DE4200576A1 - High pressure device for fluid flow machines - has piston 'shoe' running within chamber to support high pressure piston and withstand buckling - Google Patents

Abstract

A high pressure device in a high pressure machine has fluid flow into one of its chambers, which is forced from the chamber under pressure. A piston (5) has a rotating 'shoe' (447) aligned to it, having a diameter between 75 and 100 percent of the eccentric drive, and with a rotating link with a second radius about the same centre. The path of the rotating shoe inside chamber is such that its outer surface runs about the second radius. The piston shoe is then supported such that the thin high pressure piston does not buckle, and the piston shoe withstands a pressure of several thousand bar. ADVANTAGE - Increased performance, pressure, safety, machine life.

Description

The invention relates to a high-pressure arrangement (s) in high-pressure unit (s) in which fluid is admitted into a chamber which changes its volume periodically and is pressed out of the chamber by a pressure medium.

Such an aggre can be found for pressures of several hundred bars gat, for example, in German Patent 23 00 569. There is a Piston shoe dipped into a recess so that it passes through the walls the recess is prevented from dropping by the piston. Thus, the Piston head on the entire cross-sectional area of the piston the piston shoe wear and thereby allow the several hundred bars. But is the piston hub limits, which limits performance.

In the European OS 01 02 441 you can find in FIGS. 12 and 13 a piston shoe which has extensions which plunge into the recess and which extend to the center of the swivel connection between the piston and the shoe. As a result, the piston stroke was extended beyond that of the aforementioned German patent.

But even this arrangement cannot last for several thousand bars be used because the barrel at several thousand bar of fluid pressure The area of the piston shoes is large compared to the cross section of the piston have to be. The piston is then relatively thin and requires guidance, which is missing in the European publication mentioned. Although this can Disclosure guide the piston shoe when its axis with the of the piston is in alignment. But then there is no lateral force. The lateral force occurs, as the present invention recognizes, only when the The axis of the piston shoe swings away from that of the piston. Then but the butt of the European patent application has no leadership more because the outer surface of the piston shoe then from the wall of the Recess is pivoted away.

On the other hand, axial boosters are off numerous patent documents known, the prints up to several generate a thousand bars. But they lack uniformity of funding, because they work with only two pistons.

Accordingly, the known technology is still defective need to be corrected and a multi-piston is still missing Pump with high delivery uniformity by at least three or  more pistons for pressures up to a thousand bar.

The invention is therefore based on the object of an arrangement to create that allows high pressures up to a thousand bar and that too can be used in units with multiple pistons, the piston and the piston shoe also pressures when used in a single piston machine allow from over a thousand bar.

This task is performed according to the characteristic part of the patent claims 1 solved and further perfections by the current one Invention are described and defined in subclaims 2 to 33.

Figs. 21, 22 and 29 to 31 to bring panels, graphs or figures for detecting the basis of calculation or for explaining the mathematical and geometrical principles of the invention, while all other of FIGS. 1-43 sections or views showing the embodiments of the invention.

Description of the embodiments

In Figures 1, 2, 8, 9 and 14 is seen in a housing. 57 - 442 a Kolbenhubantrieb 445, arranged 446 with the piston guide surface 570, which presses against the tread 465 of a piston shoe 447 having a support bed 558 (Fig forms. 6, 7) for the pivotable therein piston head 448 of the piston 5. The piston 5 is reciprocable in the cylinder 11 , and this reciprocal movement of the piston in the cylinder is driven by the piston stroke surface 570 .

In the figures mentioned and in addition in FIGS. 6 and 7 there is an essential feature of the invention, namely:
that the piston 5 is associated with a pivotable piston shoe 447 , a swivel part 449 of the piston shoe partially engages around the piston head 448 , piston head and swivel part form first surfaces 547 , 548 with approximately the same radii 560 , 460 around a common center 546 , the swivel part 449 of the piston shoe protrudes in both axial directions beyond the common center and forms an outer surface 468 with a second radius 461 around said common center, the second radius being larger than the radii of the first surfaces, the piston shoe pivoting part at least partially in an elongated manner Space 559 of body 442 is placed and space 559 forms at least one inner wall surface 451 at a distance from the axis of space 559 , which corresponds approximately to the aforementioned second radius of the pivoting part of the piston shoe.

It is thereby achieved according to the invention that the outer surface of the piston shoe, which is designed with the second radius, is at all times the same distance from the axis of the piston and consequently is guided at all times of the pivoting movement of the piston shoe on the inner wall surface 451 of the space 559 can. Through this possi bility, which is created by the invention, the piston can become thin because the piston shoe prevents the kinking of the thin piston by its guidance on the wall surface 451 . By this basic measure of the invention, the piston can thus allow high pressures and the piston shoe can be given extensive bearing surfaces in order to press the thin piston with high force into the cylinder 11 and thus convey fluid out of the cylinder 11 at pressures of over a thousand bar.

In the figures mentioned, the following versions of the invention can be found, which serve operational safety and the generation of high pressures; these characteristics are in particular the following:
that a part of the outer surface 468 of the piston shoe swivel is partially guided on said inner wall surface 451 of the space 559 ,
and or;
that said radii form said surfaces as partially cylindrical or spherical surfaces and the inner wall surface 451 is cylindrical or is replaced by two parallel flat surfaces,
and or;
that the reciprocating piston 5 extending from the piston head 448 is arranged reciprocally in a cylinder 11 and the axis of the cylinder is aligned with the axis of the space 559 ,
and or;
that from the cylinder 11 forming body 57 a cylinder nose 454 extends into the space 559 ,
and or;
that the piston head and a part of the cylinder body form seats for compression springs arranged between them and these seats are arranged radially outside of said cylinder nose 454 ,
and or;
that a part of the swivel part 449 of the piston shoe 447 is arranged to be movable radially outside the cylinder nose 454 past the tip of this nose in the space 559 ,
and or;
that at least one conical surface 446 with an angle 469 is arranged on the piston shoe from the first surface 558 in the axial direction of the piston 5 , ie away from the tip of the piston head;
and or; also according to FIGS. 32 to 40;
that the piston shoe on its first surface 558 facing away from the axial end forms in a manner known per se a guide surface 465 which forms a radius 462 around the center of a lifting drive 444 ,
and or;
that the projection of the peripheral length of the guide surface 465 corresponds to approximately 75 to 100 percent of twice the radius 465 of the stroke drive 444 , as in FIG. 15,
and or;
that the largest cross section of the piston head is at least five times larger than the cross section of the piston 5 ,
and or;
that the guide surface 465 in the running direction relative to the stroke drive front end forms a bevel 464 at a narrow angle relative to the piston stroke guide surface 570 of the stroke drive to form a hydrodynamic supporting wedge and from approximately the center of the guide surface a line directed towards the piston head 448 458 extends through the piston shoe 447 .

