JPH0743532Y2 - Hydraulic transmission - Google Patents
Hydraulic transmissionInfo
- Publication number
- JPH0743532Y2 JPH0743532Y2 JP8254788U JP8254788U JPH0743532Y2 JP H0743532 Y2 JPH0743532 Y2 JP H0743532Y2 JP 8254788 U JP8254788 U JP 8254788U JP 8254788 U JP8254788 U JP 8254788U JP H0743532 Y2 JPH0743532 Y2 JP H0743532Y2
- Authority
- JP
- Japan
- Prior art keywords
- line
- tank
- hydraulic
- refueling
- flow
- 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
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Description
【考案の詳細な説明】 〈産業上の利用分野〉 本考案は、正逆可変容量形油圧ポンプと正逆油圧モータ
を閉回路で接続してなり、中立位置の幅が広い油圧伝動
装置に関する。DETAILED DESCRIPTION OF THE INVENTION <Industrial field of application> The present invention relates to a hydraulic transmission device in which a forward / reverse variable displacement hydraulic pump and a forward / reverse hydraulic motor are connected in a closed circuit, and the neutral position has a wide width.
〈従来の技術〉 従来、この種の油圧伝動装置として、例えば第３図に示
すようなものが知られている（「油空圧便覧」オーム社
昭和50年発行 850頁）。この油圧伝動装置は、正逆
可変容量形油圧ポンプ21と正逆可変容量形油圧モータ22
を、ライン23とライン24で接続して閉回路となし、両ラ
イン23,24をタンク26に連通する給油ライン25で接続す
るとともに、タンク接続点Ｔの両側の給油ライン25にタ
ンクへの流れを阻止するようにサクション用のチェック
弁27,28を夫々介設し、各チェック弁27,28と並列に上記
給油ライン25に過負荷用のリリーフ弁29,30を夫々接続
してなる。そして、連続的な広範囲の変速およびポンプ
とモータの圧力，流量調整によるトルク，馬力制御が可
能なので、建設機械等の車輌の駆動に用いられている。<Prior Art> Conventionally, as a hydraulic transmission of this type, for example, one as shown in FIG. 3 is known (“Pneumatic and pneumatic handbook”, Ohmsha, 1975, p. 850). This hydraulic transmission system includes a forward / reverse variable displacement hydraulic pump 21 and a forward / reverse variable displacement hydraulic motor 22.
Is connected by a line 23 and a line 24 to form a closed circuit. Both lines 23, 24 are connected by a refueling line 25 communicating with the tank 26, and the refueling lines 25 on both sides of the tank connection point T flow to the tank. Suction check valves 27, 28 are respectively provided to prevent the above-mentioned problems, and relief valves 29, 30 for overload are connected to the refueling line 25 in parallel with the check valves 27, 28, respectively. Since it is possible to continuously change a wide range of gears and control torque and horsepower by adjusting pressures and flow rates of pumps and motors, it is used for driving vehicles such as construction machines.
