JP2764292B2 - Single shaft eccentric screw pump - Google Patents
Single shaft eccentric screw pumpInfo
- Publication number
- JP2764292B2 JP2764292B2 JP63335575A JP33557588A JP2764292B2 JP 2764292 B2 JP2764292 B2 JP 2764292B2 JP 63335575 A JP63335575 A JP 63335575A JP 33557588 A JP33557588 A JP 33557588A JP 2764292 B2 JP2764292 B2 JP 2764292B2
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- male
- rotor shaft
- gear
- screw pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
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
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/18—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth
- F16D3/185—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth radial teeth connecting concentric inner and outer coupling parts
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rotary Pumps (AREA)
Description
【発明の詳細な説明】 〔産業上の利用分野〕 本発明は、流動性食品等の高粘性液の圧送に用いられ
る一軸偏心ねじポンプに関する。Description: TECHNICAL FIELD The present invention relates to a single-shaft eccentric screw pump used for pressure-feeding a highly viscous liquid such as a fluid food.
大規模なレストランや食品工場等において、カレーや
シュチュー等の流動性食品を圧送するには第５図に示し
た如き圧送ポンプＰが主に使用されている。In large-scale restaurants, food factories, and the like, a pump P as shown in FIG. 5 is mainly used to pump fluid foods such as curries and stews.
この食品圧送ポンプＰは、ポンプ室１内で駆動軸２と
給送ロータ軸３とが連結軸４を介して結合され、該駆動
軸２と連結軸４、連結軸４とロータ軸３間が駆動軸２及
びロータ軸３の各端部に取付られた雌ギヤ5,6及び連結
軸４の両端に設けられた雄ギヤ7,8によりユニバーサル
結合され、上記ロータ軸３の偏心回転するに伴い吸込口
11よりポンプ室１内に吸入された流動性食品が該ロータ
軸３を内装する給送筒12を経て圧送されるようにしたも
のである。ロータ軸３は駆動軸２に対して偏心した円形
断面を有する雌ねじ状に加工され、また給送筒12はロー
タ軸３の偏心摺接回転を許容するよう断面が長円形でピ
ッチがロータ軸３の２倍である雌ねじ状の内面を有して
いる。一方、駆動軸２と連結軸４、連結軸支４とロータ
軸支３はいずれもユニバーサル結合され、駆動軸２が軸
回転するとロータ軸３は給送筒12内を駆動軸２の軸心に
対して偏心摺接回転し、このロータ軸３の回転に伴う給
送筒12内の空間部の実質的前進移行により吸込口11から
吸入された流動性食品が給送筒12内を圧送される。上記
駆動軸２と連結軸４及び連結軸４とロータ軸３間の結合
部は、雌雄の関係でギヤ嵌合されている。駆動軸２とロ
ータ軸３の連結軸４の嵌合側には雌ギヤ5,6が、連結軸
４の両端には雄ギヤ7,8が設けられている。雌、雄ギヤ
間の歯すきまは、駆動軸２に対する連結軸４の偏心回
転、連結軸４に対するロータ軸３の偏心回転をそれぞれ
許容できるように設定されている。In this food pressure pump P, a drive shaft 2 and a feed rotor shaft 3 are connected via a connection shaft 4 in a pump chamber 1, and the drive shaft 2 and the connection shaft 4, and the connection shaft 4 and the rotor shaft 3 are connected. The female gears 5 and 6 attached to each end of the drive shaft 2 and the rotor shaft 3 and the male gears 7 and 8 provided at both ends of the connection shaft 4 are universally connected. As the rotor shaft 3 rotates eccentrically, Suction port
The fluid food sucked into the pump chamber 1 from 11 is pressure-fed through a feed cylinder 12 containing the rotor shaft 3 therein. The rotor shaft 3 is formed in a female screw shape having a circular cross section eccentric with respect to the drive shaft 2. The feeding cylinder 12 has an oval cross section and a pitch of the rotor shaft 3 so as to allow eccentric sliding contact rotation of the rotor shaft 3. Has a female screw-shaped inner surface that is twice as large as On the other hand, the drive shaft 2 and the connecting shaft 4 and the connecting shaft support 4 and the rotor shaft support 3 are all universally connected. When the drive shaft 2 rotates, the rotor shaft 3 moves inside the feeding cylinder 12 to the axis of the drive shaft 2. The fluid food sucked from the suction port 11 is pressure-fed in the feed cylinder 12 by the eccentric sliding contact rotation, and the rotation of the rotor shaft 3 causes the space in the feed cylinder 12 to move substantially forward. . The drive shaft 2 and the connecting shaft 4 and the connecting portion between the connecting shaft 4 and the rotor shaft 3 are gear-fitted in a male and female relationship. Female gears 5 and 6 are provided on the fitting side of the connection shaft 4 between the drive shaft 2 and the rotor shaft 3, and male gears 7 and 8 are provided at both ends of the connection shaft 4. The tooth clearance between the female and male gears is set to allow the eccentric rotation of the connecting shaft 4 with respect to the drive shaft 2 and the eccentric rotation of the rotor shaft 3 with respect to the connecting shaft 4.
