JPS63291791A - Device for adjusting installation angle of ship propeller - Google Patents
Device for adjusting installation angle of ship propellerInfo
- Publication number
- JPS63291791A JPS63291791A JP62128796A JP12879687A JPS63291791A JP S63291791 A JPS63291791 A JP S63291791A JP 62128796 A JP62128796 A JP 62128796A JP 12879687 A JP12879687 A JP 12879687A JP S63291791 A JPS63291791 A JP S63291791A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- cylinder
- cylinders
- hydraulic pump
- passage
- 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
- 238000009434 installation Methods 0.000 title abstract description 8
- 239000010720 hydraulic oil Substances 0.000 claims description 18
- 230000002441 reversible effect Effects 0.000 abstract description 4
- 239000012530 fluid Substances 0.000 abstract description 3
- 238000007599 discharging Methods 0.000 abstract 1
- 239000003921 oil Substances 0.000 description 6
- 230000000694 effects Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- 230000001141 propulsive effect Effects 0.000 description 2
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
Landscapes
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、モータボートや小型漁船等の船尾に傾動可能
に配設された推進機の、船体に対する取付角度を調整す
るための装置に関し、特にポンプ容量を増大することな
く推進機の動作速度を速くできるようにした装置に関す
る。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a device for adjusting the mounting angle of a propulsion unit tiltably disposed at the stern of a motor boat, small fishing boat, etc., with respect to the hull. In particular, the present invention relates to a device that can increase the operating speed of a propulsion device without increasing pump capacity.
従来からモータボート等の小型船舶に採用されている船
外推進機は、船体に対する取付角度を調整できるように
なっている。この取付角度調整装置は、推進機と船体と
の間に油圧シリンダを、例えば２本配設し、該シリンダ
で推進機を傾動駆動するように構成されており、水上の
格納位置と水没位置との間で移動させるチルト動作及び
水没位置で船体に対する傾斜角度を調整するトリム動作
が行えるようになっている。2. Description of the Related Art Outboard propulsion machines, which have been conventionally employed in small vessels such as motorboats, are designed to allow adjustment of the angle at which they are attached to the hull. This installation angle adjustment device is configured such that, for example, two hydraulic cylinders are disposed between the propulsion device and the hull, and the cylinders drive the propulsion device in a tilting manner. It is possible to perform a tilt operation to move the vessel between the two, and a trim operation to adjust the inclination angle with respect to the hull at the submerged position.
ところで、上記角度調整装置においては、相反する要件
が求められる場合があり、その例として上記推進機を各
位置に移動させる動作速度がある。By the way, in the above-mentioned angle adjustment device, contradictory requirements may be required, and an example thereof is the operating speed for moving the above-mentioned propulsion device to each position.
−ｍに上記トリム動作においては、操作し易い速度があ
り、これより速いと推進機を最適の傾斜角度に設定する
のが困難となり、遅過ぎるといらいらすることとなる。-m has a certain speed at which it is easy to operate the trim operation; if it is faster than this, it will be difficult to set the propulsion device to the optimum inclination angle, and if it is too slow, it will be irritating.
一方、上記チルト動作においては、限度はあるものので
きるだけ高速の方が望ましい。On the other hand, in the above-mentioned tilt operation, although there is a limit, it is desirable that the tilt operation be as fast as possible.
しかしながら上記従来の角度調整装置において、上記両
動作速度を満足させるには、トリム動作時に必要な高い
油圧を確保しつつ、チルト動作における大きい流量を得
ることのできるよう油圧ポンプの容量を拡大することが
必要となる。そのため従来はコスト及び配置スペース上
の問題を考慮し、これらの妥協点で上記動作速度を設定
せざるを得ないというのが実情であった。However, in order to satisfy both of the above operating speeds in the above conventional angle adjustment device, it is necessary to increase the capacity of the hydraulic pump so that it can obtain a large flow rate during tilt operation while ensuring the high oil pressure required during trim operation. Is required. For this reason, in the past, the actual situation was that the above-mentioned operating speed had to be set by taking into consideration problems in terms of cost and installation space, and making a compromise between these.
