JPH0649437Y2 - Ball joint forced lubrication device of press machine - Google Patents
Ball joint forced lubrication device of press machineInfo
- Publication number
- JPH0649437Y2 JPH0649437Y2 JP10468589U JP10468589U JPH0649437Y2 JP H0649437 Y2 JPH0649437 Y2 JP H0649437Y2 JP 10468589 U JP10468589 U JP 10468589U JP 10468589 U JP10468589 U JP 10468589U JP H0649437 Y2 JPH0649437 Y2 JP H0649437Y2
- Authority
- JP
- Japan
- Prior art keywords
- ball portion
- circuit
- retainer
- ball
- receiving member
- 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
- 238000005461 lubrication Methods 0.000 title 1
- 239000010687 lubricating oil Substances 0.000 description 11
- 239000003921 oil Substances 0.000 description 10
- 230000000694 effects Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
Landscapes
- Presses And Accessory Devices Thereof (AREA)
Description
【考案の詳細な説明】 〔産業上の利用分野〕 本考案は、コンロッドとスライドの連結部がボールジョ
イントになっているプレス機械において、ボールジョイ
ントに潤滑油を強制給油するための装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial application] The present invention relates to a device for forcibly supplying lubricating oil to a ball joint in a press machine in which a connecting portion between a connecting rod and a slide is a ball joint.
第３図はプレス機械の全体図を示し、上端がクランク軸
１に連結されたコンロッド２の下端にスライド３が連結
され、クランク軸１の回転によりコンロッド２を介して
スライド３が上下動することにより、スライド３に取り
付けられた上型４とボルスタ５に取り付けられた下型６
とで材料がプレス加工される。第４図はコンロッド２と
スライド３との連結構造を示す。コンロッド２の下端に
はボール部７が設けられ、このボール部７の下部面はス
ライド３に取り付けられた受圧部材８で受けられ、ボー
ル部７の上部面にはスライド３に取り付けられたリテー
ナ９が当てられ、これによりコンロッド２とスライド３
は、ボール部７、受圧部材８、リテーナ９による球面滑
動自在なボールジョイント10で連結される。リテーナ９
の中央部には、ボール部７から上方に延びる軸部11を挿
通させるための孔12が形成されている。FIG. 3 shows an overall view of the press machine, in which the slide 3 is connected to the lower end of the connecting rod 2 whose upper end is connected to the crankshaft 1, and the slide 3 moves up and down via the connecting rod 2 by the rotation of the crankshaft 1. The upper die 4 attached to the slide 3 and the lower die 6 attached to the bolster 5.
The material is pressed by and. FIG. 4 shows a connecting structure of the connecting rod 2 and the slide 3. A ball portion 7 is provided at the lower end of the connecting rod 2, a lower surface of the ball portion 7 is received by a pressure receiving member 8 attached to the slide 3, and an upper surface of the ball portion 7 is provided with a retainer 9 attached to the slide 3. Is applied, which results in connecting rod 2 and slide 3
Are connected by a ball portion 7, a pressure receiving member 8, and a ball joint 10 which is a spherically slidable member made of a retainer 9. Retainer 9
A hole 12 for inserting a shaft portion 11 extending upward from the ball portion 7 is formed in a central portion of the.
スライド３が上下動して材料をプレス加工するときにお
ける前記ボールジョイント10の滑らかな球面滑動を確保
するために、ボール部７の下部面と受圧部材８との間の
隙間Ａおよびボール部７の上部面とリテーナ９との間の
隙間Ｂに潤滑油を供給することが必要であり、このため
従来では、ボールジョイント10全体を潤滑油のオイルバ
ス内に浸した構造となっていた。In order to ensure a smooth spherical slide of the ball joint 10 when the slide 3 moves up and down and presses the material, the gap A between the lower surface of the ball portion 7 and the pressure receiving member 8 and the ball portion 7 are secured. It is necessary to supply the lubricating oil to the gap B between the upper surface and the retainer 9. Therefore, in the conventional structure, the entire ball joint 10 is immersed in the lubricating oil bath.
従来では前記隙間A,Bは比較的大きく、このため隙間A,B
への潤滑油の供給方式は前述のオイルバスによるもので
十分であった。Conventionally, the gaps A and B are relatively large, and therefore the gaps A and B are
The above-mentioned oil bath was sufficient for supplying lubricating oil to the.