In a known manner, the piston 5 in the cylinder 11 must perform an alternating inward and outward movement. This movement is the piston stroke. In FIGS. 1, 2, 8 and 9 are found which are also known drive arrangement for this stroke. For this purpose, a shaft 445 is mounted in the housing part 442 , which drives, for example via wedge 446, at least one eccentric 444 , the outer surface 570 of which forms the piston stroke guide surface. The tread 465 ( FIGS. 6, 7) of the piston shoe 447 slides on it. At the other end, the piston shoe forms the pivoting bed 558 for the pivotable mounting of the piston head 449 of the piston 5 therein. As the eccentric 444 rotates, the piston 5 is thereby moved out and in in the cylinder 11 . The cylinder must also be connected to a fluid inlet 410 and a fluid outlet 411 in a known manner. It is also known that inlet and outlet valves 138 and 139 should be arranged for high pressures. Likewise, it is known that one can promote directly from the cylinder 11 to the valves, or that one between the cylinder 11 and the valves in an outer chamber 135 connected to the cylinder and an inner chamber connected to the valves vibrating and separating them Can arrange membrane 58 . Here, the diaphragm 58 is between the bodies 57 and 404 by means of the screws 4 - 66 clamped sealing. This membrane arrangement can also be found in FIG. 5.

Fig. 1 also shows that the cylinder 11 at the level of the outer dead center of the piston 5, a fluid fill line 401 can be connected and the cylinder 11, an overpressure or safety valve 402 can optionally be connected to spring tension 403 . According to the invention, the body 57 , in which the cylinder 11 is formed, is provided with a cylinder nose 454 for the extended guidance and sealing of the piston 5 . A compression spring 453 can be arranged around this cylinder nose, which presses directly or indirectly onto the rear wall of the piston head 448 and serves for the outward stroke of the piston 5 . According to the invention, a guide sleeve 452 can also be arranged in the body or housing 442 to form the inner wall surface 451 , on which the outer surface 450 of the piston shoe swivel part formed by the second radius is guided. Since the outer surface with the second radius is formed around the same center as the first radius of the piston head and swivel bed, each point of the outer surface 450 always has the same distance from the common center. This enables the piston shoe to be guided in room 559 , which was not previously secured before the present invention. The body 57 can be centered in the housing 442 by means of a flange 455 and sealed by means of a sealing ring bed 456 .

The diaphragm 58 can be touched on its clamping part by relief or leakage collecting channels 61 , 62 and by sealing ring beds or sealing ring grooves 405 and 406 .

According to the invention, FIGS. 1 and 2 also show that channels (without reference numerals) can extend from the inner chamber 137 through the cover 404 to its rear plane surface 591 . In the cover 404 there are threads for the screws 409 holding the holder 408 . The bracket has a lower flat surface and the connecting lines. One sees inlet line 410 and outlet line 411 .

According to the invention, is arranged between the described flat surfaces of the cover 404 and the holder 408 of the valve housing 407 . In it are the inlet valve 148 and the outlet valve 139 , which may have corresponding sealing ring beds 412 to 415 , in which the sealing means of FIG. 4 can be inserted for sealing. The particular advantage of this design according to the invention is that the screws 409 can be loosened somewhat and then the valve housing 407 can be taken out to the side, for example in FIGS. 1 and 2 to the front, and a new one can be inserted when the valves are worn. This is important, because in practice unscrewing lines 410 and 411 could result in loss of time and, above all, contamination.

Fig. 2 shows the arrangement according to the invention of a pressure chamber with an axially movable pressure body 432 sealed therein for pressing its sealing ring nose 431 against the membrane 58 . This embodiment of the invention is shown in more detail in FIG. 5.

Fig. 8 shows that the unit can be used as a hydraulic pump (or motor) for very high pressures. The membrane 58 is then omitted. However, a self-pressing sealing arrangement can be formed for the piston 5 . Fig. 8 shows an outer chamber 472 connected to the cylinder 11 surrounding a cylinder part 437 , as a result of which the pressure in the chamber 472 compresses the cylinder part 473 somewhat, i.e. narrows the gap to the piston 5 , because the outer diameter of the cylinder part 473 is larger than its inside diameter is such that there is more force on the outside than on the inside. In this case, 8 a short axial sealing surface (sealing lip) 475 between a rear extension 474 and a front inlet chamfer 476 is formed in Fig.. If the fit gap between the main part of the cylinder 57 and the piston 5 is leaked, i.e. expanded, it seals less and the pressure in the chamber 474 is reduced. The pressure difference on the cylinder part 437 between the radially outside and inside then becomes larger and the arrangement according to the invention then creates a larger diameter reduction of the cylinder part 473 , that is to say an automatically occurring sealing of the piston 5 by the cylinder part 473 . The dashed line 477 is intended to indicate that the cylinder part 473 can also be an insert. This is sometimes desirable in order to be able to use a different metal or material for the sealing lip 475 than is used for the master cylinder 57 .

Fig. 9 still shows that from the main piston 4 from a thinner high-pressure piston 479 can be operated in a narrower high-pressure cylinder 478 . A space 482 is then arranged which touches both middle ends of the piston and is relieved by means of a line 483 , so that no compression can occur in space 482 due to piston movement.

