JPH0328935Y2

JPH0328935Y2 -

Info

Publication number: JPH0328935Y2
Application number: JP5742084U
Authority: JP
Priority date: 1984-04-20
Filing date: 1984-04-20
Publication date: 1991-06-20
Also published as: JPS60171573U

Description

【考案の詳細な説明】この考案は、クランクケース蓋の側にクランク
軸と連動するピストン形式の吸入弁を往復動可能
に設定し、クランク軸を予め設定せる一定の回転
数のもとで回転させ、しかも吐出量の増大を図り
得ると共に、構造の複雑化を招来することのない
往復式多連動力噴霧機に係るものである。[Detailed explanation of the invention] This invention has a piston-type suction valve that is connected to the crankshaft on the side of the crankcase lid so that it can move back and forth, and the crankshaft rotates at a preset constant rotation speed. The present invention relates to a reciprocating multi-interlocking power sprayer that can increase the amount of discharge and increase the discharge amount without complicating the structure.

従来の往復式動力噴霧機にあつては、シリンダ
ー内を往復動するピストンの行程、直径、形態、
ピストン桿の長さ等種々の条件に基づいてシリン
ダーに対する吸入量、吐出量、脈動等の要素を考
慮してクランク軸の最適な一定の回転数を選定し
ているが、この一定の回転数下におけるクランク
軸の回転と連動するピストンの往復動に際しての
速度も略一定である故、吐出量も略一定にして増
減することもない。よつてかかるピストンの往復
動による吐出量の増大を図るには、ピストンの直
径を大きく、かつピストンの速度を増大させる必
要があり、従つてピストンを収容するシリンダー
の大型化と原動機の馬力の増大化を余儀なくされ
るか、もしくは同一寸法のシリンダー、ピストン
を併設して吐出口の側を同一の流路で連通する形
式を採用することになるが、かかる手段において
は必ずしも夫々のピストンが最適かつ同一の状況
下で作動するとは限らない故、その調整・同期化
を考慮しなければならない等、却て作動上におい
て煩雑ともなる惧れがある等の欠点を有してい
る。 For conventional reciprocating power sprayers, the stroke, diameter, shape, and
The optimum constant rotation speed of the crankshaft is selected based on various conditions such as the length of the piston rod, taking into account factors such as intake amount, discharge amount, and pulsation into the cylinder. Since the speed of the reciprocating movement of the piston in conjunction with the rotation of the crankshaft is also substantially constant, the discharge amount is also substantially constant and does not increase or decrease. In order to increase the discharge amount due to the reciprocating motion of the piston, it is necessary to increase the diameter of the piston and increase the speed of the piston, which requires increasing the size of the cylinder that houses the piston and increasing the horsepower of the prime mover. However, in such a method, each piston is not necessarily optimal or Since they do not necessarily operate under the same conditions, they have drawbacks such as the need to take into account adjustment and synchronization, which may even complicate the operation.

そこでこの考案は前述のような欠点を是正する
意図のもとに、クランクケース蓋側にクランク軸
により連動されるピストン形式の吸入弁を往復動
させることで従来における一本のクランク軸の予
め設定された最適の一定の回転数のもとで吐出さ
れる液体の吐出量の増大を可能とすると共に、妄
りに構造の複雑化を招来することのない往復式多
連動力噴霧機を提供しようとするものである。 Therefore, with the intention of correcting the above-mentioned drawbacks, this invention was developed by reciprocating a piston-type intake valve that is linked to the crankshaft on the crankcase lid side, thereby replacing the conventional presetting of a single crankshaft. An object of the present invention is to provide a reciprocating multi-coupled power sprayer that enables an increase in the amount of liquid discharged under a certain optimum rotational speed, and does not unnecessarily complicate the structure. It is something to do.

