JPS6171564U - - Google Patents
Info
- Publication number
- JPS6171564U JPS6171564U JP15697684U JP15697684U JPS6171564U JP S6171564 U JPS6171564 U JP S6171564U JP 15697684 U JP15697684 U JP 15697684U JP 15697684 U JP15697684 U JP 15697684U JP S6171564 U JPS6171564 U JP S6171564U
- Authority
- JP
- Japan
- Prior art keywords
- diameter piston
- small
- pressurizing chamber
- diameter
- piston
- 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
- 239000012530 fluid Substances 0.000 claims 5
- 238000013459 approach Methods 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
Landscapes
- Transmission Of Braking Force In Braking Systems (AREA)
Description
第1図は本考案が適用されるタンデムマスタシ
リンダの一実施例を示す斜視図である。第2図は
第1図の実施例の縦断面図である。第3図は第1
図の実施例の作動を説明する図で、液圧と作動力
との関係を示すグラフである。第4図は第1図の
実施例におけるフロントピストン側の作動を説明
する図である。第5図は対象アクチユエータの所
要液圧と作動ストロークの一般的な関係を示すグ
ラフである。
14:シリンダ、16:貫通孔(小径孔部)、
18:フロントピストン(小径ピストン)、22
:大径孔(大径孔部)、24:テイクアツプピス
トン(大径ピストン)、58:圧縮コイルスプリ
ング(弾性部材)、66:第一加圧室、68:第
二加圧室、70:出力ポート、{74:隙間、7
6:連通溝}(コンペンセイテイング通路)、{
78:連通路、80:リーフ弁}(第一逆止弁)
、82:コンペンセイテイングポート、84:リ
ザーバ、{86:カツプシール、92:連通路、
94:薄板}(第二逆止弁)。
FIG. 1 is a perspective view showing an embodiment of a tandem master cylinder to which the present invention is applied. FIG. 2 is a longitudinal sectional view of the embodiment of FIG. 1. Figure 3 is the first
It is a diagram explaining the operation of the embodiment shown in the figure, and is a graph showing the relationship between hydraulic pressure and operating force. FIG. 4 is a diagram illustrating the operation of the front piston in the embodiment of FIG. 1. FIG. 5 is a graph showing the general relationship between required hydraulic pressure and operating stroke of the target actuator. 14: cylinder, 16: through hole (small diameter hole),
18: Front piston (small diameter piston), 22
: Large diameter hole (large diameter hole part), 24: Take-up piston (large diameter piston), 58: Compression coil spring (elastic member), 66: First pressurizing chamber, 68: Second pressurizing chamber, 70: Output port, {74: Gap, 7
6: Communication groove} (compensating passage), {
78: Communication path, 80: Leaf valve} (first check valve)
, 82: Compensating port, 84: Reservoir, {86: Cup seal, 92: Communication path,
94: Thin plate} (second check valve).
