EP1635973B1 - Piston for a cold chamber die casting machine - Google Patents
Piston for a cold chamber die casting machine Download PDFInfo
- Publication number
- EP1635973B1 EP1635973B1 EP04739812A EP04739812A EP1635973B1 EP 1635973 B1 EP1635973 B1 EP 1635973B1 EP 04739812 A EP04739812 A EP 04739812A EP 04739812 A EP04739812 A EP 04739812A EP 1635973 B1 EP1635973 B1 EP 1635973B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- sealing ring
- pressure side
- annular
- piston part
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000004512 die casting Methods 0.000 title claims abstract description 14
- 238000007789 sealing Methods 0.000 claims abstract description 207
- 238000005266 casting Methods 0.000 claims abstract description 60
- 230000002093 peripheral effect Effects 0.000 claims abstract description 31
- 238000003780 insertion Methods 0.000 claims abstract description 3
- 230000037431 insertion Effects 0.000 claims abstract description 3
- 239000007769 metal material Substances 0.000 claims abstract 2
- 230000004323 axial length Effects 0.000 claims description 8
- 239000002826 coolant Substances 0.000 claims description 8
- 230000008878 coupling Effects 0.000 claims description 8
- 238000010168 coupling process Methods 0.000 claims description 8
- 238000005859 coupling reaction Methods 0.000 claims description 8
- 229910000831 Steel Inorganic materials 0.000 claims description 5
- 239000010959 steel Substances 0.000 claims description 5
- 239000012768 molten material Substances 0.000 claims 1
- 230000000149 penetrating effect Effects 0.000 abstract description 4
- 238000000926 separation method Methods 0.000 abstract description 3
- 239000000155 melt Substances 0.000 description 9
- 230000000694 effects Effects 0.000 description 8
- 238000001816 cooling Methods 0.000 description 6
- 239000000463 material Substances 0.000 description 6
- 239000002184 metal Substances 0.000 description 6
- 229910052751 metal Inorganic materials 0.000 description 6
- 210000002105 tongue Anatomy 0.000 description 6
- 230000008901 benefit Effects 0.000 description 4
- 229910000881 Cu alloy Inorganic materials 0.000 description 3
- 238000010276 construction Methods 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 239000000289 melt material Substances 0.000 description 2
- 230000035515 penetration Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000007711 solidification Methods 0.000 description 2
- 230000008023 solidification Effects 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 239000000110 cooling liquid Substances 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000005058 metal casting Methods 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B22—CASTING; POWDER METALLURGY
- B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
- B22D17/00—Pressure die casting or injection die casting, i.e. casting in which the metal is forced into a mould under high pressure
- B22D17/20—Accessories: Details
- B22D17/2015—Means for forcing the molten metal into the die
- B22D17/203—Injection pistons
Definitions
- the invention relates to a piston for a cold chamber die casting machine.
- the piston of a cold chamber die casting machine and in particular the sealing ring of such a piston is exposed to high pressures at relatively high temperatures of the molten metal, so that the piston and in particular its sealing ring are exposed during operation very high stresses that shorten their life, which is disadvantageous to the Productivity of the casting machine affects when wearing parts of the piston must be changed and the casting machine must be shut down for this purpose.
- the slotted sealing ring is arranged in a ring recess on the circumference of a low-pressure side to be fixed to the piston rod of the die casting first piston member.
- a high pressure side piston end forming the second piston part with a central axial screw is removably attached on the high pressure side of the first piston part.
- the second piston part limits the sealing ring receiving annular recess to the high pressure side and includes distributed in the circumferential direction a plurality of channels that lead into an annular gap between the annular recess and the inner circumference of the sealing ring.
- Cooled pistons are out US 5,048,592 and US 5,233,912 known.
- the pistons are designed as a cap, which encloses the high-pressure end of the piston rod.
- the piston rod together with the cap channels or annular spaces for a circulating cooling liquid, which cools the cap, in particular in the region of its high-pressure side end wall.
- a slotted sealing ring is arranged in the area of the end wall.
- the sealing ring may be formed as a stepped slot.
- the cap can be screwed or fixed with a bayonet connection.
- the bush rests with a relatively small end face on the shoulder of the piston rod, so that it can lead to deformations on the sleeve and the piston rod on the one hand and subsequently to the thread fixing the cap. This makes disassembly of the cap difficult.
- the thread of the cap is exposed to the coolant, so that it can cause corrosion damage and thus dismantling problems.
- a piston for a cold chamber die casting machine is known, the cap removably attached to a piston rod to be mounted on its peripheral wall a sealing ring.
- the cap comprises two in a dividing surface axially abutting, to a unit detachably fastened together piston parts, of which a first piston part is formed as a socket and a second piston part forms a bushing on the high pressure side closing end wall.
- the bush has a plurality of circumferentially distributed, axial through holes through which the end wall forming the second piston part is screwed by means of fastening screws.
- the sealing ring sits in a common circumferential recess of the two piston parts and can be removed after loosening the screws.
- the invention is characterized by the features specified in claim 1.
- the invention is based on a piston in the form of a cap on the high-pressure end of a in a casting cylinder of a cold chamber die casting machine axially displaceable piston removably attachable cap with a peripheral wall and the cap high pressure side closing end wall, wherein at least one sealing ring is disposed on the outer circumference of the peripheral wall this z.
- the cap in this case comprises two in a dividing surface axially abutting, to a unit detachably attached together piston parts, of which a first piston part is formed as at least a portion of the peripheral wall forming sleeve and a second piston part forms at least the end wall and the socket closes high pressure side.
- Such a cap is divisible so that it can be maintained easier than before.
- the two piston parts can each be better adapted to the operating requirements.
- the high-pressure side second piston part made of heat-resistant, wear-resistant material such as steel, which has the advantage that the end wall formed by the second piston part can be thinner than previously dimensioned, which benefits the piston cooling.
- the cap is split, it forms a rigid assembly that can be attached as a unit to the high pressure end of the piston rod.
- the casting pressure acting on the end wall can be transmitted via the peripheral wall of the cap.
- the high-pressure side end face of the piston rod bears against the low-pressure-side surface of the end wall and directly absorbs the casting pressure acting on the end wall.
- the fastening elements, in particular designed as a bayonet, for the detachable attachment of the piston to the piston rod are expediently provided on the first piston part designed as a bushing.
- a plurality of radially acting spring elements are arranged, which press the sealing ring radially outward.
- the spring elements reinforce the radial contact pressure of the radially elastic due to its inherent elasticity, slotted sealing ring, as it can be amplified by the pressure of the melt.
- the first piston part can, as is known, have a plurality of circumferentially distributed, axial through holes, through which the second piston part is screwed by means of fastening screws to the first piston part.
- the axial through holes may in this case be provided in the wall of the socket.
- the materials of these components can be selected according to the particular purpose of the components.
- the two piston parts can be made of different materials, in particular with regard to the strength and the thermal conductivity of different materials.
- first and the second piston part can also be detachably fastened to one another via a bayonet coupling.
- the mutually associated coupling members can be formed directly on the first and the second piston part.
- an intermediate ring with bayonet coupling members is also suitable both for the first coupling part and for the second coupling part, so that the two coupling parts are coupled to one another via this intermediate ring.
- the dividing surface between the two coupling parts is arranged on the low-pressure side of at least one sealing ring in order to prevent the penetration of melt into the cap.
- the dividing surface-forming end faces of the first and second piston part is preferably a sealing faces against each other sealing sealing ring arranged, which prevents the escape of coolant from the cap in the first place.
- the sealing ring is arranged in a ring recess on the outer circumference of the peripheral wall of the cap and overlaps at least partially axially with the first and / or the second piston part.
- the outer circumference of the dividing surface opens into this annular recess and preferably in such a way that the outer circumference of the dividing surface, with respect to the high-pressure-side sealing surface edge of the sealing ring, is offset towards the low-pressure side in the annular recess.
- the dividing plane expediently opens closer to the low-pressure end of the sealing ring than to the high pressure end. In this way, the penetration of melt into the cap is made considerably difficult or impossible. In particular, it is prevented that the fastening members, which connect the two piston parts together, caked together by penetrating melt and the dismantling of the two piston parts is difficult.