そこで本発明の目的は、油圧ポンプの容量を拡大するこ
となく、最適なトリム、チルト動作速度が得られる船舶
用推進機の取付角度調整装置を提供する点にある。SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a mounting angle adjustment device for a marine propulsion device that allows optimum trim and tilt operation speeds to be obtained without increasing the capacity of a hydraulic pump.
〔問題点を解決するための手段〕
本件発明者は、上記問題点を解決するため、以下の点に
着目したものである０例えばトリム動作のように大きな
負荷が作用する場合は、これに応じた大出力が必要であ
るから、全てのシリンダに作動油を供給しなければなら
ない。一方、チルト動作のように負荷が小さい場合は、
小さい出力でよいから、必ずしも全てのシリンダに作動
油を供給する必要はない。[Means for solving the problem] In order to solve the above problem, the inventor of the present invention focused on the following points. For example, when a large load is applied such as in a trim operation, Since a large output is required, hydraulic oil must be supplied to all cylinders. On the other hand, when the load is small, such as during tilt operation,
Since a small output is sufficient, it is not necessary to supply hydraulic oil to all cylinders.
そこで本発明は、船尾に揺動可能に取り付けられた推進
機を、油圧シリンダで水没位置と水上位置との間で傾動
駆動するとともに、水没位置での船体に対する傾斜角度
を調整するようにした取付角度調整装置において、油圧
シリンダを複数本設けるとともに、該各シリンダに油圧
通路を介して油圧ポンプを接続し、該油圧ポンプからの
作動油を、負荷の大、小に応じて上記全てのシリンダ又
は一部のシリンダにそれぞれ切り換え供給する切り換え
弁を上記油圧通路に介設したことを特徴としている。In view of this, the present invention proposes an installation in which a propulsion unit, which is swingably attached to the stern of the ship, is driven to tilt between a submerged position and an above-water position using a hydraulic cylinder, and the inclination angle with respect to the hull at the submerged position is adjusted. In the angle adjustment device, a plurality of hydraulic cylinders are provided, a hydraulic pump is connected to each cylinder via a hydraulic passage, and hydraulic oil from the hydraulic pump is applied to all or all of the cylinders according to the magnitude of the load. It is characterized in that a switching valve for selectively supplying to some cylinders is interposed in the hydraulic passage.
ここで本発明における切り換え弁としては、例えば油圧
通路内の圧力で切り換えられるリリーフ弁、あるいは別
個の信号で切り換えられる電磁弁などが採用できろ。Here, as the switching valve in the present invention, for example, a relief valve that is switched by the pressure in the hydraulic passage, or an electromagnetic valve that is switched by a separate signal, etc. can be adopted.
本発明に係る取付角度調整装置によれば、トリム動作時
のような重負荷時には全てのシリンダに作動油が供給さ
れるから、推進機からの大きな推進反力に耐えることが
でき、かつチルト動作時のような軽負荷時には例えば１
本のシリンダのみに作動油が供給されるから、油圧ポン
プの吐出流量を増大することなく動作速度を大幅に速く
できる。According to the mounting angle adjustment device of the present invention, hydraulic oil is supplied to all cylinders during heavy loads such as during trim operations, so it is possible to withstand large propulsion reaction force from the propulsion machine, and also during tilt operations. For example, when the load is light like 1
Since hydraulic oil is supplied only to the main cylinders, the operating speed can be significantly increased without increasing the discharge flow rate of the hydraulic pump.
なお、この軽負荷時の動作に必要な力は小さくてすむか
ら、一部のシリンダのみに作動油を供給しても出力が不
足することはない。Note that the force required for this operation under light load is small, so there is no shortage of output even if hydraulic oil is supplied to only some of the cylinders.
