EP0797738A1

EP0797738A1 - Hydraulic pressure booster

Info

Publication number: EP0797738A1
Application number: EP95941584A
Authority: EP
Inventors: Viktor Malina
Original assignee: Tox Pressotechnik GmbH and Co KG
Current assignee: Tox Pressotechnik GmbH and Co KG
Priority date: 1994-12-16
Filing date: 1995-12-14
Publication date: 1997-10-01
Also published as: US5836161A; JPH11500516A; WO1996018825A1; CN1174597A; DE4445011A1

Abstract

A hydro-pneumatic pressure booster is proposed in which the reservoir chamber (24) is limited by an elastic partition wall (26, 126) instead of a sliding piston.

Description

Hydraulic r c transmitter

State of the art

The invention is based on a hydraulic pressure intensifier according to the preamble of the main claim. In a known generic pressure intensifier (DE-OS 42 23 41 1 or WO-93 15 323) the particular problem of such pressure intensifiers, namely the sealing between oil and air of a storage space contained between the oil and the compressed air space causing the storage pressure, is created by creating an intermediate space lying pressure-relieved room solved. Any air or liquid quantities on the plunger or the outer surface of the intermediate piston are collected and drained off via ventilation ring grooves arranged there. Such an arrangement requires an extremely precise coaxial arrangement of plunger and intermediate piston, as well as cylinder jacket. In addition, several radial seals subject to natural wear and tear are required for the required tightness. While radial sealing of the plunger is usually unproblematic due to the small diameter, this sealing problem increases disproportionately with the diameter of the outer surface of the piston.

The invention and its advantages

The hydraulic pressure intensifier according to the invention with the characterizing features of the main claim has the advantage that an absolute and virtually wear-free seal between the oil-filled storage space and the air space located on the side of the partition facing away from it can be achieved in the region of the movable partition. This can be a pressure which determines the pressure in the storage space and is under pressure act standing air space, as well as a room under atmospheric pressure, wherein there may be a spring force influencing the pressure in the storage space and acting on the partition. The storage space can also be accommodated in a separate storage, which has, for example, a connection to the working space controlled by the control piston (plunger). Such a separate arrangement of the memory means that a plurality of pressure intensifiers can be supplied from only one memory, and according to the invention, an expensive device of various types can be used at the control point between the memory space and the work space, which is largely independent of the rest of the pressure intensifier design. Any electrically operated slide valve or a valve can thus serve as the control device without the plunger being dispensed with. Due to the absolute seal between the storage space and the air space, the pressure can also be increased with the advantages mentioned below with an adapted constructive solution.

According to an advantageous embodiment of the invention, the partition is tubular, as a corrugated tube that can be changed in the axial direction in the stroke or as a tube that can be changed in diameter in the radial direction. Corrugated tubes of this type are known in many different ways, for example in the form of a metal component or odor also G umm i - or w. Plastic protection tube from telescopes. A pneumohydraulic pressure converter is also known (WO 83/04 288), in which the air pressure space is delimited by a corrugated tube which surrounds the pressure piston and thus enables its stroke. According to a further advantageous embodiment of the invention, the partition is conical. As a result, the corrugated tube material can advantageously be compressed more in the axial direction.

According to a further advantageous embodiment of the invention, the partition is designed to be elastically resilient, influencing the storage pressure.

According to a further advantageous embodiment of the invention, the bellows, rolling membrane, hose membrane, or the like. trained partition made of rubber, metal or other comparable elastic materials, such as plastic.

According to a further advantageous embodiment of the invention, a spring force, for example a helical spring, acts on the partition to influence the storage pressure. The partition can then have a corresponding base plate for the attack of the coil spring.

According to a further advantageous embodiment of the invention, the side of the partition wall facing away from the storage space is acted upon by a certain pneumatic pressure, so that the bilateral surface pressure load on the lifting wall is compensated for.