- the sealing ring is formed as a slotted sealing ring, in particular provided with a stepped slot sealing ring and the dividing surface between the first and the second piston part is offset with respect to the low pressure side edge of the sealing ring with axial distance to the low pressure side. Since the dividing surface lies completely on the low pressure side of the sealing ring, it is particularly easy to seal off.
- the low-pressure side projection of the second piston part allows the attachment of a locking pin engaging in the sealing ring for securing rotation.
- the sealing ring thus keeps in operation always the same angular position relative to the casting cylinder, which reduces the abrasion and improves the sealing effect.
- the locking pin may optionally also be attached to the first piston part and engages over the sealing ring on the second piston part.
- the above-mentioned sealing ring is axially fixed to the second piston part, that the dividing surface terminates in a ring recess surrounding the outer circumference of the first piston part and overlapping at least over part of its axial extension, and in that Ring recess at least a second sealing ring is arranged.
- the first sealing ring is arranged as a slotted sealing ring, so that it can be snapped onto the second piston part.
- the second sealing ring which is arranged to improve the sealing effect at an axial distance from the first sealing ring, can be installed in mutually separate piston parts in the annular recess of the first piston part.
- the second sealing ring is preferably a slotted sealing ring, which springs radially outward from the impression cylinder to an oversize.
- the second sealing ring is thus able to seal the piston not only with respect to the casting cylinder but also to guide radially in the casting cylinder. This is particularly advantageous if the radial guiding properties of the first sealing ring are neglected in favor of optimizing the sealing properties of the first sealing ring.
- the radially alsfedernde sealing ring has preferably at its high pressure side outer edge of a threading cone, so that the piston at the beginning of the casting stroke can be pulled out beyond the second sealing ring out of the casting cylinder. In this way, a high casting volume can be achieved without having to extend the casting cylinder accordingly.
- the second sealing ring is expediently wider to improve its guiding properties in the axial direction than the first sealing ring.
- the second sealing ring is preferably formed as a slotted sealing ring, wherein its edges forming the slot form at least one circumferentially projecting tongue and one of the tongue in the circumferential direction opposite recess into which the tongue engages axially closely fitting, but movable in the circumferential direction.
- each of the two edges forming the slot of the second sealing ring forms at least one tongue each.
- the dividing surface can end in a ring recess surrounding the outer circumference of both the first and the second piston part and axially overlapping both piston parts.
- the sealing ring may in this case be designed as a sealing bush fixed axially in the annular recess. Even if the sealing bush is not slotted and thus not formed radially resilient, it can effectively seal the piston against the casting cylinder with sufficiently tight tolerances. In this way, a simple and inexpensive piston can be provided in which the comparatively wide sealing bushing may consist of a copper alloy, while the first piston part and possibly also the second piston part may consist of a less expensive material, such as steel.
- the piston can be produced inexpensively if the first piston part is designed as a bush, in the wall of which the axial through holes for the fastening screws are provided.
- a bayonet connection is expediently provided for attachment of the piston to the piston rod.
- a suitable bayonet connection is for example in US 5,233,912 described.
- a suitable for snapping onto a cooled piston, slotted sealing ring is in US 5,048,592 ( EP 0 422 413 A2 ).
- the cap can be cooled at least in the region of the end wall of the second piston part by a cooling medium insertable into the cap, that the sealing ring in the region of the end wall on the outer circumference of the cap in a ring recess axially fixed, but movably arranged with play, that the second piston part projecting high pressure side over the sealing ring and radially overlaps the sealing ring over a portion of its radial thickness high pressure side with a projection whose outer peripheral surface adjacent the sealing ring high pressure side between itself and the casting cylinder in the Casting operation limited to freezing temperature coolable annular gap.
- the movable in the ring recess sealing ring remains sufficiently movable during operation to adapt to the shape of the casting cylinder due to its inherent elasticity.
- seals in the high pressure side of the sealing ring upstream annular gap solidified melt the ring recess and the Sealing ring so far that the mobility of the sealing ring is not unduly affected.
- the annular gap fills with melt, which, however, partially or completely solidifies in the annular gap before it reaches the sealing ring leading annular recess of the piston body.
- the melt solidified in the annular gap may remain in the annular gap or it may be scraped off in the course of the return stroke.
- the sealing effect can be further improved if the outer circumferential surface of the radially elastic annular body of the slotted sealing ring near its high-pressure side axial end has a for abutment against the inner peripheral surface of the casting certain, outer abutment annular surface whose axial length is smaller than the axial length a with this outer abutment annular surface axially overlapping, the melt, eg the molten metal exposable inner annular surface on the inner circumference of the annular body, wherein on the low pressure side of the outer peripheral surface of the annular body to the outer abutment annular surface over at least a portion of the remaining axial length of the annular body an annular surface portion connects, the diameter of which is smaller than the diameter of the outer abutment annular surface.
- the reduction of the area size of the outer abutment annular surface leads to eienr pressure increase in the sealing surface area, which improves the sealing effect. Due to the high radial contact pressure, the contact ring surface grinds better according to the cylinder shape of the casting cylinder.
- the lubricant introduced into the casting chamber prior to the molten metal may pass into the area of the reduced diameter peripheral surface of the seal ring during the pressure advance of the piston past the outer abutment annular surface. This accumulating on the low pressure side of the sealing ring lubricant lubricates the casting cylinder during the return movement of the piston.
- the reduced in diameter annular surface portion may have approximately truncated cone shape or the shape of a cylindrical step.
- the sealing ring is expediently fixed in the region of the end wall on the outer circumference of the cap.
- the annular gap can be open over its entire circumferential length to the casting cylinder.
- sealing rings which are arranged in a ring recess on the outer circumference of the cap, that the second piston part radially overlaps the sealing ring over a portion of its radial thickness with a projection, wherein the projection in the circumferential direction distributes several, in particular formed as grooves axial Has channels that connect the high pressure side of the casting cylinder with the annular gap.
- the melt which penetrates the casting chamber at high pressure into the annular gap increases the radial contact pressure of the sealing ring against the casting cylinder wall and, on the other hand, solidifies the sealing ring in the annular gap against the piston.
- the sealing of the sealing ring relative to the piston becomes more important with increasing wear of the sealing ring.
- the sealing ring is in turn arranged in a ring recess on the outer circumference of the cap, in such a way that the side surfaces of the annular recess approximately coincident parallel to the axial end faces of the sealing ring, the wear-dependent inflow of melt to seal the sealing ring relative to the piston to simple Way are controlled by the fact that the high-pressure side axial end face and the axially adjacent side surface of the annular recess are formed as conical surfaces.
- a cold chamber die casting machine comprises a bush formed as a first piston part 3, via a bayonet connection 5, as for example in US 5,233,912 is releasably secured to a in a casting cylinder 7 of the casting machine axially displaceable piston rod 9.
- a second piston part 11 is screwed on the high pressure side, which covers the indicated at 13 end of the piston rod 9 and a high pressure chamber of the casting cylinder 7 defining end wall 15 of the piston 1 forms.
- the second piston part 11 contains a central recess 17 whose bottom is formed by the end wall 15 and together with the end 13 of the piston rod 9 a coolant space 19 for cooling the piston 1 and in particular its end wall 15 limited.
- the coolant is supplied to or removed via channels indicated at 21 and 23 of the piston rod 9. Details of a suitable cooling system are in EP 0 423 413 A2 and in US 5,233,912 described. US 5,233,912 also describes details of a suitable construction of the bayonet connection 5.
- the end face 13 can lie flat against the inside of the end wall 15.
- the coolant chamber 19 has annular space here.
- a ring recess 25 is provided, in which a fitting against the inner wall of the casting cylinder 7 sealing ring 27 is seated.
- the annular recess 25 terminates at an annular shoulder 29 of the second piston part 11.
- the annular recess 25 is bounded by an end face 31 of the first piston part 3, which follows an indicated at 33 dividing surface between the two piston parts 3, 11. The division surface 33 is thus at the low-pressure side end face of the sealing ring 27th
- the dividing surface 33 is located on the low pressure side of the sealing ring 27 and the bolts 37 are screwed from the low pressure side into the blind hole thread 39 closed to the high pressure side, the operating pressure of the melt is not sufficient to penetrate into the threaded portion of the bolt 37.