以下図面についてこの考案の一実施例を述べる
に、断面が前方（図面において左側を前方、右側
を後方とする）より後方に向け拡開せるクランク
ケースＣの内側中間に、図示しない原動機たとえ
ばエンジンもしくは電動機により駆動されるクラ
ンク軸Ｓを軸受（図示しない）で回転自在に支持
し、このクランク軸Ｓを二つ割り型の連結子１，
２によりボルト、ナツトのような止着具ｊで挾
持・締着し、連結子１の前端にピンａを介入して
クロスヘツド３を可動・連結する一方、連結子２
の後端中央にピンb₁で連結された中継桿ｍの後端
にピンb₂を介してクロスヘツド４に可動連結し、
これらクロスヘツド３，４に固定したピストン桿
５，６の夫々を前・後方に延長し、クランクケー
スＣの前端にはシリンダー元７を一体的に結合す
る一方、クランクケース蓋８の後方に一体に形成
された縮径部ｒの後端に、シリンダー元９を一体
的に結合し、これらのシリンダー元７，９の夫々
中間下方に吸入孔ｈ，ｉを穿設すると共に、これ
らシリンダー元７，９の前、後端にシリンダー１
０，１１を夫々一体的に結合し、これらシリンダ
ー１０，１１の前，後端に、吐出孔ｄ，ｅを夫々
穿設したシリンダー先１２，１３を一体的に結合
し、前記吐出孔ｄ，ｅに、第１図に示されるよう
に、送液管１４の端部を連結して連通可能とな
し、前方のシリンダー先１２の一側縁には吐出管
１５が取付けてある。前記ピストン桿５，６の
夫々前、後端近傍には夫々のピストン桿５，６の
基端側から先端に向け吸入弁座１６，１７および
通孔ｔ，ｕが夫々穿設された吸入弁ストツパー１
８，１９を所定間隔下に取付け、これら吸入弁座
１６，１７を吸入弁ストツパー１８，１９との間
に、外側縁にピストンパツキン２０，２１を定着
せる吸入弁Ｐ，Ｖが前記シリンダー１０，１１内
に摺接可能に密嵌されている。しかして前記吸入
弁座１６，１７吸入弁ストツパー１８，１９、ピ
ストンパツキン２０，２１および吸入弁Ｐ，Ｖの
夫々を含めて吸入弁部Y₁，Y₂と称する。ここに
おいて吸入弁座１６，１７と吸入弁ストツパー１
８，１９との夫々の間隔と、吸入弁Ｐ，Ｖの夫々
の厚みとの差はピストン桿５，６の夫々の行程よ
りも小さくしてある。 An embodiment of this invention will be described below with reference to the drawings. A motor (not shown), such as an engine or A crankshaft S driven by an electric motor is rotatably supported by a bearing (not shown), and this crankshaft S is connected to a two-piece connector 1,
2 is clamped and fastened with a fastener j such as a bolt or nut, and a pin a is inserted at the front end of the connector 1 to move and connect the crosshead 3.
The rear end of the relay rod m is connected to the center of the rear end by pin _b1 , and is movably connected to the crosshead ₄ via pin b2.
The piston rods 5 and 6 fixed to these crossheads 3 and 4 are extended forward and backward, respectively, and the cylinder base 7 is integrally connected to the front end of the crankcase C, while the cylinder base 7 is integrally connected to the rear of the crankcase lid 8. A cylinder base 9 is integrally connected to the rear end of the formed reduced diameter part r, and suction holes h and i are bored in the middle lower part of these cylinder bases 7 and 9, respectively. Cylinder 1 at the front and rear end of 9
0 and 11 are integrally connected, and cylinder tips 12 and 13 having discharge holes d and e, respectively, are integrally connected to the front and rear ends of these cylinders 10 and 11, and the discharge holes d, 1, the ends of the liquid feed pipe 14 are connected to enable communication, and a discharge pipe 15 is attached to one side edge of the front cylinder tip 12. Suction valves are provided near the front and rear ends of the piston rods 5 and 6, respectively, with suction valve seats 16 and 17 and through holes t and u formed from the base end side to the tip end of the piston rods 5 and 6, respectively. stopper 1
Suction valves P and V are mounted on the cylinders 10 and 19 with piston packings 20 and 21 fixed on their outer edges, respectively, between the suction valve seats 16 and 17 and the suction valve stoppers 18 and 19. 11 so as to be slidably and tightly fitted. The suction valve seats 16, 17, the suction valve stoppers 18, 19, the piston packings 20, 21, and the suction valves P, V, respectively, are collectively referred to as suction valve parts _Y1 , _Y2 . Here, the suction valve seats 16 and 17 and the suction valve stopper 1
The difference between the distance between the piston rods 8 and 19 and the thickness of the suction valves P and V is smaller than the stroke of the piston rods 5 and 6, respectively.