以下、本発明の実施例を図について説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
第１図及び第２図は本発明の一実施例による船舶用推進
機の取付角度調整装置を示す。推進機の取付状態を示す
第２図において、■はモータボートの船尾であり、該船
尾ｌには船外推進機２が支持ビン３回りに揺動可能に軸
支されている。該船外推進機２はスタンドライブ型のも
ので、減速機構を収容したケーシング２ａの下端部に推
進用プロペラ２ｂを後方に向けて配設してなり、上記減
速機構には船体内に搭載されたエンジン２ｃの出力軸が
接続されている。1 and 2 show a mounting angle adjusting device for a marine propulsion device according to an embodiment of the present invention. In FIG. 2, which shows the installation state of the propulsion device, ▪ is the stern of the motor boat, and the outboard propulsion device 2 is pivotally supported at the stern 1 so as to be swingable around the support bin 3. The outboard propulsion device 2 is of a stand drive type, and has a propulsion propeller 2b disposed rearward at the lower end of a casing 2a that houses a speed reduction mechanism, and the speed reduction mechanism is mounted inside the hull. The output shaft of the engine 2c is connected thereto.
そして上記推進機２と船尾１との間には左、右一対の第
１．第２油圧シリンダ４．５が配設されており、該各シ
リンダ４．５のシリンダチューブ４ａ、５ａは上記船尾
１に、ピストンロッド４ｂ。Between the propulsion unit 2 and the stern 1 are a pair of left and right first gears. A second hydraulic cylinder 4.5 is arranged, the cylinder tube 4a, 5a of each cylinder 4.5 being connected to the stern 1 by a piston rod 4b.
５ｂは上記推進機２のケーシング２ａにそれぞれ揺動可
能に軸支されている。これにより、両シリンダ４．５の
ピストンロフト４ｂ、５ｂは上記ケーシング２ａを介し
て相互に接続されていることとなる。5b are pivotably supported by the casing 2a of the propulsion device 2, respectively. Thereby, the piston lofts 4b, 5b of both cylinders 4.5 are connected to each other via the casing 2a.
上記第１．第２油圧シリンダ４．５の油圧回路を示す第
１図において、６は吸込口を兼ねた第１゜第２吐出口６
ａ、６ｂを有し、駆動モータ６ｃで正逆回転駆動される
可逆型ギヤ式油圧ポンプであり、これは正回転時は第１
吐出ロ６ａから、逆回転時は第２吐出ロ６ｂからそれぞ
れ作動油を吐出するように構成されている。なお、９ａ
、９ｂは第１．第２吐出口６ａ、６ｂとリザーブタンク
１０とを連通ずる第１．第２吸引通路であり、該各通路
９ａ、９ｂにはリザーブタンクエ０から油圧ポンプ６へ
の流れのみを許容する逆止弁１１ａ。Above 1st. In FIG. 1 showing the hydraulic circuit of the second hydraulic cylinder 4.5, 6 is the first and second discharge ports 6 which also serve as suction ports.
a, 6b, and is a reversible gear type hydraulic pump driven by a drive motor 6c to rotate in forward and reverse directions.
The hydraulic oil is discharged from the discharge hole 6a, and from the second discharge hole 6b during reverse rotation. In addition, 9a
, 9b is the first. The first outlet communicates the second discharge ports 6a, 6b with the reserve tank 10. A check valve 11a which is a second suction passage and allows flow only from the reserve tank 0 to the hydraulic pump 6 is provided in each of the passages 9a and 9b.
１１ｂが介設されている。11b is provided.
また、上記油圧ポンプ６の第１吐出ロ６ａには第１油圧
通路７の一端が接続され、該油圧通路７の分岐通路７ａ
、７ｂはそれぞれ第１．第２油圧シリンダ４．５の第１
油圧室４ｃ、５ｃに接続されており、同様に第２吐出ロ
６ｂは第２油圧通路８の分岐通路８ａ、８ｂで第２油圧
室４ｄ、５ｄに接続されている。Further, one end of a first hydraulic passage 7 is connected to the first discharge hole 6a of the hydraulic pump 6, and a branch passage 7a of the hydraulic passage 7 is connected to the first discharge hole 6a of the hydraulic pump 6.
, 7b are the first . The first of the second hydraulic cylinder 4.5
Similarly, the second discharge hole 6b is connected to the second hydraulic chambers 4d, 5d through branch passages 8a, 8b of the second hydraulic passage 8.