- the bolts 37 bake so that in the casting operation is not fixed and can easily be solved even after use of the piston for the exchange of individual components of the piston 1, in particular the sealing ring 27 or the high-pressure piston part 11.
- the sealing ring 27 may be axially slotted, for example, be formed as a stepped slot, as in US 5,058,592 ( EP 0 423 413 A2 ) is described; but it can also be an annularly closed sealing ring. It is also advantageous if the outer shell of the annular body of the sealing ring 27 near its high-pressure side axial end has a certain contact with the inner circumferential surface of the casting cylinder 7 narrow abutment annular surface 44, which, as indicated at 43, narrows towards the low pressure side.
- Such a sealing ring when formed as a slotted, radially resilient sealing ring, generates comparatively high sealing forces in the region of its comparatively narrow, high-pressure-side sealing surface 44 due to its large suspension volume.
- this can be arranged both with axial and radial play in the annular recess 25 when the shoulder 29 high pressure side protruding end wall 15 between its axial projection 45 and the casting cylinder 7 defines an annular gap 47, in which due to Cooling of the end wall 15 can solidify the melt during operation and in this way additionally ensures a sealing of the sealing ring 27.
- At least the second piston part 11, but possibly also the first piston part 3, are preferably made of steel, which reduces the wear of the piston 1.
- Fig. 2 shows a, again designed as a cap piston 1a, in which the annular recess 25a extends almost over the entire axial extent of the two piston parts 3a and 11a, but at least over three quarters of the length of the piston 1a.
- annular recess 25a In the annular recess 25a, an annular closed socket 27a is inserted, which is axially fixed by the shoulders 29a and 31a of the piston member 11a and 3a.
- the division surface 33a extends approximately in the middle third of the axial extent of the ring recess 25a.
- the two piston parts 3a, 11a are releasably connected to one another by a plurality of bolts 37a distributed around the circumference, wherein the threaded bolts 37a are screwed into the blind hole thread 39a of the piston part 11a from the low pressure side of the piston part 3a.
- the bush 27a is closed annularly and is adapted with close tolerances to the inner diameter of the casting cylinder 7a.
- the bush 27a expediently consists of a copper alloy, while at least the piston part 3a, but preferably also the piston part 11a, consists of steel.
- a gap 47a may be formed between a projection 45a of the end wall 15a and the casting cylinder 7a, in which the melt to improve the sealing effect can solidify.
- the piston 1a is cooled according to the piston of Fig. 1 and is detachably connected by a bayonet connection 5a with the piston rod 9a.
- FIG. 3 shows a piston 1b designed as a cap, which differs from the pistons of FIGS. 1 and 2 by the way in which its sealing ring 27b is fixed.
- the sealing ring 27b is according to the in US 5,233,912 or EP 0 423 413 A2 described seal disposed near the high pressure side end of the piston member 11b and formed as a stepped slot, radially resilient sealing ring which is snapped with an inner circumferential groove 49 on a radially projecting annular web 51 of the high-pressure piston part 11b.
- annular gap 53 open to the pressure chamber of the casting cylinder 7b can be provided, which can fill with solidified melt material during operation and forces the sealing ring radially outward to increase the sealing effect.
- the sealing ring 27b similar to FIG. 1 in the region of its high-pressure-side outer edge may be provided with a narrow support area 44b compared to the axial ring thickness and, moreover, taper toward the low-pressure side as indicated at 43b.
- the dividing surface 33b is offset from the sealing ring 27b at a distance therefrom to the low pressure side and in the remaining between the dividing surface 33b and the sealing ring 27b material portion of the piston member 11b is in a bore 55 a form-fitting manner in a not-shown recess of the sealing ring 27b engaging locking pin 57 used, which secures the sealing ring 27b against rotation. In this way, consistent running-in properties of the sealing ring 27b are ensured.
- Fig. 4 shows a suitable for metal casting under high vacuum, particularly good sealing, designed as a cap piston 1 c with a high pressure side, slotted in the form of a stepped slot sealing ring 27c, which is snapped according to the description of FIG. 3 with an inner annular groove 49c on an outer annular web 51c of the high-pressure side piston part 11c.
- a cap piston 1 c with a high pressure side slotted in the form of a stepped slot sealing ring 27c, which is snapped according to the description of FIG. 3 with an inner annular groove 49c on an outer annular web 51c of the high-pressure side piston part 11c.
- a low pressure side seal ring 59 is seated in a ring recess 61 of the piston part 3c detachably connected to the piston rod 9c via a bayonet connection 5c.
- the recess 61 for the axial fixation of the sealing ring 59 forms a shoulder 63.
- the sealing ring 59 is fixed by an end face 65, which follows the division surface 33c in this position.
- the sealing ring 59 is formed radially resilient and has a radial excess outside of the casting cylinder 7c, so that it is radially clamped during insertion of the piston 1 c in the casting cylinder 7c.
- At its high pressure side edge of the sealing ring 59 has a conical Einfädelschräge 67 so that it can escape from the casting cylinder 7 c in continuous operation of the cold chamber die casting machine with retracted piston 1 c. This shortens the structural length of the casting cylinder required for a given casting volume.
- Fig. 5 shows a plan view of the compared with the sealing ring 27c axially comparatively long sealing ring 59, which occupies almost the entire axial length of the piston part 3c in the illustrated embodiment.
- the sealing ring 59 is made of a resilient copper alloy and carries on each of the circumferentially opposite edges 69, 71 circumferentially projecting tongues 73, which are opposed to recesses 75 of the other slot edge.
- the tongues 73 engage closely in the axial direction, but are movable in each case one of the recesses 75, so that the overall result is a meander-shaped axial seal.
- FIG. 6 shows a piston 1d in turn embodied as a cap according to the invention, which essentially differs from the piston 1c of FIG. 4 only in that the sealing ring 59 formed there as a wide ring is axially centered in two separate sealing rings 67, 69 is divided, each of which has a stepped slot and which are guided together in the annular recess 61 d of the first piston part 3d.
- a plurality of radial blind holes 71 are provided distributed in the circumferential direction of the first piston part 3d, in which prestressed helical compression springs 73 are inserted (FIG. 7).
- the helical compression springs 73 rest on pressure bodies 75, here in the form of balls, on the inner circumference of the sealing rings 67 and 69, respectively.
- the blind holes 71 are circumferentially offset centrally of the through holes 35d of the fixing screws 37d.
- the sealing ring 27d in the region of its high-pressure side outer edge have a narrow support area compared to the axial ring width, which can otherwise taper towards the low-pressure side. Otherwise, the piston rod 9d is sealed against the first piston part 3d by means of an encircling sealing ring 77 surrounding it.
- Such a sealing ring can also be provided in the previously explained variants.
- FIGS. 8 to 10 again designed as a cap piston 1e differs from that explained with reference to FIG. 1 piston 1 primarily in that the annular recess 25e extends over almost the entire axial length of the piston 1e and in addition to the high-pressure side in the region of the end wall 1e of the second piston part 11e arranged sealing ring 27e, a second sealing ring 79 is disposed in the annular recess 25e.
- the sealing rings 27e and 79 are axially fixed by the end faces 29e of the second piston part 11e on the one hand and the end face 31e of the first piston part 3e on the other hand.
- the high-pressure side sealing ring 27e is, as FIG.
- the low-pressure side sealing ring 79 is formed as a closed sealing ring whose outer diameter is fitted snugly the casting cylinder 7 e.
- annular gap 53e Due to the radial clearance between the inner circumference of the sealing ring 27e and the annular bottom of the annular recess 25e, an annular gap 53e is formed, which communicates with the melt of the casting chamber via a plurality of channels 83 distributed in the circumferential direction.
- the channels 83 have in the illustrated embodiment, the shape of axial grooves on the periphery of the front wall 15e radially outwardly projecting, the annular shoulder 29e of the annular recess 25e forming projection 45e.
- the annular gap 53e penetrating melt solidifies due to the cooling of the piston 1e in the annular gap 53e and ensures an improved seal.
- the projection 45e may in turn be formed so that it forms an annular gap 47e to the inner surface of the casting cylinder 7e, as was explained with reference to FIG.
- the components 43 and 44 of the piston of Fig. 1 may also be provided on the high pressure side seal ring 27e.
