EP0012769A1

EP0012769A1 - Pressure raising hydropneumatic control device.

Info

Publication number: EP0012769A1
Application number: EP79900462A
Authority: EP
Inventors: Artur Grullmeier
Original assignee: Individual
Current assignee: Individual
Priority date: 1978-04-26
Filing date: 1979-12-05
Publication date: 1980-07-09
Also published as: ATA301279A; IT7922103A0; EP0012769B1; DE2818337C2; DD143296A5; WO1979000986A1; AT380542B; SE7910518L; GB2055972B; SE433650B; DE2818337B1; US4300351A; IT1112714B; CH640312A5; GB2055972A

Abstract

Pour la commande hydropneumatique d'un mouvement rapide et une course motrice, notamment pour la commande d'outils de poinconnage, il est prevu un cylindre (1, 4) muni d'une paroi transversale (12), un piston a disque (7) avec plongeur (8), un piston de travail (2), actionnable dans la direction de retour avec de l'air sous pression, et un piston annulaire (9) entourant le plongeur (8). Les portions du cylindre situees de part et d'autre de la paroi transversale, entre le piston de travail (2) et le piston annulaire (9), sont remplies de fluide hydraulique. Afin de diminuer le besoin d'air sous pression et d'augmenter la vitesse de reaction, ainsi que pour une raison de simplification, le piston de travail (2) presente une surface annulaire (16a) destinee a recevoir l'air sous pression qui actionne ce piston dans la direction d'avancement tandis que, entre le piston a disque (7) et le piston annulaire (9), est insere un ressort de pression (10). La portion du cylindre contenant le ressort (10) est constamment reliee avec l'exterieur, de preference par l'intermediaire d'un filtre (11).For the hydropneumatic control of a rapid movement and a driving stroke, in particular for the control of punching tools, a cylinder (1, 4) provided with a transverse wall (12), a disc piston (7) is provided. ) with plunger (8), a working piston (2), operable in the return direction with pressurized air, and an annular piston (9) surrounding the plunger (8). The portions of the cylinder located on either side of the transverse wall, between the working piston (2) and the annular piston (9), are filled with hydraulic fluid. In order to reduce the need for pressurized air and to increase the reaction rate, as well as for the sake of simplification, the working piston (2) has an annular surface (16a) intended to receive the pressurized air which actuates this piston in the direction of advance while, between the disc piston (7) and the annular piston (9), is inserted a pressure spring (10). The portion of the cylinder containing the spring (10) is constantly connected with the exterior, preferably through a filter (11).

Description

Pressure-boosted hydropneu atic drive

Technical field:

The invention relates to a pressure-translated hydropneumatic drive for rapid traverse and power stroke, in particular for driving punching tools, consisting of a cylinder housing with a transverse wall, a disk piston with a plunger, a working piston which can be pressurized with compressed air and a ring comprising the plunger for the return stroke. piston. The cylinder spaces between the working piston and the annular piston on both sides of the transverse wall are filled with hydraulic oil.

Underlying state of the art: US-PS 34 26 530 US-PS 40 72 013

In a drive of this type known from US Pat. No. 3,426,530, compressed air is introduced at rapid traverse into the space between the annular piston and the disk piston. The ring piston moves the

OMPI Hydraulic oil orrate and with its help moves the working piston. The space mentioned is also the displacement of the disk piston during the power stroke and represents a dead air space which is relatively large in rapid traverse. This has the disadvantageous consequence that a lot of drive compressed air is consumed in the rapid traverse. The pressure build-up and reduction in this large space also requires a relatively long time, which reduces the response speed of this known drive. It must be taken into account here that the drive air pressure of the rapid traverse must be completely reduced during the power stroke, since it counteracts the beginning movement of the disk piston.

Since the annular piston of the known drive is acted upon on one side with compressed air and on the other side with hydraulic oil, it has a special sealing arrangement, consisting of two sealing rings and a venting of the annular space located therebetween. Experience has shown that this is unavoidable, since no seal is completely tight in the long run and therefore air would get into the hydraulic oil without venting the intermediate space and this would foam up. This would result in the desired force not being generated on the working piston and the drive being able to heat up excessively. However, since the ventilation opening in the cylinder housing

- not moved with the annular piston, the sealing rings must be moved apart by at least the stroke length of this piston. This entails an unfavorable extension of the entire cylinder housing of the drive according to US Pat. No. 3,426,530.

Finally, this known drive shows a complicated construction insofar as the plunger is a hollow body, into which a trunk-shaped extension of the cylinder end wall protrudes in a sealed manner.

