JPS60142077A - Rotor supporting device for single-shaft eccentric screw pump - Google Patents
Rotor supporting device for single-shaft eccentric screw pumpInfo
- Publication number
- JPS60142077A JPS60142077A JP24570983A JP24570983A JPS60142077A JP S60142077 A JPS60142077 A JP S60142077A JP 24570983 A JP24570983 A JP 24570983A JP 24570983 A JP24570983 A JP 24570983A JP S60142077 A JPS60142077 A JP S60142077A
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- eccentric
- drum
- stator
- crank
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/107—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth
- F04C2/1071—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type
- F04C2/1073—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with helical teeth the inner and outer member having a different number of threads and one of the two being made of elastic materials, e.g. Moineau type where one member is stationary while the other member rotates and orbits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0076—Fixing rotors on shafts, e.g. by clamping together hub and shaft
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
この発明は、ステーターに形成される雌ねじ孔を、その
断面形が長円形の内面とし−Ｕ Ｍねじローターに対す
る係合部に形成し、断面が円形の雄ねじロータ〜は偏心
ローター軸を中心にして係合回転する構造の一軸偏心ね
じポンプにお（プるローター支持装置に関゛する。Detailed Description of the Invention (Industrial Application Field) This invention provides a female threaded hole formed in a stator with an inner surface having an oval cross-section, and is formed at an engaging portion for a U M threaded rotor. The circular male screw rotor is related to a rotor support device for a uniaxial eccentric screw pump that engages and rotates around an eccentric rotor shaft.
（従来技術）
この種ポンプは」二記しノこ構造からなり、ｌｊＬねじ
ローターは偏心して［ｉｊ１転するため、ローターを駆
動軸に直結して回転させることかでさ′ず、従来はロー
ター４と駆動軸３２との間をユニバーザルジョインｉ〜
６０を介して接続していた。第１図は従来構造の一例を
示ず。このため、［１−ター４自体は何ら支持されてお
らず、また回転に際してもステーター２の１ｆｆｌねじ
孔３壁而との係合によってのみ運動が規制されてポンプ
作用を行なうので、［＋−クー４の回転が不安定で振れ
が人さくなり、ステーター２１１／）ｄｌＩＩねじ孔３
の内壁面を疲労させ、待に直線部分が摩耗しゃづく、ス
ープ−ター２を頻繁に交換しなけれぽならイ１がった。(Prior art) This type of pump has a two-groove structure, and the ljL screw rotor rotates eccentrically, so the rotor cannot be directly connected to the drive shaft to rotate. Universal join i~ between and the drive shaft 32
It was connected via 60. FIG. 1 does not show an example of a conventional structure. For this reason, the [1-tor 4 itself is not supported in any way, and even when rotating, its movement is restricted only by engagement with the wall of the 1ffl screw hole 3 of the stator 2, so that the [+- The rotation of the rotor 4 is unstable and the vibration is small, and the stator 211/) dlII screw hole 3
This would cause fatigue to the inner wall surface of the suction tank, and the straight parts would eventually wear out, making it difficult to replace the soup tar 2 frequently.
なａ３、第１１図のポンプはローター４の回１転を円ｉ
ｆ）にりるため、２つのユニパーザルジョイン１〜６０
を中間側１６１の両側に段（′Ｊ−ｃローター４ど駆動
軸３２を−ｊ宕続しているが、この構造にＪ３い（もロ
ータル１島体は支持されていないので、上記欠点を解消
できながった。A3, the pump in Fig. 11 has one revolution of the rotor 4 as a circle i.
f) Two uniparsal joins 1 to 60 to join
The drive shaft 32 is connected to the drive shaft 32 on both sides of the intermediate side 161 (J-c rotor 4), but in this structure J3 (also the rotor 1 island is not supported, so the above drawbacks can be avoided) I couldn't resolve it.
まｌζ、従来の構造では、一般に一１ニバーサルショイ
ン１へ６０がステーター２の動ねじ孔３人［１何近に配
首されるため、流路抵抗が増大してポンプの能力が低下
覆ると共に、コニバーザルジョイン（へ６０部位に長尺
の流入物が捲付（おそれがあった。In the conventional structure, generally the 11 universal joints 1 and 60 are placed close to the three movable screw holes of the stator 2, which increases flow resistance and reduces pump performance. At the same time, there was a risk that a long inflow material would wrap around the conniversal joint (60 parts).
