JPS5853689A - Gear pump - Google Patents
Gear pumpInfo
- Publication number
- JPS5853689A JPS5853689A JP15178281A JP15178281A JPS5853689A JP S5853689 A JPS5853689 A JP S5853689A JP 15178281 A JP15178281 A JP 15178281A JP 15178281 A JP15178281 A JP 15178281A JP S5853689 A JPS5853689 A JP S5853689A
- Authority
- JP
- Japan
- Prior art keywords
- gears
- gear
- rotating shaft
- helical gear
- double helical
- 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
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/16—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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】
本発明は各種流体とくに高粘稠材料の送給に適した歯車
ポンプに関するものである０
従来、流体を定量、定圧に送る装置の一つとして、Ｚｌ
：いに噛合する一対のギヤと該両ギヤを囲撓するハウジ
ングとからなる歯車ポンプがあり、この歯車ポンプは、
一般には水や油等の低粘度の流体の送給に用いられてい
るが、最近、高分子材料の射出成形や押出成形において
、ミキサー等で溶融された高分子材料を押出してダイあ
るいは射出成形機等に送る手段としても、スクリュー押
出機より小型で構造が簡単なことから上記歯車ポンプが
利用されつつある。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a gear pump suitable for feeding various fluids, especially highly viscous materials.
There is a gear pump that consists of a pair of gears that mesh with each other and a housing that surrounds both gears.
It is generally used to feed low-viscosity fluids such as water and oil, but recently, in injection molding and extrusion molding of polymer materials, the melted polymer material is extruded with a mixer etc. and molded into a die or injection mold. The gear pump is also being used as a means for feeding the product to a machine, etc., because it is smaller and has a simpler structure than a screw extruder.
ところで、かかる歯車ポンプにおいては、所謂閉じ込み
と呼ばれる問題があり、これは第１図に示すように、一
対のギヤＧ１．Ｇ２が噛み合うとき２点Ｐ、Ｑで接して
その間の密閉空間Ａに材料が閉じ込められ、かつ、第１
図（ａ）に示す閉込み開始時点と同（ｂ）に示す閉込み
中央時点と同（Ｃ１に示す閉込み終了時点とにわたり上
記密閉空間Ａの体積が漸次変化することにより、該空間
Ａに閉じ込められた材料に大きな圧力変化が生じる現象
を言う。このような現象は歯車ポンプにとって障害とな
り、また高分子材料に使用する場合は品質にも悪影響を
及ぼす。By the way, in such a gear pump, there is a problem called so-called confinement, which occurs when the pair of gears G1. When G2 engages, they touch at two points P and Q, and the material is confined in the sealed space A between them, and the first
As the volume of the closed space A gradually changes from the start of confinement shown in Figure (a), the middle time of confinement shown in Figure (b), and the end of confinement (C1), the volume of the closed space A gradually changes. This refers to a phenomenon in which a large pressure change occurs in a confined material.Such a phenomenon is a problem for gear pumps, and also has a negative impact on quality when used with polymeric materials.
この閉込みの解決方法としては、従来、上記密閉空間Ａ
に連通ずるように逃げ溝をギヤＧｌ 、 Ｇ２に設ける
方法、あるいは一対のギヤにへりカルギヤを用いる方法
が知られている。しかしながら、逃げ溝を設ける方法で
は逃げ溝に材料が滞留し、とくに高粘度の高分子材料に
使用する場合は材料が逃げ溝をつまらせる虞れが生じ、
かつ、材料の滞留による品質劣化等も問題となる。また
、ギヤにシングルへりカルギヤを用いる方法では、駆動
に伴ってギヤにスラスト力が発生し、駆動部およびヘア
リング端部等にかかる負担が大きくなるなどの欠点があ
った。そこで、前述の閉込み現象を解消するとともに材
料の滞留およびスラスト力の発生を防止するには、歯車
ポンプの一対のギヤにダブルへりカルギヤを用いること
が望ましいが、この場合、ギヤ相互の歯当りが難しく、
製作誤差等により、例えば相対応するダブルへりカルギ
ヤの各片半部側だけが歯当りして他生部側が歯当りしな
いというような状態が生じ易く、これによって回転力伝
達作用やポンピング作用に障害を生する虞れがある。Conventionally, as a solution to this confinement, the above-mentioned closed space A
A method is known in which relief grooves are provided in the gears Gl and G2 so that they communicate with each other, or a method in which a helical gear is used as a pair of gears. However, with the method of providing relief grooves, material accumulates in the relief grooves, and there is a risk that the material may clog the relief grooves, especially when used with high-viscosity polymeric materials.