前記シリンダー１０，１１とシリンダー先１
２，１３との間に夫々狭持された吐出弁座ｋ，ｎ
に吐出弁サツク２９，３０の周縁を固定し、これ
ら吐出弁サツク２９，３０に内装される断面が略
Ｔ字形の吐出弁２２，２３を、コイルばね２４，
２５によりピストン桿５，６の側に付勢・着座さ
せてある。しかして前記吐出弁座Ｋ，ｎ、吐出弁
２２，２３、コイルばね２４，２５および吐出弁
サツク２９，３０の夫々を含めて吐出弁部X₁，
X₂と称し、シリンダー１０，１１から送出され
る流体の逆流を阻止可能としてある。 The cylinders 10 and 11 and the cylinder tip 1
Discharge valve seats k and n held between 2 and 13, respectively.
The circumferences of the discharge valve sockets 29, 30 are fixed to the coil springs 24,
25, it is biased and seated on the side of the piston rods 5 and 6. Therefore, the discharge valve portion X ₁ , including the discharge valve seats K, n, the discharge valves 22, 23, the coil springs 24, 25, and the discharge valve sucks 29, 30, respectively,
It is called X ₂ and is capable of preventing backflow of the fluid sent out from the cylinders 10 and 11.

なお本件考案にあつては、空気室、調圧弁、圧
力計等の機器を付設してあるが、この考案の趣旨
や目的および機能の点において特に深い関連性を
有していないので省略してある。図中２６は注油
口蓋である。 Although this invention is equipped with equipment such as an air chamber, a pressure regulating valve, and a pressure gauge, these have been omitted as they are not particularly closely related to the purpose, purpose, or function of this invention. be. In the figure, 26 is an oil filler cap.

この考案は前述のような構成であるから、いま
クランク軸Ｓの回転でピストン桿５，６の夫々が
第３図の位置から左方に移行する際、ピストン桿
５の吸入弁座１６が吸入弁Ｐに当接して一体的に
左方に移行し、吸入弁Ｐの左方のシリンダー１０
内における液体を押圧し、コイルばね２４の弾発
力に抗して吐出弁２２を吐出弁座Ｋから離脱さ
せ、液体をシリンダー先１２内に流出させ、つい
で吐出管１５に流出させる一方、ピストン桿６側
の吸入弁ストツパー１９が吸入弁Ｖに当接して一
体的に左方に移行するが、吐出弁２３がコイルば
ね２５により吐出弁座ｎに着座していることで、
吸入弁Ｖと吐出弁座ｎとの間が負圧となるため、
液体は吸入孔ｉから吸入弁Ｖとピストン桿６との
間の間隙および吸入弁ストツパー１９に穿設せる
通孔ｕを経て右方のシリンダー１１内に流入す
る。 Since this device has the above-mentioned configuration, when the piston rods 5 and 6 move to the left from the position shown in FIG. The cylinder 10 on the left side of the suction valve P contacts the valve P and moves integrally to the left.
Pressing the liquid inside the piston, the discharge valve 22 is separated from the discharge valve seat K against the elastic force of the coil spring 24, and the liquid flows out into the cylinder tip 12 and then into the discharge pipe 15. The suction valve stopper 19 on the side of the rod 6 comes into contact with the suction valve V and moves integrally to the left, but since the discharge valve 23 is seated on the discharge valve seat n by the coil spring 25,
Since there is negative pressure between the suction valve V and the discharge valve seat n,
The liquid flows from the suction hole i into the right cylinder 11 through the gap between the suction valve V and the piston rod 6 and through the through hole u formed in the suction valve stopper 19.