（発明の１］的）
この発明は−上述の点に鑑みなされたものであって、ス
テーターの雌ねじ孔内て、〃［ねじローターを偏心［Ｊ
−ター輔を中心に回転させる際、偏心１」−ターｈｌ＋
がステーター軸線がＩろの偏心重を一定に保って回転（
公転）づるように顛４υじ孔を形成した一軸幅心ボンブ
にＪ３いて、ステーター輔わｊＩのグ［艮線十に回転軸
線をイＪし、回ｉ１すＪ自在に配設したクランクドラム
により、ｊｉＡドラムの回転軸線り目ら偏心ローター軸
の偏心ｈ）に簀しく偏心させたイ１′ｌ貿に前記偏心ロ
ーター軸を回動自在に支持させることにＪ、って、ロー
ターのＩＱ１転を円滑にして安定ざぜ、ステーターの一
■ねじ孔壁部の摩耗を減少さけ、長期に亙り１島いポン
プ１ｊヒノ〕を維持し、また従来のユ：バーザルシ１イ
ン（〜を介した駆動装置どローターの接続ｆ段に代えＣ
本発明のローター支持装置を用いることによって、吸込
］＝１がらポンプ装置Ｎに至る流路抵抗が小さくなりポ
ンプ１ｊピカを向トし得るローター支持装置を提供しよ
うどりるものＣある。(Objective of Invention 1) This invention has been made in view of the above-mentioned points, and the present invention has been made in view of the above-mentioned points.
- When rotating around the tarsuke, eccentricity 1" - tar hl+
The stator axis rotates while keeping the eccentric weight of the I filter constant (
The stator is mounted on a uniaxially wide center bomb with a 4mm hole formed so that it rotates (revolution), and the stator is rotated by a crank drum that is freely arranged to rotate. , jiA The eccentric rotor shaft is slightly eccentric (h) from the rotational axis of the drum, and the eccentric rotor shaft is rotatably supported by the eccentric rotor shaft. This ensures smooth and stable ripples, reduces wear on the wall of the screw hole in the stator, and maintains a single pump over a long period of time. C instead of rotor connection f stage
By using the rotor support device of the present invention, there is an attempt to provide a rotor support device in which the resistance of the flow path from the suction to the pump device N is reduced and the pump 1j can be directed.
（発明の構成）
上述の目的を達成づるこの発明は、スーツ−ターの雌ね
じ孔内を、偏心重ｅの偏Ｉひローター幀を中心にしＣＡ
ｌｌねしローターが係合回転し、かつ該細ねし孔はその
断面形を該ローターの円形［（万１ｎ１の半分に等しい
対向手内部分と両手内部分を接わＣづる前記偏心重Ｏの
／１倍長さの直線部分７ｐ ＋うなる長円形に形成した
一軸幅心ねじポンプにｄ５いて前記ローターの少なくと
も一方を支持Ｊる装置であって、前記ステ−ター軸線の
延長％Ｈ上に回転軸線を一致さＵ（クランクドラムを回
動白（１に配設し、該クランクドラムにより前記「Ｉ〜
ツタ−偏心ローター軸を１ｉｊｌ動自在に支持させると
共に、該支持中心位（６をクランクドラムから前記偏心
量Ｇ７．ニーＧ：Ｉ偏心させ、また前記偏心１ｉ１ｃの
２イ８の南中径をもつ外歯車を前記偏心ローター軸の後
端部に設り、該外歯車を、前記クランクドラムの後端に
隣接固定され、かつ前記偏心重ｅの４イ８の歯車径をも
つ外輪内歯車に、内接噛合さけたことを特徴とりる１−
１−ター支持装置を升旨どづるものである。(Structure of the Invention) This invention, which achieves the above-mentioned object, is configured to carry out CA in a female screw hole of a suit-tor with an eccentric weight e centered on an eccentric rotor wall.
The threaded rotor engages and rotates, and the threaded hole has a cross-sectional shape of the rotor's circular shape [(If the eccentric weight O A device for supporting at least one of the rotors on a uniaxial width central screw pump formed into a snarling oval shape, the linear portion 7p having a length of /1 times that of The rotation axes are aligned with each other, and the crank drum is placed in
The eccentric rotor shaft is supported so as to be freely movable, and the support center position (6 is eccentric from the crank drum by the eccentric amount G7. an external gear is provided at the rear end of the eccentric rotor shaft, the external gear is fixed adjacent to the rear end of the crank drum, and the eccentric weight e is an outer ring internal gear having a gear diameter of 4-8; 1-, which is characterized by avoiding internal interlocking
This is a 1-tar support device.
以下、この発明の実施例を図面に基いてｕ２明づ−る。Hereinafter, embodiments of this invention will be explained based on the drawings.