According to a further advantageous embodiment of the invention, which is also claimed for itself, the lateral surface of the storage space is at least partially white transparent. In this way, it can be determined in a simple manner how much liquid is present in the storage space and whether refilling or complete replenishment is necessary at all. This characteristic is also valid in itself made because it can also be used advantageously in the known pressure intensifiers, but in particular can advantageously be used in the invention. Such a simple visual inspection is particularly advantageous in the case of a reservoir supplying several pressure intensifiers with liquid and in particular when the storage pressure is lower.

According to a further advantageous embodiment of the invention, the partition is clamped at one end and connected on the end region facing away from the clamp by a base plate which is movable but rigid in itself with the partition. The clamp is advantageously present on the outer edge region.

According to a further advantageous embodiment of the invention, the control device is a plunger piston arranged axially with the working piston, the separating walls having a penetrated ring (bottom plate) penetrated radially by the plunger. Such a ring is suitable both as a support for a helical spring and also for the application of air or possibly also a liquid which determines the storage pressure. Alternatively, the partition can also be firmly connected to the plunger.

According to a further advantageous embodiment of the invention, the ring on the plunger is displaceable in its axial direction, the radial tightness being relatively easy to achieve here due to the relatively small diameter.

According to a further advantageous embodiment of the invention, the one acting on the partition engages the storage pressure influencing spring force on the one hand on the partition and on the other hand on a control piston connected to the plunger. A gas spring or a mechanical spring, for example a helical spring, can serve as the spring force. In the latter case, the structure can be similar to that of the generic pressure intensifier.

According to a further advantageous embodiment of the invention, which is also claimed for itself, an intermediate piston is arranged between the lifting wall and the control piston, floating in the lifting direction, on which on the one hand the spring force acting towards the control piston and on the other hand the spring force acting towards the lifting wall acts.

According to a further advantageous embodiment of the invention, the container of the pressure intensifier that holds the storage space is spatially independent of the cylinder that receives the plunger, whereby according to a related embodiment of the invention, several working spaces can be supplied by this only one storage space. Particularly when several pressure intensifiers are provided in a production facility, the use of only one store can save considerable material costs, but also control effort. Last but not least, such an arrangement is also space-saving.

According to a further advantageous embodiment of the invention, the connection of the storage space to several work spaces can be controlled by only one control point. As a result, the pressure stroke can start simultaneously with several pressure boosters under the control of a control point. According to a further advantageous embodiment of the invention, the partition is arranged concentrically with the working piston and in the housing surrounding it (hose membrane). As a result, the overall length of the pressure intensifier is shortened using the unused housing volume around the work space.

According to an advantageous embodiment of the invention in this regard, a jacket tube is arranged radially around the partition, the annular space between the partition and the jacket tube serving as a pneumatic chamber. The partition is designed as a hose membrane.

According to a further advantageous embodiment of the invention, the pressure in the pneumatic space corresponds to the accumulator pressure or to a pneumatic pressure causing the rapid traverse of the working piston. With the pneumatic rapid traverse pressure, the hose membrane and the auxiliary ring piston of the working piston can be acted on at the same time.

According to an alternative further advantageous embodiment of the invention, the pressure fluid supplied from the storage space under storage pressure serves to drive the rapid stroke of the working piston. While an extra, usually pneumatically driven piston usually brings about the rapid stroke in such pressure intensifiers, such a piston can be saved according to this embodiment of the invention, since the higher storage pressure that can be achieved with the invention enables the correspondingly larger amount of liquid required for the rapid traverse to be conveyed per unit of time.

According to a further advantageous embodiment of the invention, only one working space can be connected to the pressure spaces of a plurality of working pistons, so that after actuation of the Connection between the storage space and the working space and immersion of the plunger in the working space, several working pistons can be moved under the same working pressure. In this embodiment of the invention, which is also claimed for itself, a plurality of working pistons can advantageously be actuated via a central storage and pressure generating device, which pistons can be connected to the central office via lines at a corresponding distance from the central office.