そして上記第１．第２油圧通路７．８の途中にはシャト
ル弁１２が介設されている。該シャトル弁１２は、一対
のリリーフ弁１３ａ、１３ｂと、円筒状の油室１２ａ内
に、油圧が作用したとき低圧側のリリーフ弁を解放する
フリーピストン１２ｂを摺動自在に配置して構成されて
いる。And the first one above. A shuttle valve 12 is interposed in the middle of the second hydraulic passage 7.8. The shuttle valve 12 includes a pair of relief valves 13a and 13b, and a free piston 12b slidably arranged in a cylindrical oil chamber 12a to release the relief valve on the low pressure side when hydraulic pressure is applied. ing.
また、上記第１．第２油圧通路７．８の分岐通路７ｂ、
８ｂには、油圧ポンプ６からの作動油を第１．第２シリ
ンダ４，５の両方又は第１シリンダ４のみに供給するた
めの第１．第２切り換え弁１４．１５が介設されている
。該各項り換え弁１４．１５は、第２シリンダ５から油
圧ポンプ６方向への流れのみを許容する逆止弁１４ａ、
１５ａと、油圧ポンプ６から第２シリンダ５方向への圧
力が設定圧力以上になった時、該方向の流れのみを許容
するリリーフ弁１４ｂ、１５ｂとがら構成されている。In addition, the above 1. branch passage 7b of the second hydraulic passage 7.8;
8b, the hydraulic oil from the hydraulic pump 6 is supplied to the first. The first cylinder for feeding both the second cylinders 4, 5 or only the first cylinder 4. A second switching valve 14.15 is provided. Each of the switching valves 14 and 15 is a check valve 14a that only allows flow from the second cylinder 5 in the direction of the hydraulic pump 6;
15a, and relief valves 14b and 15b that allow flow only in that direction when the pressure from the hydraulic pump 6 in the direction of the second cylinder 5 exceeds a set pressure.
また、上記分岐通路７ｂ、８ｂのシリンダ５と切り換え
弁１４又は１５との間にはリザーブタンク１０に連通さ
れた補給通路７ｃ、８ｃが接続されており、該各通路に
はリザーブタンク１０がら第２シリンダ５への流れのみ
を許容する逆止弁１６ａ、１６ｂが介設されている。な
お、１７は排油弁、１８ａ〜１８ｄはリリーフ弁である
。Further, supply passages 7c and 8c, which communicate with the reserve tank 10, are connected between the cylinder 5 of the branch passages 7b and 8b and the switching valve 14 or 15, and each passage has a supply passage 7c and 8c connected to the reserve tank 10. Check valves 16a and 16b that allow flow only to the two cylinders 5 are interposed. Note that 17 is an oil drain valve, and 18a to 18d are relief valves.
次に本実施例の作用効果について説明する。Next, the effects of this embodiment will be explained.
まず、走行状態で推進機２の船体に対する傾斜角度を調
整するトリム動作において、推進機２を第２図の一点鎖
線の状態から推進反力に抗して実線の状態に移動させる
場合は、駆動モータ６ｃが正回転し、第１吐出ロ６ａか
らの油圧によりシャトル弁１２のフリーピストン１２ｂ
が図示右方に移動して第２リリーフ弁１３ｂを開くとと
もに、作動油が該シャトル弁１２．第１リリーフ弁１３
ａ、第１油圧通路７の分岐通路７ａを通って第１シリン
ダ４の第１油圧室４ｃに供給される。そしてこのとき該
油圧通路７内の油圧は上記推進反力に応じて高圧となり
、即ち重負荷状態となっており、これにより第１切り換
え弁１４のリリーフ弁１４ｂが開き、上記作動油は第２
シリンダ５の第１油圧室５ｃにも供給され、その結果上
記推進反力に必要な出力が得られ、該トリム動作がスム
ーズに行われることとなる。なお、このとき第２シリン
ダ５からの戻り油は分岐通路８ｂ、逆止弁１５ａ、
シャトル弁１２を介して油圧ポンプ６に押し込まれ、か
つピストンロッド４ｂ、５ｂの断面積に相当する戻り油
の不足分はリザーブタンク１０から第２吸引通路９ｂを
介して油圧ポンプ６に吸引される。First, in a trim operation to adjust the inclination angle of the propulsion device 2 with respect to the hull while the vehicle is running, when moving the propulsion device 2 from the state shown by the dashed line in Fig. 2 to the state shown by the solid line against the propulsion reaction force, the drive The motor 6c rotates forward, and the free piston 12b of the shuttle valve 12 is moved by the hydraulic pressure from the first discharge roller 6a.