- Fig. 11 shows a variant of the piston of Figs. 8-10, which differs from this piston substantially in that the annular recess 25f, which leads the two axially adjacent sealing rings 27f and 79f, high pressure side by a convex-conical, i. to the low pressure side is tapered end face 29 f is limited, while the high-pressure side end face 85 of the high-pressure side, slotted sealing ring 27 f is concave-conical.
- the two conical surfaces 29f and 85 have the same cone angle and thus mutually parallel generatrix.
- the sealing ring 27f is held radially elastic and with radial play in the annular recess 25f, so that between the conical surfaces 29f and 85 a conical annular gap 87 remains through which in turn melt can enter into the annular gap 53f, which solidifies due to the cooling in the annular gaps 53f and 87 and ensures a sealing of the sealing ring 27f relative to the piston 1f.
- the annular gap 87 becomes wider, with which more melt material can penetrate into the annular gap 87, which improves the sealing effect after solidification.
- the conical design of the high pressure side end face can also be used in low pressure side sealing rings, such as. the sealing ring 67 of the piston of Fig. 6, use.
- components 43 and 44 may also be provided in the sealing ring 27 f.
- channels formed as grooves may be additionally provided on the circumference of the protrusion 45f, which introduce additional melt into the annular gap 53f.
- the two piston parts are connected by screws.
- 12 and 13 show a variant in which the first piston part 3g with the second piston part 11g via a bayonet connection with a plurality of circumferentially distributed bayonet projections 89 and 91 on each of the two piston parts 3g and 11 g.
- the bayonet projections 89, 91 are each separated by gaps 93, so that the piston parts 3g, 11 g axially inserted into one another and can be brought by rotation relative to each other in an engaged position.
- a sealing ring 41 g is arranged between axially mutually adjacent end faces of the bayonet projections 89, 91 passing away division surface 33g.
- the bayonet connection of Figs. 12 and 13 can be used in any of the foregoing embodiments of the piston.
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- Engineering & Computer Science (AREA)
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- Pistons, Piston Rings, And Cylinders (AREA)
- Molds, Cores, And Manufacturing Methods Thereof (AREA)
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Abstract
Description
Die Erfindung betrifft einen Kolben für eine Kaltkammer-Druckgießmaschine.The invention relates to a piston for a cold chamber die casting machine.
Der Kolben einer Kaltkammer-Druckgießmaschine und insbesondere der Dichtring eines solchen Kolbens ist hohen Drücken bei vergleichsweise hohen Temperaturen der Metallschmelze ausgesetzt, so dass der Kolben und insbesondere sein Dichtring im Betrieb sehr hohen Beanspruchungen ausgesetzt sind, die deren Lebensdauer verkürzen, was sich nachteilig auf die Produktivität der Gießmaschine auswirkt, wenn Verschleißteile des Kolbens gewechselt werden müssen und die Gießmaschine hierzu stillgesetzt werden muss.The piston of a cold chamber die casting machine and in particular the sealing ring of such a piston is exposed to high pressures at relatively high temperatures of the molten metal, so that the piston and in particular its sealing ring are exposed during operation very high stresses that shorten their life, which is disadvantageous to the Productivity of the casting machine affects when wearing parts of the piston must be changed and the casting machine must be shut down for this purpose.
Aus der deutschen Auslegeschrift 1 080 739 ist ein ungekühlter, mehrteiliger Kolben bekannt, dessen geschlitzter Dichtring in einer Ringaussparung am Umfang eines niederdruckseitig an der Kolbenstange der Druckgießmaschine zu befestigenden ersten Kolbenteils angeordnet ist. Auf der Hochdruckseite des ersten Kolbenteils ist ein die hochdruckseitige Kolbenstirn bildender zweiter Kolbenteil mit einer zentralen, axialen Schraube abnehmbar befestigt. Der zweite Kolbenteil begrenzt die den Dichtring aufnehmende Ringaussparung zur Hochdruckseite hin und enthält in Umfangsrichtung verteilt eine Vielzahl Kanäle, die in einen Ringspalt zwischen der Ringaussparung und dem Innenumfang des Dichtrings führen. In den Ringspalt unter dem Gießdruck einfließende Metallschmelze zwängt den Dichtring nach radial außen gegen die Innenwand des Gießzylinders. Auf diese Weise kann die Abdichtung des sich im Betrieb abnutzenden Dichtrings verbessert werden. Allerdings hat sich gezeigt, dass die in den Teilungsflächenspalt zwischen den beiden Kolbenteilen einfließende und dort erstarrende Schmelze das Trennen der beiden Kolbenteile erschwert und im Einzelfall auch unmöglich macht, insbesondere wenn die Schmelze bis an die Befestigungsschrauben vordringt.From
Gekühlte Kolben sind aus
Aus
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Es ist Aufgabe der Erfindung, einen Kolben für eine Kaltkammer-Druckgießmaschine zu schaffen, der sich im Betrieb einfacher als bisher handhaben lässt und insbesondere ein leichteres Auswechseln von Verschleißteilen ermöglicht. Hierbei soll zugleich eine verbesserte Dichtwirkung erreicht werden.It is an object of the invention to provide a piston for a cold chamber die casting machine, which is easier to handle in operation than before and in particular allows easier replacement of wearing parts. At the same time an improved sealing effect should be achieved.
Die Erfindung ist durch die in Anspruch 1 angegebenen Merkmale gekennzeichnet.The invention is characterized by the features specified in
Die Erfindung geht aus von einem Kolben in Form einer am hochdruckseitigen Ende einer in einem Gießzylinder einer Kaltkammer-Druckgießmaschine axial verschiebbaren Kolbenstange abnehmbar befestigbaren Kappe mit einer Umfangswand und einer die Kappe hochdruckseitig verschließenden Stirnwand, wobei am Außenumfang der Umfangswand wenigstens ein Dichtring angeordnet ist, wie dies z. B. in
Gemäß der Erfindung ist vorgesehen, dass am Außenumfang des ersten Kolbenteils in Umfangsrichtung verteilt mehrere radial wirkende Federelemente angeordnet sind, die den Dichtring nach radial außen drücken. Die Federelemente verstärken den radialen Anpressdruck des auf Grund seiner Eigenelastizität radial federnden, geschlitzten Dichtrings, wie er auch durch den Druck der Schmelze verstärkt werden kann.According to the invention it is provided that distributed on the outer circumference of the first piston member in the circumferential direction a plurality of radially acting spring elements are arranged, which press the sealing ring radially outward. The spring elements reinforce the radial contact pressure of the radially elastic due to its inherent elasticity, slotted sealing ring, as it can be amplified by the pressure of the melt.
Der erste Kolbenteil kann, wie an sich bekannt, mehrere in Umfangsrichtung verteilt angeordnete, axiale Durchgangslöcher aufweisen, durch die hindurch der zweite Kolbenteil mittels Befestigungsschrauben an dem ersten Kolbenteil angeschraubt ist. Die axialen Durchgangslöcher können hierbei in der Wand der Buchse vorgesehen sein. Hierdurch werden der äußere Rand der Teilungsfläche oder/und die freiliegenden Mündungen der Durchgangslöcher axial zur Niederdruckseite des Kolbens hin verlegt, um so die Drosselwirkung des Kolbens bei der Druckminderung der Metallschmelze auszunutzen. Auf diese Weise kann verhindert werden, dass die Metallschmelze bis in den Gewindebereich der Befestigungsschrauben vordringt und dort erstarren kann, was ansonsten zu unlösbar verbackenden Schraubverbindungen führen würde. Da die beiden Kolbenteile wie auch der Dichtring lösbar miteinander verbunden sind, können die Materialien dieser Komponenten dem jeweiligen Zweck der Komponenten entsprechend gewählt werden. Insbesondere können die beiden Kolbenteile aus unterschiedlichen Materialien, insbesondere hinsichtlich der Festigkeit und der Wärmeleitfähigkeit unterschiedlichen Materialien hergestellt werden.The first piston part can, as is known, have a plurality of circumferentially distributed, axial through holes, through which the second piston part is screwed by means of fastening screws to the first piston part. The axial through holes may in this case be provided in the wall of the socket. As a result, the outer edge of the dividing surface and / or the exposed mouths of the through holes are axially displaced toward the low pressure side of the piston, so as to take advantage of the throttling action of the piston in the pressure reduction of the molten metal. In this way it can be prevented that the molten metal penetrates into the threaded portion of the fastening screws and solidify there, which would otherwise lead to insoluble clogging screw. Since the two piston parts as well as the sealing ring are releasably connected to each other, the materials of these components can be selected according to the particular purpose of the components. In particular, the two piston parts can be made of different materials, in particular with regard to the strength and the thermal conductivity of different materials.