Fig. 9 is therefore a unit for particularly high pressures of several thousand bar. Thus, the cylinder 478 under the high pressure little or no expansion of the Passungs-gap undergoes the piston 479, a sealing cylinder is let into the main cylinder 57 480 and compressed therein . For example, the master cylinder 57 is formed with an inner diameter narrower relative to the inner cylinder 480 , then heated and placed over the inner cylinder 480 when hot. When the outer cylinder cools down, the inner cylinder is then compressed so that it contains higher tension and the inner diameter of the high-pressure cylinder 478 expands less when the internal fluid pressure is high.

Since, at the high pressures in assemblies of the invention, the screws 4066 can fatigue or age under the alternating load, that is, they can lengthen, narrow gaps may form around the membrane 58 over time. These must then be sealed, and such sealing is not possible with previously known seals. The same applies to the sealing of the lines by the cover of FIG. 1 or 2.

In the sealing ring groove (s) 412 , 405 , 406 , etc., therefore, a corner support ring 427 , 418 , 423 is inserted according to the invention, which is made of strong metal, in principle triangular cross-section with weakly machined or machined parts so inserted that the corner support ring or corner sealing ring touches a wall of the groove and the membrane 58 with at least one line each. When the membrane opens a gap, the corner ring follows the membrane and remains in contact with the membrane. In order to prevent extrusion of the soft sealing ring material of the pressure chamber, the other end of the sealing ring groove has inserted too thin a retaining ring with a U- or V-shaped cross section 429 , 420 , 424 , which is thin and flexible due to the possible movements of the membrane 58 can follow. The actual sealing ring made of flexible sealing material, such as a ring made of rubber, Teflon, Jurakon, graphite-Teflon, carbon-Teflon, glass-Teflon, Polimeid-Teflon or the like, is inserted between the relevant corner ring and the relevant retaining ring.

In FIG. 5, it is important that the pressure body 432 forms the sealing ring nose 431 for contact with the membrane 58 with the outer diameter "d" and the inner diameter "delta", while the pressure body 432 has the outer diameter "D" with which it seals into the the pressure chamber 440 connected to the cylinder is inserted. The pressure from the back of the pressure body presses the ring nose 431 against the membrane 58 and seals it because outside of the ring nose 431 the discharge chamber 430 connected by line 441 with low pressure is formed between the diameters "D" and "d". This difference in diameter determines the contact pressure with which the ring nose 431 is pressed against the membrane 58 . To seal the pressure body 432 in the pressure chamber 440 , a sealing ring groove 433 with a built-in corner ring 434 , retaining ring 435 and sealing ring groove 436 is again arranged. Likewise, a chamber 438 can be arranged to receive a pressure spring 437 . A cylinder extension 11 'of the cylinder 11 may extend through the pressure body 432 and have a slightly larger diameter than the actual cylinder 11 .

FIGS. 6 and 7 one can see the actual parts of the piston shoe OF INVENTION to the invention, which are described for the most part already based ande rer figures. End surfaces 470 are advantageously formed at the lateral ends so that they can be guided on the guide rings 507 of FIG. 14. Fig. 6 shows particularly clearly, the first and second radii 460 and 461 about the common center 546, while Fig. 7 shows the cones 466 axially above the pivot bed with the pivoting bed surface 467th These cones 466 prevent the compression springs from striking piston shoe parts. Fig. 7 shows that on the tread 465 of the piston shoe hydrodynamic rapid wedges 464 can be formed, for example, by grinding a radius 463 which is somewhat larger than the tread radius 462 , or by means of lips on a shaft with radius 463 in a simple manner can manufacture. The width "B" of the piston shoe is important for the guidance on the walls 507 of FIG. 14, and it usually corresponds to twice the second radius 461 .

Fig. 10 shows the connection of the piston 5 and 479 of. The piston 479 may be an expensive shaft made of sapphire or tungsten carbide or similar expensive material and therefore have the same outer diameter throughout because a one-piece collar would be too expensive. Then, a ring is shown in FIG. 10 assembled 489 with a press fit around one end of the piston 479, to the case of play by the ring 489 narrower inner diameter than the outer diameter of the piston 479 and is placed after heating of the ring 489 on the piston end, so that after cooling, the ring 489 firmly adheres to the piston 479 . The piston 479 can then be held in the recess 490 of the piston 5 by means of the locking ring 487 and the spacer ring 488 .

FIGS. 11 and 12 show seals of the high-pressure plunger 479 by means of lip ring 495, spread by inner spring lip ring 500 and behind the lips arranged polymeric support rings 496 or slanted support rings (gekonte support rings) 497, 498 and front, channeled retaining rings 493 and Rooms 492 . The channels 494 mentioned pass through the rings 493 .

In Fig. 13 it is shown that the piston and piston shoe arrangement according to the invention can also be arranged in axial piston units. One then has the following design, which can be seen from the fact that the space 559 ', the piston 4 ', the cylinder 11 ', the cylinder nose 454 ' and the inner wall surface 451 'parallel to the axis of the linear actuator 503 , that is, axially directed are, as well as the tread 504 of the piston shoe and the piston stroke guide surface 505 are designed as flat surfaces.