ついでクランク軸Ｓの回転でピストン桿５，６
の夫々が第３図の位置から右方に移行する際、吸
入弁Ｐに吸入弁ストツパー１８が当接して一体的
に右方に移行するが、吐出弁２２がコイルばね２
４の弾発力で吐出弁座Ｋに着座していることで、
吸入弁Ｐと吐出弁座Ｋとの間は負圧となるため、
液体は吸入孔ｈから吸入弁Ｐとピストン桿５との
間の間隙および吸入弁ストツパー１８に穿設され
た通孔ｔを経てシリンダー１０内に流入する。他
方ピストン桿６の右方への移行で吸入弁座１７が
吸入弁Ｖに当接して一体的になり右方に移行し、
吸入弁Ｖの右方でのシリンダー１１内における液
体を押圧し、コイルばね２５の弾発力に抗して吐
出弁２３を吐出弁座ｎから離脱させ、液体をシリ
ンダー先１３に送り込む。このシリンダー先１３
に送り込まれた液体は送液管１４を介してシリン
ダー先１２に移送された後、吐出管１５から所望
地点に流出される。この流出によりピストン桿
５，６の左方への移行により吐出管１５から流出
せる流量に加えて、ピストン桿５，６の右方への
移行に際し、送液管１４を介してシリンダー先１
３側の液体をシリンダー先１２側に供給するの
で、クランク軸Ｓの回転数が一定でもクランクケ
ース蓋を以てクランクケースの一側を閉塞した形
式の動力噴霧機における吐出量に対し、吐出量増
加が確実に期待できる。 Then, as the crankshaft S rotates, the piston rods 5 and 6
When each of them moves to the right from the position shown in FIG.
By being seated on the discharge valve seat K with an elastic force of 4,
Since there is negative pressure between the suction valve P and the discharge valve seat K,
The liquid flows into the cylinder 10 from the suction hole h through the gap between the suction valve P and the piston rod 5 and through the through hole t formed in the suction valve stopper 18. On the other hand, as the piston rod 6 moves to the right, the suction valve seat 17 comes into contact with the suction valve V and becomes integral with it, and moves to the right.
The liquid in the cylinder 11 on the right side of the suction valve V is pressed, the discharge valve 23 is disengaged from the discharge valve seat n against the elastic force of the coil spring 25, and the liquid is sent into the cylinder tip 13. This cylinder tip 13
The liquid sent into the cylinder is transferred to the cylinder tip 12 via the liquid feed pipe 14, and then flows out from the discharge pipe 15 to a desired point. Due to this outflow, in addition to the amount of flow that flows out from the discharge pipe 15 due to the movement of the piston rods 5 and 6 to the left, when the piston rods 5 and 6 move to the right, the flow rate is increased to the cylinder end through the liquid sending pipe 14.
Since the liquid from the third side is supplied to the cylinder tip 12 side, even if the rotation speed of the crankshaft S is constant, the discharge amount increases compared to the discharge amount in a power sprayer of the type where one side of the crankcase is closed with a crankcase lid. You can definitely expect it.

この考案によればクランク軸の前後において之
と連動する吸入弁の夫々を、クランクケースの前
方およびクランクケース蓋後方に連設したシリン
ダーに摺動自在に密嵌し、これらシリンダーの端
部の夫々を送液管を介して相互に連通させてある
ので、往復式動力噴霧機においてその構造上、ク
ランク軸の回転数を一定値のもとに選定を余儀な
くされる結果、吐出量の増大を所期し得なかつた
従来の形式に比し、この考案にあつてはクランク
ケース蓋の後方においてクランク軸と連動する吸
入弁をシリンダー内に摺動可能に密嵌すること
で、シリンダーの数に相当するだけの吐出量を確
実に増大可能であり、しかもクランク軸の回転数
を規定の一定値のもとで事足りる故、特にポンプ
機構に新規な構造を採用することなく、従来利用
されていたポンプ機構をクランクケース蓋の後方
にも付加すればよいので、全体としての構造の複
雑化を招来する惧れがないと共に、吐出量増大の
ための原動機の比例的に大型化や増設も必要がな
いため、施設費、運転費等の著しい高騰を回避で
き、なお、吸入液は必ずしも同一種類である必要
はなく、異種の液体をシリンダー先にして混合・
吐出することも可能である等、需要家にとつては
好都合である。 According to this invention, the suction valves that are connected to the front and rear of the crankshaft are slidably and tightly fitted into cylinders that are connected to the front of the crankcase and the rear of the crankcase lid, and are connected to each other via a liquid feed pipe, so due to the structure of a reciprocating power sprayer, the number of revolutions of the crankshaft must be selected based on a constant value, which makes it difficult to increase the discharge amount. Compared to the conventional type, which was unexpected, in this invention, the intake valve that is linked to the crankshaft is slidably fitted tightly into the cylinder at the rear of the crankcase lid. Since it is possible to reliably increase the discharge amount by a certain amount, and the number of revolutions of the crankshaft is kept at a specified constant value, there is no need to adopt a new structure for the pump mechanism, and the pump mechanism used in the past can be used. Since it is sufficient to add this to the rear of the crankcase lid, there is no risk of complicating the overall structure, and there is no need to proportionately enlarge or add an engine to increase the discharge amount. In addition, the suction liquid does not necessarily have to be of the same type, and different types of liquids can be mixed at the end of the cylinder.
This is convenient for consumers, as it is also possible to discharge the product.