しかし、近年、プレス加工の高精度化が求められ、これ
に応えるためには隙間A,Bを小さくすることが必要であ
り、オイルバスによる潤滑油供給方式では小さな隙間A,
Bに十分な潤滑油を供給できない。However, in recent years, high precision press working is required, and in order to meet this demand, it is necessary to reduce the clearances A and B. In the lubricating oil supply system using an oil bath, a small clearance A,
Not enough lubricating oil can be supplied to B.
十分な潤滑油を小さい隙間A,Bに供給するためには、油
圧源から圧力をもって潤滑油を強制的に隙間A,Bに給油
することが考えられるが、構造の簡単化およびコストの
低減化のため油圧源を１個とし、この油圧源から潤滑油
を同じ圧力で隙間A,Bの両方に供給するようにすると、
前記リテーナ９には前述の通りボール部７の軸部11を挿
通させる孔12が設けられ、従って、ボール部７の下部面
と受圧部材８との接触面積はボール部７の上部面とリテ
ーナ９との接触面積より大きいことから、油圧によりボ
ール部７に作用する上向き力と下向き力とに差が生じ、
この結果、ボール部７が上方へ押されてリテーナ９に強
く押し付けられ、ボールジョイント10の円滑な球面滑動
を期待できなくなる。In order to supply sufficient lubricating oil to the small gaps A and B, it is conceivable to forcibly supply the lubricating oil to the gaps A and B with pressure from a hydraulic source, but the structure is simplified and the cost is reduced. Therefore, if there is only one hydraulic source and the lubricating oil is supplied from this hydraulic source to both gaps A and B at the same pressure,
As described above, the retainer 9 is provided with the hole 12 through which the shaft portion 11 of the ball portion 7 is inserted. Therefore, the contact area between the lower surface of the ball portion 7 and the pressure receiving member 8 is the same as that of the upper surface of the ball portion 7 and the retainer 9. Since it is larger than the contact area with, the difference between the upward force and the downward force that acts on the ball portion 7 due to the hydraulic pressure,
As a result, the ball portion 7 is pushed upward and strongly pressed against the retainer 9, and smooth spherical sliding of the ball joint 10 cannot be expected.
本考案の目的は、潤滑油の油圧によってボール部に作用
する上向き力と下向き力とを等しくすることができ、こ
れによりボールジョイントの円滑な球面滑動を確保でき
るプレス機械のボールジョイント強制給油装置を提供す
るところにある。An object of the present invention is to provide a ball joint forced oiling device of a press machine capable of equalizing the upward force and the downward force acting on the ball portion by the hydraulic pressure of the lubricating oil, thereby ensuring smooth spherical sliding of the ball joint. It is in the place of providing.
本考案に係るプレス機械のボールジョイント強制給油装
置は、上端がクランク軸に連結されたクランク軸の下端
にボール部を設け、このボール部の下部面をスライドに
取り付けられた受圧部材で受け、ボール部の上部面にス
ライドに取り付けられたリテーナを当て、このリテーナ
にボール部の上方に延びる軸部を挿通させる孔を設けた
プレス機械において、１個の油圧源からリテーナを経て
ボール部の上部面とリテーナとの間の隙間に至る第１回
路およびこの第１回路の途中からスライド、受圧部材を
経てボール部の下部面と受圧部材との間の隙間に至る第
２回路を設け、この第２回路に減圧手段を設けることに
より、第１回路によってボール部の上部面とリテーナと
の間の隙間に供給される油圧よりも第２回路によってボ
ール部の下部面と受圧部材との間の隙間に供給される油
圧を小さくすることを特徴とするものである。A ball joint forced oiling device of a press machine according to the present invention has a ball portion provided at a lower end of a crank shaft whose upper end is connected to a crank shaft, and a lower surface of the ball portion is received by a pressure receiving member attached to a slide. In a press machine in which a retainer attached to a slide is applied to the upper surface of the ball section, and a hole through which the shaft section extending above the ball section is inserted is provided in this retainer, the upper surface of the ball section is passed from one hydraulic source through the retainer. And a retainer, and a second circuit that extends from the middle of the first circuit to the gap between the lower surface of the ball portion and the pressure receiving member through the pressure receiving member and the second circuit. By providing the pressure reducing means in the circuit, the hydraulic pressure supplied to the gap between the upper surface of the ball portion and the retainer by the first circuit is lower than that of the lower surface of the ball portion by the second circuit. It is characterized in that to reduce the hydraulic pressure supplied to the gap between the member.