moves to the right in the figure to open the second relief valve 13b, and the hydraulic oil flows into the shuttle valve 12. First relief valve 13
a, is supplied to the first hydraulic chamber 4c of the first cylinder 4 through the branch passage 7a of the first hydraulic passage 7. At this time, the hydraulic pressure in the hydraulic passage 7 becomes high pressure in response to the above-mentioned propulsion reaction force, that is, it is in a heavy load state, and as a result, the relief valve 14b of the first switching valve 14 opens, and the above-mentioned hydraulic oil flows into the second
It is also supplied to the first hydraulic chamber 5c of the cylinder 5, and as a result, the output necessary for the above-mentioned propulsive reaction force is obtained, and the trim operation is performed smoothly. In addition, at this time, the return oil from the second cylinder 5 flows through the branch passage 8b, the check valve 15a,
The shortfall in the returned oil, which is pushed into the hydraulic pump 6 via the shuttle valve 12 and corresponds to the cross-sectional area of the piston rods 4b and 5b, is sucked into the hydraulic pump 6 from the reserve tank 10 via the second suction passage 9b. .
次にエンジン停止状態等で推進機２を、第２図に実線で
示す水没位置から二点鎖線で示す水上の格納位置に移動
させるチルト動作においては、上記推進反力が作用しな
いことから、上記第１油圧通路７内の油圧は非常に低く
なり、即ち軽負荷状態となり、そのためリリーフ弁１４
ｂが閉じ、油圧ポンプ６からの作動油は全て分岐通路７
ａを通って第１シリンダ４のみに供給され、これにより
該シリンダ４の伸長速度が上記トリム動作の場合に比べ
て略２倍となり、推進機２の上方への移動速度が速（な
る、なお、このとき第２シリンダ５は推進機２を介して
第１シリンダ４によって引っばられることとなる。これ
により第１補給室５Ｃ内は負圧となり、その結果リザー
ブタンクｌＯ内の作動油が第１吸引通路７Ｃを介して吸
引されることとなる。Next, in a tilt operation in which the propulsion unit 2 is moved from the submerged position shown by the solid line in FIG. 2 to the retracted position above the water shown by the two-dot chain line when the engine is stopped, etc., the above-mentioned propulsive reaction force does not act. The oil pressure in the first hydraulic passage 7 becomes very low, i.e. in a light load condition, so that the relief valve 14
b is closed, and all the hydraulic oil from the hydraulic pump 6 flows into the branch passage 7.
a, and is supplied only to the first cylinder 4, and as a result, the extension speed of the cylinder 4 is approximately twice that of the above trim operation, and the upward movement speed of the propulsion device 2 is increased. , at this time, the second cylinder 5 is pulled by the first cylinder 4 via the propulsion device 2. As a result, the inside of the first supply chamber 5C becomes negative pressure, and as a result, the hydraulic oil in the reserve tank IO becomes 1 suction passage 7C.
また、推進機２を上記格納位置から水中に移動させる場
合は、駆動モータ６Ｃが逆回転し、上記場合と同様にし
て、作動油が第２油圧通路８１分枝通路８ａを介して第
１シリンダ４の第２油圧室４ｄに供給される。このとき
該第２油圧通路８内の油圧は低圧であり、即ち軽負荷状
態であるので、第２切り換え弁１５のリリーフ弁１５ｂ
は閉じており、これにより作動油は全て第１シリンダ４
のみに供給され、その結果推進機２は高速で下方に移動
することとなる。In addition, when moving the propulsion device 2 into the water from the storage position, the drive motor 6C rotates in the opposite direction, and in the same manner as in the above case, the hydraulic oil is transferred to the first cylinder through the second hydraulic passage 81 and the branch passage 8a. 4 is supplied to the second hydraulic chamber 4d. At this time, the hydraulic pressure in the second hydraulic passage 8 is low, that is, the load is light, so the relief valve 15b of the second switching valve 15
is closed, which allows all the hydraulic fluid to flow into the first cylinder 4.