〈考案が解決しようとする課題〉 ところで、上記従来の油圧伝動装置は、正逆自在に動作
する可変容量油圧ポンプ21により閉回路を介して油圧モ
ータ22を駆動しているため、正逆の境界たる中立位置が
理論上一点しかなく、その幅が非常に狭いという性質を
有する。従って、油圧モータ22を停止させるには、油圧
ポンプ21の例えば斜板21aを斜板シリンダで正確に中立
位置に位置付けるように制御しなければならない。とこ
ろが、斜板21aを傾けて電動機Ｍを正転させ、ライン23
側から圧油を供給して油圧モータ22を正転させていた状
態から、油圧モータ22を停止させる場合、斜板シリンダ
によって斜板21aを一点しかない中立位置に正確に位置
付けることが難しく、斜板が中立位置を越えて逆方向に
傾くと、逆にライン24側から圧油が供給されて油圧モー
タ22が逆転してしまうという問題がある。また、電動機
Ｍを回転させながら斜板21aを中立位置に保持して、直
ちに起動できる状態で油圧モータ22を一時停止させる場
合も、同様の理由から制御が難しいという問題がある。
そのため、このような油圧伝動装置を搭載した建設機械
事態の前進，後退等の操縦性や制御性が悪化する。<Problems to be solved by the invention> By the way, in the conventional hydraulic transmission described above, since the hydraulic motor 22 is driven through the closed circuit by the variable displacement hydraulic pump 21 that operates in the forward and reverse directions, the forward and reverse boundaries are Theoretically, there is only one neutral position, and its width is extremely narrow. Therefore, in order to stop the hydraulic motor 22, the swash plate 21a of the hydraulic pump 21, for example, must be controlled by the swash plate cylinder to be accurately positioned at the neutral position. However, the swash plate 21a is tilted to rotate the electric motor M forward, and the line 23
When stopping the hydraulic motor 22 from the state where the hydraulic motor 22 was normally rotated by supplying pressure oil from the side, it is difficult to accurately position the swash plate 21a at the neutral position with only one point by the swash plate cylinder. If the plate exceeds the neutral position and tilts in the opposite direction, there is a problem in that pressure oil is supplied from the line 24 side and the hydraulic motor 22 reversely rotates. Further, when the swash plate 21a is held at the neutral position while rotating the electric motor M and the hydraulic motor 22 is temporarily stopped in a state where it can be immediately started, there is a problem that control is difficult for the same reason.
As a result, maneuverability and controllability such as forward and backward movement of a construction machine situation equipped with such a hydraulic transmission device deteriorates.
そこで、本考案の目的は、簡素かつ安価な構成でもって
中立位置の幅を拡大でき、これを用いた建設機械等の車
両の操縦性や制御性を改善することができる油圧伝動装
置を提供することである。Therefore, an object of the present invention is to provide a hydraulic transmission device capable of expanding the width of the neutral position with a simple and inexpensive structure and improving the maneuverability and controllability of a vehicle such as a construction machine using the neutral position. That is.
〈課題を解決するための手段〉 上記目的を達成するため、本考案の油圧伝動装置は、第
１図に例示するように、車両の走行に用いられるもの
で、正逆可変容量形油圧ポンプ１と正逆油圧モータ２を
接続する閉回路を構成する前進時高圧ライン３と後退時
高圧ライン４を連通する給油ライン５と、この給油ライ
ン５とタンク７とを接続するタンクライン６と、上記給
油ライン５とタンクライン６の接続点Ｔよりも前進時高
圧ライン３側の給油ライン5aにタンク７への流れを阻止
するように介設された第１のチエック弁８と、上記給油
ライン５とタンクライン６の接続点Ｔよりも後退時高圧
ライン４側の給油ライン5bに、タンク７への流れを阻止
するように介設された第２のチエック弁９及びタンク７
への流れを許容する絞り通路10を備え、上記絞り通路10
は、上記第２チエック弁９における弁体14の軸心にオリ
フィス14aとして形成したことを特徴とする。<Means for Solving the Problems> In order to achieve the above object, the hydraulic transmission of the present invention is used for traveling of a vehicle as illustrated in FIG. And a refueling line 5 that connects a forward high pressure line 3 and a backward high pressure line 4 that form a closed circuit that connects the forward and reverse hydraulic motors 2, a tank line 6 that connects the refueling line 5 and the tank 7, and The first check valve 8 installed to prevent the flow to the tank 7 in the oil supply line 5a on the high pressure line 3 side when moving forward from the connection point T between the oil supply line 5 and the tank line 6, and the oil supply line 5 described above. The second check valve 9 and the tank 7 which are provided in the refueling line 5b on the high pressure line 4 side at the time of retreating from the connection point T between the tank line 6 and the tank line 6 so as to prevent the flow to the tank 7.
Is provided with a throttle passage 10 that allows the flow to the
Is formed as an orifice 14a in the axial center of the valve body 14 of the second check valve 9.