A pressure-translated hydropneumatic drive of another type is known from US Pat. No. 40 72 013. In order to move the working piston in rapid traverse, it has an annular surface that can be pressurized with compressed air in the feed direction. This will shorten the response time. However, this known arrangement consumes a lot of drive compressed air because compressed air is also applied to an annular piston surrounding the working piston and guided in its own cylinder housing. Moreover, the concentrically nested design of this known drive has significant manufacturing disadvantages, which also reveals the large number of individual parts required. Disclosure of the Invention:

The present invention is that in a pressure-translated hydropneumatic drive according to features a) to g) of the claim

the working piston has an annular surface which can be pressurized with air in the feed direction,

- A compression spring is clamped between the disc piston and the annular piston and - The space containing the compression spring is always connected to the atmosphere.

Such a drive consumes little drive compressed air per stroke, responds quickly, has a short overall length and is easy to manufacture.

A significant reduction in compressed air consumption results on the one hand from the elimination of any dead air space and on the other hand from the fact that the annular piston is no longer driven by compressed air but by means of the compression spring. At the same time, there is an increase in the response speed, i.e. a shortening of the time interval from the start signal to the end of the power stroke, to which the compression spring advantageously contributes, because the one caused by it

Initial pressure in the oil reservoir supports the pneumatic Rapid piston drive of the working piston. The previously necessary double seal of the annular piston is no longer necessary since it is no longer pressurized with compressed air. Rather, as mentioned, the hydraulic oil is constantly under pressure, so that at most oil can escape, but air can never get into the oil. The elimination of the double seal placed at a distance allows the ring piston and thus the entire cylinder housing to be shortened considerably. Finally, the invention achieves a structural simplification by eliminating both tubular and multiply concentrically nested elements, which results in a tangible manufacturing and thus price advantage.

Since the space containing the compression spring in operation shrinks and increases its volume with each work cycle, air is expelled and sucked in again from the environment. This breathing process advantageously cools the drive. In order to keep the air flow resistance low and to prevent the ingress of dust and foreign bodies into the room, it is proposed in a further development of the invention that the connection to the atmosphere takes place via a filter.

_OMPI Brief description of the drawing:

The drawing shows a longitudinal section of a pressurized hydropneumatic drive with a working piston designed as a stepped piston.

Best way to carry out the invention:

The arrangement shown is composed of a high-pressure cylinder 1, in which a stepped working piston 2, which has a piston rod 3, can move and a compressed-air cylinder 4, the cover 5 of which, with the aid of a plurality of long tensioning screws 6 distributed over the circumference the high pressure cylinder 1 is clamped. The

Compressed air cylinder 4 contains a disc piston 7, which is fixedly connected to a plunger 8, and a ring piston 9, which is sealed on the inside against the plunger and on the outside against the compressed air cylinder 4. A pressure spring 10 is clamped between the annular piston 9 and the disk piston 7. The part of the compressed air cylinder interior space in which this compression spring 10 is located is connected to the outside air via a filter 11. The space between the annular piston 9 and the upper transverse wall 12 of the high pressure cylinder is drawn as an oil reservoir 13 b, the space between the working piston 2 and the

^< & This transverse wall as an oil chamber 14. Both are filled with hydraulic oil. In the transverse wall 12 there is an upwardly widening funnel-shaped opening 15 with a sealing ring, which can be sealed off by the plunger 8 going downwards.

The high-pressure cylinder 1 has two compressed air connections A and B. The connection A is connected to the annular space 16 formed by the step, as a result of which an annular surface 16a of the working piston 2 can be acted upon. The other compressed air connection B leads to the space 18 formed between the working piston 2 and a lower cover 17 of the high pressure cylinder. The working piston 2 has an upwardly open central bore 19 for receiving the plunger 8, the diameter of this bore is significantly larger than the outer diameter of the plunger 8.

