JPS6347531A - Structure of disk brake - Google Patents
Structure of disk brakeInfo
- Publication number
- JPS6347531A JPS6347531A JP61190327A JP19032786A JPS6347531A JP S6347531 A JPS6347531 A JP S6347531A JP 61190327 A JP61190327 A JP 61190327A JP 19032786 A JP19032786 A JP 19032786A JP S6347531 A JPS6347531 A JP S6347531A
- Authority
- JP
- Japan
- Prior art keywords
- brake
- piston member
- peripheral face
- inner peripheral
- case
- 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.)
- Granted
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 10
- 238000003825 pressing Methods 0.000 claims description 2
- 238000003754 machining Methods 0.000 abstract description 7
- 230000005540 biological transmission Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Landscapes
- Braking Arrangements (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明はブレーキディスクと同芯状に配置されたリング
状のピストン部材を油圧によって前記ブレーキディスク
押圧側に駆動シフトするように構成してあるディスクブ
レーキ構造に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention is configured such that a ring-shaped piston member arranged concentrically with a brake disc is driven and shifted to the brake disc pressing side by hydraulic pressure. Regarding disc brake structure.
前述のようにリング状のピストン部材を用いたディスク
ブレーキ構造としては第2図に示すように、ブレーキケ
ース(6)とミッションケース(1)の間のリング状の
支持座(16)に環状溝を形成すると共に、ピストン部
材(13)の環状の脚部を環状溝にはいり込ませて、ピ
ストン部材(13)と環状溝で形成される環状の油室に
圧油を送り込んでビントン部材(13)を駆動シフトし
てブレーキディスク(10)を押圧するように構成して
いる機種がある。As shown in Fig. 2, the disc brake structure using the ring-shaped piston member as described above has an annular groove in the ring-shaped support seat (16) between the brake case (6) and the transmission case (1). At the same time, the annular leg of the piston member (13) is inserted into the annular groove, and pressure oil is sent into the annular oil chamber formed by the piston member (13) and the annular groove to form the Vinton member (13). ) is configured to press the brake disc (10) by shifting the drive.
前述の構造であると、ピストン部材の脚部と環状溝とで
形成される環状の油室を十分な油密状態にしなければな
らず、その為にはピストン部材の脚部の内外周面及び環
状溝の内外周面を、その真円度及び同心度が十分な高精
度になるように加工しなければならない。With the above structure, the annular oil chamber formed by the legs of the piston member and the annular groove must be kept in a sufficiently oil-tight state. The inner and outer circumferential surfaces of the annular groove must be machined so that their roundness and concentricity are sufficiently accurate.
前記ピストン部材の脚部は円筒の内外面を加工するのと
略同じであり、高精度の加工が比較的容易なのであるが
、高精度の溝加工は作業効率が低く高コストの加工につ
きやすいものであった。The leg part of the piston member is almost the same as machining the inner and outer surfaces of a cylinder, and high-precision machining is relatively easy, but high-precision groove machining has low work efficiency and tends to be expensive. Met.
ここで本発明は、ピストン部材駆動シフト用の油室の高
油密性を比較的容易にかつ低コストの加工で得られるよ
うなディスクブレーキ構°造を提供することを目的とし
ている。SUMMARY OF THE INVENTION An object of the present invention is to provide a disc brake structure in which high oil tightness of an oil chamber for piston member drive shifting can be obtained relatively easily and at low cost.
本発明の特徴は奮起したディスクブレーキ構造において
、ブレーキディスクを内嵌するブレーキケースの内壁面
に、径の異なる第1内周面及び第2内周面を段状で、且
つ同芯状に形成すると共に、前記ピストン部材を前記第
1・第2内周面に亘って油密状に摺動可能に内嵌し、第
1・第2内周面の段差部とピストン部材との間にピスト
ン駆動用油室を形成してあることにあり、その作用及び
効果は次のとおりである。The feature of the present invention is that, in an improved disc brake structure, a first inner circumferential surface and a second inner circumferential surface having different diameters are formed in a stepped and concentric manner on the inner wall surface of a brake case into which a brake disc is fitted. At the same time, the piston member is slidably fitted in an oil-tight manner over the first and second inner circumferential surfaces, and the piston is fitted between the stepped portion of the first and second inner circumferential surfaces and the piston member. The reason is that a driving oil chamber is formed, and its functions and effects are as follows.