〈作用〉 給油ライン５のタンクライン６との接続点Ｔよりも後退
時高圧ライン４側の給油ライン5bにチェック弁９と絞り
通路10が並列に接続されている。電動機等で駆動される
正逆可変容量形油圧ポンプ１の例えば斜板1aが正方向に
傾いていると、ポンプ１から吐出油は、チェック弁８で
タンク７への流れを阻止された前進時高圧ライン３を経
て正逆油圧モータ２に供給され、正逆油圧モータ２は正
転する。この状態から油圧ポンプ１の斜板1aを斜板シリ
ンダで中立方向へ傾動させたとき、斜板1aが中立位置を
越えて僅かに逆方向に傾いたとする。すると、油圧ポン
プ１は前述とは逆に後退時高圧ライン４を経て油圧モー
タ２に吐出油を供給しようとする。このとき、上記後退
時高圧ライン４から分岐する給油ライン5bには、タンク
７への流れを阻止するチェック弁９とタンク７への流れ
を許容するオリフィス14aからなる絞り通路10が接続さ
れているので、上記吐出油は慣性で僅かに正転する油圧
モータ２よりも油路抵抗の小さい上記絞り通路10および
タンクライン６を経てタンク７に流れ込み、油圧モータ
２は逆転することなく停止する。換言すれば、この絞り
通路10を経るドレン流によって油圧ポンプ１の中立位置
の幅が拡大でき、しかも、絞り通路10をオリフィス14a
とすることにより、油温の変化に影響されることなく開
度に比例したドレン流が得られるから、中立位置の幅が
変化することがなく、常に一定の中立幅に維持できる。
さらに、油圧モータ２を逆転させるべく油圧ポンプ１の
斜板1aを逆方向に所定角度以上傾けると、高圧となる後
退時高圧ライン４に対して上記絞り通路10は抵抗として
作用し、僅かのドレン流を除く大部分の吐出油は、後退
時高圧ライン４から油圧モータ２に供給され、油圧モー
タ２は逆転する。なお、上記中立位置の幅の拡大によ
り、油圧ポンプ１を駆動したままで斜板1aを中立位置に
して、油圧モータ２を直ちに軌道できる状態で一時停止
させることも容易になる。<Operation> A check valve 9 and a throttle passage 10 are connected in parallel to the oil supply line 5b on the side of the high pressure line 4 at the time of retreating from the connection point T of the oil supply line 5 with the tank line 6. When, for example, the swash plate 1a of the forward / reverse variable displacement hydraulic pump 1 driven by an electric motor is tilted in the forward direction, the discharge oil from the pump 1 is prevented from flowing to the tank 7 by the check valve 8 during forward movement. It is supplied to the forward / reverse hydraulic motor 2 via the high-pressure line 3, and the forward / reverse hydraulic motor 2 rotates normally. When the swash plate 1a of the hydraulic pump 1 is tilted in the neutral direction by the swash plate cylinder from this state, it is assumed that the swash plate 1a slightly tilts in the opposite direction beyond the neutral position. Then, contrary to the above, the hydraulic pump 1 tries to supply the discharge oil to the hydraulic motor 2 via the high pressure line 4 at the time of backward movement. At this time, a throttle passage 10 including a check valve 9 for blocking the flow to the tank 7 and an orifice 14a for allowing the flow to the tank 7 is connected to the oil supply line 5b branched from the high pressure line 4 at the time of retreat. Therefore, the discharged oil flows into the tank 7 via the throttle passage 10 and the tank line 6 which have a smaller oil passage resistance than the hydraulic motor 2 which rotates slightly forward due to inertia, and the hydraulic motor 2 stops without rotating in the reverse direction. In other words, the drain flow through the throttle passage 10 can increase the width of the hydraulic pump 1 at the neutral position, and the throttle passage 10 can be provided with the orifice 14a.