第２図〜第５図にｄ３いて、第２１章１（Ｊｌ、−り？
ｌＩ ｆ＝心ねしポンプの全体図を示し、ポンプ装置Δ
、吸込部Ｂ、吐出部Ｃ１ねじ１−］−ター支持技；αＤ
、並びに駆動装置Ｅからなる。d3 in Figures 2 to 5, Chapter 21 1 (Jl, -ri?
lI f=shows the overall view of the core screw pump, pump device Δ
, suction part B, discharge part C1 screw 1-]-tar support technique; αD
, and a drive device E.
ポンプ装置△の構造は従来のポンプど同様で、円筒状の
ステーク−ハウシング′ｌ内にステーター２が固着され
、このステーター２に形成した畑ねじ孔３に、１ｄｔね
じ［」−クー４を回転可能に係合さＵてＩｉ’ｈ）【１
１シてあり、またＡｌｌねじローター４の吸込部Ｂ １
１１１１の端面にはローター４の断面中心／から偏心ｇ
ａだ（）偏心さけ”’ＣＩｌｉ＋ｉ心ローター軸５を一
体に突設している。The structure of the pump device △ is the same as that of a conventional pump, with a stator 2 fixed in a cylindrical stake-housing 'l, and a 1dt screw [''-ku 4 rotated through a field screw hole 3 formed in the stator 2. Possibly engaged (Ii'h) [1
There is also a suction part B1 of the All screw rotor 4.
The end face of 1111 has an eccentricity g from the cross-sectional center/of the rotor 4.
The eccentric rotor shaft 5 is integrally provided.
また、ｊ、ｆｉねしローター４は断面形が円形をなす１
条ねじから形成し、一方スチーター２の１１１１ねじ孔
３は断面形が対向覆る手内部分と両手内部分を連接ゴる
直線部分からなる長円形をなす２条ねしから形成し、か
つ第３図に承り−Ｊ：うに手内部分の直径はローター４
の円形断面の直径ｄに等しく覆ると共に、直線部分の長
き゛りなわら対向する手内部分の中心点Ｘ−Ｙ間のに’
ｌｊ ｌ１ｌｔｌはａ−ター１のｌＯｉ面中心Ｚに対づ
る偏心１−Ｊ−ター軸５の偏心ｆｊ５ａの４イ８である
４ｅにしている。In addition, the j, fi-neshi rotor 4 has a circular cross-sectional shape.
On the other hand, the 1111 threaded hole 3 of the stealer 2 is formed from a two-thread thread having an oval cross-sectional shape consisting of a straight part connecting the inner part of the hand that covers the opposite hand and the inner part of both hands. According to the figure - J: The diameter of the inner part of the sea urchin is rotor 4
It covers the diameter d of the circular cross section equally, and the distance between the center point
lj l1ltl is set to 4e, which is the eccentricity 1 of the a-tar 1 with respect to the center Z of the lOi plane, which is 4i8 of the eccentricity fj5a of the a-tar axis 5.
なｄｊ、１１１１ねし孔３のピッチは［」−ター４より
も人きくすればよいが、ここでは２イ８に設定している
。ところで、劃ねじ孔３と雄ねしローター４と（ま断面
にａ３いＣ上記の関係に設定されているから、（！−心
ローター軸５を一方に１回転させるど、ローター４は雌
ねじ孔３壁面に係合しながら逆方向に１回転してロータ
ー４の断面中心Ｚは第３四のｘ−ｙ間を一直線状に往復
して元に戻るど」（に、偏心ローター１＋ｂ ５の断面
中心Ｓの運動軌跡は、第３図に示Ｊように［ねじ孔３の
Ｗｉ面中心○、いいかればステーター２軸線Ｐを中心と
した偏心ｍｅを半径とした円を描く。dj, 1111 The pitch of the through holes 3 should be made wider than the pitch of the holes 4, but here it is set to 2-8. By the way, since the male-threaded hole 3 and the male-threaded rotor 4 are set in the above-mentioned relationship (A3C on the cross-section), when the rotor shaft 5 is rotated one turn in one direction, the rotor 4 is connected to the female-threaded hole. The cross-sectional center Z of the rotor 4 reciprocates in a straight line between the 34th x and y and returns to the original position. The motion locus of the center S, as shown in FIG. 3, draws a circle whose radius is the center ○ of the Wi plane of the screw hole 3, or in other words, the eccentricity me centered on the axis P of the stator 2.