ところが、偏心運動を許容するために通常よりも大き
な歯隙間を設ける必要があるため、噛み合い部の接触面
積や伝遠力を受けるギヤの受圧面積を大きくすることが
できず、耐久性に問題があった。また、歯隙間が大きい
とバックラッシュが大きいため起動時、停止時の応答遅
れを生じやすい。However, since it is necessary to provide a larger tooth gap than usual in order to allow eccentric movement, it is not possible to increase the contact area of the meshing portion and the pressure receiving area of the gear receiving the transmitting force, and there is a problem in durability. there were. Further, if the tooth gap is large, the backlash is large, so that a response delay at the time of starting and stopping is likely to occur.
さらに、ギヤの噛み合い部において初期の段階では点
当たりすることが多く、特に連結軸４の雄ギヤ7,8の端
部においてはそれが原因でチッピングが発生することが
多かった。Furthermore, in the early stage of the meshing portion of the gears, there are many hits, and especially at the ends of the male gears 7 and 8 of the connecting shaft 4, chipping often occurs due to this.
上記に鑑みて、本発明は連結軸４の雄ギヤ7,8に歯幅
中心から両サイドに向かって歯先円径及び歯底円径が減
少するようなテーパを設け、また、歯幅中心から両サイ
ドに向かって歯厚が漸減するようなクラウニングを設
け、さらに前記歯幅中心より両サイドに向けてつけた中
凸のテーパを２段、すなわちダブルアングルとすること
により、ギヤ噛み合い部の耐久性の向上、応答性の向
上、初期テッピングの低減を図るものである。In view of the above, according to the present invention, the male gears 7, 8 of the connecting shaft 4 are provided with a taper such that the diameter of the tooth tip circle and the diameter of the tooth bottom circle decrease from the center of the tooth width toward both sides, and By providing crowning such that the tooth thickness gradually decreases from both sides to the both sides, and furthermore, by making the middle convex taper applied to both sides from the center of the tooth width into two steps, that is, a double angle, the gear meshing part It is intended to improve durability, response, and reduce initial stepping.
以下、本発明の実施例について説明する。（従来例と
同一部分は同一符号を付した）第１図は本発明ポンプの
断面図、第２図（イ）はユニバーサルジョイント部の拡
大要部断面図、第３図は連結軸４の雄ギヤ部の拡大説明
図、第４図はダブルアングルの場合の連結軸４の雄ギヤ
の部分拡大図である。Hereinafter, examples of the present invention will be described. FIG. 1 is a sectional view of the pump of the present invention, FIG. 2 (a) is an enlarged sectional view of an essential part of a universal joint, and FIG. FIG. 4 is an enlarged explanatory view of a gear portion, and FIG. 4 is a partially enlarged view of a male gear of the connecting shaft 4 in a double angle case.