前述のように構成すると、ピストン駆動用油室の油密性
はブレーキケースの第1・第2内周面とピストン部材の
外周面との両接触摺動面の精度、つまりブレーキケース
の前記第1・第2内周面の真円度とピストン部材の外周
面の真円度及び各内外周面の同心度に基づくものとなる
。When configured as described above, the oil tightness of the piston driving oil chamber is determined by the accuracy of both contact sliding surfaces between the first and second inner circumferential surfaces of the brake case and the outer circumferential surface of the piston member, that is, the accuracy of the first and second inner circumferential surfaces of the brake case and the outer circumferential surface of the piston member. It is based on the circularity of the first and second inner circumferential surfaces, the circularity of the outer circumferential surface of the piston member, and the concentricity of each inner and outer circumferential surface.
そして、以上の内外周面は通常の円筒の工作と略同様で
あり、溝加工を行うものに比べて真円度及び同心度共に
高精度なものが比較的容易に得られる。The inner and outer circumferential surfaces described above are substantially the same as the machining of a normal cylinder, and it is relatively easy to obtain high precision in both roundness and concentricity compared to the case where groove machining is performed.
以上のように、溝加工部分を廃止しブレーキケース内周
面とピストン部材外周面とでビス1〜ン駆動用油室を形
成するように構成したので、比較的加工が容易な構造と
なりピストン駆動用油室の油密性を維持しながら製作コ
ストを抑えることが可能となった。As described above, since the grooved part is eliminated and the oil chamber for driving the screws 1 to 1 is formed between the inner peripheral surface of the brake case and the outer peripheral surface of the piston member, the structure is relatively easy to process and the piston is driven. It has become possible to reduce manufacturing costs while maintaining the oil tightness of the oil chamber.
以下、本発明を図面に基づいて説明する。 Hereinafter, the present invention will be explained based on the drawings.
第1図は農用トラクタ等の作業車におけるミッションケ
ース(1)の後輪デフ機構(2)付近の縦断正面図であ
り、図に示すようにミッションケース(1)内に後輪デ
フ機構(2)が配置され、後輪デフ機構(2)から左右
に差動輪(3)が突出している。この後輪デフ機構(2
)はケースサポート(14)を介して支持されており、
ケースサポート(14)はミッションケース(1)の外
側面(la)に形成した凹部内方でミッションケース(
1)に連結されている。Figure 1 is a longitudinal sectional front view of the vicinity of the rear wheel differential mechanism (2) of the transmission case (1) of a work vehicle such as an agricultural tractor. ) are arranged, and differential wheels (3) protrude left and right from the rear wheel differential mechanism (2). This rear wheel differential mechanism (2
) is supported via the case support (14),
The case support (14) supports the mission case (1) inside the recess formed on the outer surface (la) of the mission case (1).
1).
そして、前記差動輪(3)にはデフロック用のシフト部
材(4)がスプライン嵌合されており、スプリング(1
5)により切り側に付勢されたシフト部材(4)をシフ
ター(5)によって軸芯方向に摺動させデフケース(2
a)に咬合せることによりデフロック操作を行う。A differential lock shift member (4) is spline-fitted to the differential wheel (3), and a spring (1) is fitted to the differential wheel (3).
The shift member (4), which is biased toward the cutting side by the shifter (5), is slid in the axial direction by the shifter (5), and the differential case (2
Perform differential lock operation by engaging a).
前記ミッションケース(1)側面にはブレーキケース(
6)、車軸ケース(7)が連結され、前記差動輪(3)
からの動力は遊星減速機構(8)を介し車軸(9)に伝
達され後輪(図外)を駆動する。A brake case (
6), the axle case (7) is connected, and the differential wheel (3)
The power is transmitted to the axle (9) via the planetary reduction mechanism (8) and drives the rear wheels (not shown).
