JPH0372846B2 - - Google Patents
Info
- Publication number
- JPH0372846B2 JPH0372846B2 JP59210228A JP21022884A JPH0372846B2 JP H0372846 B2 JPH0372846 B2 JP H0372846B2 JP 59210228 A JP59210228 A JP 59210228A JP 21022884 A JP21022884 A JP 21022884A JP H0372846 B2 JPH0372846 B2 JP H0372846B2
- Authority
- JP
- Japan
- Prior art keywords
- clutch
- transmission
- load
- pressure
- reducing valve
- 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 - Lifetime
Links
- 230000005540 biological transmission Effects 0.000 claims description 42
- 230000005284 excitation Effects 0.000 claims description 10
- 238000001514 detection method Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000000605 extraction Methods 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Landscapes
- Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Gear-Shifting Mechanisms (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明はトラクタ等に搭載されて使用されるも
ので、詳しくは変速用油圧クラツチへの圧油供給
系統に、電磁比例減圧弁を設け、クラツチオン作
動時におけるクラツチの起動を短時間に行なえる
ように初期昇圧速度が大きく、かつ、以降のつな
がりを衝撃少なく円滑に行なえるように昇圧速度
が小さくなるように前記減圧弁への励磁電圧を自
動制御する制御回路を備えてある油圧操作式ギヤ
変速装置に関する。[Detailed Description of the Invention] [Field of Industrial Application] The present invention is used mounted on a tractor or the like, and more specifically, an electromagnetic proportional pressure reducing valve is provided in a pressure oil supply system to a hydraulic clutch for shifting. The excitation voltage to the pressure reducing valve is set so that the initial pressure increase rate is large so that the clutch can be started in a short time when the clutch is activated, and the pressure increase rate is small so that the subsequent connection can be carried out smoothly with less impact. The present invention relates to a hydraulically operated gear transmission equipped with a control circuit for automatic control.
従来は、第４図に示すように、前記昇圧速度
OQ1，OQ2は一定のものであつた（例えば特願昭
59−93136号）。
Conventionally, as shown in FIG.
OQ 1 and OQ 2 were constant (for example,
59-93136).
その為に、初期昇圧速度を以降の昇圧速度に比
べて大きく設定はしているが、負荷が大きくなれ
ば油圧クラツチが作動するまでに時間t1がかか
り、クラツチの立上りにかかる無駄時間ｔが負荷
の増大とともに大になる欠点があつた。
For this reason, the initial pressure increase speed is set higher than the subsequent pressure increase speed, but as the load increases, it takes time t1 for the hydraulic clutch to operate, and the wasted time t required for the clutch to start up increases. There was a drawback that increased as the load increased.
本発明の目的は負荷の大小に関係なく、油圧ク
ラツチが作動するに要する無駄時間を最小限のも
のに抑えれるものを提供する点にある。 SUMMARY OF THE INVENTION It is an object of the present invention to provide a hydraulic clutch which can minimize the wasted time required to actuate it, regardless of the load.
本発明による特徴構成は伝動負荷を検出する機
構を備えるとともに、前記減圧弁への励磁電圧の
立上り特性を変更可能に前記制御回路を構成し、
変速切換えに伴うクラツチオン作動時における励
磁電圧の立上り特性を、変速切換え前の伝動状態
での負荷が大きいほど初期昇圧速度が大きくなる
ように自動変更させる回路構成としてある点にあ
り、その作用効果は次の通りである。
The characteristic configuration according to the present invention includes a mechanism for detecting a transmission load, and the control circuit is configured to be able to change the rise characteristic of the excitation voltage to the pressure reducing valve,
The circuit is configured to automatically change the rise characteristics of the excitation voltage when the clutch is activated during gear shifting so that the larger the load in the transmission state before gear shifting, the greater the initial boost speed. It is as follows.
つまり、励磁電圧を変化させることによつて油
圧クラツチへの昇圧特性を任意に変更可能な電磁
比例減圧弁の電気制御可能な特性を利用して、伝
動負荷を検出することによつて、この検出結果に
基づいて前記初期昇圧速度Q1を可変可能にでき
る。
In other words, the transmission load can be detected by utilizing the electrically controllable characteristics of the electromagnetic proportional pressure reducing valve, which can arbitrarily change the pressure increase characteristics to the hydraulic clutch by changing the excitation voltage. Based on the results, the initial boosting rate Q1 can be made variable.