As a result, the propulsion device 2 moves downward at high speed.
さらにまた、後進状態のように推進機２に上記と逆の後
方向への推進反力が作用する場合に、該推進機２の傾斜
角度を第２図に一点鎖線で示す前方位置に調整する時は
、第２油圧通路８内の油圧が上昇し、これによりリリー
フ弁１５ｂが開き、作動油が第１．第２シリンダ４．５
の両方に供給され、所定の出力が得られる。Furthermore, when a propulsion reaction force in the backward direction opposite to the above acts on the propulsion device 2, such as in a backward state, the inclination angle of the propulsion device 2 is adjusted to the forward position shown by the dashed line in FIG. When the hydraulic pressure in the second hydraulic passage 8 increases, the relief valve 15b opens and the hydraulic oil flows into the first hydraulic passage. 2nd cylinder 4.5
is supplied to both, and a predetermined output is obtained.
このように、本実施例では作動油を、重負荷時は第１．
第２シリンダ４．５の両方に供給するとともに、軽負荷
時は第１シリンダ４のみに供給するようにしたので、重
負荷時は必要な出力を確保でき、かつ軽負荷時は推進機
２の移動速度を略２倍にすることができ、しかも油圧ポ
ンプ６の容量は従来のものと同じでよく、コスト上昇、
配置スペースの拡大等の問題が生じることもない。In this way, in this embodiment, the hydraulic oil is changed to the first one when the load is heavy.
In addition to supplying power to both the second cylinders 4.5 and only the first cylinder 4 during light loads, the necessary output can be secured during heavy loads, and the propulsion unit 2 during light loads. The moving speed can be approximately doubled, and the capacity of the hydraulic pump 6 can be the same as the conventional one, which reduces costs and
Problems such as expansion of the arrangement space do not arise.
なお、上記実施例では、切り換え弁１４．１５を油圧通
路内の油圧で開閉するリリーフ弁１４ｂ。In the above embodiment, the relief valve 14b opens and closes the switching valves 14 and 15 using the hydraulic pressure in the hydraulic passage.
１５ｂで構成したが、本発明の切り換え弁はこのような
ものに限定されるものではなく、例えば第３図に示すよ
うに、外部信号で切り換えられる電磁弁１９．２０を採
用してもよい。15b, however, the switching valve of the present invention is not limited to this type of valve. For example, as shown in FIG. 3, electromagnetic valves 19 and 20 that can be switched by an external signal may be employed.
この場合、電磁弁１９．２０は、変速位置、エンジンの
運転状態あるいは手動スイッチによって切り換えるよう
にすればよく、例えば、変速位置がニュートラル時、エ
ンジンが停止あるいは低速回転時は軽負荷状態と判断で
きるから、この状態では作動油が１本のシリンダのみに
供給されるようにすればよい。In this case, the solenoid valves 19 and 20 may be switched depending on the gear shift position, the engine operating state, or a manual switch. For example, when the gear shift position is neutral, the engine is stopped, or is rotating at low speed, it can be determined that the load is light. Therefore, in this state, hydraulic oil may be supplied to only one cylinder.
また、上記実施例では、切り換え弁を第１．第２の両道
路に配設したが、この切り換え弁は一方だけに設けても
よい、さらにまた上記実施例では、シリンダが２本の場
合について説明したが、本発明はシ、リングが３本以上
の場合にも適用できる。Further, in the above embodiment, the switching valve is the first one. Although this switching valve is provided on both roads in the second example, it may be provided on only one side.Furthermore, in the above embodiment, the case where there are two cylinders has been explained, but the present invention has three cylinders. It can also be applied to the above cases.