In einer Variante können der erste und der zweite Kolbenteil auch über eine Bajonett-Kupplung lösbar aneinander befestigt sein. Die einander zugeordneten Kupplungsorgane können unmittelbar an dem ersten und dem zweiten Kolbenteil angeformt sein. Geeignet ist aber auch ein Zwischenring mit Bajonett-Kupplungorganen sowohl zum ersten Kupplungsteil hin als auch zum zweiten Kupplungsteil hin, so dass die beiden Kupplungsteile über diesen Zwischenring miteinander gekuppelt sind.In one variant, the first and the second piston part can also be detachably fastened to one another via a bayonet coupling. The mutually associated coupling members can be formed directly on the first and the second piston part. However, an intermediate ring with bayonet coupling members is also suitable both for the first coupling part and for the second coupling part, so that the two coupling parts are coupled to one another via this intermediate ring.
Bevorzugt ist die Teilungsfläche zwischen den beiden Kupplungsteilen auf der Niederdruckseite zumindest eines Dichtrings angeordnet, um das Eindringen von Schmelze in die Kappe zu verhindern. Zwischen axial einander gegenüberliegenden, die Teilungsfläche bildenden Stirnflächen des ersten und des zweiten Kolbenteils ist bevorzugt ein die Stirnflächen gegeneinander abdichtender Abdichtring angeordnet, der in erster Linie das Austreten von Kühlflüssigkeit aus der Kappe verhindert.Preferably, the dividing surface between the two coupling parts is arranged on the low-pressure side of at least one sealing ring in order to prevent the penetration of melt into the cap. Between axially each other opposite, the dividing surface-forming end faces of the first and second piston part is preferably a sealing faces against each other sealing sealing ring arranged, which prevents the escape of coolant from the cap in the first place.
Ein wesentlicher Vorteil der voranstehend erläuterten mehrteiligen Kappe ist, dass sie es erlaubt den Dichtring einfach demontierbar an dem Kolben zu fixieren. Zweckmäßigerweise ist der Dichtring in einer Ringaussparung am Außenumfang der Umfangswand der Kappe angeordnet und überlappt mit dem ersten oder/und dem zweiten Kolbenteil zumindest teilsweise axial. Der Außenumfang der Teilungsfläche mündet in dieser Ringaussparung und zwar bevorzugt so, dass der Außenumfang der Teilungsfläche bezogen auf den hochdruckseitigen Dichtflächenrand des Dichtrings zur Niederdruckseite hin versetzt in der Ringaussparung mündet. Die Teilungsebene mündet zweckmäßigerweise näher zum niederdruckseitigen Ende des Dichtrings als zum hochdruckseitigen Ende. Auf diese Weise wird das Eindringen von Schmelze in die Kappe beträchtlich erschwert bzw. unmöglich gemacht. Insbesondere wird verhindert, dass die Befestigungsorgane, die die beiden Kolbenteile miteinander verbinden, durch eindringende Schmelze miteinander verbacken und das Demontieren der beiden Kolbenteile erschwert wird.A significant advantage of the above-explained multi-part cap is that it allows the sealing ring to be easily removable on the piston to fix. Conveniently, the sealing ring is arranged in a ring recess on the outer circumference of the peripheral wall of the cap and overlaps at least partially axially with the first and / or the second piston part. The outer circumference of the dividing surface opens into this annular recess and preferably in such a way that the outer circumference of the dividing surface, with respect to the high-pressure-side sealing surface edge of the sealing ring, is offset towards the low-pressure side in the annular recess. The dividing plane expediently opens closer to the low-pressure end of the sealing ring than to the high pressure end. In this way, the penetration of melt into the cap is made considerably difficult or impossible. In particular, it is prevented that the fastening members, which connect the two piston parts together, caked together by penetrating melt and the dismantling of the two piston parts is difficult.
In einer bevorzugten Ausgestaltung ist der Dichtring als geschlitzter Dichtring, insbesondere mit einem Stufenschlitz versehener Dichtring ausgebildet und die Teilungsfläche zwischen dem ersten und dem zweiten Kolbenteil ist bezogen auf den niederdruckseitigen Rand des Dichtrings mit axialem Abstand zur Niederdruckseite hin versetzt. Da die Teilungsfläche vollständig auf der Niederdruckseite des Dichtrings liegt, lässt sie sich besonders einfach abdichten. Der niederdruckseitige Überstand des zweiten Kolbenteils erlaubt das Anbringen eines in den Dichtring zur Drehsicherung eingreifenden Sicherungsstifts. Der Dichtring behält damit im Betrieb stets die gleiche Winkellage relativ zum Gießzylinder, was den Abrieb mindert und die Dichtwirkung verbessert. Es versteht sich, dass der Sicherungsstift gegebenenfalls auch an dem ersten Kolbenteil befestigt sein kann und zum Dichtring auf den zweiten Kolbenteil hinübergreift.In a preferred embodiment, the sealing ring is formed as a slotted sealing ring, in particular provided with a stepped slot sealing ring and the dividing surface between the first and the second piston part is offset with respect to the low pressure side edge of the sealing ring with axial distance to the low pressure side. Since the dividing surface lies completely on the low pressure side of the sealing ring, it is particularly easy to seal off. The low-pressure side projection of the second piston part allows the attachment of a locking pin engaging in the sealing ring for securing rotation. The sealing ring thus keeps in operation always the same angular position relative to the casting cylinder, which reduces the abrasion and improves the sealing effect. It is understood that the locking pin may optionally also be attached to the first piston part and engages over the sealing ring on the second piston part.
In der Hochvakuum-Gießtechnik werden besonders hohe Anforderungen an die Abdichtung des Kolbens relativ zum Gießzylinder gestellt. In einer bevorzugten Ausgestaltung mit besonders guten Dichteigenschaften ist vorgesehen, dass der vorstehend erstgenannte Dichtring an dem zweiten Kolbenteil axial fixiert ist, dass die Teilungsfläche in einer den Außenumfang des ersten Kolbenteils umschließenden und zumindest über einen Teil ihrer axialen Erstreckung überlappenden Ringaussparung endet und dass in der Ringaussparung wenigstens ein zweiter Dichtring angeordnet ist. Der erste Dichtring ist als geschlitzter Dichtring angeordnet, so dass er auf den zweiten Kolbenteil aufgeschnappt werden kann. Der zweite Dichtring, der zur Verbesserung der Dichtwirkung in axialem Abstand von dem ersten Dichtring angeordnet ist, kann bei voneinander getrennten Kolbenteilen in die Ringaussparung des ersten Kolbenteils eingebaut werden.In high-vacuum casting technology, particularly high demands are placed on the sealing of the piston relative to the casting cylinder. In a preferred embodiment with particularly good sealing properties, it is provided that the above-mentioned sealing ring is axially fixed to the second piston part, that the dividing surface terminates in a ring recess surrounding the outer circumference of the first piston part and overlapping at least over part of its axial extension, and in that Ring recess at least a second sealing ring is arranged. The first sealing ring is arranged as a slotted sealing ring, so that it can be snapped onto the second piston part. The second sealing ring, which is arranged to improve the sealing effect at an axial distance from the first sealing ring, can be installed in mutually separate piston parts in the annular recess of the first piston part.
Bevorzugt handelt es sich bei dem zweiten Dichtring um einen geschlitzten, außerhalb des Druckzylinders auf ein Übermaß radial auffedernden Dichtring. Der zweite Dichtring ist damit in der Lage, den Kolben nicht nur gegenüber dem Gießzylinder abzudichten sondern auch radial in dem Gießzylinder zu führen. Dies ist insbesondere von Vorteil, wenn die radialen Führungseigenschaften des ersten Dichtrings zugunsten einer Optimierung der Dichteigenschaften des ersten Dichtrings vernachlässigt sind.The second sealing ring is preferably a slotted sealing ring, which springs radially outward from the impression cylinder to an oversize. The second sealing ring is thus able to seal the piston not only with respect to the casting cylinder but also to guide radially in the casting cylinder. This is particularly advantageous if the radial guiding properties of the first sealing ring are neglected in favor of optimizing the sealing properties of the first sealing ring.