By doing so, a drain flow proportional to the opening is obtained without being affected by changes in the oil temperature, so that the width of the neutral position does not change, and the neutral width can always be maintained at a constant neutral width.
Further, when the swash plate 1a of the hydraulic pump 1 is tilted in the opposite direction by a predetermined angle or more in order to reverse the hydraulic motor 2, the throttle passage 10 acts as a resistance against the high pressure line 4 at the time of retreat which becomes a high pressure, and a slight drainage occurs. Most of the discharged oil except the flow is supplied to the hydraulic motor 2 from the high pressure line 4 at the time of retreat, and the hydraulic motor 2 rotates in the reverse direction. By increasing the width of the neutral position, it becomes easy to set the swash plate 1a to the neutral position while the hydraulic pump 1 is still driven and to temporarily stop the hydraulic motor 2 in a state where it can immediately orbit.
〈実施例〉 以下、本考案を図示の実施例により詳細に説明する。<Embodiment> The present invention will be described in detail below with reference to an illustrated embodiment.
第１図は油圧伝動装置の一例を示しており、この油圧伝
動装置は、斜板式正逆可変容量形油圧ポンプ１と正逆油
圧モータ２を、車両が前進するときに高圧となる前進時
高圧ラインとしての第１ライン３と、車両が後退すると
きに高圧となる後退時高圧ラインとしての第２ライン４
とで接続して閉回路となし、上記第１ライン３と第２ラ
イン４を給油ライン５で連通し、この給油ライン５の分
岐点Ｔからタンク７に連なるタンクライン６を分岐させ
るとともに、上記分岐点Ｔの両側の給油ライン5a,5bに
タンク７への流れを阻止するサクション用のチェック弁
8,9を夫々介設し、第２ライン４側のチェック弁９と並
列に上記給油ライン5bに絞り10を接続してなる。FIG. 1 shows an example of a hydraulic power transmission system. This hydraulic power transmission system comprises a swash plate type forward / reverse variable displacement hydraulic pump 1 and a forward / reverse hydraulic motor 2 which have a high pressure when moving forward and a high pressure when moving forward. The first line 3 as a line and the second line 4 as a high-pressure backward line that becomes high pressure when the vehicle moves backward
To form a closed circuit, the first line 3 and the second line 4 are communicated with each other through a refueling line 5, and a tank line 6 that is connected to a tank 7 is branched from a branch point T of the refueling line 5 and Suction check valves for blocking the flow to the tank 7 in the oil supply lines 5a and 5b on both sides of the branch point T
8 and 9 are provided respectively, and a throttle 10 is connected to the refueling line 5b in parallel with the check valve 9 on the second line 4 side.
第２図（ａ）は、上記チェック弁８および上記絞り10を
有するチェック弁９即ちオリフィス付チェック弁19を一
体化した複合弁の軸方向断面図である。この複合弁は、
本体11内に１次ポートA3をもつ弁室12と１次ポートA4を
もつ弁室13を対向して設け、両弁室間を共通のタンクポ
ートＴにするとともに、上記弁室13に先端に上記絞り10
をなすオリフィス14aを有する筒状の弁体14を挿入し、
これを弁室13の後端に液密に螺着したプラグ15との間に
縮装したばね16で付勢して着座させる一方、上記弁室12
に球状の弁体17を挿入し、これを弁室12の後端に液密に
螺着したプラグ18との間に縮装したばね19で付勢して着
座させている。FIG. 2 (a) is an axial sectional view of a composite valve in which the check valve 8 and the check valve 9 having the throttle 10, that is, the check valve 19 with an orifice are integrated. This compound valve
A valve chamber 12 having a primary port A 3 and a valve chamber 13 having a primary port A 4 are provided in the main body 11 so as to face each other, and a common tank port T is provided between both valve chambers. The above diaphragm 10 at the tip
Insert the cylindrical valve body 14 having the orifice 14a forming
This is seated by urging it with a spring 16 compressed between a plug 15 and a plug 15 that is liquid-tightly screwed to the rear end of the valve chamber 13.