従つて、第１図のイ，ロ，ハに示すように負荷
によつてクラツチの初期作動圧Ｐが変化する点を
昇圧速度を可変する方式によつてその初期作動ま
での無駄時間を極力最小にして解消しようとする
もので負荷にかかわらず前記無駄時間を一定かつ
最小限のものにできる。 Therefore, as shown in A, B, and C of Fig. 1, by varying the pressure increase rate at the point where the initial operating pressure P of the clutch changes depending on the load, the wasted time until the initial operation is minimized as much as possible. Therefore, the wasted time can be kept constant and minimized regardless of the load.
その結果、負荷変動に対応した昇圧特性の変更
も可能になり、油圧クラツチの作動をより無駄時
間の少ない、円滑な作動特性を有するものを提供
できるに至つた。
As a result, it has become possible to change the pressure increase characteristics in response to load fluctuations, and it has become possible to provide a hydraulic clutch with smoother operating characteristics and less wasted time.
第２図はトラクタに装備のミツシヨンケースＭ
内の伝動構造を示し、エンジンＥに連動連結させ
た入力軸１と走行用第１伝動軸２とに亘つて、４
段切換自在なシンクロメツシユ式主ギヤ変速装置
H1を設け、第１伝動軸２と走行用第２伝動軸３
との間に、摩擦板式油圧クラツチＣを設け、第２
伝動軸３の出力を正逆転変更するシンクロメツシ
ユ式前後進ギヤ変速装置H2、それからの出力を
高低２段に切換自在なシンクロメツシユ式第１副
ギヤ変速装置H3、及び、それからの出力を高低
２段に切換自在な第２副ギヤ変速装置H4の夫々
を設け、そして、第２副ギヤ変速装置H4の出力
を後輪４の差動機構４Ａ、及び、前輪５の差動機
構５Ａに伝動させるように構成してある。
Figure 2 shows the transmission case M installed on the tractor.
4, spanning the input shaft 1 interlockingly connected to the engine E and the first driving transmission shaft 2.
Synchronous mesh main gear transmission with variable speed
H 1 is provided, and the first transmission shaft 2 and the second transmission shaft 3 for traveling are provided.
A friction plate type hydraulic clutch C is provided between the second
A synchromesh type forward/reverse gear transmission H 2 that changes the output of the transmission shaft 3 in forward and reverse directions, a synchromesh type first auxiliary gear transmission H 3 that can freely switch the output therefrom into two high and low stages, and A second auxiliary gear transmission H 4 that can freely switch the output between high and low two stages is provided, and the output of the second auxiliary gear transmission H 4 is transmitted to the differential mechanism 4A of the rear wheels 4 and the differential mechanism of the front wheels 5. It is configured to transmit power to the driving mechanism 5A.
前記入力軸１の動力を４段に変速して動力取出
用伝動軸６に伝動するシンクロメツシユ式ギヤ変
速装置７を設けると共に、伝動軸６と動力取出軸
８との間に、中継伝動軸９を設け、もつて、動力
取出軸８を変速できるように構成してある。 A synchromesh type gear transmission 7 is provided which changes the power of the input shaft 1 into four stages and transmits it to the power extraction transmission shaft 6, and a relay transmission shaft is provided between the transmission shaft 6 and the power extraction shaft 8. 9 is provided so that the power take-off shaft 8 can be changed in speed.
次に、走行用伝動系に対する変速操作構造につ
いて、第２図及び第３図に基づいて詳述する。 Next, the speed change operation structure for the driving transmission system will be described in detail with reference to FIGS. 2 and 3.
すなわち、主ギヤ変速装置H1に、択一的に作
動される変速用シフター操作用油圧シリンダ１０
Ａ，１０Ｂの２個を付設すると共に、前後進ギヤ
変速装置H2及び第１副ギヤ変速装置H3の夫々
に、変速シフター操作用油圧シリンダ１１，１２
の１個を付設し、そして、前記伝動クラツチＣ
に、入り操作用の油圧シリンダ１３を付設してあ
る。 That is, the main gear transmission H 1 includes a hydraulic cylinder 10 for operating a gear shifter that is selectively operated.
A and 10B are attached, and hydraulic cylinders 11 and 12 for operating the transmission shifter are attached to the forward and reverse gear transmission H 2 and the first auxiliary gear transmission H 3 , respectively.
one of the transmission clutches C is attached, and the transmission clutch C
A hydraulic cylinder 13 for entering operation is attached to the holder.