Further advantages and advantageous embodiments of the invention can be found in the following description, the drawing and the claims.

drawing

Three embodiments of the object of the invention are shown with variants in the drawing and described in more detail below. Show it:

1 shows a hydropneumatic pressure intensifier with an elastic storage wall in longitudinal section.

Fig. 2 likewise with external memory;

Fig. 3 likewise with a simple piston;

Fig. 4 shows an embodiment with several pistons and

Fig. 5 shows an execution with S peic herwan d al s

Hose membrane. Description of the embodiment

The hydropneumatic pressure intensifier shown in FIG. 1 has a housing 1, in which a working piston 2 is arranged in a radially sealing and axially displaceable manner via seals 3. The housing 1 is closed at the top by an axially inserted housing piece 4 using radial sealing elements 5, a working space 6 being formed.

The working piston 2 has an auxiliary piston 7 of larger diameter, which acts axially displaceably in a radial manner in a working cylinder 8 and can be pneumatically actuated for a rapid drive of the working piston 2. Depending on the direction of adjustment, the compressed air is either conducted via the connections and channels 9 above the auxiliary piston into an upper pneumatic chamber 11, which is delimited by the housing 1, working piston 2, auxiliary piston 7 and working cylinder 8, or the compressed air is via a connector and channels 12 passed into a lower pneumatic chamber 13 which is delimited by the working piston 2, the auxiliary piston 7, the working cylinder 8 and a lower housing cover 14, the working piston 2 being guided centrally and radially sealingly in the lower housing cover 14, in which the channels 12 are also arranged are. In addition, this lower housing cover 14 serves as an abutment for the tie rods (not shown) of the pressure intensifier running parallel to the housing 1 and the working cylinder 8.

On the housing piece 4, a casing tube 15 is placed, which in turn is closed at the top by an upper housing cover 16 and in which connections and channels 17 for control compressed air are provided from above in the casing tube 15. A control piston works in the casing tube 15 96/18825 PCIYDE95 / 01795

18, on which a plunger 19 is arranged and which delimits a control chamber 21 with the casing tube 15 and the housing cover 16. After a certain stroke, the plunger 19 plunges into a central bore 22 of the housing piece 4 and into a radial seal 23 arranged there, as a result of which the working space 6 is closed at the top. With increasing immersion in the working space 6, the oil displaced there causes a corresponding displacement of the working piston 2 downward, so that with a relatively low pneumatic control pressure in the control chamber 21 and due to the small diameter of the plunger 19 in relation to the diameter of the working piston which is substantially larger in diameter 2 A hydropneumatic pressure transmission takes place. In order to ensure a refill of oil into the working chamber 6 during the rapid traverse caused by the auxiliary piston 7, which takes place before the actuation of the plunger 19 and serves to drive the working piston 2 towards the product, is a pressurized one

Oil storage space 24 required. The control piston 18 is reset via a helical spring 25 arranged inside the casing tube 15, which is supported on the side facing away from the control piston 18 on an intermediate piston 20 which is floating in the casing tube 15 and is shown in two working positions.