To summarize what has been described so far, one can see in particular the following embodiments of the invention, which emerge from the fact that an outer chamber 135 , possibly a safety valve 401 and, in the outer dead center position of the piston 5, a fluid supply line 401 are connected to the cylinder 11 , as in FIG. 1;
that the outer chamber 135 is closed by a membrane 58 , beyond the membrane an inner chamber 137 connected to inlet and outlet valves 138 , 139 is formed in a body 404 and the membrane 58 with its radially outer part between the inner and outer Chamber-forming bodies 57 and 404 is clamped sealingly, such as. B. in Fig. 1, 2, 5, 9;
that the sealing clamping of the membrane 58 touching the membrane and in at least one (or both) body 57 , 404 extending sealing ring beds 405 , 406 and / or pressure relief grooves 61 , 62 are formed, and, according to FIGS. 3, 4, etc. ;
that in the sealing ring grooves (the sealing ring groove) corner sealing rings 418 (a corner sealing ring 418 ) with a substantially triangular cross-section, one of the groove walls and part of the diaphragm 58 are inserted (is) near the other radial end of the sealing ring groove in question (the one in question) Sealing ring bed) 405 , 406 a resilient sealing ring retaining ring 442 is inserted and between the respective corner sealing ring and the relevant retaining ring a membrane 58 sealing sealing ring 419 is arranged, or, as in FIGS. 2 and 5,
that the cylinder 11 is connected to a pressure chamber 440 , a pressure body 432 is axially movably fitted in the pressure chamber, the pressure body forms an annular lug 431 which closes an outer chamber 135 radially outward, protrudes in the direction of the membrane 58 and contacts the membrane, radially outside the ring nose 431 a low-pressure chamber 430 is formed and a corner sealing ring 434 is inserted between a wall surface of the pressure chamber and a rear part of the pressure body, or;
that the ring nose 431 the inner diameter "delta" and the outer diameter "d", the pressure body has the outer diameter "D", a low-pressure space is formed between the diameters "d" and "D" and the outer diameter "D" of the body is larger, than the outside diameter "d" of the nose,
or, as for example in FIGS. 1, 2 and 9,
that channels extend from the inner chamber 137 to the rear end surface 591 of the body 404 , on the end surface 591 a valve housing 407 containing the inlet and outlet valves is placed and is tensioned by a line connector body 408 against the surface 491 during a loosening of the Holding screws 409 are arranged for removing and inserting the valve housing without removing the lines 410 , 411 , and the body and screws are arranged, or, according to FIG. 8,
that an axially short, sealing lip 475 surrounding the piston 5 in places is arranged on a part 473 of the wall 57 of the cylinder 11 , or, according to FIG. 1,
that the piston 5 is a extends from it in the piston head its abgewand th towards a relatively thinner to him piston 479 and a piston, both ends touching area 482 are arranged with a relief line 483, and to Fig. 10,
that the thinner piston 479 is a shaft with the same outer diameter throughout, at its rear end a 489 z. B. is attached by a press fit and the ring 479 is held together with one end of the thinner piston 489 in a recess 486 in the thicker piston 5 .

Further important arrangements of the invention are, according to FIGS. 35 to 37,
that the guide surface 465 is broken into the piston shoe into it extending grooves 575 , transverse to the relative running direction extending groove parts 576 and z. B. parallel to the relative running direction extending groove parts 577 are formed, between the groove parts arranged transversely to the relative running direction, webs 578 are formed with short bearing surfaces 580 in the relative running direction, from one of the groove parts a line 458 directed toward the piston head 448 through the piston shoe 447 extends and forms at the rear end of the guide surface 465 in the relative running direction, the end web 579 which closes the grooves and the bearing surface 581 which closes the grooves, according to FIGS. 14 and 17 to 20,
that a stroke drive 445 , 444 for pistons 5 that can be reciprocated in cylinders 11 is arranged in an assembly, three cylinder groups IIA-HC are placed one behind the other in the direction of the axis 582 of the stroke drive, and each of the cylinder groups has an individual piston stroke guide surface 582 that is eccentric to the stroke axis 582 ( 570 to 574 ), the eccentricities A, B and C of the three guide surfaces being rotated relative to one another in an angular manner and the running surfaces 465 of the piston shoes 447 concerned, the relevant guide surfaces 570 , 571 , 572 , 573 or 574 of the lifting drive 444 -A, 444 - Touch B or 444 -C, according to Fig. 18 and 20;
that in each of the three cylinder groups angularly offset from one another by 120 degrees, there are three cylinders 11 , the axes of which, viewed in the direction of the axis of the linear actuator, lie one behind the other and the second eccentric guide surface of the linear actuator is offset by 160 degrees to the first, the third to the second Is offset by 160 degrees and an angular offset (FIGS . 18, 20) of 40 degrees remains between the third and the first of the said guide surfaces, according to FIGS. 17 and 19,
that three cylinders are arranged in each of the three cylinder groups 11 -A, 11 -B, 11 -C, the three cylinders 1 , 2 , 3 of the first group being oriented at an angle of 120 degrees relative to one another, the cylinders 4 , 5 , 6 of the second of the groups are offset clockwise by four tens of degrees relative to the cylinders 1 , 2 , 3 of the first group and the cylinders 7 , 8 , 9 of the third group in a clockwise direction relative to the cylinders 4 , 5 , 6 of the second group rotated by forty degrees, or the relative angular differences are counterclockwise, and the three piston stroke guide surfaces 570 , 573 , 574 are offset perpendicular to the piston stroke drive axis 582 by 120 degrees relative to each other, according to FIGS. 23 and 24,
that three cylinder groups 523 , 524 , 525 , each with three cylinders, are arranged axially one behind the other, a bore 519 sealingly enclosing a control shaft 517 and lines 526 , 527 , 528 extending from the cylinders to the bore and to the control shaft are arranged, the control shaft has an inlet channel and For each of the cylinders, a control orifice and a pressure fluid line 520 connecting the orifices and the feed line 522 are contained, and two of the control orifices 529 , 530 , 531 are angularly offset from one another by forty degrees, while the other control orifices are directed at an angle of 160 degrees to one another are arranged,
or that according to Fig. 41,
that a filling pump is connected to a cylinder, or that the filling pump, possibly via a pressure accumulator, fluid is connected to a cylinder of the unit via a non-return valve under a pressure which is almost the same as the delivery pressure of the unit, thereby providing an arrangement for rapidly filling the relevant cylinder with precompressed fluid is hit.

These further and previously described arrangements of Invention are made in particular for the following reasons:

The piston units for under a thousand bar have five to 7 pistons per piston group. The piston shoe treads are too small to be able to press pistons against pressures of several thousand bars. The invention has correctly recognized this and eliminates the problem in that with one piston per piston group, as shown in FIG. 15, the projection of the running surface of the piston shoe can correspond to twice the radius of the eccentric 444 . The projection then has the length L = D = 513 and the tread itself is pi / 2 times longer, that is 2 times the radius 462 (of FIG. 6) times 1.57. Such length enables high load capacity and thus high pressure in the cylinder.