In addition, quality deterioration due to material retention also becomes a problem. Furthermore, the method of using a single helical gear for the gear has the disadvantage that thrust force is generated in the gear during driving, increasing the load on the drive portion, the end of the hair ring, and the like. Therefore, in order to eliminate the above-mentioned confinement phenomenon and to prevent the accumulation of material and the generation of thrust force, it is desirable to use double helical gears for the pair of gears in the gear pump. is difficult,
Due to manufacturing errors, for example, a situation can easily occur where only one half of a corresponding double helical gear makes contact with the teeth and the other half does not make contact with the teeth, which can impede the rotational force transmission action and pumping action. There is a risk of causing
本発明はこれらの事情に鑑み、一対のギヤをダブルヘリ
カル状とし、これによって閉込み現象を解消するととも
に材料の滞留およびスラスト力の発生を防止しながら、
ギヤ相互の歯当りを容易且つ確実にすることができ、と
くに高粘稠材料の送給用として好適な歯車ポンプを提供
するものである。In view of these circumstances, the present invention has a pair of gears in a double helical shape, thereby eliminating the confinement phenomenon and preventing the accumulation of material and the generation of thrust force.
The present invention provides a gear pump that allows gears to contact each other easily and reliably, and is particularly suitable for feeding highly viscous materials.
以下、本発明を図示せる実施例に依拠して説明する。The present invention will be described below with reference to illustrative embodiments.
第２図乃至第４図において、１および２は互いに噛合す
る一対のダブルへりカルギヤ、６および４はそれぞれ上
記各ダブルへりカルギヤ１，２の軸心を貫通する回転軸
、５は上記両ギヤ１，２を囲繞するハウジングである。2 to 4, 1 and 2 are a pair of double helical gears that mesh with each other, 6 and 4 are rotating shafts passing through the axes of the double helical gears 1 and 2, respectively, and 5 is a pair of double helical gears 1 and 2, respectively. , 2.
上記ハウジング５は、上方に材料取入口６、下方に材料
送出ロアをそれぞれ有し、上記各ギヤ１，２の軸方向両
端面に対して前後壁内面がシール状態を保つように密接
し、かつ、上記各ギヤ１，２の外周に対して両側部内弧
状壁の内面が歯先に摺接する形状としている。The housing 5 has a material intake port 6 at the top and a material delivery lower at the bottom, and the inner surfaces of the front and rear walls are in close contact with both axial end surfaces of the gears 1 and 2 to maintain a sealing state. , the inner surfaces of the inner arc-shaped walls on both sides of the outer periphery of each of the gears 1 and 2 are in sliding contact with the tips of the teeth.
また、上記両回転軸３，４は、それぞれベアリング８・
・・を介してハウジング５に回転自在に支持され、かつ
、一方の回転軸６は外部駆動装置（図示せす）に連動連
結されて駆動側回転軸となり、他方の回転軸４は被駆動
側回転軸となる。In addition, both the rotating shafts 3 and 4 have bearings 8 and 4, respectively.
... is rotatably supported by the housing 5 via..., and one rotating shaft 6 is interlocked and connected to an external drive device (not shown) to become a driving side rotating shaft, and the other rotating shaft 4 is a driven side rotating shaft. It becomes the axis of rotation.