以上の実施例にあつては、クランクケース蓋の
後方にシリンダーが一個連設されているが、之に
限らず、二個、三個等、所謂複数個を設定するこ
とで、吐出量の増大を図り得るものである。 In the above embodiment, one cylinder is installed in a row behind the crankcase lid, but the discharge amount can be increased by setting multiple cylinders such as two or three cylinders. It is possible to achieve this.

以上はピストン式往復ポンプ型式について例示
したが、プランジヤー式往復ポンプ型式について
も同様な取扱が可能である。 Although the piston-type reciprocating pump type has been illustrated above, the same treatment can also be applied to the plunger-type reciprocating pump type.

[Brief explanation of the drawing]

図面はこの考案に係る一実施例にして、第１図
は本案品の要部平面図、第２図は仝上正面図、第
３図は第１図の−０−０−線拡大断面図であ
る。５，６……ピストン桿、７，９……シリンダー
元、８……クランクケース蓋、１０，１１……シ
リンダー、１２，１３……シリンダー先、１４…
…送液管、Ｃ……クランクケース、Ｓ……クラン
ク軸、X₁，X₂……吐出弁部、Y₁，Y₂……吸入弁
部、ｈ，ｉ……吸入孔。 The drawings show one embodiment of this invention; FIG. 1 is a plan view of the main parts of the product, FIG. 2 is a front view of the product, and FIG. 3 is an enlarged sectional view taken along the line -0-0 in FIG. 1. It is. 5, 6... Piston rod, 7, 9... Cylinder base, 8... Crankcase lid, 10, 11... Cylinder, 12, 13... Cylinder tip, 14...
...liquid pipe, C...crankcase, S...crankshaft, _X1 , _X2 ...discharge valve section, _Y1 , _Y2 ...suction valve section, h, i...suction hole.

Claims

[Scope of claims for utility model registration] (1) A crankcase C that can support the crankshaft S;
A cylinder base 7 that is connected to the front of the crankcase C and has a suction hole h on the side edge, a cylinder 10 that is connected to the cylinder base 7, and a cylinder 10 that is connected to the front of the cylinder 10 and houses the discharge valve part _X1 . Connect the cylinder tips 12 in series,
A piston rod 5 movably connected to the crankshaft S is housed in the cylinder base 7 and the cylinder 10 so as to be reciprocally movable, and the piston rod 5 is movably connected to the crankshaft S.
In a reciprocating power sprayer in which a suction valve _Y1 mounted near the front end is slidably and tightly fitted into the cylinder 10, the suction valve Y1 is connected to the rear of the crankcase lid 8 that covers the rear of the crankcase C, A cylinder base 9 having a suction hole i on the side, a cylinder 11 connected to the rear of the cylinder base 9, and a cylinder tip ₁₃ housing a discharge valve A movably connected piston rod 6 is housed so as to be able to reciprocate within the cylinder base 9 and the cylinder 11, and a suction valve portion _Y2 mounted near the rear end of the piston rod 6 can be slidably contacted within the cylinder 11. While tightly fitting, the cylinder tip 1
A reciprocating multi-linked power sprayer in which 2 and 13 are communicated with each other through a liquid feed pipe 14. (2) The reciprocating multi-coupled power sprayer according to claim 1, in which one or more cylinders are set behind the crankcase lid 8.