According to the invention, a maximum of three cylinders and pistons per cylinder group are therefore arranged for very high pressures. This can be seen in FIG. 16. The piston shoe tread projection then becomes approximately 75 times the diameter “D” of the eccentric 444 , that is to say still sufficiently long. Namely, if one looks again at FIG. 16 with FIG. 6, 0.75 times twice radius 462 of the eccentric times 1.57.

With only three pistons in only three cylinders, the delivery is very non-uniform. The unit cannot then be used for water jet cutting without a pressure accumulator. This is a major disadvantage of the well-known three-plunger pumps. At high pressures, the level of support is much higher. This can be seen from Fig. 31, in which in the calculated example the fluctuation in the delivery flow is between 0.74 and 1.18 m-meter per second piston speed, because at 4000 bar and diaphragm pump the first 25 percent of the pressure stroke is required to compress the fluids will. The pistons then only deliver after the eccentric has turned 20 degrees.

The invention overcomes this disadvantage recognized by it in that three cylinder groups, each with three pistons, are arranged axially one behind the other. This is shown in FIGS. 14, 17 to 18, 26 to 28, 17 to 20 or FIGS. 23 to 25.

Such arrangements are not possible without further measures of the invention. For even need to Fig. 14, the piston shoes laterally by guide rings 507 are chert gesi against axial displacement. Each piston shoe group is therefore assigned a first guide ring 507 at one axial end and a second guide ring 507 at the other axial end. Otherwise, FIG. 14 shows the position of the bearings, eccentrics and piston or cylinder groups relative to one another.

Another problem that the invention recognizes is that it is not yet possible to achieve delivery uniformity by simply arranging three piston groups one behind the other, each with three cylinders. The delivery inequality would be just as great as with the three-plunger pumps, i.e. as in the left side of FIG. 31.

Therefore, in order to achieve high delivery uniformity through three cylinder groups, each with three cylinders, special additional inventions must be used. Either one has to build according to FIGS. 18 and 20 or according to FIGS. 17 and 19. In Fig. 18 the axes of the cylinders (and pistons) are exactly axially one behind the other. Then according to the invention the eccentrics must have a special angular rotation according to the invention relative to each other. Between two eccentrics A and B or B and C of FIG. 20, the angular rotations must be 160 degrees, while that between two eccentrics A and C may only be 40 degrees. This is a surprise and in itself not easily conceivable, but necessary according to the invention, as shown in FIGS. 21 and 22.

On the other hand, if you do not want this so different, but easy to manufacture, angular displacement of the eccentric of Fig. 20, then you can use the same 120-degree angle adjustments A, B and C of Fig. 19, but then the cylinders 4 , 5 , 6 of the second cylinder group compared to the first cylinder group 1 , 2 , 3 rotated by forty degrees in the same direction and in the same direction, the cylinders 7 , 8 , 9 of the third cylinder group must be 40 degrees relative to the second , so be rotated by eighty degrees relative to the first cylinder group.

In addition, the supply lines of the individual cylinders beyond the valves must be connected to one another to form a common drain line, as shown in FIGS . 26 to 28. The inlet lines are 5401 to 5403 , while the drain lines are represented by 5411 to 5413 . The drain lines must, for. B. via lines 543 , 544 to a common high-pressure drain line 545 , see Fig. 27, 28, so that a low-pulsation high-pressure fluid stream is formed in the drain line 545 .

Table 21 of FIG. 21 shows the beginning of the respective pressure stroke of the respective piston for the FIGS . 17 with 19 and 18 with 20 at the relevant rotation angle "alpha" of the shaft or the eccentric.

Fig. 22 is then, of which angle "alpha" up to what angle "alpha" to perform the piston in question the pressure stroke.

The stroke movements of the pistons can be calculated very precisely on the basis of the invention, specifically according to FIG. 29. The piston stroke is "S" and can easily be calculated from the relevant formula. The calculation formulas for the piston speed “V” and the piston acceleration “b” are also recognized and shown in FIG. 29 by the invention. For an assembly with "g" = 18 mm, "R" = 30 mm and "e" = 8 mm, the piston speed "V" in m / s is obtained at 1000 revolutions per minute. The promotion is piston cross section times piston speed "V". This makes "V" the most important value in Fig. 30. The piston stroke itself is not dependent on the speed of the shaft, but only on the angle of rotation "alpha". The acceleration is needed to calculate the mass forces.

In FIG. 31, the speeds of the pistons are plotted and summed in the left part, in the right part between 200 and 320 degrees of the rotation angle "alpha" they are given and the summation for the nine pistons of FIGS. 17 to 20.

The invention also recognizes that the promotion can not begin immediately with the piston pressure stroke when high pressures of z. B. 2500 to 4000 bar in the common drain line 454 of FIG. 28 prevail. Because the exhaust valves can only open when the fluid in the cylinder is compressed to the same pressure that prevails in said common drain line 454 . For example, 25 percent of the pressure stroke movement is assumed for the compression of the fluids in the cylinders 11 and chambers 135 , 137 . According to FIG. 30, this is the case with a piston stroke of approximately 4 mm, ie approximately 20 degrees with “alpha”. See "V" over "alpha" in Fig. 30.

The delivery of the piston in question therefore only begins when the pressure stroke has already been active at 20 degrees alpha. This can be seen in Fig. 31 and it leads to the non-uniformity 1.18 minus 0.74 = 51 percent, ie much higher non-uniformity than in low-pressure operation. With the 9 pistons between 200 and 220 degrees, under the same conditions, the non-uniformity is still 3.28 minus 2.83 = 0.45 to 2.83 = 15.9 percent.