リテーナの前記孔のため、ボール部の下部面と受圧部材
との接触面積がボール部の上部面とリテーナとの接触面
積よりも大きくても、ボール部の下部面と受圧部材との
間の隙間に供給される油圧がボール部の上部面とリテー
ナとの間の隙間に供給される油圧よりも小さくなること
により、ボール部に作用する上向き力と下向き力とを同
じ大きさにすることができる。Due to the hole of the retainer, even if the contact area between the lower surface of the ball portion and the pressure receiving member is larger than the contact area between the upper surface of the ball portion and the retainer, a gap between the lower surface of the ball portion and the pressure receiving member. Since the hydraulic pressure supplied to the ball is smaller than the hydraulic pressure supplied to the gap between the upper surface of the ball portion and the retainer, the upward force and the downward force acting on the ball portion can be made equal. .
以下に本考案の一実施例を添付図面に基づいて説明す
る。An embodiment of the present invention will be described below with reference to the accompanying drawings.
以下の説明では第４図で述べた部材と同じ部材には同一
符号を付し、その説明を簡略または省略する。In the following description, the same members as those shown in FIG. 4 are designated by the same reference numerals, and the description thereof will be simplified or omitted.
第１図において、タンク20とモータ21とモータ21で駆動
されるポンプ22とからなる油圧源23からは主回路24が延
び、この主回路24はリテーナ９内部の通路25に接続さ
れ、通路25はボール部７の上部面とリテーナ９との間の
隙間Ｂまで達している。これらの主回路24、通路25によ
り、油圧源23からの潤滑油を隙間Ｂに圧油として供給す
るための第１回路26が構成される。In FIG. 1, a main circuit 24 extends from a hydraulic pressure source 23 composed of a tank 20, a motor 21, and a pump 22 driven by the motor 21, and the main circuit 24 is connected to a passage 25 inside the retainer 9, and a passage 25 Reaches a gap B between the upper surface of the ball portion 7 and the retainer 9. The main circuit 24 and the passage 25 constitute a first circuit 26 for supplying the lubricating oil from the hydraulic pressure source 23 to the clearance B as pressure oil.
第１回路26中にレギュレータを設け、このレギュレータ
により圧油を所定圧力まで減圧して隙間Ｂに供給するよ
うにしてもよい。A regulator may be provided in the first circuit 26, and the pressure oil may be reduced to a predetermined pressure by this regulator and supplied to the gap B.
第１回路26の途中（第１回路26中にレギュレータが設け
られる場合には、このレギュレータよりも下流側の途
中）には、分岐回路27が設けられ、この分岐回路27はス
ライド３内部の通路28さらには受圧部材８内部の通路29
に接続され、通路29はボール部７の下部面と受圧部材８
との間の隙間Ａに開口している。これらの分岐回路27、
通路28,29により、第１回路26から隙間Ａまで達する第
２回路30が構成される。A branch circuit 27 is provided in the middle of the first circuit 26 (in the middle of the downstream side of the regulator when a regulator is provided in the first circuit 26), and the branch circuit 27 is a passage inside the slide 3. 28 Furthermore, the passage inside the pressure receiving member 8 29
Is connected to the lower surface of the ball portion 7 and the pressure receiving member 8.
It opens to a gap A between These branch circuits 27,
The passages 28 and 29 form a second circuit 30 that reaches the gap A from the first circuit 26.
第２回路30の分岐回路27中には第１絞り31が設けられ、
この第１絞り31よりも下流側において分岐回路27には前
記タンク20まで延びる戻し回路32が接続され、この戻し
回路32には第２絞り33が設けられる。The first aperture 31 is provided in the branch circuit 27 of the second circuit 30,
On the downstream side of the first throttle 31, a branch circuit 27 is connected to a return circuit 32 extending to the tank 20, and the return circuit 32 is provided with a second throttle 33.