次にローター支持装ｊ行りの構造を説明づるど、ｉ’＋
１′ｌ記ステーター２の軸ＦｉｌＰの延長上に、回転軸
線Ｑを一致させてクランクドラム１１を、軸受ハウジン
グ１２下部内に設りた軸受１２′に回動自在に支持さｌ
、前記偏心ローター軸５と一体回転可１１ヒにキーレス
ジヨイント１４を介して接続し、偏心ローター軸５の一
部を４１４成りるクランク軸１３を、クランクドラム１
１の回転軸線Ｑから偏心ωｅを偏心させた位回に軸受１
５を介しＣ回動自在に支持させる。Next, I will explain the structure of the rotor support device for j, i'+
The crank drum 11 is rotatably supported on a bearing 12' provided in the lower part of the bearing housing 12, with the rotational axis Q coincident with the extension of the shaft FILP of the stator 2.
, the crankshaft 13, which is connected to the eccentric rotor shaft 5 and integrally rotatable 11 through a keyless joint 14 and constitutes a part of the eccentric rotor shaft 5, is attached to the crank drum 1.
Bearing 1 is placed at a position where eccentricity ωe is offset from the rotational axis Q of Bearing 1.
C is rotatably supported via C.
１Ｇはクランクドラム１１の前端部外周壁ど軸受ハウシ
ング１２の内周壁間に介装したダブルバッキング機４７
４．１７は偏心［」−ター６１１５の外周壁とクランク
ドラム１１の前端部内周壁間に介装したダブルバラ−１
：ング機４１４で、各パッＡ−ング機（１１５１Ｇ、１
６間ｄ５よび７？、’ｌ ７ ＩＩＩの空間部はり＝ク
シ二ｉンケーシング３５周壁を貫通づるドレーン孔１８
およびクランクドラム１１周壁を貫通Ｊるドレーン孔１
９ににり人気に連通させている。1G is a double backing machine 47 interposed between the front end outer peripheral wall of the crank drum 11 and the inner peripheral wall of the bearing housing 12.
4.17 is a double rose 1 interposed between the outer circumferential wall of the eccentric [''-tar 6115 and the inner circumferential wall of the front end portion of the crank drum 11]
: In the packing machine 414, each packing machine (1151G, 1
6 between d5 and 7? , 'l 7 III space beam = Drain hole 18 passing through the peripheral wall of the casing 35
and a drain hole 1 passing through the peripheral wall of the crank drum 11
It has become popular since 9th.
２０はクランクドラム１１の中間部外周にＩＩＭ看した
歯車Ｃある。A gear C 20 is located on the outer periphery of the intermediate portion of the crank drum 11 as viewed from IIM.
２１は前記ローター４の偏心回転運動を規制りるカルタ
ンリ゛−クル歯車（幾構で゛、詳ｊ小すると１］−ター
４を１ｕ（ねし孔ａ内で偏心ローター軸ｊうを中心に回
転させた際、雌ねし孔３壁而との係合作用によって、ロ
ーター４の断面中心Ｚの＋ｌ／＋跡か第３図の×−Ｙ間
を１１復−づる−１１〜線を描くように偏心回転運動り
るか、このような１」−ター４ど酊１ねし孔３檗面との
係合１′１川の有無にかかわらず、ローター４の断面中
心７が前記ど同様のｖｔ跡を描（Ｊ：うに、偏心ロータ
ー１１１Ｉ１５をステーター２の軸Ｈ’Ａ Ｐを中心に
偏心運動させるためのもので、この歯ｉ１？機構２１は
前記偏心重Ｃの４１８、づなわち４ｅの歯車径を右する
外輪内歯車２２と、前記偏心ｆｉｌｅの２４８．１〕な
りも２（！の歯車径を右づる外歯車２３からなり、外輪
内歯車２２１；１スアータ−２の軸線１〕延長−ｊ−に
軸線Ｒを一致させ−Ｕ’ １１１受ハウジング１２の後
☆罎にハウジングカバー２４を介して固定し、また外歯
車２３はクランク軸１３の後端部に形成して外輪内歯車
２２に内接噛合さμる。Reference numeral 21 denotes a Cartan leak gear (number of parts, details: 1) that regulates the eccentric rotational movement of the rotor 4. When rotated, due to the engagement action with the wall of the female threaded hole 3, a line 11-11 is drawn between the +l/+ mark of the cross-sectional center Z of the rotor 4 and the x-Y in Figure 3. Irrespective of whether there is an eccentric rotational movement like this, the cross-sectional center 7 of the rotor 4 is the same as above, regardless of whether there is an (J: uni, this is for eccentrically moving the eccentric rotor 111I15 around the axis H'A P of the stator 2, and this tooth i1? mechanism 21 is 418 of the eccentric weight C, i.e. The outer ring internal gear 22 has a gear diameter of 4e to the right, and the external gear 23 has a gear diameter of 248.1 of the eccentric file to the right, and an outer ring internal gear 221; ] The axis R is aligned with the extension -J- and is fixed to the rear of the housing 12 via the housing cover 24, and the external gear 23 is formed at the rear end of the crankshaft 13 and inserted into the outer ring. It is internally meshed with the gear 22.