前記ダブルへりカルギヤ１，２は、少なくとも一方が別
体の２個のシングルへリヵルギャを組合わせて形成され
る。当実施例では、被駆動側回転軸４上に装備された被
駆動側のギヤ２が予め別体に形成された２個のシングル
へりカルギヤ２１゜２２からなり、該両シングルへりカ
ルギヤ２１゜２２は、互いに捩れ角が同じで捩れ方向の
異なるヘリカルな歯を有（、直列状に被駆動側回転軸４
に装備されることにより、ダブルへりカルギヤ２を構成
している。さらに、この両シングルへりカルギヤ２１．
２２のうちの少な（とも−個は回転軸４に対して回転自
在とし、当実施例では片側（第２図における上部側）の
シングルへりカルギヤ２１が回転軸４に対してキー止め
等の固定手段を有することなく回転自在に嵌められ、他
の側（第２図における下部側）のシングルへりカルギヤ
２２は回転軸４に対してキー２６で固定されている。ま
た、駆動側回転軸６上に装備された駆動側のギヤ１は、
歯の捩れ方向が互いに異なる軸方向両半部１１，１２が
一体物に作られ、かつ、回転軸６に対してキー１３で固
定されている。上記の各キー２３．１３はスプラインに
替えてもよい。The double helical gears 1 and 2 are formed by combining two single helical gears, at least one of which is separate. In this embodiment, the gear 2 on the driven side installed on the rotating shaft 4 on the driven side consists of two single helical gears 21° 22 formed separately in advance, and both single helical gears 21° 22 have helical teeth with the same twist angle but different twist directions (, driven side rotating shaft 4 in series).
A double helical gear 2 is constructed by being equipped with the double helical gear 2. Furthermore, both single helical gears 21.
A small number of the 22 are rotatable with respect to the rotating shaft 4, and in this embodiment, the single helical gear 21 on one side (the upper side in FIG. 2) is fixed to the rotating shaft 4 with a key or the like. The single helical gear 22 on the other side (lower side in FIG. 2) is fixed to the rotating shaft 4 with a key 26. Gear 1 on the drive side equipped with
Both axial half portions 11 and 12 whose teeth are twisted in different directions are integrally formed and fixed to the rotating shaft 6 with a key 13. Each of the above keys 23.13 may be replaced by a spline.
上記の駆動側回転軸６と一体に回転する駆動側のギヤ１
およびこれに従動回転する被駆動側のギヤ２の回転方向
は、第６図および第４図に矢印で示すように、両ギヤ１
．２上に供給される材料を外向き周方向に案内する方向
とする。Drive-side gear 1 that rotates integrally with the drive-side rotating shaft 6 described above
The direction of rotation of the gear 2 on the driven side, which rotates as a result of this rotation, is as shown by the arrows in FIGS. 6 and 4.
．． The direction is to guide the material fed onto 2 in an outward circumferential direction.
なお、高粘稠材料に適用する場合、上記両ギヤ１．２上
に供給される高粘稠材料が即時には各ギヤ１，２の歯溝
に入り込みにくいことから、各ギヤ１，２の外周に対応
するハウジング５の両側円弧状壁の内面には、図示しな
いが、各ギヤ１，２の歯先に摺接する部分をポンプ送り
機能に必要な範囲で極力小さくした状態でその上流側に
、ギヤ１．２の回転につれて漸次材料を歯溝に入り込み
易くするための空間を形成するアンダーカフ）部を設け
ておくことが望ましい。When applied to highly viscous materials, it is difficult for the highly viscous material supplied onto both gears 1 and 2 to immediately enter the tooth grooves of each gear 1 and 2. Although not shown, on the inner surfaces of the arcuate walls on both sides of the housing 5 corresponding to It is desirable to provide an undercuff portion that forms a space to facilitate the gradual entry of material into the tooth grooves as the gear 1.2 rotates.