The slight leakage of the media air and oil that may occur after prolonged operation is discharged to the outside via an annular groove and a longitudinal bore 20 in the working piston 2 and its piston rod 3. Hydraulic oil can be refilled into the oil reservoir 13 at any time via a nipple 21 attached to the high-pressure cylinder 1 become. The annular space 16 is connected via a connecting line 22 and a valve unit 23 to the space 24 between the disk piston 7 and the cover 5 of the compressed air cylinder. The valve unit contains a pressure relief valve 25, which is only shown schematically and opens upwards. Furthermore, a quick exhaust valve 26 is provided in the valve unit, which establishes the connection between the connecting line 22 and the space 24 when pressure prevails in the connecting line 22 and the pressure relief valve 25 opens and which, on the other hand, makes it possible to vent the space 24 via an outlet 27 in the event of a pressure drop in this connecting line 22. The quick exhaust valve 26 contains an up and down movable plate with a lip-like sealing edge. So that this plate can retreat downward when the disk piston returns, the pressure relief valve 25 is connected in parallel as a bypass with a check valve which discharges the air pent up between the pressure relief valve 25 and the plate into the annular space 16, which in this phase is open to the outside.

The drive described works as follows: In the shown rest position, the lower compressed air connection B is pressurized with compressed air. As a result, the working piston 2 is in its upper position. Likewise, the disk piston 7 is held in its upper position by the compression spring 10. For the rapid traverse, the upper compressed air circuit A and thus the annular surface 16a are acted upon, while the space 18 is vented. As a result, the working piston 2 moves downward. At the same time, the annular piston 9 presses hydraulic oil from the oil reservoir 13 into the oil chamber 14 through the open passage opening 15 under the action of the compression spring 10. This hydraulic oil also presses on the working piston 2 in the feed direction.

If the working piston 2 now encounters resistance, a pressure builds up in the annular space 16, which opens the pressure relief valve 25, so that the compressed air pushes the disc piston 7 with the plunger 8 downward against the force of the compression spring 10 emotional.

As soon as the plunger 8 passes through the passage opening 15 and its sealing ring, the annular piston 9 stands still and the hydraulic oil in the oil chamber 14 is displaced by the penetration of the plunger 8, so that a very high pressure arises in the oil chamber which causes the working piston 2 moved down with the highest strength on his remaining way to work. The force generated corresponds essentially to the ratio of the cross section of the upper part of the working piston to the cross section of the plunger times that of the compressed air on the disc piston. exercised strength. In addition, the compressed air continues to act on the annular surface 16a of the working piston 2.

When the power stroke has ended, the compressed air is switched back to port B and the working piston 2 is pushed back into its starting position. At the same time, the oil pressure arising above the working piston pushes the plunger 8 back, the compression spring 10 also acting. The oil finally expelled from the oil chamber 14 is taken up by the oil reservoir 13, which is prestressed by the compression spring 10, without air bubbles.

The atmospheric air flowing in and out through the filter 11 is not compressed. It contributes significantly to the cooling of the arrangement, particularly in continuous operation.

The most important technical data of a prototype of such a drive are given below only as an example: Pneumatic operating pressure 6 bears, rapid traverse force 430 kp, work force 10,000 kp, retraction force 780 kp, total stroke 30 mm, stroke 6 mm, stroke rate 40 / min., Overall height 500 mm. In view of the high workforce, the air consumption with 1.8 1 compressed air, corresponding to 10.8 1 intake air per stroke, is extremely low. It is also important to note the optimal ratio of the forces to each other with regard to the application in the Stamping technology, where the retraction force of the working piston in relation to the working force must not be too small.

Commercial usability:

The invention is implemented by a specific embodiment of a physical object, namely a piston-cylinder arrangement. It can therefore be exploited in particular through industrial production, through the sale or use of these objects, and through the fact that the activities mentioned are permitted to third parties for a fee.

-gT REΛ /

OMPI

Claims

Expectations

1. Pressure-translated hydropneumatic drive for rapid traverse and power stroke, in particular for driving punching tools, with the following features: a) a cylinder housing with two sections separated by a transverse wall is provided; b) in the first cylinder section is a pneumatically pressurized, a plunger small diameter bearing piston disc sealed c) the plunger can penetrate the transverse wall in a sealed manner after a predetermined stroke; d) a working piston with a piston rod leading to the outside is arranged in the second cylinder section; _, e) the working piston can be charged with compressed air on the piston rod side for the return stroke; f) an annular piston comprising the plunger is provided in the first cylinder section; g) the limited by the working piston and the annular piston th cylinder spaces on both sides of the transverse wall are filled with hydraulic oil;

-G characterized by the following features: h) the working piston (2) has an annular surface (16a) which can be pressurized with compressed air in the feed direction; i) a compression spring (10) is clamped between the disk piston (7) and the annular piston (9); j) the space containing the compression spring (10) is always connected to the atmosphere.

Drive according to claim 1, characterized in that the connection to the atmosphere takes place via a filter (.11).

-ξtTREA T OMPI / .. WIPO -Λ. _J