前記主ギヤ変速用油圧シリンダ１０Ａ，１０Ｂ
及び前記第１副変速用油圧シリンダ１２夫々に対
する主制御弁V1、並びに、前記前後進変速用油
圧シリンダ１１に対する補助制御弁V2を、油圧
ポンプ１６に並列接続してある。そして、前記各
油圧シリンダ１０Ａ…のピストンを摺動スプール
として兼用利用する状態で３位置切換弁S1，S2，
S3，S4の４個を構成し、前後進変速用油圧シリン
ダ１１にて構成した切換弁S1からの圧油をクラツ
チ操作用油圧シリンダ１３に供給する油路１４を
設けると共に、その油路１４を開閉するためのパ
イロツト圧操作式切換弁T1，T2，T3の３個を、
直列状に並べる状態で、且つ、主ギヤ変速用油圧
シリンダ１０Ａ，１０Ｂ及び第１副変速用油圧シ
リンダ１２の夫々にて構成した切換弁S3，S4及び
S2からの圧油にて操作される状態で設け、もつ
て、クラツチ操作用シリンダ１３の作動を制御す
る弁S1，T1，T2，T3を、主ギヤ変速装置H1、前
後進ギヤ変速装置H2、及び、第１副ギヤ変速装
置H3の伝動状態においてのみ入り操作位置に切
換えるべく、変速操作に伴つて自動的に切換操作
されるように構成してある。 The main gear shifting hydraulic cylinders 10A, 10B
A main control valve V 1 for each of the first auxiliary transmission hydraulic cylinders 12 and an auxiliary control valve V 2 for the forward/reverse transmission hydraulic cylinder 11 are connected to the hydraulic pump 16 in parallel. Then, the three-position switching valves S 1 , S 2 ,
An oil passage 14 is provided to supply pressurized oil from the switching valve S 1 , which is composed of four hydraulic cylinders 11 for forward/reverse transmission , to the hydraulic cylinder 13 for clutch operation. Three pilot pressure-operated switching valves T 1 , T 2 , and T 3 for opening and closing the passage 14 are provided.
Switching valves S 3 , S 4 and S 4 are arranged in series and are constituted by the main gear shifting hydraulic cylinders 10A, 10B and the first sub-shifting hydraulic cylinder 12, respectively.
Valves S 1 , T 1 , T 2 , and T 3 which are provided to be operated by pressure oil from S 2 and which control the operation of the clutch operation cylinder 13 are connected to the main gear transmission H 1 , front and rear. It is configured to be automatically switched in conjunction with a gear change operation so that the forward gear transmission H 2 and the first auxiliary gear transmission H 3 are switched to the engaged operation position only in the transmission state.
但し、主ギヤ変速装置H1の２個の油圧シリン
ダ１０Ａ，１０Ｂの一方を変速側に操作した状態
において、他方の油圧シリンダを変速中立位置に
圧油によつて操作保持させるように構成してあ
る。又、第２副ギヤ変速装置H4には、変速レバ
ーにて操作自在なシフターを付設してある。さら
に、動力取出軸８に対する変速装置７を人為的に
操作するように構成してある。 However, when one of the two hydraulic cylinders 10A, 10B of the main gear transmission H1 is operated to the gear shifting side, the other hydraulic cylinder is operated and held in the shifting neutral position by pressure oil. be. Further, the second auxiliary gear transmission H4 is provided with a shifter that can be operated using a speed change lever. Furthermore, the transmission device 7 relative to the power take-off shaft 8 is configured to be manually operated.
主及び補助制御弁V1，V2並びにクラツチ作動
制御の弁S1，T1，T2，T3よりも流路上手側に、
メインリリーフバルブ１５を付設すると共に、そ
れからの排油を潤滑のために油圧クラツチＣに供
給させるようにしてある。 On the flow upstream side of the main and auxiliary control valves V 1 , V 2 and the clutch operation control valves S 1 , T 1 , T 2 , T 3 ,
A main relief valve 15 is provided, and drained oil from the main relief valve 15 is supplied to the hydraulic clutch C for lubrication.
但し、図中、Ｎ及びF1乃至F8の夫々は、主制
御弁V1の操作位置を示し、又、Ｆ及びＲは、補
助制御弁V2の操作位置を示す。 However, in the figure, N and F 1 to F 8 each indicate the operating position of the main control valve V 1 , and F and R indicate the operating position of the auxiliary control valve V 2 .