この歯車ポンプの作用の説明を次に説明する。The operation of this gear pump will now be explained.
前記両ギヤ１，２上に供給された流体材料は、両ギヤ１
，２の回転に伴い、各ギヤ１，２の歯溝に入り込みつつ
外側周方向に案内され、ハウジング５の内周面に沿って
移動し、ハウジング５の内周面と上記各ギヤ１．２の歯
先とが摺接する部分を通過した後、歯溝に保持された材
料だけが材料送出口Ｚ側へ送られる。そして、上記のハ
ウジング５の内周面とギヤ１，２の歯先との摺接部分で
その上流側と下流側との連通が遮断される一方、ハウシ
ング５内中央部における両ギヤ１，２の噛合部分で歯溝
から材料が押出されることにより、定量、定圧的に材料
が前記送出ロアから送り出される。The fluid material supplied onto both gears 1 and 2 is
, 2, it is guided in the outer circumferential direction while entering the tooth grooves of each gear 1, 2, and moves along the inner circumferential surface of the housing 5, causing the inner circumferential surface of the housing 5 and each of the gears 1, 2 After passing through the part where the tooth tips make sliding contact, only the material held in the tooth grooves is sent to the material delivery port Z side. Communication between the upstream side and the downstream side is cut off at the sliding contact portion between the inner circumferential surface of the housing 5 and the tooth tips of the gears 1 and 2, while the communication between the gears 1 and 2 at the central part of the housing 5 is interrupted. By extruding the material from the tooth groove at the meshing portion of the material, the material is delivered from the delivery lower in a fixed amount and at a constant pressure.
この動作において、上記両ギヤ１，２をへりカルギヤと
することにより、両ギヤ１，２の噛合部分で密閉空間を
生ずることなく前述の閉じ込み現象が解消され、かつ、
歯の捩れ方向に沿って材料が押出されるので材料の滞留
を生ずることがない。In this operation, by making both the gears 1 and 2 helical gears, the above-mentioned confinement phenomenon is eliminated without creating a sealed space at the meshing portion of the two gears 1 and 2, and
Since the material is extruded along the twisting direction of the teeth, no material stagnation occurs.
また、ダブルへりカルギヤ１，２を用いることにより、
噛合回転に伴い軸方向両半部に生ずるスラスト力は互い
に相殺され、全体としてはスラスト力を発生することが
ない。Also, by using double helical gears 1 and 2,
The thrust forces generated in both halves in the axial direction due to meshing rotation cancel each other out, and no thrust force is generated as a whole.
さらに、前記被駆動側のダブルへりカルギヤ２が別体の
２個のシングルへりカルギヤ２１．２２で構成されて、
その１個が回転軸４に対して回転自在としていることに
より、駆動側のダブルへりカルギヤ２に対する歯当りが
容易になる。すなわち、運転開始時点において、被駆動
側回転軸４に対する固定側のシングルへりカルギヤ２２
がこれに対応する駆動側のダブルへりカルギヤ１の片半
部１２に歯当りした状態で、被駆動側回転軸４に対する
可動側のシングルへりカルギヤ２１が当初適正な歯当り
位置になくとも、当該シングルへりカルギヤ２１が回転
軸４および固定側シングルへりカルギヤ２２に対して相
対的に微少回転することにより、駆動側のダブルへりカ
ルギヤ１の回転に伴って自然にこのギヤ１に歯当りする
状態に是正される。そして、このような歯当りのための
上記シングルへりカルギヤ２１の相対的微少回転は運転
開始時点で生ずるだけで、運転中は、適正な歯当り状態
が確保されたまま、被駆動側の両シングルへりカルギヤ
２１．２２が一体的に、駆動側のダブルへりカルギヤ１
の回転に伴って従動回転し、回転力伝達作用およびポン
ピング作用が良好に保たれる。Furthermore, the double helical gear 2 on the driven side is composed of two separate single helical gears 21 and 22,
Since one of them is rotatable with respect to the rotating shaft 4, the teeth can easily contact the double helical gear 2 on the driving side. That is, at the start of operation, the fixed side single helical gear 22 with respect to the driven side rotating shaft 4
is in tooth contact with one half 12 of the corresponding driving side double helical gear 1, even if the movable side single helical gear 21 is not initially in the appropriate tooth contact position with respect to the driven side rotating shaft 4, the corresponding By slightly rotating the single helical gear 21 relative to the rotating shaft 4 and the fixed single helical gear 22, the teeth of the single helical gear 21 naturally come into contact with the gear 1 as the drive side double helical gear 1 rotates. Corrected. The relative slight rotation of the single helical gear 21 for such tooth contact occurs only at the start of operation, and during operation, both single helical gears on the driven side The helical gears 21 and 22 are integrally connected to the double helical gear 1 on the drive side.