A spherical valve body 17 is inserted into the valve chamber 12 and is seated by being biased by a spring 19 compressed between a valve 18 and a plug 18 screwed in a liquid-tight manner at a rear end of the valve chamber 12.
上記プラグ15は、先端に、弁体14のオリフィス14aに連
通する内孔14bに挿入される細径のガイドシャフト15bと
これに続く太径のストッパ部15aを有し、後端のねじ部
端面に、第２図（ｂ）に示すようにレンチ用の六角穴15
cと識別用の環状溝15dを有して、弁体14の開閉動を案内
し規制するとともに、球状の弁体17を挿入した弁室12へ
の誤装着を防止するようになっている。一方、上記プラ
グ18は、先端に太径のストッパ部18aと後端のねじ部端
面に六角穴18c（第２図（ｃ）参照）を有して、弁体17
の開動を規制し、オリフィス付チェック弁19の弁体14を
挿入した弁室13への挿着ができないようになっている。
なお、上記１次ポートA3，A4およびタンクポートＴは、
第１図の油圧回路中の同一記号で示す点に夫々対応して
いる。こうしてなる第２図に示す弁は、球状の弁体17に
よって１次ポートA3からタンクポートＴの油流を阻止
し、タンクポートＴから１次ポートA3への作動油の吸入
を許容するとともに、弁体14によって上述と同様の逆止
作用をなし、かつそのオリフィス14aで１次ポートA4と
タンクポートＴ間の油流を絞るものであって、第１図の
チェック弁8,9および絞り10をコンパクトに一体化した
実用性に富む複合弁である。The plug 15 has a small diameter guide shaft 15b inserted into an inner hole 14b communicating with the orifice 14a of the valve body 14 and a large diameter stopper portion 15a following the guide shaft 15b at the tip, and the screw portion end surface at the rear end. In addition, as shown in Fig. 2 (b), the hexagon socket for the wrench 15
c and an annular groove 15d for identification are provided to guide and regulate the opening / closing movement of the valve body 14 and prevent erroneous mounting in the valve chamber 12 into which the spherical valve body 17 is inserted. On the other hand, the plug 18 has a large-diameter stopper portion 18a at the front end and a hexagonal hole 18c (see FIG. 2 (c)) at the end surface of the screw portion at the rear end.
Of the check valve 19 with an orifice cannot be inserted into the valve chamber 13 in which the valve body 14 is inserted.
The primary ports A 3 , A 4 and the tank port T are
These points correspond to the same symbols in the hydraulic circuit of FIG. 1, respectively. The valve shown in FIG. 2 thus configured blocks the oil flow from the primary port A 3 to the tank port T by means of the spherical valve element 17, and allows the suction of hydraulic oil from the tank port T to the primary port A 3 . At the same time, the valve body 14 performs the same check function as described above, and the orifice 14a restricts the oil flow between the primary port A 4 and the tank port T. It is a highly practical compound valve in which the throttle 10 and the throttle 10 are integrated compactly.
上記構成の油圧伝動装置の動作について、第１図を参照
しつつ次に述べる。The operation of the hydraulic transmission having the above structure will be described below with reference to FIG.