In the first exemplary embodiment shown in FIG. 1, the oil storage space 24 is arranged above the housing piece 4 and delimited by the housing piece 4, the casing tube 15 and the plunger 19, and an elastic partition wall 26, which consists of a corrugated tube 27 and a base plate 28, the corrugated tube 27 is fastened with its upper outer edge at 29 on the inside of the casing tube 15 and with its lower end at 31 on the outer circumference of the base plate 28. The corrugated tube 27 can be an input Have spring action in the direction of the oil storage space 24. Between the base plate 28 and the intermediate piston 20, a helical spring 30 is arranged, by means of which the storage pressure is determined. Of course, another spring force acting on the base plate could also serve instead of this spring pressure, for example a pneumatic working pressure provided above the partition. The base plate 28 penetrated centrally by the plunger 19 has a radial seal 22 toward the plunger 19. In the drawing, the bottom plate 28 is shown largely shifted downward in the left half - for a better understanding - although the right half of the working position shown corresponds to that of the working piston 2. In the housing piece 4 there is also an oil filler nipple with channels 33 for filling the oil storage space 24 with oil or to compensate for leakage losses. The space 34 provided above the partition 26 is relieved of pressure to the atmosphere via openings 35. In the section of the casing tube 15 between the connection point 29 and the housing piece 4, a sight glass 36 for checking the oil in the oil storage space 24 is arranged s. Since there are relatively low oil pressures in the oil storage space 24 and, moreover, the use of the partition wall according to the invention in this section 37 of the casing tube 15 surrounding the oil storage space 24 means that no piston is radially sealing, the entire section 37, which also acts as a casing pipe, can be made of transparent material consist.

For the description of the exemplary embodiments shown in FIGS. 2 to 5 and their variants, the same reference numbers are used below for the parts that can also be seen in FIG. 1, but increased by the number 100, 200, 300 and 400, respectively that for these parts an extra Explanation is not required. In contrast, new parts not yet mentioned in FIG. 1 are numbered consecutively.

In the second exemplary embodiment according to FIG. 2, the oil storage space 124 is arranged in an oil reservoir 38 which is independent of the housing 101 and is connected to the working space 106 via a line 39, specifically via the housing piece 104 upstream of the central bore 122 or. the radial seal 123. The plunger 119 does not fully emerge from the bore 122 in its return stroke in this exemplary embodiment, but in the upper starting position shown it keeps the mouth 41 of the line 39 open in the bore 122. A radial seal 42 is arranged in the housing piece 104 in the remaining immersion area of the plunger 11 in the bore 122. With correspondingly good guidance and a given seal between the plunger 11 and the wall of the bore 122, the radial seal 123 can be dispensed with if the mouth 41 is closed properly during the downward stroke of the plunger 119 and the working pressure is not too high. The oil reservoir 38 has a pot-like housing 43, on the upper edge of which the corrugated tube 127 is fastened and which is closed at the top by a cover 44, in which ventilation openings 45 are arranged. Otherwise, the lifting wall 126 is designed as in the first exemplary embodiment, although the base plate 128 has no central opening due to the lack of a plunger. Here too, the housing 43 or parts of the housing can be made of a transparent material in order to be able to recognize the respective oil level.

In the embodiment shown in FIG. 3, the working piston 202 is of considerably slimmer design and has only one piston stage 46 of larger diameter at the top, which The working space 206 is delimited at the top and the pneumatic space 213 is delimited at the bottom. By arranging the oil reservoir 38 externally, much more hydraulic oil and also under higher pressure can be available than with an arrangement as shown in FIG. As a result, there is the possibility that the rapid stroke of the working piston 202 can be carried out quickly and sufficiently by oil flowing in via the line 239, until the line 239 is then blocked by the plunger 219, after which the high pressure phase or the working stroke of the working piston 202 then begins. The rapid return is pneumatically effected in a known manner via the lower pneumatic space 213, as described for FIG. 1. Since the cross section of the piston stage 46 is decisive for the working force of the working piston 202, the same work performance as that in FIG. To achieve 1 pressure intensifier shown, this training shown in Fig. 3 is significantly slimmer and therefore less massive, and more versatile. The decisive factor is the sufficient oil supply from the oil store.

In the variant shown in FIG. 4, both the arrangement and actuation of the plunger 319 and the oil reservoir 338 correspond to the embodiment shown in FIG. 2. The working space 306 is here only designed as a piece of pipe, from which lines 47 and 48 lead to working pistons 303 which are independent of the working space 306 or the pressure spaces 49 and 51 present there , The work unit shown below is designed with the pressure chamber 51 corresponding to that in FIG. 3. It is thus possible to use an oil reservoir 338 and a plunger 319 to actuate several working units via a common working space 306. It is also of importance here that the oil reservoir 338 provides the sufficient amount of oil as well as the required pressure.