It rotates as a result of the rotation of , and good rotational force transmission and pumping effects are maintained.
なお、被駆動側のダブルへりカルギヤ２を構成する両シ
ングルへりカルギヤ２１．２２は、互いに相対的に回転
自在で且つ回転軸４に対してともに回転自在としてもよ
く、この場合も、被駆動側回転軸４のまわりのベアリン
グ８・・・の抵抗が充分小さい時には、運転中、両シン
グルへりカルギヤ２１．２２および回転軸４が一体的に
、駆動側のダブルへりカルギヤ２に対して従動回転する
状態が保たれる。また、駆動側のダブルへりカルギヤ１
も、必ずしも予め一体に形成するに限られず、製作りの
便宜のため、このギヤ１の軸方向両半部１１、＋２を予
め別体のシングルへりカルギヤにて形成し、この両シン
グルへりカルギヤをそれぞれ駆動側回転軸５にキー止め
等により固定するようにしてもよい。Note that both single helical gears 21 and 22 constituting the double helical gear 2 on the driven side may be rotatable relative to each other and rotatable together with respect to the rotating shaft 4; When the resistance of the bearings 8 around the rotating shaft 4 is sufficiently small, during operation, both single helical gears 21, 22 and the rotating shaft 4 rotate as a unit with respect to the double helical gear 2 on the drive side. The condition is maintained. In addition, the double helical gear 1 on the drive side
However, for convenience of manufacturing, both axial half portions 11 and +2 of the gear 1 are formed in advance as separate single helical gears, and these two single helical gears are not necessarily formed integrally in advance. Each of them may be fixed to the drive-side rotating shaft 5 with a key or the like.
以上説明したように、本発明は、歯車ポンプにおける一
対の互いに噛合する歯車をダブルへりカルギヤとすると
ともに、その少なくとも一方を別体の２個のシングルへ
りカルギヤにて構成し、その少なくとも１個のシングル
へりカルギヤを回転軸に対して回転可能としているため
、前述の閉込み現象を解消し、かつ、材料の滞留および
スラスト力の発生を防止し、しかも、容易に相対応する
ギヤ同志の歯当りを完全なものとすることができ、もっ
て、溶融高分子材料等の送給に好適に使用し得るもので
ある。As explained above, the present invention uses a pair of mutually meshing gears in a gear pump as a double helical gear, at least one of which is composed of two separate single helical gears, and at least one of the gears is configured with two separate single helical gears. Since the single helical gear is rotatable about the rotating shaft, it eliminates the above-mentioned confinement phenomenon, prevents material retention and the generation of thrust force, and also makes it easy to reduce the contact between gears that correspond to each other. Therefore, it can be suitably used for feeding molten polymeric materials, etc.