第３図に示すように、圧油供給系統でクラツチ
作動制御弁T3と油圧クラツチＣとの間には、電
磁比例減圧弁１７が設けられており、その構造を
第５図に基づいて詳述すると、左右に揺動可能な
スプール１８の一端側にソレノイドコイル１９及
び、他端側に油圧ポート２０Ｐ，２０Ｃ，２０Ｔ
を形成するとともに、スプール１８の肉厚内に油
圧ポート２０Ｃ及びスプール１８先端側圧力室２
１とに連通可能な通路２２を形成し、もつて、ソ
レノイドコイル１９によつて押出力Ｆを受けたス
プール１８の移動によつて、油圧ポート２０Ｐ，
２０Ｃが連通状態になり、この連通状態になるこ
とによつて、ポート２０Ｐからポート２０Ｃに圧
油が供給され、このポート２０Ｃに供給された圧
油が通路２２を通つて圧力室２１に導入され、ス
プール１８を前記押出力Ｆに抗して、力ｆで現状
復帰させようとし、両者Ｆ，Ｆがつり合つた所で
スプール１８は静止し、ポート２０Ｃ圧力が設定
され、この設定された圧油が油圧クラツチＣに送
られることになる。つまり、ソレノイド１９の励
磁電圧に比例した圧力調整が可能である。 As shown in Fig. 3, an electromagnetic proportional pressure reducing valve 17 is provided between the clutch actuation control valve T3 and the hydraulic clutch C in the pressure oil supply system, and its structure is explained in detail based on Fig. 5. Specifically, a solenoid coil 19 is provided at one end of a spool 18 that can swing left and right, and hydraulic ports 20P, 20C, and 20T are provided at the other end.
At the same time, a hydraulic port 20C and a pressure chamber 2 on the tip side of the spool 18 are formed within the wall thickness of the spool 18.
1, and by the movement of the spool 18 which receives the pushing force F by the solenoid coil 19, the hydraulic ports 20P,
20C enters a communication state, and by entering into this communication state, pressure oil is supplied from the port 20P to the port 20C, and the pressure oil supplied to the port 20C is introduced into the pressure chamber 21 through the passage 22. , an attempt is made to return the spool 18 to its current state with a force f against the pushing force F, and when both F and F are balanced, the spool 18 comes to rest, and the port 20C pressure is set, and this set pressure Oil will be sent to hydraulic clutch C. In other words, the pressure can be adjusted in proportion to the excitation voltage of the solenoid 19.
従つて、この電磁比例減圧弁１７に対して、こ
の励磁電圧を自動制御するマイコンを内蔵した制
御回路２３が備えてあり、第４図に示すように、
クラツチオン作動時における初期昇圧速度OQ1が
大きく、以降の昇圧速度OQ2が小さくなるように
励磁電圧を制御でき、クラツチ作動における無駄
時間を抑え、円滑なクラツチ作動が可能である。
しかも、負荷の状態によつて変化するエンジンガ
バナーのコントロールラツクに対する位置検出セ
ンサ２４とエンジン回転数の測定センサ２５とか
らなる伝動負荷検出機構２６を設け、これらによ
つてクラツチ変速前の負荷状態を検出し、これら
の検出結果を負荷演算回路２７に入力し、この回
路２７での演算結果によつて前記制御回路２３に
あらかじめ設定された第１図イ，ロ，ハに示す負
荷対応して選択可能な初期昇圧速度Q1パターン
を選択できるようにしてある。 Therefore, the electromagnetic proportional pressure reducing valve 17 is provided with a control circuit 23 containing a microcomputer that automatically controls the excitation voltage, as shown in FIG.
The excitation voltage can be controlled so that the initial voltage increase rate OQ 1 at the time of clutch-on operation is large and the subsequent voltage increase rate OQ 2 is small, thereby suppressing wasted time in clutch operation and enabling smooth clutch operation.
In addition, a transmission load detection mechanism 26 is provided, which consists of a sensor 24 for detecting the position of the engine governor relative to the control rack, which changes depending on the load condition, and a sensor 25 for measuring the engine speed. These detection results are input to the load calculation circuit 27, and based on the calculation results of this circuit 27, the load shown in FIG. It is possible to select one possible initial boost rate Q pattern.