第１図において、モータにより動力伝達される駆動軸
２の先端には、雌ギヤ５を有するスリーブ2aがねじ止め
20またはピン止めあるいは嵌合されており、連結軸４の
一端に設けられた雄ギヤ７と噛み合っている。一方、ロ
ータ軸３の端部にも駆動軸２の先端と同様に雌ギヤを有
するスリーブ3aが取り付けられており、駆動軸４の他端
に設けられた雄ギヤ８と噛み合っており、駆動軸２から
の動力はギヤ結合によりロータ軸３に伝達される。In FIG. 1, a sleeve 2a having a female gear 5 is screwed to the tip of a drive shaft 2 to which power is transmitted by a motor.
20 or pinned or fitted, and meshes with a male gear 7 provided at one end of the connecting shaft 4. On the other hand, a sleeve 3a having a female gear is also attached to the end of the rotor shaft 3 similarly to the tip of the drive shaft 2, and is engaged with a male gear 8 provided at the other end of the drive shaft 4. 2 is transmitted to the rotor shaft 3 by gear coupling.
ロータ軸３は、駆動軸２に対して編心した円形断面を
有する雄ねじ状に加工されたものであり、該ロータ軸３
を内装する給送筒12の内壁は、該ロータ軸３の偏心摺接
回転を許容するよう長円形断面を有し、ピッチがロータ
軸３の２倍である雌ねじ状に賦型されている。The rotor shaft 3 is formed into a male screw shape having a circular cross section knitted with respect to the drive shaft 2.
The inner wall of the feed cylinder 12 having the inside is formed into an internal thread shape having an oblong cross section so as to allow the eccentric sliding rotation of the rotor shaft 3 and having a pitch twice that of the rotor shaft 3.
上述のごとく、駆動軸２の軸回転によりロータ軸３が
偏心回転すると、該ロータ軸３と給送筒12の軸回転によ
りロータ軸３が偏心回転すると、該ロータ軸３と給送筒
12の内壁との間で形成される空間部分が実質的に前方に
移行する。これにより吸込口11からの流動性食品がポン
プ室１内に吸入され、上記空間部の前方への移行に伴い
圧送され、給送筒12の前端から吐出される。As described above, when the rotor shaft 3 rotates eccentrically due to the rotation of the drive shaft 2, the rotor shaft 3 rotates eccentrically due to the rotation of the rotor shaft 3 and the feed cylinder 12.
The space formed between the inner wall and the inner wall moves substantially forward. As a result, the fluid food is sucked into the pump chamber 1 from the suction port 11, is pressure-fed as the space moves forward, and is discharged from the front end of the feeding tube 12.
第２図、第３図において、連結軸４の軸偏の駆動軸２
の軸心に対する傾斜角度をθ1、ロータ軸３の軸心の連
結軸４の軸心に対する傾斜角度をθ2とすると（通常θ1
＝θ2＝１〜３°である）、連結軸４両端の雄ギヤ7,8の
テーパ角度θ3、θ4（通常θ3＝θ4）は、θ1（θ2）≦
θ3（θ4）≦θ1（θ2）＋３°とすることが望ましい。
θ3（θ4）＜θ1（θ2）の場合、ギヤ噛み合い部の径方
向すきまにもよるが、連結軸４の駆動軸２に対する及び
ロータ軸３の連結軸４に対する所定の角度が得られなく
なる。2 and 3, the drive shaft 2 with the bias of the connecting shaft 4 offset
1 the inclination angle theta with respect to the axis of the inclination angle with respect to the axis of the connecting shaft 4 of axis of the rotor shaft 3 When theta 2 (usually theta 1
= Θ 2 = 1 to 3 °), and the taper angles θ 3 , θ 4 (normally θ 3 = θ 4 ) of the male gears 7,8 at both ends of the connecting shaft 4 are θ 1 (θ 2 ) ≦
It is preferable that θ 3 (θ 4 ) ≦ θ 1 (θ 2 ) + 3 °.