次に、前記ブレーキケース(6)内に収められた湿式の
ディスクブレーキ構造について詳述すると、図に示すよ
うに差動軸(3)にはブレーキディスク(10)がスプ
ライン嵌合されており、このブレーキディスク(10)
の間にリング状のプレート(11)が挟まれた状態でブ
レーキケース(6)内に内嵌配置されている。そして、
このプレー) (11)外周複数箇所に切欠き部を設け
、ブレーキケース(6)内複数箇所に配置した係止ピン
(12)に前記切欠き部を係入させて、差動輪(3)及
びブレーキディスク(10)の回転に伴い、プレート(
11)が連れ回りしないような構造としている。Next, to explain in detail the wet type disc brake structure housed in the brake case (6), as shown in the figure, a brake disc (10) is spline-fitted to the differential shaft (3). This brake disc (10)
A ring-shaped plate (11) is inserted into the brake case (6) with a ring-shaped plate (11) sandwiched therebetween. and,
(11) Provide notches at multiple locations on the outer periphery, engage the locking pins (12) located at multiple locations within the brake case (6), and insert the differential wheels (3) and As the brake disc (10) rotates, the plate (
11) is structured so that it does not rotate together.
次に、前記ブレーキディスク(10)及びプレート(1
1)をミッションケース(1)側に押圧するリング状の
ピストン部材(13)の構造について詳述すると、ブレ
ーキケース(6)には第1内周面(6a)とこれより大
径の第2内周面(6b)とが同芯状に設けられ段差部を
形成している。そして、この第1・第2内周面(6a)
、 (6b)に亘って摺接する段状の外周面をピスト
ン部材(13)に設けてこれをブレーキケース(6)に
油密状に内嵌すると共に、ピストン部材(13)外周の
複数箇所に設けた切欠き部を前記係止ピン(12)に係
入している。Next, the brake disc (10) and the plate (1
1) toward the mission case (1) side. The brake case (6) has a first inner circumferential surface (6a) and a second inner circumferential surface (6a) with a larger diameter. The inner circumferential surface (6b) is provided concentrically to form a stepped portion. And this first and second inner circumferential surfaces (6a)
, (6b), the piston member (13) is provided with a step-shaped outer circumferential surface that slides into contact with the brake case (6), and is fitted into the brake case (6) in an oil-tight manner. The provided notch is engaged with the locking pin (12).
そして、ブレーキケース(16)の第1・第2内周面(
6a) 、 (6b)の間の段差部とピストン部材(1
3)との間に形成される環状のピストン駆動用油室(S
)内に操作用の圧油を送り込み、ピストン部材(13)
を摺動駆動して、ブレーキディスク(10)及びプレー
ト(11)をミッションケース(1)の外側面(1a)
に押圧して制動するのである。Then, the first and second inner circumferential surfaces (
6a) and (6b) and the piston member (1
3) an annular piston drive oil chamber (S
) into the piston member (13).
by slidingly driving the brake disc (10) and plate (11) to the outer surface (1a) of the transmission case (1).
It applies pressure to brake.
図面は本発明に係るディスクブレーキ構造の実施例を示
し、第1図は後輪デフ機構付近の縦断正面図、第2図は
従来構造における後輪デフ機構付近の縦断正面図である
。
(6)・・・・・・ブレーキケース、(6a)・・・・
・・第1内周面、(6b)・・・・・・第2内周面、(
10)・・・・・・ブレーキディスク、(13)・・・
・・・ピストン部材、(S)・・・・・・ピストン駆動
用油室。The drawings show an embodiment of the disc brake structure according to the present invention, in which FIG. 1 is a longitudinal sectional front view of the vicinity of the rear wheel differential mechanism, and FIG. 2 is a longitudinal sectional front view of the vicinity of the rear wheel differential mechanism in a conventional structure. (6)... Brake case, (6a)...
...First inner circumferential surface, (6b)...Second inner circumferential surface, (
10)...Brake disc, (13)...