ここで、第１絞り31を流通する油量をQ1、第１絞り31の
前後のＣ点、Ｄ点における油圧をp1，p2とすると、 である。なお、F1は第１絞り31の開口断面積、ｇは重力
加速度、υは油の運動粘性係数、γは油の比重量、l1は
第１絞り31の長さである。Here, if the amount of oil flowing through the first throttle 31 is Q 1 , and the hydraulic pressures at points C and D before and after the first throttle 31 are p 1 and p 2 , Is. Note that F 1 is the opening cross-sectional area of the first aperture 31, g is the acceleration of gravity, υ is the kinematic viscosity coefficient of oil, γ is the specific weight of oil, and l 1 is the length of the first aperture 31.
また、第２絞り33を流通する油量をQ2、第２絞り33の前
後のＥ点、Ｆ点における油圧をp3，p4とすると、 である。なお、F2は第２絞り33の開口断面積、l2は第２
絞り33の長さである。If the amount of oil flowing through the second throttle 33 is Q 2 , and the hydraulic pressures at points E and F before and after the second throttle 33 are p 3 and p 4 , Is. In addition, F 2 is the opening cross-sectional area of the second diaphragm 33, and l 2 is the second
The length of the diaphragm 33.
Ｆ点は大気に連通しているため、p4＝０であり、また、
Ｄ点とＥ点では同圧であるため、p3＝p2である。従っ
て、 また、隙間Ａは隙間Ｂと同様に極めて小さく、このため
隙間Ａに漏出する油量は微量であり、このことから近似
式として Q1＝Q2 … （３） が成立する。Since point F communicates with the atmosphere, p 4 = 0, and
Since the pressure is the same at points D and E, p 3 = p 2 . Therefore, Further, the clearance A is extremely small like the clearance B, so that the amount of oil leaking into the clearance A is very small, and from this, Q 1 = Q 2 (3) is established as an approximate expression.
以上の（１），（２），（３）の各式により となり、l1＝l2のときは となる。According to the above equations (1), (2), and (3), And when l 1 = l 2 Becomes
以上において、p1は第１回路26を介して隙間に供給され
る油圧となり、またp2は第２回路30を介して隙間Ａに供
給される油圧となる。In the above, p 1 is the hydraulic pressure supplied to the gap via the first circuit 26, and p 2 is the hydraulic pressure supplied to the gap A via the second circuit 30.
（４）の式が示すようにp1よりもp2を低圧にすることが
でき、F1とF2との比率を適宜に定めることにより、p1に
対するp2の値を任意に設定できる。なお、第１図で示す
装置を実際に作り、F1，F2を種々変更して実験したとこ
ろ、（４）の式による理論値とほぼ等しいp1に対するp2
の実験値を得られた。The p 2 than p 1 as shown by equation (4) can be a low pressure, by determining appropriately the ratio of F 1 and F 2, it can be arbitrarily set the value of p 2 for p 1 . In addition, when the device shown in FIG. 1 was actually made and F 1 and F 2 were variously changed and tested, p 2 for p 1 which is almost equal to the theoretical value by the equation (4) was obtained.
The experimental value of was obtained.
以上のように本実施例では第１、第２絞り31,33は、隙
間Ｂに供給される油圧よりも隙間Ａに供給される油圧を
小さくする減圧手段34を構成するものとなっており、こ
の減圧手段34は第１回路26に対する第２回路30に設けら
れたものとなっている。As described above, in the present embodiment, the first and second throttles 31 and 33 constitute the pressure reducing means 34 that reduces the hydraulic pressure supplied to the gap A to be smaller than the hydraulic pressure supplied to the gap B. The pressure reducing means 34 is provided in the second circuit 30 with respect to the first circuit 26.