In the case of θ 3 (θ 4 ) <θ 1 (θ 2 ), depending on the radial clearance of the gear meshing portion, a predetermined angle between the connecting shaft 4 with respect to the driving shaft 2 and the rotor shaft 3 with respect to the connecting shaft 4 is obtained. Can not be.
また、θ3（θ4）＞θ1（θ2）＋３°の場合、ギヤ噛
み合い時の歯接触面積が小さいため、面圧が大きくなり
耐久性が低下する。When θ 3 (θ 4 )> θ 1 (θ 2 ) + 3 °, the contact area of the teeth during gear engagement is small, so that the surface pressure increases and the durability decreases.
連結軸４両端雄ギヤ7,8のクラウニング量δは、歯幅
をｌとすると とすることが望ましい。The crowning amount δ of the male gears 7, 8 at both ends of the connecting shaft 4 is given by It is desirable that
δがこの範囲より小さいと連結軸４の駆動軸２に対す
る及びロータ軸３の連結軸４に対する所定の角度が得ら
れなくなる。またδがこの範囲より大きいと、ギヤ噛み
合い時の接触面積が小さくなり、ギヤ部の耐久性が低下
する。If δ is smaller than this range, a predetermined angle of the connecting shaft 4 with respect to the driving shaft 2 and a predetermined angle of the rotor shaft 3 with respect to the connecting shaft 4 cannot be obtained. If δ is larger than this range, the contact area at the time of gear engagement is reduced, and the durability of the gear portion is reduced.
第４図において連結軸４両端の雄ギヤ7,8のダブルア
ングル２段目の長さl1及び角度θ5は次の範囲とするこ
とが望ましい。In FIG. 4, it is desirable that the length l 1 and the angle θ 5 of the second stage of the double angle of the male gears 7 and 8 at both ends of the connecting shaft 4 be in the following ranges.
０≦l1≦l/4、０≦θ5≦θ1（θ2）＋３° l1＞l/4、θ5＞３°の場合、ギヤ噛み合い時の接触面積
が小さく面圧が大きくなり、耐久性が低下する。0 ≦ l 1 ≦ l / 4, 0 ≦ θ 5 ≦ θ 1 (θ 2 ) + 3 ° When l 1 > l / 4, θ 5 > 3 °, the contact area at the time of gear meshing is small and the surface pressure increases. , Durability is reduced.
以上の如く、本発明の偏心ねじポンプにおけるユニバ
ーサルジョイント部と各軸間のギヤ結合は、連結軸両端
の雄ギヤに前記テーパ、クラウニング、及びダブルアン
グルを設けることにより、従来に比べギヤ部耐久性の向
上、起動、停止時の応答性の向上及び連結軸の雄ギヤ端
部の初期チッピング発生の低減を図ることができるもの
であり、その有用性は極めて大である。As described above, the gear coupling between the universal joint portion and each shaft in the eccentric screw pump of the present invention is achieved by providing the male gears at both ends of the connection shaft with the taper, crowning, and double angle, thereby making the gear portion more durable than the conventional one. It is possible to improve the responsiveness at the time of starting and stopping, and to reduce the occurrence of initial chipping at the male gear end of the connecting shaft, and its usefulness is extremely large.
第１図は本発明実施例による一軸偏心ねじポンプの縦断
面図、第２図（イ）はユニバーサルジョイント部の拡大
図、第２図（ロ）は同図（イ）におけるＸ−Ｘ線断面
図、第３図（イ）は連結軸の雄ギヤにおける歯のみの平
面図、第３図（ロ）は連結軸雄ギヤ部の縦断面図、第４
図はダブルアングルの場合における連結軸の雄ギヤの部
分拡大断面図、第５図は従来例による一軸偏心ねじポン
プの縦断面図である。 1:ポンプ室、2:駆動軸、3:ロータ軸 4:連結軸、5,6:雌ギヤ、7,8:雄ギヤ 12:給送筒、20,30:止めねじ1 is a longitudinal sectional view of a single-shaft eccentric screw pump according to an embodiment of the present invention, FIG. 2 (a) is an enlarged view of a universal joint portion, and FIG. 2 (b) is a sectional view taken along line XX in FIG. FIG. 3 (a) is a plan view of only the teeth of the male gear of the connecting shaft, FIG. 3 (b) is a longitudinal sectional view of the male shaft of the connecting shaft, and FIG.