The third exemplary embodiment shown in FIG. 5 works in principle in the same way as the second exemplary embodiment shown in FIG. 2, so that there is no need to repeat the description. The difference lies in the arrangement of the storage space 424 or the elastic partition wall 426. The storage space 424 and the partition wall 427 are arranged concentrically to the working piston 402, specifically in the housing 401 surrounding this working piston. The partition wall 426, which is designed in the manner of a hose membrane 427, has an upper connection point 429 to the housing piece 404 and a lower connection point 54 to the housing 401. The storage space 424 is connected via a channel 55 to the central bore 422 in which the plunger 419 operates and controls the mouth 441. On the side of the partition wall 426 facing away from the oil storage space 424, a pneumatic space 53 is arranged, which is closed to the outside by a jacket tube 52 which extends between the housing 401 and the housing 404. This pneumatic chamber 53 is connected by a channel 56 to the channel 409, which opens into the upper pneumatic chamber 41 1 of the auxiliary piston 407, via which the rapid traverse of the working piston 402 is controlled. Advantageously, this given arrangement of the partition 426 with the storage space 424 and the pneumatic space 53 or jacket tube 52 utilizes space in the housing 401 which is not used per se, without the need for an additional space for the storage space, with the result that the pressure intensifier is shorter overall can be built without having to have a larger diameter. All features shown in the description, the following claims and the drawing can be essential to the invention both individually and in any combination with one another.

LIST OF REFERENCE NUMBERS

1, 101, 401 housing 30

2, 202, 402 working piston 3 1 radial seal

3, 303 seals 32 radial seal

4, 104, 404 housing piece 33 nipple u. channels

5 radial sealing elements 34 space

6, 106, 206,

306. 406 workspace 35 openings

7, 407 auxiliary piston (compressed air for rapid drive) 36 sight glass

8 working cylinder 37 section v. 15

9, 409 connection u. Channels 38, 338 oil storage

10 39, 239 line

11, 41 1 Upper pneumatic room 40

12 connection u. Channels 41, 441 estuary

13, 213 Lower pneumatic chamber 42 radial seal

14 Lower housing cover 43 housing

15 casing tube 44 cover

16 Upper housing cover 45 ventilation opening

17 connection u. Channels 46 piston stage

18 control spool 47 line

19, 1 19, 219, 19, 419 plunger 48 line 0 49 pressure chamber 1 pressure chamber 50 2, 122, 422 central bore 51 pressure chamber 3, 123 radial seal 52 jacket tube 4, 124, 424 oil storage chamber 53 pneumatic chamber 5 S coil spring 54 connection point 6, 126, 426 partition 55 channel 7, 127, 427 corrugated tube, hose membrane 56 channel 8, 128 base plate 9, 429 connection point

Claims

Expectations

Hydraulic pressure intensifier

- With a liquid-filled working space (6, 106) for changing pressures, namely a low storage pressure and a high working pressure, with a hydraulically connectable to the working space (6, 106), liquid-filled and under storage pressure, a movable partition (26, 126) having storage space (24, 124),

with a working piston (2, 102) acting in the working space (6, 106), the stroke of which can be transferred outside the pressure intensifier, - With an externally actuated (pneumatic) plunger (19, 1 19), which for driving (control piston 18, 1 18) of the working piston (2, 102) in the working space (6, 106) and

- With a control point in the connection (22, 122, 41, 39) between the working space (6, 106) and the storage space (24, 124), which to generate the high working pressure in the working space (6, 106) after immersion of the plunger (19th , 1 19) can be blocked by a control device (plunger 19, 1 19), characterized in that

- That the movable partition (26, 126, 426) is fixed at least at one of its end regions (29, 129, 429) and

- That the partition (26) as a storage space (24, 124, 424) delimiting membrane (27, 127, 427) is made of elastic material.