以上のように本発明に係る船舶用推進機の取付角度調整
装置によれば、作動油を、複数のシリンダの全部又は一
部のみに切り換えて供給する切り換え弁を設けたので、
油圧ポンプの容量を大きくすることなく、必要な出力を
確保しつつ推進機の動作速度を大きく同上できる効果が
ある。As described above, according to the installation angle adjustment device for a marine propulsion device according to the present invention, since the switching valve is provided to switch and supply hydraulic oil to all or only some of the plurality of cylinders,
This has the effect of greatly increasing the operating speed of the propulsion device while ensuring the necessary output without increasing the capacity of the hydraulic pump.
第１図及び第２図は本発明の一実施例による船舶用推進
機の取付角度調整装置を説明するための図で、第１図は
その油圧回路図、第２図は推進機の取付状態を示す概略
構成図、第３図は上記実施例の変形例を示す油圧回路図
である。
図において、１は船尾、２は推進機、４．５はシリンダ
、４ａ、５ａはシリンダチューブ、４ｂ５ｂはピストン
ロッド、６は油圧ポンプ、７．８は油圧通路、１４，１
５．１９．２０は切り換え弁である。
特許出願人 株式会社昌和製作所
第１図1 and 2 are diagrams for explaining a mounting angle adjustment device for a marine propulsion device according to an embodiment of the present invention, FIG. 1 is a hydraulic circuit diagram thereof, and FIG. 2 is a state in which the propulsion device is installed. FIG. 3 is a hydraulic circuit diagram showing a modification of the above embodiment. In the figure, 1 is the stern, 2 is the propulsion device, 4.5 is the cylinder, 4a, 5a are the cylinder tubes, 4b5b is the piston rod, 6 is the hydraulic pump, 7.8 is the hydraulic passage, 14, 1
5.19.20 is a switching valve. Patent applicant Showa Seisakusho Co., Ltd. Figure 1
Claims (1)
の間に複数の油圧シリンダを配設し、該油圧シリンダに
よって上記推進機を水没位置と水上位置との間で傾動駆
動するとともに、水没位置での船体に対する傾斜角度を
調整する船舶用推進機の取付角度調整装置において、上
記各シリンダのシリンダチューブ又はピストンロッドの
いずれか一方を船体に揺動可能に連結し、他方を上記推
進機に揺動可能に連結し、上記各シリンダに油圧通路を
介して油圧ポンプを接続し、該油圧ポンプからの作動油
を、負荷の大、小に応じて上記全てのシリンダ、又は一
部のシリンダにそれぞれ切り換え供給する切り換え弁を
上記油圧通路に介設したことを特徴とする船舶用推進機
の取付角度調整装置。(1) A plurality of hydraulic cylinders are disposed between a propulsion unit that is swingably attached to the stern and the hull, and the hydraulic cylinders tilt and drive the propulsion unit between a submerged position and a surface position. , in a mounting angle adjustment device for a marine propulsion device that adjusts the inclination angle with respect to the hull at a submerged position, either one of the cylinder tube or the piston rod of each cylinder is swingably connected to the hull, and the other is connected to the marine propulsion device. A hydraulic pump is connected to each of the above cylinders via a hydraulic passage, and hydraulic oil from the hydraulic pump is applied to all or some of the above cylinders depending on whether the load is large or small. A mounting angle adjusting device for a marine propulsion device, characterized in that a switching valve for switching and supplying to each cylinder is interposed in the hydraulic passage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62128796A JPS63291791A (en) | 1987-05-25 | 1987-05-25 | Device for adjusting installation angle of ship propeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62128796A JPS63291791A (en) | 1987-05-25 | 1987-05-25 | Device for adjusting installation angle of ship propeller |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63291791A true JPS63291791A (en) | 1988-11-29 |
Family
ID=14993653
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62128796A Pending JPS63291791A (en) | 1987-05-25 | 1987-05-25 | Device for adjusting installation angle of ship propeller |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63291791A (en) |
-
1987
- 1987-05-25 JP JP62128796A patent/JPS63291791A/en active Pending
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