次に駆動装置［の構造は、前記軸受ハウジング１２１７
Ｘ１ｉ内ｄ３よびハウジングカバー３４内に設【）た軸
受３１に＠動自７［に支承され、し−ター（図示１’Ｊ
’）が接続される駆動軸３２かうなり、駆動軸３２の中
間部外周には前記歯車２０に噛合ブる歯車３３が取着さ
れ、駆動軸３２の回転に連動して前記クランクドラム１
１が回転づるようになつ（いる。Next, the structure of the drive device is the bearing housing 1217.
The motor 7 is supported by a bearing 31 installed in d3 inside X1i and housing cover 34, and
A gear 33 that meshes with the gear 20 is attached to the outer periphery of the intermediate portion of the drive shaft 32, and rotates in conjunction with the rotation of the drive shaft 32 to
1 begins to rotate.
更に、吸込部Ｂはポンプ装：６Δどローター支持装置り
間にあって、上方に開口する吸込口４１ｄ５よびこの吸
込［１４１からステーター２の１１１１１ねし孔３人口
に至る流通路４２かうなる。Furthermore, the suction part B is located between the pump equipment 6Δ and the rotor support device, and includes a suction port 41d5 that opens upward and a flow path 42 from this suction [141 to the 11111 through hole 3 of the stator 2.
また、吐出部Ｃはポンプ駁ｊｉ、７△の後端に設けられ
、その先端に吐出口５１を有する。＜＞ Ｊ＞、吸込部
［３と吐出部Ｃはボンノ装置ΔのＥ」−ター４の回転方
向が逆向きになると、入れ昌わることになる。Further, the discharge portion C is provided at the rear end of the pump 7△, and has a discharge port 51 at its tip. <>J>, the suction part [3] and the discharge part C will be switched if the rotational direction of the E'-tar 4 of the bonnet device Δ is reversed.
次に、上記構成の実施例につき作動態様を説明する。Next, the operation mode of the embodiment of the above configuration will be explained.
第 図にｄｊいて駆動軸３２を回転させると、歯車２０
．３３を介しＣクランクドラム１１が回転し、ドラム１
１の回転に伴つでクランク軸１３ＪＪよび偏心ローター
軸５がステーター２の軸線又（よその延長わｉ）からｅ
だ（）偏心して回転し、これど同１１，７にローター４
が雌ねじ孔３壁而に係合しイｊ／バら回転運動し、畑ね
じ孔３の各…ｉ面においてローター４の断面中心が第４
図（ａ ）〜（ｄ ）に承りように、第３図のＸ−Ｙ間
を直線状に往復してポンプ作用を行ない、吸込口４１に
り流入された被ＩＷｊ、３！ｙｉ物が畑ねじ孔３内を通
って吐出Ｄ ５１ カ）ら圧送される。When the drive shaft 32 is rotated by dj as shown in the figure, the gear 20
．． 33, the C crank drum 11 rotates, and the drum 1
1, the crankshaft 13JJ and the eccentric rotor shaft 5 move away from the axis of the stator 2 (other extension i).
() It rotates eccentrically, and rotor 4 is located at 11 and 7.
engages with the wall of the female threaded hole 3 and rotates, and the cross-sectional center of the rotor 4 is aligned with the fourth
As shown in Figures (a) to (d), the pumping action is performed by reciprocating in a straight line between X and Y in Figure 3, and the IWj, 3! The material is pumped through the field screw hole 3 from the discharge D51.
ところぐ、クランク軸１３はクランクドラム１１の回転
に伴ってクランクドラム１１の回転軸線Ｑを中心にｅだ
【プ偏心して公転覆る際、第５図に示すようにカルダン
量ナークル歯車機構２１により公１１：ど逆方向に自転
させられるので、このクランク（１＋１３と一体回転す
る偏心ローター軸５はローター１の断面中心Ｚが第３図
にａ３＋）るＸ−Ｙ間を直線状に往復するようにロータ
ー４を回転運動させることになる。As the crankshaft 13 rotates, the crankshaft 13 rotates eccentrically around the rotational axis Q of the crank drum 11 as the crank drum 11 rotates, as shown in FIG. Public 11: Since it is rotated in the opposite direction, the eccentric rotor shaft 5, which rotates integrally with this crank (1+13), reciprocates in a straight line between X and Y, where the cross-sectional center Z of the rotor 1 is a3+ in Fig. 3. The rotor 4 will be rotated.