This non-uniformity can be radically reduced by the invention with the aid of FIG. 41. The supplier 593 (for example a pump 593 driven by the motor 592 ) may connect a pressure fluid supplier 595 to the line 401 of FIGS. 1, 41 etc. via pressure accumulator 594 and lines 594 . As a result, the cylinder 11 is immediately filled with high-pressure fluid in the outer dead center position of the piston 5 . The piston stroke is then a high-pressure fluid delivery stroke immediately from the relative rotation angle "alpha". This is shown in dashed lines in the right part of FIG. 31 and brings the dashed summation of the conveying speeds of the nine pistons between angles "alpha" = 200 to 320 degrees. You can now see 3.28 minus 3.20 = 0.08 to 3.20 = only 2.5 percent non-uniformity in the flow rate. The effect of the invention is very high and the flow rate is now sufficiently uniform to be used for water jet cutting without a pressure accumulator in the delivery line.

In Figs. 23 to 25, the unit is driven by a medium pressure fluid flow. The medium pressure fluid flows through line 534 via line 520 in a rotating control shaft 517 via control orifices 529 , 530 and 531 from the individual cylinders 523 to 525 through the cylinder channels 526 to 528 . Since the cylinder groups are arranged axially one behind the other, there must be an angle difference of 160 degrees between the control ports 531 and 530 and between 530 and 529 in the sense of FIG. 20, but only forty degrees between the control ports 531 and 529 . This is shown in FIG. 25, while FIG. 24 is the cross section through the inlet line of FIG. 23. Also in these Figs. 23 to 25, the high-pressure discharge lines of the individual cylinders must be reconnected to a common high pressure outlet line 545 in the sense of Fig. 28, in order to achieve relatively uniform flow. The control shaft 517 can be driven, for example, by a fluid motor (not shown in the figure) which is driven into the return flow from lines 521 .

The Figs. 32 to 40 show alternatives for the Formge collar of the piston head and the piston shoe. In Fig. 32, 33 piston head and swivel beds 558 are spherical, but in Fig. 35, 36 they are cylindrical. This can be seen when looking at FIGS. 35 and 38, and 36 and 39, which see the parts in question rotated by 90 degrees. See the arrowed section lines in Figs. 36 and 39.

Fig. 34, 37 and 40 show alternatives for the running surfaces of the piston shoe. In Fig. 34 two hydrodynamic inlet wedges 464 are arranged, but in Fig. 40 only one, namely in the relative running direction to the piston stroke surface 570 at the front. In Fig. 37, the embodiment is shown for long same relative velocities in which no sufficiently strong hydrodynamic bearing fields may arise. One can see in the running direction from the front the inlet grooves 557 , which are also connecting grooves to the transverse grooves 576 . Between the transverse grooves 567 supporting bearing fields 578 are formed, which are lubricated from transverse grooves 576 and 576 'and must be short in order to reduce hot running in the relative running direction.

The bores 458 extend from the running surfaces through the piston shoe to the swivel bed 558 in order to lubricate the piston head in the swivel bed. It is useful and often necessary to provide the inner chamber 443 in the housing 442 with low pressure lubricating fluid under several atmospheres pressure, to ensure lubrication of the piston shoes and swivel joints, if no oil level in the cylinder 11 is formed, the Zylin of 11 ie with no lubricating fluid, for example with water. Then the leakage of the fit gap between piston 5 and cylinder 11 is to be separated from the inner chamber 443 of the housing 442 by an interposed seal.

If the eccentricity "e" is large compared to the diameter of the eccentric, the piston stroke becomes long and the swivel angle of the piston shoe becomes large. Then, at the high pressures in the unit, high force components arise on the surface with the second radius and on the inner wall surface 451 of the chamber 559 . This can lead to wear of the piston shoe outer surface with the second radius 461 and wear to the wall surface 451 . To prevent this wear, the piston shoe swivel part according to FIGS . 42 and 43 can be surrounded with a guide bush 601 , 602 . This is then divided in two by the slot 603 and inserted around the piston shoe swivel part between the latter and the guide surface 451 of the chamber 559 . A pin 604 can be arranged to secure the guide sleeve against rotation. The pin 604 then protrudes somewhat into the piston shoe, as can be seen in FIG. 43. You can still see the inner surface 608 of the guide ring formed as a spherical partial surface with the radius 608 , which then corresponds approximately to the second radius 461 of the piston shoe. The outer surface of the guide ring 601-602 is a cylindrical surface 609 which has a radius matching the guide surface 451 of the chamber 559 . According to the inventor's German patent specification 14 53 433, a tangential pressure balance 605 , 606 , 607 plus control by the piston head can be arranged.

If the unit of the invention as an oil-producing high pressure pump is inserted, the piston shoe can still be designed to be reliable, by giving it oil pressure in places for hydrostatic storage leads.

However, if the piston 5 in question presses against water or other non-lubricating fluid, no pressure fluid can be removed from the cylinder 11 for piston shoe lubrication purposes. A piston shoe for high pressures then particularly urgently requires training and dimensioning according to the present invention. The inner 443 of the housing 442 should then be filled with lubricating fluid under some atmospheric pressure, if possible, so that the running surfaces and pivoting surfaces of the piston and the piston shoe are somewhat lubricated.

If the unit of FIG. 8 works against water, a piston seal with leakage drainage should be installed, as shown in dashed lines and partly analogously, as in FIG. 9.

The space 482 of FIG. 9 can also be used as a second pump if it is assigned inlet and outlet means.

If you want to use the arrangements according to the invention for pumping water at high pressure, then the arrangement of sealing rings with flexible lips for piston sealing in the sense of FIGS. 11 or 12 is the simplest solution. This is the most compact way of building the system. But some problems arise:

One is the life of such seals at high pressures and water as a pumped medium is relatively low. They hold about 200 plus minus 150 hours or about 150 kilometers plus minus 120 kilometers Stroke, depending on pressure and relative speeds. It also arises then the problem that there is a lack of lubrication of the piston shoe and the piston shoe with special attention to the details of the current invention must be built, otherwise it will overheat or its lifespan is too short.

The version with oil pressure level under a membrane, for example according to Fig. 1, is then more voluminous and complex. However, it has the advantage that the service life of the unit can then be 30 million strokes or ten thousand operating hours. Of course, only if the rules of this invention and its "know how" are strictly observed.