The figure is a partially enlarged sectional view of a male gear of a connecting shaft in the case of a double angle, and FIG. 5 is a longitudinal sectional view of a conventional one-axis eccentric screw pump. 1: Pump chamber, 2: Drive shaft, 3: Rotor shaft 4: Connection shaft, 5, 6: Female gear, 7,8: Male gear 12: Feed cylinder, 20, 30: Set screw
Claims (1)
して駆動軸と結合され、これら駆動軸と連結軸及び連結
軸とロータ軸の間が雌、雄ギヤの噛み合わせによってユ
ニバーサル結合された一軸偏心ねじポンプにおいて、上
記雌、雄ギヤの径方向隙間及び歯隙間を小さくするとと
もに、上記連結軸両端を成す雄ギヤに、歯幅の中心部よ
り両サイドに向かって歯先円径、歯底円径の中央部が凸
状となるテーパと、歯厚の中央部が凸状となるダブルア
ングルの２段テーパを備えたクラウニングを形成したこ
とを特徴とする一軸偏心ねじポンプ。1. A rotor shaft rotating in a feed cylinder is connected to a drive shaft via a connection shaft, and the drive shaft and the connection shaft, and the space between the connection shaft and the rotor shaft are engaged by female and male gears to form a universal shaft. In the combined single-shaft eccentric screw pump, the radial gap and the tooth gap between the female and male gears are reduced, and the male gears forming both ends of the connecting shaft are provided with a tip circle toward the both sides from the center of the tooth width. A single-shaft eccentric screw pump characterized by forming a crowning having a taper having a convex central portion of a diameter and a root bottom diameter and a double angle taper having a double angle having a central central portion of a tooth thickness.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63335575A JP2764292B2 (en) | 1988-12-28 | 1988-12-28 | Single shaft eccentric screw pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63335575A JP2764292B2 (en) | 1988-12-28 | 1988-12-28 | Single shaft eccentric screw pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02181081A JPH02181081A (en) | 1990-07-13 |
| JP2764292B2 true JP2764292B2 (en) | 1998-06-11 |
Family
ID=18290115
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63335575A Expired - Lifetime JP2764292B2 (en) | 1988-12-28 | 1988-12-28 | Single shaft eccentric screw pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2764292B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5501580A (en) * | 1995-05-08 | 1996-03-26 | Baker Hughes Incorporated | Progressive cavity pump with flexible coupling |
| FR2876755B1 (en) | 2004-10-20 | 2007-01-26 | Pcm Pompes Sa | PUMPING DEVICE WITH PROGRESSIVE CAVITY PUMP |
| CN103452839B (en) * | 2013-09-12 | 2017-02-15 | 朱海川 | Inner screw rod type fluid conveying equipment |
| US10280683B1 (en) * | 2015-06-12 | 2019-05-07 | National Oilwell Dht, Lp | Mud motor apparatus and system |
| DE102021132561A1 (en) | 2021-12-09 | 2023-06-15 | Seepex Gmbh | Articulated joint, rotating unit and progressive cavity pump |
| DE102021132549A1 (en) | 2021-12-09 | 2023-06-15 | Seepex Gmbh | Articulated joint, rotating unit and progressive cavity pump |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS551422A (en) * | 1978-06-20 | 1980-01-08 | Kojiro Hamada | Monolithic screw pump |
| JPS5538529A (en) * | 1978-09-12 | 1980-03-18 | Ricoh Co Ltd | Light scanning device |
-
1988
- 1988-12-28 JP JP63335575A patent/JP2764292B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH02181081A (en) | 1990-07-13 |
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