つまり、クラツチ変速前の負荷が小である場合
はイで示すパターンを、その負荷が大である場合
には、その負荷が大である程ロからハで示すパタ
ーンを選択するようになつているので、負荷変動
に対しても前記無駄時間を抑えた、円滑なクラツ
チ作動が可能である。又、中立停止状態から発進
する場合には例えば第１図イで示すような発進用
としてあらかじめ決められたパターンを選択する
ようになつている。 In other words, if the load before the clutch shift is small, the pattern shown in A is selected, and if the load is large, the patterns shown in B to C are selected as the load increases. Therefore, smooth clutch operation is possible while suppressing the dead time even in response to load fluctuations. Further, when starting from a neutral stopped state, a predetermined pattern for starting, such as that shown in FIG. 1A, is selected.
図面は本発明に係る油圧操作式ギヤ変速装置の
実施例を示し、第１図イ，ロ，ハ夫々は初期昇圧
パターンを変化させたグラフ、第２図は伝動構造
を示す概略平面図、第３図は油圧操作構造を示す
回路図、第４図はクラツチの昇圧パターンの従来
例を示すグラフ、第５図は電磁比例減圧弁を示す
一部切欠側面図である。
１７…電磁比例減圧弁、２３…制御回路、２６
…伝動負荷検出機構、Ｃ…油圧クラツチ、Q1…
初期昇圧速度、Q2…以降の昇圧速度。
The drawings show an embodiment of the hydraulically operated gear transmission according to the present invention, and FIG. FIG. 3 is a circuit diagram showing a hydraulic operation structure, FIG. 4 is a graph showing a conventional example of a clutch pressure increase pattern, and FIG. 5 is a partially cutaway side view showing an electromagnetic proportional pressure reducing valve. 17... Solenoid proportional pressure reducing valve, 23... Control circuit, 26
…Transmission load detection mechanism, C…Hydraulic clutch, Q 1 …
Initial pressure increase rate, Q 2 ... subsequent pressure increase rate.
Claims (1)
電磁比例減圧弁１７を設け、クラツチオン作動時
における初期昇圧速度Q1が大きく、以降の昇圧
速度Q2が小さくなるように前記減圧弁１７への
励磁電圧を自動制御する制御回路２３を備えてあ
る油圧操作式ギヤ変速装置であつて、伝動負荷を
検出する機構２６を備えるとともに、前記減圧弁
１７への励磁電圧の立上り特性を変更可能に前記
制御回路２３を構成し、変速切換えに伴うクラツ
チオン作動時における励磁電圧の立上り特性を、
変速切換え前の伝動状態での負荷が大きいほど初
期昇圧速度Q1が大きくなるように自動変更させ
る回路構成としてある油圧操作式ギヤ変速装置。1 In the pressure oil supply system to the hydraulic clutch C for shifting,
An electromagnetic proportional pressure reducing valve 17 is provided, and a control circuit 23 is provided to automatically control the excitation voltage to the pressure reducing valve 17 so that the initial pressure increase rate Q 1 at the time of clutch-on operation is large and the subsequent pressure increase rate Q 2 is small. The hydraulically operated gear transmission is equipped with a mechanism 26 for detecting a transmission load, and the control circuit 23 is configured to be able to change the rise characteristics of the excitation voltage applied to the pressure reducing valve 17, and the clutch-on operation associated with gear change. The rise characteristics of the excitation voltage at
A hydraulically operated gear transmission device having a circuit configuration that automatically changes the initial pressure increase rate Q 1 to increase as the load in the transmission state before gear changeover increases.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59210228A JPS6189133A (en) | 1984-10-05 | 1984-10-05 | Hydraulic-operation type speed change gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59210228A JPS6189133A (en) | 1984-10-05 | 1984-10-05 | Hydraulic-operation type speed change gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6189133A JPS6189133A (en) | 1986-05-07 |
| JPH0372846B2 true JPH0372846B2 (en) | 1991-11-20 |
Family
ID=16585903
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59210228A Granted JPS6189133A (en) | 1984-10-05 | 1984-10-05 | Hydraulic-operation type speed change gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6189133A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6435150A (en) * | 1987-07-31 | 1989-02-06 | Kubota Ltd | Hydraulic clutch for speed change of working vehicle |
| JPH03186661A (en) * | 1989-12-15 | 1991-08-14 | Kubota Corp | Speed changing hydraulic structure |
| JP4655482B2 (en) * | 2004-02-09 | 2011-03-23 | 井関農機株式会社 | Gearbox for work vehicle |
-
1984
- 1984-10-05 JP JP59210228A patent/JPS6189133A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6189133A (en) | 1986-05-07 |
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