The units can also be used as high-pressure pulsators if the outlet valves 139 are dismantled.

Claims (33)

1. High-pressure arrangement (s) in high-pressure unit (s) in which fluid is admitted to a chamber which changes its volume periodically and is pressed out of the chamber by a pressure medium, characterized in that means for increasing the power, the pressure, operational safety, service life or efficiency are arranged. 2. Arrangement according to claim 1, characterized in that the piston 5 is associated with a pivotable piston shoe 447 , a pivot part 449 of the piston shoe partially engages around the piston head 448 , piston head and pivot part first surfaces 547 , 548 with approximately the same radii 560 , 460 form around a common center 546 , the pivoting part 449 of the piston shoe protrudes in both axial directions beyond the common center and forms an outer surface 468 with a second radius 461 around said common center, the second radius being larger than the radii of the first surfaces the piston shoe swivel part is at least partially placed in an elongated space 559 of a body 442 and the space 559 forms at least one inner wall surface 451 at a distance from the axis of the space 559 which corresponds approximately to the aforementioned second radius of the swivel part of the piston shoe ( Fig. 1, 2, 6, 7, 9 etc). 3. Arrangement according to claim 2, characterized in that a part of the outer surface 468 of the piston shoe pivot is partially guided on said inner wall surface 451 of the space 559 ( Fig. 1, 2, 6, 7, 9, etc.). 4. Arrangement according to claim 2, characterized in that the said radii form the said surfaces as teilzylin drische or spherical part-shaped surfaces and the inner wall surface 451 is a cylindrical or is replaced by two mutually parallel flat surfaces ( Fig. 1, 2, 9, etc. .). 5. Arrangement according to claim 2, characterized in that the piston piston 448 extending reciprocating 5 is arranged reciprocally in a cylinder 11 and the axis of the cylinder is aligned with the axis of the space 559 ( Fig. 1, 2, 9, etc.) . 6. Arrangement according to claim 5, characterized in that from the cylinder 11 forming body 57 from a cylinder nose 454 extends into the space 559 in ( Fig. 1, 2, 9, etc.). 7. Arrangement according to claim 6, characterized in that the piston head and part of the cylinder body form seats for compression springs arranged between them and these seats are arranged radially outside said cylinder nose 454 ( Fig. 1, 2, 9, etc.). 8. Arrangement according to claim 6, characterized in that a part of the pivot part 449 of the piston shoe 447 is arranged radially outside the cylinder nose 454 at the tip of this nose in the space 559 movable ( Fig. 1, 2, 9, etc.). 9. Arrangement according to claim 2, characterized in that at least one conical surface 446 with an angle 469 in the axial direction of the piston 5 , ie away from the tip of the piston head, is arranged on the piston shoe from the first surface 558 ( FIGS. 1, 2, 6, 7, 9, 13). 10. The arrangement according to claim 2, characterized in that the piston shoe on its first surface 558 facing away from the axial end in a conventional manner forms a guide surface 465 which forms a radius 462 around the center of a lifting drive 444 ( Fig. 1, 2, 6th , 7, 9, etc.). 11. The arrangement according to claim 10, characterized in that the projection of the peripheral length of the guide surface 465 corresponds to approximately 75 to 100 percent of twice the radius 465 of the stroke drive 444 ( Fig. 15, 16). 12. The arrangement according to claim 2, characterized in that the largest cross section of the piston head is at least five times larger than the cross section of the piston 5 ( Fig. 1, 2, 9, etc.). 13. Arrangement according to claim 10, characterized in that the guide surface 465 in the running direction relative to the stroke drive front end forms a bevel 464 at a narrow angle relative to the piston stroke guide surface 570 of the stroke drive to form a hydrodynamic support wedge and from about the middle of the Guide surface extends from a line 458 directed toward the piston head 448 through the piston shoe 447 ( FIGS. 6, 7). 14. Arrangement according to claim 10, characterized in that the guide surface 465 is broken through into the piston shoe into which it is extended grooves 575 , transverse to the relative running direction extending groove parts 576 and z. B. parallel to the relative running direction extending groove parts 577 are formed, between the transverse to the relative direction of the groove parts webs 578 are formed with short bearing surfaces 580 in the relative running direction, from one of the groove parts a 458 directed towards the piston head 448 through the piston shoe 447 extends and at the rear end of the guide surface 465 in the relative running direction forms a groove closing end web 579 with the grooves ver closing bearing surface 581 ( Fig. 35 to 37). 15. An arrangement according to claim 1, characterized in that in one unit a linear actuator 445 is positioned 444 for reziprozierbare in cylinders 11 piston 5, three cylinder groups IIA-HC 582 of the linear actuator are consecutively placed in the direction of the axis, and each of the cylinder groups, a Individual to the Huban drive axis 582 eccentric piston stroke guide surface ( 570 to 574 ) is assigned, wherein the eccentricities A, B and C of the three guide surfaces are rotated at an angle to each other and the running surfaces 465 of the piston shoes 447 in question the guide surfaces 570 , 571 , 572 , 573 or 574 of the actuator 444 -A, 444 -B or 444 -C touch ( Fig. 14 and 17 to 20). 16. The arrangement according to claim 15, characterized in that in each of the three cylinder groups angularly offset by 120 degrees to each other, three cylinders 11 are present, the axis of which is seen in the direction of the axis of the linear actuator, are one behind the other and the second eccentric guide surface of the linear actuator for the first offset by 160 degrees, the third to the second is offset by 160 degrees and an angular offset of 40 degrees remains between the third and the first of the said guide surfaces (FIGS . 18, 20). 17. The arrangement according to claim 1, characterized in that three cylinders are arranged in each of the three cylinder groups 11 -A, 11 -B, 11 -C, the three cylinders 1 , 2 , 3 of the first group being angularly relative by 120 degrees are directed towards one another, the cylinders 4 , 5 , 6 of the second of the groups are offset clockwise by four hundred degrees relative to the cylinders 1 , 2 , 3 of the first group and the cylinders 7 , 8 , 9 of the third group are displaced clockwise relative to the cylinders 4 , 5 , 6 of the second group are rotated by forty degrees, or the relative angular differences are counterclockwise, and the three piston stroke guide surfaces 570 , 573 , 574 are offset perpendicular to the piston stroke drive axis 582 by 120 degrees relative to one another ( Fig. 17, 19). 