Der radial auffedernde Dichtring hat bevorzugt an seinem hochdruckseitigen Außenrand einen Einfädelkonus, so dass der Kolben bei Beginn des Gießhubs bis über den zweiten Dichtring hinaus aus dem Gießzylinder herausgezogen werden kann. Auf diese Weise kann ein hohes Gußvolumen erreicht werden, ohne den Gießzylinder entsprechend verlängern zu müssen.The radially auffedernde sealing ring has preferably at its high pressure side outer edge of a threading cone, so that the piston at the beginning of the casting stroke can be pulled out beyond the second sealing ring out of the casting cylinder. In this way, a high casting volume can be achieved without having to extend the casting cylinder accordingly.
Der zweite Dichtring ist zur Verbesserung seiner Führungseigenschaften in axialer Richtung zweckmäßigerweise breiter als der erste Dichtring. Auch der zweite Dichtring ist bevorzugt als geschlitzter Dichtring ausgebildet, wobei seine den Schlitz bildenden Ränder wenigstens eine in Umfangsrichtung vorstehende Zunge und einer der Zunge in Umfangsrichtung gegenüberliegende Aussparung bilden, in die die Zunge axial eng passend, jedoch in Umfangsrichtung beweglich eingreift. Bevorzugt bildet jeder der beiden den Schlitz bildenden Ränder des zweiten Dichtrings zumindest je eine Zunge. Die hierdurch entstehende Mäanderstruktur erlaubt es, in axialer Richtung relativ breite Dichtringe hinreichend dicht zu bekommen.The second sealing ring is expediently wider to improve its guiding properties in the axial direction than the first sealing ring. Also, the second sealing ring is preferably formed as a slotted sealing ring, wherein its edges forming the slot form at least one circumferentially projecting tongue and one of the tongue in the circumferential direction opposite recess into which the tongue engages axially closely fitting, but movable in the circumferential direction. Preferably, each of the two edges forming the slot of the second sealing ring forms at least one tongue each. The resulting meandering structure allows relatively wide sealing rings to be sufficiently tight in the axial direction.
Die Teilungsfläche kann in einer den Außenumfang sowohl des ersten als auch des zweiten Kolbenteils umschließenden und beide Kolbenteile axial überlappenden Ringaussparung enden. Der Dichtring kann hierbei als in der Ringaussparung axial fixierte Dichtbuchse ausgebildet sein. Selbst wenn die Dichtbuchse nicht geschlitzt und damit nicht radial federnd ausgebildet ist, so kann sie bei hinreichend engen Toleranzen den Kolben wirksam gegen den Gießzylinder abdichten. Auf diese Weise lässt sich ein einfacher und kostengünstiger Kolben schaffen, bei welchem die vergleichsweise breite Dichtbuchse aus einer Kupferlegierung bestehen kann, während der erste Kolbenteil und gegebenenfalls auch der zweite Kolbenteil aus einem kostengünstigeren Material, wie zum Beispiel Stahl, bestehen kann.The dividing surface can end in a ring recess surrounding the outer circumference of both the first and the second piston part and axially overlapping both piston parts. The sealing ring may in this case be designed as a sealing bush fixed axially in the annular recess. Even if the sealing bush is not slotted and thus not formed radially resilient, it can effectively seal the piston against the casting cylinder with sufficiently tight tolerances. In this way, a simple and inexpensive piston can be provided in which the comparatively wide sealing bushing may consist of a copper alloy, while the first piston part and possibly also the second piston part may consist of a less expensive material, such as steel.
Der Kolben lässt sich kostengünstig herstellen, wenn der erste Kolbenteil als Buchse ausgebildet ist, in deren Wand die axialen Durchgangslöcher für die Befestigungsschrauben vorgesehen sind. Um den Kolben einerseits stabil mit der Kolbenstange verbinden zu können und andererseite die Wandstärke der Buchse dennoch zur Aufnahme der Durchgangslöcher hinreichend dick bemessen zu können, ist zur Befestigung des Kolbens an der Kolbenstange zweckmäßigerweise eine Bajonettverbindung vorgesehen. Eine geeignete Bajonettverbindung ist beispielsweise in
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Um die Dichtringabnutzung zu verringern, ist in einer bevorzugten Ausgestaltung der Erfindung vorgesehen, dass die Kappe zumindest im Bereich der Stirnwand des zweiten Kolbenteils durch ein in die Kappe einführbares Kühlmedium kühlbar ist, dass der Dichtring im Bereich der Stirnwand am Außenumfang der Kappe in einer Ringaussparung axial fixiert, jedoch mit Spiel beweglich angeordnet ist, dass der zweite Kolbenteil hochdruckseitig über den Dichtring axial vorsteht und den Dichtring über einen Teil seiner radialen Dicke hochdruckseitig mit einem Vorsprung radial übergreift, dessen äußere Umfangsfläche dem Dichtring hochdruckseitig benachbart zwischen sich und dem Gießzylinder einen im Gießbetrieb auf Erstarrungstemperatur kühlbaren Ringspalt begrenzt.In order to reduce the sealing ring wear, it is provided in a preferred embodiment of the invention that the cap can be cooled at least in the region of the end wall of the second piston part by a cooling medium insertable into the cap, that the sealing ring in the region of the end wall on the outer circumference of the cap in a ring recess axially fixed, but movably arranged with play, that the second piston part projecting high pressure side over the sealing ring and radially overlaps the sealing ring over a portion of its radial thickness high pressure side with a projection whose outer peripheral surface adjacent the sealing ring high pressure side between itself and the casting cylinder in the Casting operation limited to freezing temperature coolable annular gap.
Bei einem solchen Kolben bleibt der in der Ringaussparung bewegliche Dichtring auch im Betrieb hinreichend beweglich, um sich auf Grund seiner Eigenelastizität der Form des Gießzylinders anpassen zu können. Anders als bei herkömmlichen Kolben dichtet die in dem hochdruckseitig dem Dichtring vorgelagerten Ringspalt erstarrte Schmelze die Ringaussparung und den Dichtring so weit ab, dass die Beweglichkeit des Dichtrings nicht unzulässig beeinträchtigt wird. Während des Druckhubs des Kolbens füllt sich der Ringspalt mit Schmelze, die jedoch in dem Ringspalt teilweise oder ganz erstarrt, bevor sie die den Dichtring führende Ringaussparung des Kolbenkörpers erreicht. Beim Rückhub des Kolbens kann die in dem Ringspalt erstarrte Schmelze in dem Ringspalt verbleiben oder aber sie wird im Verlauf des Rückhubs abgestreift. Mit Hilfe einer solchen hochdruckseitigen Vorabdichtung läßt sich eine radiale Beweglichkeit des Dichtrings auch bei geschlossenen Dichtringen erreichen.In such a piston, the movable in the ring recess sealing ring remains sufficiently movable during operation to adapt to the shape of the casting cylinder due to its inherent elasticity. Unlike conventional pistons seals in the high pressure side of the sealing ring upstream annular gap solidified melt the ring recess and the Sealing ring so far that the mobility of the sealing ring is not unduly affected. During the pressure stroke of the piston, the annular gap fills with melt, which, however, partially or completely solidifies in the annular gap before it reaches the sealing ring leading annular recess of the piston body. During the return stroke of the piston, the melt solidified in the annular gap may remain in the annular gap or it may be scraped off in the course of the return stroke. With the help of such a high-pressure side pre-seal, a radial mobility of the sealing ring can be achieved even with closed sealing rings.