第６図は本発明の他の実施例を示し、前記した［１−タ
ー支持装置りをローター４の駆動側だけでなく、被駆動
側にも接続した両端支持構造からなり、吐出１コ５１が
ステーター２の軸線に直交する方向へ開口して設りられ
ている。この構造のポンプはねじれ数の多い多段高圧形
のローターや人容量用の口径か大きい１］−ターを使用
Ｊ８場合に特に有効である。FIG. 6 shows another embodiment of the present invention, which has a both-end support structure in which the above-mentioned 1-tor support device is connected not only to the drive side of the rotor 4 but also to the driven side. is provided with an opening in a direction perpendicular to the axis of the stator 2. A pump with this structure is particularly effective when using a multi-stage high-pressure type rotor with a large number of twists or a large diameter 1]-tor for human capacity.
また、第７図は従来のユニバーザルジョイン１−６０を
介して１１−ター１ど駆動装岡りを接続したポンプにお
いて、ローター４の被駆動側に１コーター支持装置αＤ
を接続した実施例を承りが、このポンプの場合も機能上
前記実施例と同様の効果が発揮される１、
（発明の効果）
然してこの発明は、ステーターの酊１ねじ孔内を、偏心
Ｌｌｅの偏心ローター軸を中心にし−Ｕ Ｊｊｔねじロ
ーターが係合回転し、かつ法灯ねじ孔はその断面形を該
ローターの円形断面の半分に等しい対向？１′１部分と
両生内部分を接続する前記錫心吊Ｃの４倍長さの直線部
分からなる長円形に形成した一軸偏心ねじポンプにａ３
いて、前記ステーター軸線の延長線上に回転軸線を一致
さμてクランクドラムを回動自在に配脱し、該クランク
ドラムにより前記ローターの偏心ローター軸を回動白イ
１に支持さＬると共に、該支持中心位置をクランクドラ
ムから前記偏心量ｅだ１ノ１１ｍ１心さ、せ、また前記
偏心ｍｅの２倍の歯車径をもつ外歯車を前記偏心ローク
ー軸の後端部に設り、法外１ｌｌｌｑＬＩＪを、前記ク
ランクドラムの後端に隣接固定され、かつ前記偏心ａｅ
の４倍の歯車径をもつ外輪内山巾に、内接噛合させたロ
ーター支持装置にＪｚり前記ローターの少なくとも−ｈ
を支持するようにしたから、下記のような効果を秦り゛
る。In addition, FIG. 7 shows a pump in which an 11-tor 1 drive device is connected via a conventional universal joint 1-60, and a 1-coater support device αD is attached to the driven side of the rotor 4.
However, in the case of this pump, the same effect as that of the above-mentioned embodiment is exhibited functionally. The -U Jjt threaded rotor engages and rotates around the eccentric rotor axis, and the light threaded holes are opposite to each other with a cross-sectional shape equal to half of the circular cross-section of the rotor. A3 is attached to a uniaxial eccentric screw pump formed into an oval shape consisting of a straight line part four times as long as the tin-centered suspension C connecting the 1'1 part and both internal parts.
Then, a crank drum is rotatably disposed and removed with its rotational axis aligned with the extension line of the stator axis, and the eccentric rotor shaft of the rotor is supported by the crank drum on the rotation white 1, and The support center position is set at the eccentricity e1 no 11m1 center from the crank drum, and an external gear with a gear diameter twice the eccentricity me is provided at the rear end of the eccentric low-coupling shaft. is fixed adjacent to the rear end of the crank drum, and the eccentric ae
At least -h of the rotor
Since it supports the following, the following effects are obtained.
＋１）Ｌ：］−ターの偏心回転運動かカルダンサークル
歯車機構によって、正規のハイボサイクロイ１く運動を
皐し、ステーターのｆｉｆｌ＋ねし孔内５！面にロータ
ーの負伺がかからないから、雌ねじ孔内壁面かｌ１ｆｉ
耗＋！ず、またステーターの月利の選定に際し、従来の
様な制限がなく広範囲の材料を使用でき、更に、ロータ
ーおよびステーターの雌ねじ孔の寸法精度を高くしても
焼付が生ぜず、かつ摩耗を促進しないので、ポンプ効率
が極めて向上する。+1) L: ] - The eccentric rotational movement of the stator or the cardan circle gear mechanism is used to create a regular high-cycle movement, and the stator's fifl+threaded hole is 5! Since the load of the rotor is not applied to the surface, the inner wall surface of the female screw hole is l1fi.
Wear +! In addition, when selecting the stator monthly rate, there are no restrictions like in the past, and a wide range of materials can be used.Furthermore, even if the dimensional accuracy of the female threaded holes in the rotor and stator is increased, seizure will not occur and wear will be accelerated. This greatly improves pump efficiency.
