12035684U patent/JPS6135259U/en active Granted
Also Published As
Publication number | Publication date |
---|---|
JPS6135259U (en) | 1986-03-04 |
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