... Piston member, (S) ... Piston drive oil chamber.
Claims (1)
グ状のピストン部材(13)を油圧によって前記ブレー
キディスク(10)押圧側に駆動シフトするように構成
してあるディスクブレーキ構造であって、前記ブレーキ
ディスク(10)を内嵌するブレーキケース(6)の内
壁面に、径の異なる第1内周面(6a)及び第2内周面
(6b)を段状で、且つ同芯状に形成すると共に、前記
ピストン部材(13)を前記第1・第2内周面(6a)
、(6b)に亘って油密状に摺動可能に内嵌し、第1・
第2内周面(6a)、(6b)の段差部とピストン部材
(13)との間にピストン駆動用油室(S)を形成して
あるディスクブレーキ構造。The disc brake structure is configured such that a ring-shaped piston member (13) arranged concentrically with the brake disc (10) is driven and shifted by hydraulic pressure toward the pressing side of the brake disc (10), A first inner circumferential surface (6a) and a second inner circumferential surface (6b) having different diameters are formed in a stepped and concentric manner on the inner wall surface of the brake case (6) into which the brake disc (10) is fitted. At the same time, the piston member (13) is attached to the first and second inner circumferential surfaces (6a).
, (6b), and is slidably fitted in an oil-tight manner over the first and second parts.
A disc brake structure in which a piston driving oil chamber (S) is formed between the stepped portion of the second inner peripheral surfaces (6a) and (6b) and the piston member (13).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP61190327A JPH0668299B2 (en) | 1986-08-13 | 1986-08-13 | Work vehicle disc brake structure |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP61190327A JPH0668299B2 (en) | 1986-08-13 | 1986-08-13 | Work vehicle disc brake structure |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6347531A true JPS6347531A (en) | 1988-02-29 |
JPH0668299B2 JPH0668299B2 (en) | 1994-08-31 |
Family
ID=16256337
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP61190327A Expired - Lifetime JPH0668299B2 (en) | 1986-08-13 | 1986-08-13 | Work vehicle disc brake structure |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0668299B2 (en) |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5352869A (en) * | 1976-10-16 | 1978-05-13 | Wabco Westinghouse Gmbh | Pressure medium type disk brake for automobile |
JPS5533878U (en) * | 1978-08-28 | 1980-03-04 | ||
JPS56108951U (en) * | 1980-01-24 | 1981-08-24 | ||
JPS57200747U (en) * | 1981-06-16 | 1982-12-21 | ||
JPS5875027U (en) * | 1981-11-13 | 1983-05-20 | ヤンマーディーゼル株式会社 | Agricultural tractor deflock device |
JPS5874633U (en) * | 1981-11-13 | 1983-05-20 | ヤンマーディーゼル株式会社 | Agricultural tractor brake device |
JPS60100256U (en) * | 1983-12-15 | 1985-07-08 | 株式会社クボタ | Hydraulic operated brake device |
-
1986
- 1986-08-13 JP JP61190327A patent/JPH0668299B2/en not_active Expired - Lifetime
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5352869A (en) * | 1976-10-16 | 1978-05-13 | Wabco Westinghouse Gmbh | Pressure medium type disk brake for automobile |
JPS5533878U (en) * | 1978-08-28 | 1980-03-04 | ||
JPS56108951U (en) * | 1980-01-24 | 1981-08-24 | ||
JPS57200747U (en) * | 1981-06-16 | 1982-12-21 | ||
JPS5875027U (en) * | 1981-11-13 | 1983-05-20 | ヤンマーディーゼル株式会社 | Agricultural tractor deflock device |
JPS5874633U (en) * | 1981-11-13 | 1983-05-20 | ヤンマーディーゼル株式会社 | Agricultural tractor brake device |
JPS60100256U (en) * | 1983-12-15 | 1985-07-08 | 株式会社クボタ | Hydraulic operated brake device |
Also Published As
Publication number | Publication date |
---|---|
JPH0668299B2 (en) | 1994-08-31 |
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