（２）ステーターの紺１ねじ孔内におけるロータ″−の
回転が円滑で安定するため、雌ねじ孔内壁面の疲労が小
さくなり摩耗が大幅に減少ＩＪるので、メインテナンス
が楽になると共に、民期に亙り畠いポンプ能力を維持す
る。(2) Rotation of the rotor in the navy blue 1 screw hole of the stator is smooth and stable, reducing fatigue on the inner wall surface of the female screw hole and significantly reducing wear, making maintenance easier and improving Maintain continuous pumping capacity.
（３）従来のユニバー４ツルジヨイントを介装（）た接
続手段に代えＣ本発明のローター支持具ｆｉ’ｉにより
ローターの駆動側を持づることによって、吸込Ｌ１から
１ｕ１ねじ孔の入１−１に至る流′Ｉｉｔ紙抗を減少し
、ポンプ能力が向上するとＪＪ、に、良１（のｉ１！Ｉ
ｆｌｌ送物による流通路の閉塞が防止Ｃ′さる。(3) Instead of the conventional connection means using a universal 4 truss joint, by holding the driving side of the rotor with the rotor support fi'i of the present invention, the 1u1 screw hole is inserted from the suction L1 into the 1-1 When the flow 'Iit paper resistance is reduced and the pumping capacity is improved, JJ,
This prevents clogging of the flow passage by the transported materials C'.
（４）ローターを両端で支持υることにより、多段高圧
形のねじれ数の多い［、ｊ−ターを円（１゛１にトリ転
できるので、駆動１ヘルクか小さくなり、省エネルギー
化がはかれる。(4) By supporting the rotor at both ends, the multi-stage high-pressure type has a large number of twists, and the rotor can be tri-rotated in a circle (1゛1), which reduces the driving force per herk and saves energy.
第１図は従来の一軸偏心ねじポンプを示り断面図、第２
図は本発明の実施例を示づ１１Ｊｉ面図、第３図１．１
本発明にａ月〕るス“アーータ−のｊｕｌねじ孔とロー
ターの関係を示１−断面図、第４図（ａ ）〜（ｄ ）
は劃ねじ孔内に＆３１ノるローターの運動を段階的に示
づ断面円、第５図【；１力ルダンサークル南ｔｉ機４１
４の拡大正面図、第６図は本発明の他の実施例を示づ１
既要図、第７図は本発明の更に他の実施例を承り概要図
である。
１・・・ステーターハウジング、２・・・ステーター、
３・・・雌４つし孔、４・・・ローター、５・・・偏心
［Ｊ−ター軸、１１・・・クランクドラム、１２・・・
軸受ハウジング、１３・・・クランク軸、１７１・・・
キーレスジヨイント、１５・・・軸受、ｊ６，１７・・
・ダブルパラ−１−ング機構、１８．１９・・・Ｕｉ通
孔、２０・・・歯巾、２１・・・カルダンサークル歯車
機構、２２・・・外輪内歯巾、２３・・・内歯車、２４
・・・ハウジングカバー、３１・・・軸受、３２・・・
駆動軸ζ３３・・・歯車、３４・・・ハウジングカバー
、３５・・・リークショシケーシング、 ４１・・・吸
込口、４２・・・流路、５１・・・１１出１」、６０・
・・ユニバー１ツルジヨイント、６１・・・中間軸、△
・・・ポンプ装置、Ｂ・・・吸込部、Ｃ・・・吐出部、
Ｄ・・・ローター支持［ｉα、Ｅ・・・駆動装置。Figure 1 shows a sectional view of a conventional uniaxial eccentric screw pump;
The figure shows an embodiment of the present invention.
Figures 4(a) to 4(d) are cross-sectional views showing the relationship between the rotor and the rotor's screw hole in the spacer according to the present invention.
Figure 5 shows the movement of the rotor in the screw hole step by step.
An enlarged front view of No. 4 and FIG. 6 show another embodiment of the present invention.
The existing drawings and FIG. 7 are schematic diagrams of still another embodiment of the present invention. 1... Stator housing, 2... Stator,
3...Four female holes, 4...Rotor, 5...Eccentric [J-tar shaft, 11...Crank drum, 12...
Bearing housing, 13... Crankshaft, 171...
Keyless joint, 15...Bearing, j6, 17...
・Double paralleling mechanism, 18. 19... Ui through hole, 20... Tooth width, 21... Cardan circle gear mechanism, 22... Outer ring inner tooth width, 23... Internal gear, 24
...Housing cover, 31...Bearing, 32...
Drive shaft ζ33...Gear, 34...Housing cover, 35...Leakage casing, 41...Suction port, 42...Flow path, 51...11 output 1'', 60.