隙間Ｂに供給される油圧に対する隙間Ａに供給される油
圧の比率は、ボール部７の上部面とリテーナ９との接触
面積に対するボール部７の下部面と受圧部材８との接触
面積の比率に応じて定められ、これにより、リテーナ９
にボール部７の軸部11を挿通させる孔12が設けられて前
記両接触面積に差があっても、隙間A,Bの油圧によって
ボール部７に作用する上向き力と下向き力とを等しくす
ることができ、この結果、ボールジョイント10の球面滑
動を円滑なものにすることができる。The ratio of the hydraulic pressure supplied to the clearance A to the hydraulic pressure supplied to the clearance B is the ratio of the contact area between the lower surface of the ball portion 7 and the pressure receiving member 8 to the contact area between the upper surface of the ball portion 7 and the retainer 9. According to the retainer 9
A hole 12 for inserting the shaft portion 11 of the ball portion 7 is provided in the same so that even if there is a difference in both contact areas, the upward force and the downward force acting on the ball portion 7 by the hydraulic pressure in the gaps A and B are made equal. As a result, the spherical sliding of the ball joint 10 can be made smooth.
第２図は本考案の別実施例を示す。この実施例では、第
２回路30に設けられる減圧手段34はタンク20まで延びる
戻し回路35を備えたレギュレータ36となっている。これ
によっても隙間Ｂに供給される油圧よりも隙間Ａに供給
される油圧を小さくでき、レギュレータ36の設定圧を適
宜に定めることにより、第１図の実施例と同じ作用効果
を得られる。FIG. 2 shows another embodiment of the present invention. In this embodiment, the pressure reducing means 34 provided in the second circuit 30 is a regulator 36 having a return circuit 35 extending to the tank 20. This also makes it possible to make the hydraulic pressure supplied to the clearance A smaller than the hydraulic pressure supplied to the clearance B, and by appropriately setting the set pressure of the regulator 36, the same effect as the embodiment of FIG. 1 can be obtained.
なお、第２図の実施例では、スライド３内部における受
圧部材８とリテーナ９との間の空間37に溜まる油をタン
ク20に戻すための還流回路38が設けられている。このよ
うな還流回路は第１図の実施例に係る装置にも設けても
よい。In the embodiment shown in FIG. 2, a reflux circuit 38 is provided for returning the oil accumulated in the space 37 between the pressure receiving member 8 and the retainer 9 inside the slide 3 to the tank 20. Such a return circuit may also be provided in the device according to the embodiment of FIG.
以上説明したように減圧手段は第１図、第２図で示すい
ずれのものでもよく、あるいは他の方式によるものでも
よい。しかし、第１図で示す減圧手段によれば、隙間Ａ
とＢに供給すべき油圧の大きさは計算上求められ、求め
た計算値に基づいて所定の開口断面積を有する第１、第
２絞りを使用すればよく、これにより設定圧調整の不要
化、油圧回路全体の簡単化を実現できるとともに、第
１、第２絞りは可動部材のない固定絞りであるため、プ
レス機械の自動運転時における振動によって故障する虞
れがないという利点を得られる。As described above, the pressure reducing means may be any of those shown in FIGS. 1 and 2, or may be of another type. However, according to the pressure reducing means shown in FIG.
The magnitude of the hydraulic pressure to be supplied to B and B is calculated, and the first and second throttles having a predetermined opening cross-sectional area may be used based on the calculated value, thereby making it unnecessary to adjust the set pressure. It is possible to realize simplification of the entire hydraulic circuit, and since the first and second throttles are fixed throttles having no movable member, there is an advantage that there is no risk of failure due to vibration during automatic operation of the press machine.
本考案によれば、リテーナにボール部の軸部を挿通させ
る孔が形成されることによってボール部の下部面と受圧
部材との接触面積がボール部の上部面とリテーナとの接
触面積よりも大きくなっても、第１回路を介してボール
部の上部面とリテーナとの間の隙間に供給される油圧よ
りも第２回路を介してボール部の下部面と受圧部材との
間の隙間に供給される油圧を小さくできるため、ボール
部に作用する上向き力と下向き力とを同じ大きさにする
ことができるようになり、このため、ボールジョイント
の円滑な球面滑動を確保できるようになる。According to the present invention, the contact area between the lower surface of the ball section and the pressure receiving member is larger than the contact area between the upper surface of the ball section and the retainer by forming the hole through which the shaft section of the ball section is inserted. Even so, the hydraulic pressure supplied to the gap between the upper surface of the ball portion and the retainer via the first circuit is supplied to the gap between the lower surface of the ball portion and the pressure receiving member via the second circuit. Since the hydraulic pressure to be applied can be reduced, the upward force and the downward force acting on the ball portion can be made to have the same magnitude, so that the smooth spherical sliding of the ball joint can be ensured.