Herkömmliche, geschlitzte Dichtringe sollen im Betrieb radial federnd am Innenumfang des Gießzylinders anliegen. Um den radialen Anpressdruck zu erhöhen, ist es z.B. aus
Die Dichtwirkung kann noch weiter verbessert werden, wenn die äußere Umfangsfläche des radial elastischen Ringkörpers des geschlitzten Dichtrings nahe ihrem hochdruckseitigen axialen Ende eine zur Anlage an der inneren Umfangsfläche des Gießzylinders bestimmte, äußere Anlage-Ringfläche hat, deren axiale Länge kleiner ist als die axiale Länge einer mit dieser äußeren Anlage-Ringfläche axial überlappende, der Schmelze, z.B. der Metallschmelze aussetzbaren inneren Ringfläche am Innenumfang des Ringkörpers, wobei sich auf der Niederdruckseite der äußeren Umfangsfläche des Ringkörpers an die äußere Anlage-Ringfläche zumindest über einen Teilbereich der verbleibenden axialen Länge des Ringkörpers ein Ringflächenabschnitt anschließt, dessen Durchmesser kleiner ist als der Durchmesser der äußeren Anlage-Ringfläche. Die Verringerung der Flächengröße der äußeren Anlage-Ringfläche führt zu eienr Druckerhöhung im Dichtflächenbereich, was die Dichtwirkung verbessert. Auf Grund des hohen radialen Anpressdrucks schleift sich die Anlage-Ringfläche besser entsprechend der Zylinderform des Gießzylinders ein. Bei geschmiertem Betrieb der Druckgießmaschine kann das in die Gießkammer vor der Metallschmelze eingeführte Schmiermittel während des Druckvorschubs des Kolbens an der äußeren Anlage-Ringfläche vorbei zur Niederdruckseite in den Bereich der im Durchmesser verkleinerten Umfangsfläche des Dichtrings treten. Dieses auf der Niederdruckseite des Dichtrings sich sammelnde Schmiermittel schmiert den Gießzylinder bei der Rückzugsbewegung des Kolbens. Der im Durchmesser verkleinerte Ringflächenabschnitt kann angenähert Kegelstumpfform oder aber die Form einer zylindrischen Stufe haben.The sealing effect can be further improved if the outer circumferential surface of the radially elastic annular body of the slotted sealing ring near its high-pressure side axial end has a for abutment against the inner peripheral surface of the casting certain, outer abutment annular surface whose axial length is smaller than the axial length a with this outer abutment annular surface axially overlapping, the melt, eg the molten metal exposable inner annular surface on the inner circumference of the annular body, wherein on the low pressure side of the outer peripheral surface of the annular body to the outer abutment annular surface over at least a portion of the remaining axial length of the annular body an annular surface portion connects, the diameter of which is smaller than the diameter of the outer abutment annular surface. The reduction of the area size of the outer abutment annular surface leads to eienr pressure increase in the sealing surface area, which improves the sealing effect. Due to the high radial contact pressure, the contact ring surface grinds better according to the cylinder shape of the casting cylinder. During lubricated operation of the die casting machine, the lubricant introduced into the casting chamber prior to the molten metal may pass into the area of the reduced diameter peripheral surface of the seal ring during the pressure advance of the piston past the outer abutment annular surface. This accumulating on the low pressure side of the sealing ring lubricant lubricates the casting cylinder during the return movement of the piston. The reduced in diameter annular surface portion may have approximately truncated cone shape or the shape of a cylindrical step.
Der Dichtring ist zweckmäßigerweise im Bereich der Stirnwand am Außenumfang der Kappe fixiert. Insbesondere bei einem radial elastischen, geschlitzten Dichtring kann es vorteilhaft sein, dass zwischen der inneren Umfangsfläche des Dichtrings und der äußeren Umfangsfläche der Kappe ein auf der Hochdruckseite des Ringkörpers des Dichtrings zumindest über einen Teil seiner Umfangslänge zur Hochdruckseite des Gießzylinders offener Ringspalt vorgesehen ist. Der Ringspalt kann über seine Gesamtumfangslänge zum Gießzylinder hin offen sein. Es genügt jedoch beispielsweise bei Dichtringen, die in einer Ringaussparung am Außenumfang der Kappe angeordnet sind, dass der zweite Kolbenteil den Dichtring über einen Teil seiner radialen Dicke hochdruckseitig mit einem Vorsprung radial übergreift, wobei der Vorsprung in Umfangsrichtung verteilt mehrere, insbesondere als Nuten ausgebildete axiale Kanäle aufweist, die die Hochdruckseite des Gießzylinders mit dem Ringspalt verbinden. Die von der Gießkammer mit Hochdruck in den Ringspalt eindringende Schmelze erhöht einerseits den radialen Anpressdruck des Dichtrings gegen die Gießzylinderwand und zum anderen dichtet in dem Ringspalt erstarrtes Material der Schmelze den Dichtring gegenüber dem Kolben ab.The sealing ring is expediently fixed in the region of the end wall on the outer circumference of the cap. In particular, in the case of a radially elastic, slotted sealing ring, it may be advantageous that between the inner peripheral surface of the sealing ring and the outer peripheral surface of the cap is provided on the high pressure side of the annular body of the sealing ring at least over part of its circumferential length to the high pressure side of the casting cylinder open annular gap. The annular gap can be open over its entire circumferential length to the casting cylinder. However, it suffices, for example, in sealing rings, which are arranged in a ring recess on the outer circumference of the cap, that the second piston part radially overlaps the sealing ring over a portion of its radial thickness with a projection, wherein the projection in the circumferential direction distributes several, in particular formed as grooves axial Has channels that connect the high pressure side of the casting cylinder with the annular gap. On the one hand, the melt which penetrates the casting chamber at high pressure into the annular gap increases the radial contact pressure of the sealing ring against the casting cylinder wall and, on the other hand, solidifies the sealing ring in the annular gap against the piston.
Die Abdichtung des Dichtrings relativ zum Kolben wird mit zunehmendem Verschleiß des Dichtrings wichtiger. In einer bevorzugten Ausgestaltung, bei welcher der Dichtring wiederum in einer Ringaussparung am Außenumfang der Kappe angeordnet ist, und zwar so, dass die Seitenflächen der Ringaussparung etwa konturgleich parallel zu den axialen Stirnflächen des Dichtrings verlaufen, kann der verschleißabhängige Zufluss von Schmelze zur Abdichtung des Dichtrings relativ zum Kolben auf einfache Weise dadurch gesteuert werden, dass die hochdruckseitige axiale Stirnfläche und die axial benachbarte Seitenfläche der Ringaussparung als konische Flächen ausgebildet sind. Auf diese Weise entsteht zwischen den konischen Flächen ein konischer Ringspalt, dessen Spaltbreite mit wachsendem Verschleiß zunimmt, da die konkav-konische Stirnfläche des Dichtrings mit wachsendem Verschleiß von der konvex-konischen Seitenfläche der Ringaussparung radial abhebt und auf diese Weise besser mit bei Erstarren den Ringspalt abdichtender Schmelze gefüllt werden kann.The sealing of the sealing ring relative to the piston becomes more important with increasing wear of the sealing ring. In a preferred embodiment, in which the sealing ring is in turn arranged in a ring recess on the outer circumference of the cap, in such a way that the side surfaces of the annular recess approximately coincident parallel to the axial end faces of the sealing ring, the wear-dependent inflow of melt to seal the sealing ring relative to the piston to simple Way are controlled by the fact that the high-pressure side axial end face and the axially adjacent side surface of the annular recess are formed as conical surfaces. In this way arises between the conical surfaces a conical annular gap whose gap width increases with increasing wear, since the concave-conical face of the sealing ring with increasing wear of the convex-conical side surface of the ring recess radially lifts and in this way better with solidification of the annular gap sealing melt can be filled.
Im Folgenden wird die Erfindung anhand einer Zeichnung näher erläutert. Hierbei zeigt:
- Fig. 1
- einen Axiallängsschnitt durch ein Ausführungsbeispiel eines geteilten Kolbens einer Kaltkammer-Druckgießmaschine;
- Fig. 2
- einen Axiallängsschnitt durch einen Teil einer Variante des Kolbens;
- Fig. 3
- einen Axiallängsschnitt durch einen Teil einer zweiten Variante des Kolbens;
- Fig. 4
- einen Axiallängsschnitt durch einen Teil einer dritten Variante des Kolbens;
- Fig. 5
- eine Radialansicht eines Dichtrings des Kolbens aus Fig. 4;
- Fig. 6
- einen Axiallängsschnitt durch eine erfindungsgemäße Variante des Kolbens;
- Fig. 7
- ein vergrößertes Detail des Kolbens, das in Fig. 6 durch einen Pfeil VII markiert ist;
- Fig. 8
- einen Axiallängsschnitt durch eine vierte Variante des Kolbens;
- Fig. 9
- eine Radialansicht des hochdruckseitigen Bereichs des Kolbens aus Fig. 8;
- Fig. 10
- eine Stirnansicht des Kolbens, gesehen in Richtung eines Pfeils X in Fig. 8;
- Fig. 11
- einen Axiallängsschnitt durch eine fünfte Variante des Kolbens;
- Fig. 12
- einen Axiallängsschnitt durch eine Variante von bei den Kolben der Fig. 1
bis 11 verwendbaren Variante von Befestigungsorganen und - Fig. 13
- einen Axialquerschnitt durch die Befestigungsorgane, gesehen entlang einer Linie XIII-XIII in Fig. 12.