・Univer 1 sill joint, 61 ・Intermediate shaft, △
... Pump device, B... Suction part, C... Discharge part,
D... Rotor support [iα, E... Drive device.
Claims (1)
を中心にして雄ねじローターが係合回転し、かつ該ｌね
じ孔はその断面形を該ローターの円形断面の半分に等し
い対向手内部分と両生内部分を接続する前記偏心ｍｅの
４１８長さの直線部分からなる長円形に形成した一軸偏
心ねじポンプにａ３いて前記ローターの少なくとも一方
を支持する装置であって、 前記スデーター軸線の延長線上に回転軸線を一致させて
クランクドラムを回動自在に配設し、該クランクドラム
ににり前記ロークーの偏心ローター軸を回動自在に支持
させると共に、該支持中心位置をクランクドラムから前
記偏心量ｅだけ偏心ざぜ、また前記偏心量ｅの２倍の歯
車径をもつ外歯車を前記偏心ローター軸の後端部に設け
、該外歯車を前記クランクドラムの後端に隣接固定され
、かつ前記１−６棗ｅの／１ｆ１°１の歯車径をもつ内
輪外歯車に、内接噛合さけたことを特徴とするローター
支持装置。[Scope of Claims] A male threaded rotor engages and rotates in a moving threaded hole of the stator around an eccentric rotor shaft having an eccentricity me, and the threaded hole has a cross section that is half of the circular cross section of the rotor. A device for supporting at least one of the rotors in a uniaxial eccentric screw pump formed into an oval shape consisting of a straight line portion of 418 length of the eccentricity me connecting equal and opposite internal parts and both internal parts, A crank drum is rotatably disposed with its rotational axis aligned with an extension of the data axis, and the eccentric rotor shaft of the rotor is rotatably supported on the crank drum, and the support center position is set to the crank drum. An external gear that is eccentric from the drum by the eccentric amount e and has a gear diameter twice the eccentric amount e is provided at the rear end of the eccentric rotor shaft, and the external gear is fixed adjacent to the rear end of the crank drum. A rotor support device characterized in that the rotor support device is internally meshed with an inner ring external gear having a gear diameter of /1f1°1.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24570983A JPS60142077A (en) | 1983-12-29 | 1983-12-29 | Rotor supporting device for single-shaft eccentric screw pump |
| KR1019840008444A KR850004305A (en) | 1983-12-28 | 1984-12-27 | Rotary Displacement Eccentric Archimedes Principle Screw Pump |
| US06/687,011 US4591322A (en) | 1983-12-28 | 1984-12-28 | Eccentric archimedian screw pump of rotary displacement type |
| FR848420039A FR2557642B1 (en) | 1983-12-28 | 1984-12-28 | ROTARY DELIVERY TYPE ECCENTRIC ARCHIVEDIC PUMP |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24570983A JPS60142077A (en) | 1983-12-29 | 1983-12-29 | Rotor supporting device for single-shaft eccentric screw pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60142077A true JPS60142077A (en) | 1985-07-27 |
Family
ID=17137637
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24570983A Pending JPS60142077A (en) | 1983-12-28 | 1983-12-29 | Rotor supporting device for single-shaft eccentric screw pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60142077A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5553742A (en) * | 1994-03-23 | 1996-09-10 | Matsushita Electric Industrial Co., Ltd. | Fluid feed apparatus and method |
| CN1076225C (en) * | 1994-06-27 | 2001-12-19 | 松下电器产业株式会社 | Fluid supplying apparatus |
| JP2008223492A (en) * | 2007-03-08 | 2008-09-25 | Heishin Engineering & Equipment Co Ltd | Rotor drive mechanism, sealing structure for eccentric shaft, and pump device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4947911A (en) * | 1972-09-13 | 1974-05-09 | ||
| JPS5634082B2 (en) * | 1977-03-19 | 1981-08-07 |
-
1983
- 1983-12-29 JP JP24570983A patent/JPS60142077A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4947911A (en) * | 1972-09-13 | 1974-05-09 | ||
| JPS5634082B2 (en) * | 1977-03-19 | 1981-08-07 |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5553742A (en) * | 1994-03-23 | 1996-09-10 | Matsushita Electric Industrial Co., Ltd. | Fluid feed apparatus and method |
| CN1076225C (en) * | 1994-06-27 | 2001-12-19 | 松下电器产业株式会社 | Fluid supplying apparatus |
| JP2008223492A (en) * | 2007-03-08 | 2008-09-25 | Heishin Engineering & Equipment Co Ltd | Rotor drive mechanism, sealing structure for eccentric shaft, and pump device |
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