いま、斜板1aが正方向に傾いた油圧ポンプ１が図示しな
い電動機で傾転駆動されると、油圧ポンプ１からの吐出
油は、チェック弁８でタンク７への流れを阻止された第
１ライン３を経て油圧モータ２に供給され、油圧モータ
２は正転する。この状態から油圧ポンプ１の斜板1aを図
示しない斜板シリンダで中立方向へ傾動させたとき、斜
板1aが中立位置を越えて僅かに逆方向に傾いたとする。
すると、油圧ポンプ１は、前述と逆に第２ライン４を経
て油圧モータ２に吐出油を供給しようとする。このと
き、上記第２ライン４から分岐する給油ライン5bには、
タンク７への流れを阻止するチェック弁９とタンク７へ
の流れを許容するオリフィス14aからなる絞り10が接続
されており、絞り10の油路抵抗は慣性で僅かに正転しよ
うとする油圧モータ２の油路抵抗よりも小さいので、上
記吐出油は絞り10およびタンクライン６を経てタンク７
に流れ込み、油圧モータ２は逆転することなく停止す
る。換言すれば、絞り10を経るドレン流によって油圧ポ
ンプの中立位置の幅が拡大でき、しかも、絞り通路10を
オリフィス14aとすることにより、油温の変化に影響さ
れることなく開度に比例したドレン流が得られるから、
中立位置の幅が変化することがなく、常に一定の中立幅
に維持できる。従って、油圧ポンプ１の電動機を動かし
たままで斜板1aを中立位置にして、油圧モータ２を直ち
に起動できる待機状態で一時停止させる場合も、中立位
置の幅が従来よりも広いので、斜板シリンダによる中立
位置保持の制御が格段に容易化する。When the hydraulic pump 1 in which the swash plate 1a is tilted in the forward direction is tilted by an electric motor (not shown), the discharge oil from the hydraulic pump 1 is blocked by the check valve 8 from flowing into the tank 7. It is supplied to the hydraulic motor 2 via the line 3, and the hydraulic motor 2 rotates normally. It is assumed that when the swash plate 1a of the hydraulic pump 1 is tilted in the neutral direction by a swash plate cylinder (not shown) from this state, the swash plate 1a slightly tilts in the opposite direction beyond the neutral position.
Then, the hydraulic pump 1 tries to supply the discharge oil to the hydraulic motor 2 via the second line 4 contrary to the above. At this time, in the refueling line 5b branched from the second line 4,
A check valve 9 that blocks the flow to the tank 7 and a throttle 10 that is made up of an orifice 14a that allows the flow to the tank 7 are connected, and the oil passage resistance of the throttle 10 is a hydraulic motor that tends to rotate slightly forward due to inertia. Since it is smaller than the oil passage resistance of No. 2, the discharge oil passes through the throttle 10 and the tank line 6 and then to the tank 7
And the hydraulic motor 2 stops without reverse rotation. In other words, the width of the neutral position of the hydraulic pump can be expanded by the drain flow passing through the throttle 10. Moreover, by making the throttle passage 10 the orifice 14a, it is proportional to the opening degree without being affected by the change in the oil temperature. Because the drain flow is obtained,
The width of the neutral position does not change, and the neutral width can always be kept constant. Therefore, even when the swash plate 1a is set to the neutral position while the electric motor of the hydraulic pump 1 is moving and the hydraulic motor 2 is temporarily stopped in a standby state in which the hydraulic motor 2 can be immediately started, the width of the neutral position is wider than in the conventional case. The control of holding the neutral position by means of is greatly facilitated.
次に、油圧モータ２を逆転させるべく斜板1aを逆方向に
所定角度以上傾けて油圧ポンプ１を傾転駆動すると、高
圧となる第２ライン４に対して上記絞り10は抵抗として
働き、油圧ポンプ１からの吐出油は、絞り10を経る僅か
のドレン流を除く大部分が油圧モータ２に供給され、油
圧モータ２は逆転する。Next, when the swash plate 1a is tilted in the opposite direction by a predetermined angle or more to reversely rotate the hydraulic motor 2, the hydraulic pump 1 is tilted and driven, and the throttle 10 acts as a resistance against the second line 4 having a high pressure. Most of the oil discharged from the pump 1 is supplied to the hydraulic motor 2 except for a slight drain flow passing through the throttle 10, and the hydraulic motor 2 rotates in the reverse direction.