18. Arrangement according to claim 2, characterized in that the space 559 ', the piston 4 ', the cylinder 11 ', the cylinder nose 454 ', the inner wall surface 451 'are directed parallel to the axis of the linear actuator 503 , that is, axially, and the running surface 504 of the piston shoe and the piston stroke guide surface 505 are designed as flat surfaces ( FIG. 13). 19. The arrangement according to claim 15, characterized in that the cylinders are assigned beyond their exhaust valves 139 exhaust channels 540 , 5412 , 5413 which lead to at least one connecting line 544 and are connected in an end body part 542 to a common drain line 545 ( Fig. 26 to 28). 20. The arrangement according to claim 2, characterized in that the cylinder 11, an outer chamber 135 , optionally a safety valve 401 and in the outer dead center position of the piston 5, a fluid supply line 401 are connected ( Fig. 1). 21. The arrangement according to claim 2, characterized in that the outer chamber 135 is closed by a membrane 58 , beyond the membrane, an inner chamber 137 connected to inlet and outlet valves 138 , 139 is formed in a body 404 and the membrane 58 with it radially outer part between the bodies forming the inner and the outer chamber 57 and 404 is sealingly clamped ( Fig. 1). 22. The arrangement according to claim 1, characterized in that the sealing clamping of the membrane 58 touching the membrane and in at least one (or both) body 57 , 404 extending sealing ring beds 405 , 406 and / or pressure relief grooves 61 , 62 are formed ( Fig. 1, 3, 4). 23. The arrangement according to claim 22, characterized in that in the sealing ring grooves (the sealing ring groove) corner sealing rings 418 (a corner sealing ring 418 ) with a substantially triangular cross-section, one of the groove walls and part of the membrane 58 are used touching, is close the other radial end of the relevant sealing ring groove (the relevant sealing ring bed) 405 , 406 a resilient sealing ring retaining ring 442 is inserted and between the respective corner sealing ring and the relevant retaining ring a membrane ring 58 sealing ring 419 is arranged ( FIG. 3) . 24. The arrangement according to claim 2, characterized in that the cylinder 11 is connected to a pressure chamber 440 , a pressure body 432 is axially movably fitted in the pressure chamber, the pressure body a radially outwardly closing an outer chamber 135 , projecting in the direction of the diaphragm 58 and the membrane-contacting ring nose 431 forms, radially outwardly of the ring lug 431 a low pressure chamber 430 is formed between a wall surface of the Anpreßkammer and a rear portion of ring of the pressing body, a corner seal is inserted 434 (Fig. 2, 5). 25. The arrangement according to claim 24, characterized in that the ring nose 431 the inner diameter "delta" and the outer diameter "d", the pressing body has the outer diameter "D", between the diameters "d" and "D" a low pressure space is formed and the outer diameter "D" of the body is larger than the outer diameter "d" of the nose ( Fig. 5). 26. The arrangement according to claim 21, characterized in that from the inner chamber 137 channels extend to the rear end face 591 of the body 404 , on the end face 591 a valve housing 407 containing the inlet and outlet valves and placed against by a line connector body 408 the surface 491 is tensioned, while a loosening of the retaining screws 409, the removal and insertion of the valve housing without removing the lines 410 , 411 is possible, allowing the body and screws to be designed ( FIGS. 1, 2). 27. The arrangement according to claim 2, characterized in that a piston 5 surrounding in places, axially short, sealing lip 475 on a part 473 of the wall 57 of the cylinder 11 is angeord net ( Fig. 8). 28. The arrangement according to claim 2, characterized in that one of him in the direction of the piston head extends a piston thinner 479 relative to him from the piston 5 and a chamber 482 contacting both piston ends with a relief line 483 are arranged ( FIG. 9 ). 29. The arrangement according to claim 28, characterized in that the thinner piston 479 is a shaft with the same outer diameter throughout, at its rear end a 489 z. B. is attached by a press fit and the ring 479 is held together with one end of the thinner piston 489 in a recess 486 in the thicker piston 5 ( Fig. 10). 30. The arrangement according to claim 1, characterized in that three cylinder groups 523 , 524 , 525 , each with three cylinders are arranged axially one behind the other, a control shaft 517 sealingly enclosing bore 519 and from the cylinders to the bore and the control shaft extending line 526 , 527 , 528 are arranged, the control shaft an inlet channel and to each of the cylinder groups each contain a control orifice and a pressure fluid line 520 connecting the orifices and the feed line 522 , and two of the control orifices 529 , 530 , 531 are offset by forty degrees to one another, while the other control mouths are offset by 160 degrees angularly offset from each other ( Fig. 23, 24). 31. Arrangement according to claims 15, 16, 17, 30 or another of the claims, characterized, that a filling pump is connected to a cylinder. 32. Arrangement according to claim 31, characterized in that the filling pump, possibly via a pressure accumulator, Fluid under a pressure that is almost the same as the delivery pressure of the unit Pressure a cylinder of the unit via a check valve is connected and thereby an arrangement for quick filling of the cylinder concerned with pre-compressed fluid is. 33. Arrangement according to claim 2, characterized in that the piston shoe swivel joint part is surrounded by a guide ring such that the guide ring is divided lengthways through the slot 603 in two halves 601 and 602 , the inner surface of the guide ring a spherical surface with Radius 608 , where the radius 608 corresponds to the second radius 461 of the piston shoe 477 and the outer surface of the guide ring 609 is a cylindrical surface with a diameter matching the guide surface 451 of the recess 559 , the guide ring is the center point of the first and second radii of the piston shoe in both Exceeds directions parallel to the axis of the piston and the two halves are inserted around the piston shoe part with the second radius 461 between the piston shoe 447 and the inner wall surface 451 of the space 559 .