第１図師）乃至同（Ｃ）は従来の歯車ポンプの基本的な
構造による場合の閉込み現象を示す説明図、第２図は本
発明歯車ポンプの実施例を示す概略横断面図、第６図は
第２図のＩｌｌ −Ｉｌｌ線に沿った断面図、第４図は
第２図のＩＶ−ＩＶ線に沿った断面図である。
１．２・・・ダブルへりカルギヤ、６，４・・・回転軸
、５・・・ハウジング、２１．２２・・・一方のタプル
ヘリカルギヤを構成する２個のシングルへりカルギヤ。
特許出願人 株式会社神戸製鋼所
代理人 弁理士 小 谷 悦 司Figures 1) to (C) are explanatory diagrams showing the confinement phenomenon caused by the basic structure of a conventional gear pump, Figure 2 is a schematic cross-sectional view showing an embodiment of the gear pump of the present invention, and Figure 6 The figure is a cross-sectional view taken along the line Ill--Ill in FIG. 2, and FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. 2. 1.2... Double helical gear, 6, 4... Rotating shaft, 5... Housing, 21.22... Two single helical gears forming one tuple helical gear. Patent applicant Kobe Steel, Ltd. Representative Patent attorney Etsuji Kotani
Claims (1)
各ダブルへりカルギヤの軸心に設けた回転軸と、両ダブ
ルへりカルギヤを囲撓するノーウシングとを具備し、上
記一対のダブルへリカルギャのうち少なくとも一方を、
別体の２個のシング／Ｌヘリカルギヤを組合わせて形成
し、かつ、少なくとも一方の回転軸上に配置された２個
のシングルへりカルギヤのうちの１個は、該回転軸に対
してキー止め等の固定手段を介することなく回転自在に
装着したことを特徴とする歯車ポンプ。1 comprising a pair of double helical gears that mesh with each other, a rotating shaft provided at the axis of each of the double helical gears, and a nousing that surrounds both the double helical gears; at least one,
One of the two single helical gears formed by combining two separate single/L helical gears and arranged on at least one of the rotating shafts is keyed to the rotating shaft. A gear pump characterized in that it is rotatably mounted without using fixing means such as.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15178281A JPS5853689A (en) | 1981-09-24 | 1981-09-24 | Gear pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15178281A JPS5853689A (en) | 1981-09-24 | 1981-09-24 | Gear pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5853689A true JPS5853689A (en) | 1983-03-30 |
Family
ID=15526176
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15178281A Pending JPS5853689A (en) | 1981-09-24 | 1981-09-24 | Gear pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5853689A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01219103A (en) * | 1988-02-26 | 1989-09-01 | Titan Kogyo Kk | Magnetic metal powder for magnetic recording |
| US5143542A (en) * | 1989-12-22 | 1992-09-01 | Ishihara Sangyo Kaisha, Ltd. | Process for producing magnetic metal powder for magnetic recording |
| US9464632B2 (en) * | 2011-07-19 | 2016-10-11 | Settima Meccanica S.R.L. | Double-helical gear rotary positive displacement pump |
| CN107100835A (en) * | 2017-06-28 | 2017-08-29 | 珠海市洪富食品机械制造有限公司 | A kind of herringbone wildhaber-novikov gear constant displacement pump |
-
1981
- 1981-09-24 JP JP15178281A patent/JPS5853689A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01219103A (en) * | 1988-02-26 | 1989-09-01 | Titan Kogyo Kk | Magnetic metal powder for magnetic recording |
| US5143542A (en) * | 1989-12-22 | 1992-09-01 | Ishihara Sangyo Kaisha, Ltd. | Process for producing magnetic metal powder for magnetic recording |
| US9464632B2 (en) * | 2011-07-19 | 2016-10-11 | Settima Meccanica S.R.L. | Double-helical gear rotary positive displacement pump |
| CN107100835A (en) * | 2017-06-28 | 2017-08-29 | 珠海市洪富食品机械制造有限公司 | A kind of herringbone wildhaber-novikov gear constant displacement pump |
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