従って、このような油圧伝動装置を負荷変動の激しい建
設機械等に搭載すれば、簡素かつ安価な構成でもって、
トルクの必要な前進方向の操縦性能や操作感覚を低下さ
せることなく中立位置の幅を拡大でき、建設機械自体の
操縦性や制御性を大いに改善することができる。さら
に、この油圧伝動装置に第２図で述べた複合弁を用いれ
ば、装置をコンパクト化し、保守点検も容易化するう
え、前述の構造によりオリフェイス付チェック弁19とボ
ール式のチェック弁８を付け間違う虞れもなくなるとい
う利点がある。Therefore, if such a hydraulic power transmission device is mounted on a construction machine or the like in which load fluctuations are severe, a simple and inexpensive structure can be obtained.
It is possible to expand the width of the neutral position without deteriorating the steering performance and the operation feeling in the forward direction that require torque, and it is possible to greatly improve the maneuverability and controllability of the construction machine itself. Further, if the compound valve described in FIG. 2 is used for this hydraulic transmission, the apparatus can be made compact and maintenance and inspection can be facilitated, and the check valve 19 with an orientation and the ball type check valve 8 can be provided by the above-mentioned structure. There is an advantage that there is no risk of making a mistake.
なお、本考案が図示の実施例に限られないのはいうまで
もない。Needless to say, the present invention is not limited to the illustrated embodiment.
〈考案の効果〉 以上の説明で明らかなように、本考案の油圧伝動装置
は、車両の走行に用いられるものであって、正逆可変容
量形油圧ポンプと正逆油圧モータを前進時高圧ラインと
後退時高圧ラインで接続して閉回路となし、上記両ライ
ンをタンクに連通する給油ラインで接続するとともに、
タンク接続点の両側の給油ラインにサクション用のチェ
ック弁を夫々介設し、後退時高圧ライン側の給油ライン
に、タンクへの流れを許容する絞り通路を設け、この絞
り通路を、第２チエック弁における弁体の軸心にオリフ
ィスとして形成しているので、簡素かつ安価な構成でも
って、上記絞り通路を経るドレン流によって油圧ポンプ
の中立位置の幅を拡大でき、しかも、絞り通路をオリフ
ィスとすることにより、油温の変化に影響されることな
く開度に比例したドレン流が得られるから、中立位置の
幅が変化することなく、常に一定の中立幅を維持するこ
とができ、この油圧伝動装置を用いた建設機械等の車両
の操縦性や制御性を大いに改善することができる。<Effect of the Invention> As is clear from the above description, the hydraulic transmission of the present invention is used for traveling of a vehicle, and includes a forward / reverse variable displacement hydraulic pump and a forward / reverse hydraulic motor for a high pressure line during forward movement. And a high pressure line at the time of retreating to form a closed circuit, connecting both lines with an oil supply line communicating with the tank,
Check valves for suction are provided in the oil supply lines on both sides of the tank connection point, and a throttle passage that allows the flow to the tank is provided in the oil supply line on the high pressure line side when retreating. This throttle passage is connected to the second check. Since the orifice is formed in the axial center of the valve body of the valve, the width of the neutral position of the hydraulic pump can be increased by the drain flow through the throttle passage with a simple and inexpensive structure, and the throttle passage can be used as an orifice. By doing so, a drain flow proportional to the opening can be obtained without being affected by changes in oil temperature, so that the neutral width can always be maintained without changing the width of the neutral position. The maneuverability and controllability of a vehicle such as a construction machine using a transmission device can be greatly improved.
第１図は本考案の油圧伝動装置の一実施例を示す回路
図、第２図は上記実施例に用いられる複合弁を示す図、
第３図は従来の油圧伝動装置を示す回路図である。 １……斜板式正逆可変容量形油圧ポンプ、２……正逆油
圧モータ、３……第１ライン、４……第２ライン、５…
…給油ライン、６……タンクライン、７……タンク、8,
9……チェック弁、10……絞り、Ｔ……分岐点。FIG. 1 is a circuit diagram showing an embodiment of the hydraulic transmission of the present invention, and FIG. 2 is a view showing a compound valve used in the above embodiment,
FIG. 3 is a circuit diagram showing a conventional hydraulic transmission device. 1 ... Swash plate type forward / reverse variable displacement hydraulic pump, 2 ... Forward / reverse hydraulic motor, 3 ... First line, 4 ... Second line, 5 ...