第１図は本考案の一実施例に係る装置のボールジョイン
ト断面と油圧回路の図、第２図は別実施例を示す第１図
と同様の図、第３図はプレス機械の全体を示す正面図、
第４図は従来例を説明するためのボールジョイント断面
図である。 １…クランク軸、２…コンロッド、３…スライド、７…
ボール部、８…受圧部材、９…リテーナ、10…ボールジ
ョイント、11…軸部、12…孔、23…油圧源、26…第１回
路、30…第２回路、31,33…絞り、34…減圧手段、32,35
…戻し回路、36…レギュレータ、A,B…隙間。FIG. 1 is a view of a ball joint section and a hydraulic circuit of a device according to an embodiment of the present invention, FIG. 2 is a view similar to FIG. 1 showing another embodiment, and FIG. 3 shows the entire press machine. Front view,
FIG. 4 is a sectional view of a ball joint for explaining a conventional example. 1 ... Crank shaft, 2 ... Connecting rod, 3 ... Slide, 7 ...
Ball portion, 8 ... Pressure receiving member, 9 ... Retainer, 10 ... Ball joint, 11 ... Shaft portion, 12 ... Hole, 23 ... Hydraulic source, 26 ... First circuit, 30 ... Second circuit, 31, 33 ... Throttle, 34 … Decompression means, 32,35
… Return circuit, 36… Regulator, A, B… Gap.
Claims (1)
の下端にボール部が設けられ、このボール部の下部面が
スライドに取り付けられた受圧部材で受けられるととも
に、前記ボール部の上部面に前記スライドに取り付けら
れたリテーナが当てられ、このリテーナに前記ボール部
から上方に延びる軸部を挿通させる孔が形成されている
プレス機械において、油圧源から前記リテーナを経て前
記ボール部の上部面と前記リテーナとの間の隙間に達す
る第１回路を設けるとともに、この第１回路の途中から
前記スライド、前記受圧部材を経て前記ボール部の下部
面と前記受圧部材との間の隙間に達する第２回路を設
け、この第２回路に減圧手段を設けたことを特徴とする
プレス機械のボールジョイント強制給油装置。1. A ball portion is provided at a lower end of a connecting rod having an upper end connected to a crankshaft, a lower surface of the ball portion is received by a pressure receiving member attached to a slide, and an upper surface of the ball portion is provided with the ball portion. In a press machine in which a retainer attached to a slide is applied, and a hole through which a shaft portion extending upward from the ball portion is inserted is formed in the retainer, an upper surface of the ball portion and an upper surface of the ball portion from a hydraulic pressure source through the retainer. A second circuit is provided that reaches a gap between the retainer and the retainer, and reaches the gap between the lower surface of the ball portion and the pressure receiving member through the slide and the pressure receiving member from the middle of the first circuit. A ball joint forced oiling device for a press machine, characterized in that a pressure reducing means is provided in the second circuit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10468589U JPH0649437Y2 (en) | 1989-09-06 | 1989-09-06 | Ball joint forced lubrication device of press machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10468589U JPH0649437Y2 (en) | 1989-09-06 | 1989-09-06 | Ball joint forced lubrication device of press machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0347697U JPH0347697U (en) | 1991-05-02 |
| JPH0649437Y2 true JPH0649437Y2 (en) | 1994-12-14 |
Family
ID=31653473
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10468589U Expired - Lifetime JPH0649437Y2 (en) | 1989-09-06 | 1989-09-06 | Ball joint forced lubrication device of press machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0649437Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103791218A (en) * | 2014-01-23 | 2014-05-14 | 江苏省徐州锻压机床厂集团有限公司 | Circulating lubrication cooling structure for lubricating oil of bulb spherical bowl of high-speed press machine |
-
1989
- 1989-09-06 JP JP10468589U patent/JPH0649437Y2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103791218A (en) * | 2014-01-23 | 2014-05-14 | 江苏省徐州锻压机床厂集团有限公司 | Circulating lubrication cooling structure for lubricating oil of bulb spherical bowl of high-speed press machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0347697U (en) | 1991-05-02 |
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