Claims (1)
アクチユエータに供給するマスタシリンダであつ
て、 小径孔部とその前方に形成された大径孔部とを
有するシリンダと、 前記小径孔部に液密かつ摺動可能に嵌合され、
前記操作部材により進退させられる小径ピストン
と、 その小径ピストンに対して軸方向に相対移動可
能かつ一定限度以上離間不能に設けられ、前記大
径孔部に液密かつ摺動可能に嵌合された大径ピス
トンと、 その大径ピストンと前記小径ピストスとを互い
に離間する方向に常時付勢する弾性部材と、 前記大径ピストンの前方に形成された第一加圧
室を前記アクチユエータに連通させるための出力
ポートと、 前記大径ピストンと小径ピストンとの間に形成
された第二加圧室を、大径ピストンが後退端にあ
る状態では前記第一加圧室に連通させ、大径ピス
トンがその後退端から小距離前進した状態ではそ
れら両室を連通させないコンペンセイテイング通
路と、 前記小径ピストンが後退端にある状態では前記
第二加圧室を外部のリザーバに連通させ、小径ピ
ストンがその後退端から小距離前進した状態では
連通させないコンペンセイテイングポートと、 前記大径ピストンに設けられ、前記第二加圧室
から前記第一加圧室への作動液の流れは許容する
逆方向の流れは阻止する第一逆止弁と、 前記小径ピストンに設けられ、前記リザーバか
ら前記第二加圧室への作動液の流れは許容するが
逆方向の流れは阻止する第二逆止弁と を含み、前記第一加圧室の液圧が低い間は前記大
径ピストンが前記弾性部材を圧縮することなく前
記小径ピストンと一体的に前進して前記操作部材
の操作ストロークの割に多量の作動液を前記アク
チユエータに供給し、前記第一加圧室の液圧が設
定値を超えた後は前記大径ピストンが前記弾性部
材を圧縮しつつ前記小径ピストンに接近して前記
操作部材の操作力の割に高圧の作動液を前記アク
チユエータに供給することを特徴とするテイクア
ツプマスタシリンダ。[Scope of Claim for Utility Model Registration] A master cylinder that generates hydraulic pressure in response to the operation of an operating member and supplies it to the target actuator, the cylinder having a small diameter hole and a large diameter hole formed in front of the master cylinder. and, liquid-tightly and slidably fitted into the small diameter hole,
a small-diameter piston that is moved forward and backward by the operating member; and a small-diameter piston that is movable relative to the small-diameter piston in the axial direction and cannot be separated beyond a certain limit, and is fluid-tightly and slidably fitted into the large-diameter hole. a large-diameter piston; an elastic member that constantly biases the large-diameter piston and the small-diameter piston in a direction away from each other; and a first pressurizing chamber formed in front of the large-diameter piston for communicating with the actuator. A second pressurizing chamber formed between the large-diameter piston and the small-diameter piston is communicated with the first pressurizing chamber when the large-diameter piston is at the retreating end, and the large-diameter piston is in communication with the first pressurizing chamber. a compensating passage that does not communicate between the two chambers when the small diameter piston is advanced a short distance from the retreating end; and a compensating passage that communicates the second pressurizing chamber with an external reservoir when the small diameter piston is at the retreating end; a compensating port that is not allowed to communicate when the piston is advanced a short distance from the retracted end; and a compensating port that is provided on the large diameter piston and that allows hydraulic fluid to flow from the second pressurizing chamber to the first pressurizing chamber. a first check valve that blocks the flow; and a second check valve that is provided on the small diameter piston and allows the flow of the hydraulic fluid from the reservoir to the second pressurizing chamber but blocks flow in the opposite direction. While the fluid pressure in the first pressurizing chamber is low, the large-diameter piston moves forward together with the small-diameter piston without compressing the elastic member, and the large-diameter piston moves forward in unison with the small-diameter piston, so that the large-diameter piston moves forward in unison with the small-diameter piston, and the large-diameter piston moves forward in unison with the small-diameter piston without compressing the elastic member. After the hydraulic fluid is supplied to the actuator and the hydraulic pressure in the first pressurizing chamber exceeds a set value, the large diameter piston approaches the small diameter piston while compressing the elastic member to operate the operating member. A take-up master cylinder characterized in that a hydraulic fluid having a high pressure relative to the force is supplied to the actuator.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15697684U JPS6171564U (en) | 1984-10-17 | 1984-10-17 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP15697684U JPS6171564U (en) | 1984-10-17 | 1984-10-17 |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS6171564U true JPS6171564U (en) | 1986-05-15 |
Family
ID=30714978
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP15697684U Pending JPS6171564U (en) | 1984-10-17 | 1984-10-17 |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6171564U (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012017096A (en) * | 2010-07-09 | 2012-01-26 | Robert Bosch Gmbh | Fast fill tandem master cylinder |
-
1984
- 1984-10-17 JP JP15697684U patent/JPS6171564U/ja active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2012017096A (en) * | 2010-07-09 | 2012-01-26 | Robert Bosch Gmbh | Fast fill tandem master cylinder |
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