… Refueling line, 6 …… Tank line, 7 …… Tank, 8,
9 …… Check valve, 10 …… Throttle, T …… Branch point.
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭57−116964（ＪＰ，Ａ) 特開 昭54−71258（ＪＰ，Ａ) 特公 昭42−14887（ＪＰ，Ｂ１) ─────────────────────────────────────────────────── ─── Continuation of front page (56) References JP-A-57-116964 (JP, A) JP-A-54-71258 (JP, A) JP-B-42-14887 (JP, B1)
Claims (1)
圧ポンプ（１）と正逆油圧モータ（２）を閉回路で接続
した油圧伝動装置において、上記閉回路を構成する前進
時高圧ライン（３）と後退時高圧ライン（４）を連通す
る給油ライン（５）と、この給油ライン（５）とタンク
（７）とを接続するタンクライン（６）と、上記給油ラ
イン（５）とタンクライン（６）の接続点（Ｔ）よりも
前進時高圧ライン（３）側の給油ライン（5a）にタンク
（７）への流れを阻止するように介設された第１のチエ
ック弁（８）と、上記給油ライン（５）とタンクライン
（６）の接続点（Ｔ）よりも後退時高圧ライン（４）側
の給油ライン（5b）に、タンク（７）への流れを阻止す
るように介設された第２のチエック弁（９）及びタンク
（７）への流れを許容する絞り通路（10）を備え、上記
絞り通路（10）は、上記第２チエック弁（９）における
弁体（14）の軸心にオリフィス（14a）として形成した
ことを特徴とする油圧伝動装置。1. A hydraulic transmission device used for traveling of a vehicle, wherein a forward / reverse variable displacement hydraulic pump (1) and a forward / reverse hydraulic motor (2) are connected by a closed circuit. A refueling line (5) that communicates the line (3) with the high-pressure backward line (4), a tank line (6) that connects the refueling line (5) and the tank (7), and the refueling line (5). And a tank line (6), a first check valve provided in the oil supply line (5a) on the high pressure line (3) side when advancing beyond the connection point (T) so as to prevent the flow to the tank (7). (8) and the refueling line (5b) on the high pressure line (4) side when retreating from the connection point (T) between the refueling line (5) and the tank line (6) prevents the flow to the tank (7) Flow to the second check valve (9) and the tank (7) that are installed A hydraulic transmission characterized in that the throttle passage (10) is formed as an orifice (14a) at the axial center of the valve body (14) of the second check valve (9). apparatus.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8254788U JPH0743532Y2 (en) | 1988-06-22 | 1988-06-22 | Hydraulic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8254788U JPH0743532Y2 (en) | 1988-06-22 | 1988-06-22 | Hydraulic transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH024059U JPH024059U (en) | 1990-01-11 |
| JPH0743532Y2 true JPH0743532Y2 (en) | 1995-10-09 |
Family
ID=31307298
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8254788U Expired - Lifetime JPH0743532Y2 (en) | 1988-06-22 | 1988-06-22 | Hydraulic transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0743532Y2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4589574B2 (en) * | 2001-06-28 | 2010-12-01 | ヤンマー株式会社 | Hydraulic continuously variable transmission and power transmission device |
| JP4510332B2 (en) * | 2001-06-28 | 2010-07-21 | ヤンマー株式会社 | Hydraulic continuously variable transmission and power transmission device |
| JP4510333B2 (en) * | 2001-06-28 | 2010-07-21 | ヤンマー株式会社 | Hydraulic continuously variable transmission and power transmission device |
| EP2824028B2 (en) | 2013-07-09 | 2021-10-27 | ABB Oy | Ship's propulsion unit |
-
1988
- 1988-06-22 JP JP8254788U patent/JPH0743532Y2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH024059U (en) | 1990-01-11 |
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