2. Pressure intensifier according to spruc h 1, characterized in that the partition (26, 126, 426) is tubular, as a changeable in the axial direction in the stroke corrugated tube (27, 127) or as a radially changeable in diameter tube (427 ).

3. Pressure intensifier according to claim 2, dadurc h characterized in that the partition tube (27, 127) is conical.

4. Pressure intensifier according to one of the preceding claims, characterized in that the partition (427) influencing the storage pressure is designed to be resilient in itself.

5. Pressure intensifier according to one of the preceding claims, characterized in that the partition (bellows 27, 127, rolling membrane, hose membrane 427) consists of rubber, metal or a comparable elastic material.

6. Pressure intensifier according to one of the preceding claims, characterized in that a spring force acts to influence the storage pressure on the partition (base plate 28).

7. Pressure intensifier according to one of the preceding claims, characterized in that the side of the partition (26, 126, 426) facing away from the storage space (24, 124, 424) is acted upon by a certain pneumatic pressure.

8. Pressure intensifier in particular according to one of the preceding claims, characterized in that the outer surface (37, 43) of the storage space (24, 124) is at least partially (36) transparent.

9. Pressure intensifier according to one of the preceding claims, characterized in that the partition wall (26, 126) clamped at one end and on the end region facing away from the clamping by means of a partition plate (26, 126) which is movable but rigid in itself (28, 128) connected is.

10. Pressure intensifier according to claim 9, characterized in that as control means an ac hsleich with the working piston (2, 102) arranged plunger (19, 119) and that the partition (26, 126) has a central, penetrated by the plunger (19, 119) to it radially sealing ring (base plate 28).

11. Pressure intensifier according to claim 10, characterized in that the ring (28) on the plunger (19) is displaceable.

12. Pressure intensifier according to one of claims 9 or 11, characterized in that the spring force acting on the partition wall, influencing the storage pressure, of gas spring and or mechanical spring (25) on the one hand on the partition wall (26) and on the other hand on one with the plunger (19 ) connected control piston (18).

13. Pressure intensifier in particular according to claim 12, characterized in that between the partition (26) and the control piston (18) floating in the stroke direction, an intermediate piston (20) is arranged, on the one hand acting to the control piston (18) and on the other hand to the partition ( 26) Apply spring force (25, 30).

14. Pressure intensifier according to one of the preceding claims 1 to 9, characterized in that the storage space (124) receiving container (housing 43) is spatially independent of the plunger (119) receiving jacket tube (115).

15. Pressure intensifier according to one of the preceding claims, characterized in that several work spaces (106) are supplied by only one storage space (324).

16. Pressure intensifier according to claim 1 5, characterized in that the connection of the storage space to several work spaces can be controlled by only one control point.

17. Pressure intensifier according to one of claims 1 to 8, characterized in that the partition (427) is arranged concentrically to the working piston (2) and in the housing (401) surrounding it (hose membrane).

1 8. Pressure intensifier according to claim 1 7, characterized in that a jacket tube (52) is arranged radially around the partition (427).

19. Pressure intensifier according to claim 1 8, characterized in that the existing between the partition (427) and jacket tube (52) existing annular space serves as a pneumatic space (53).

20. Pressure intensifier according to claim 19, characterized in that the pressure in the pneumatic chamber (53) corresponds to the accumulator pressure or to the rapid traverse of the working piston (2) causing pneumatic pressure.

21. Pressure intensifier according to one of the preceding claims, characterized in that the pressure fluid supplied from the storage space below Storage pressure to drive the rapid stroke of the working piston (202) is used.

22. Pressure translator according to one of the preceding

Claims, characterized in that only one working space can be connected to the pressure spaces (49, 50) by several working pistons (303)