- Fig. 1
- an axial longitudinal section through an embodiment of a divided piston of a cold chamber die casting machine;
- Fig. 2
- a Axiallängsschnitt through a part of a variant of the piston;
- Fig. 3
- a Axiallängsschnitt through a part of a second variant of the piston;
- Fig. 4
- a Axiallängsschnitt through a part of a third variant of the piston;
- Fig. 5
- a radial view of a sealing ring of the piston of Fig. 4;
- Fig. 6
- an axial longitudinal section through a variant of the piston according to the invention;
- Fig. 7
- an enlarged detail of the piston, which is marked in Figure 6 by an arrow VII.
- Fig. 8
- a Axiallängsschnitt by a fourth variant of the piston;
- Fig. 9
- a radial view of the high-pressure side portion of the piston of Fig. 8;
- Fig. 10
- an end view of the piston, as seen in the direction of an arrow X in Fig. 8;
- Fig. 11
- a Axiallängsschnitt by a fifth variant of the piston;
- Fig. 12
- a Axiallängsschnitt by a variant of usable in the piston of Fig. 1 to 11 variant of fastening members and
- Fig. 13
- an axial cross section through the fastening members, as seen along a line XIII-XIII in Fig. 12th
Zunächst sollen die grundsätzlichen Konstruktionen eines Kolbens erläutert werden, von denen die Erfindung ausgeht,First, the basic constructions of a piston will be explained, from which the invention proceeds,
Der in Fig. 1 dargestellte, in Form einer Kappe ausgebildete Kolben 1 einer Kaltkammer-Druckgießmaschine umfasst einen als Buchse ausgebildeten ersten Kolbenteil 3, der über eine Bajonettverbindung 5, wie sie beispielsweise in
Zur Ableitung des auf die Stirnwand 15 wirkenden Gießdrucks in die Stirnfläche 13 der Kolbenstange 9, kann die Stirnfläche 13 flächig an der Innenseite der Stirnwand 15 anliegen. Der Kühlmittelraum 19 hat hier Ringraumform.In order to derive the casting pressure acting on the
Am Außenumfang des zweiten Kolbenteils 11 ist eine Ringaussparung 25 vorgesehen, in der ein an der Innenwand des Gießzylinders 7 anliegender Dichtring 27 sitzt. Zur Hochdruckseite hin endet die Ringaussparung 25 an einer Ringschulter 29 des zweiten Kolbenteils 11. Niederdruckseitig wird die Ringaussparung 25 durch eine Stirnfläche 31 des ersten Kolbenteils 3 begrenzt, die einer bei 33 angedeuteten Teilungsfläche zwischen den beiden Kolbenteilen 3, 11 folgt. Die Teilungsfläche 33 liegt damit am niederdruckseitigen Stirnende des Dichtrings 27.On the outer circumference of the
Für die lösbare Verbindung der beiden Kolbenteile 3, 11 sind in der Wand des niederdruckseitigen Kolbenteils 3 mehrere, hier sechs in Umfangsrichtung gleich verteilte, axial verlaufende Durchgangslöcher 35 vorgesehen, durch die hindurch von der Niederdruckseite her Schraubbolzen 37 in Gewindesacklöcher 39 des zweiten Kolbenteils 11 eingeschraubt sind. Die Schraubbolzen 37 spannen die beiden Kolbenteile 3, 11 flächig gegeneinander. Eine am radial inneren Umfang der Teilungsfläche 33 vorgesehene Ringdichtung 41 dichtet die Teilungsfläche kühlmitteldicht ab.For the detachable connection of the two
Da die Teilungsfläche 33 auf der Niederdruckseite des Dichtrings 27 gelegen ist und die Schraubbolzen 37 von der Niederdruckseite her in zur Hochdruckseite geschlossene Sacklochgewinde 39 eingeschraubt sind, reicht der Betriebsdruck der Schmelze nicht aus, um in den Gewindebereich der Schraubbolzen 37 einzudringen. Die Schraubbolzen 37 backen damit im Gießbetrieb nicht fest und können auch nach Gebrauch des Kolbens problemlos für den Tausch einzelner Komponenten des Kolbens 1, insbesondere des Dichtrings 27 oder des hochdruckseitigen Kolbenteils 11 problemlos gelöst werden.Since the dividing
Der Dichtring 27 kann axial geschlitzt sein, beispielsweise als Stufenschlitz ausgebildet sein, wie er in
In einer Variante des Dichtrings 27 kann dieser sowohl mit axialem als auch radialem Spiel in der Ringaussparung 25 angeordnet sein, wenn die als Schulter 29 hochdruckseitig vorstehende Stirnwand 15 zwischen ihrem axialen Überstand 45 und dem Gießzylinder 7 einen Ringspalt 47 begrenzt, in welchem auf Grund der Kühlung der Stirnwand 15 im Betrieb die Schmelze erstarren kann und auf diese Weise zusätzlich für eine Abdichtung des Dichtrings 27 sorgt.In a variant of the sealing
Zumindest der zweite Kolbenteil 11, gegebenenfalls aber auch der erste Kolbenteil 3, bestehen bevorzugt aus Stahl, was den Verschleiß des Kolbens 1 mindert.At least the
Im Folgenden werden Varianten des Kolbens aus Fig. 1 beschrieben. Gleichwirkende Komponenten sind mit den Bezugszahlen der Fig. 1 bezeichnet und zur Unterscheidung mit einem Buchstaben versehen. Zur Erläuterung des Aufbaus und der Wirkungsweise wird jweils auf die gesamte vorangegangene Beschreibung Bezug genommen. Vorangegangen erläuterte Varianten, insbesondere des Dichtrings, treffen auch auf die nachfolgend erläuterten Versionen des Kolbens zu.In the following, variants of the piston from FIG. 1 will be described. Equivalent components are denoted by the reference numerals of Fig. 1 and provided with a letter for distinction. For an explanation of the construction and the mode of operation, reference is made in each case to the entire preceding description. Previously explained variants, in particular of the sealing ring, also apply to the versions of the piston explained below.
Fig. 2 zeigt einen, wiederum als Kappe ausgebildeten Kolben 1a, bei welchem sich die Ringaussparung 25a nahezu über die gesamte axiale Erstreckung der beiden Kolbenteile 3a und 11a, jedoch wenigstens über drei Viertel der Länge des Kolbens 1a erstreckt. In die Ringaussparung 25a ist eine ringförmig geschlossene Buchse 27a eingesetzt, die von den Schultern 29a und 31a des Kolbenteils 11a bzw. 3a axial fixiert wird. Die Teilungsfläche 33a verläuft etwa im mittleren Drittel der axialen Erstreckung der Ringaussparung 25a. Auch in dieser Variante sind die beiden Kolbenteile 3a, 11a durch mehrere am Umfang verteilte Schraubbolzen 37a lösbar miteinander verbunden, wobei die Schraubbolzen 37a von der Niederdruckseite des Kolbenteils 3a her in Sacklochgewinde 39a des Kolbenteils 11a eingeschraubt sind.Fig. 2 shows a, again designed as a cap piston 1a, in which the annular recess 25a extends almost over the entire axial extent of the two piston parts 3a and 11a, but at least over three quarters of the length of the piston 1a. In the annular recess 25a, an annular closed socket 27a is inserted, which is axially fixed by the shoulders 29a and 31a of the piston member 11a and 3a. The division surface 33a extends approximately in the middle third of the axial extent of the ring recess 25a. In this variant too, the two piston parts 3a, 11a are releasably connected to one another by a plurality of bolts 37a distributed around the circumference, wherein the threaded bolts 37a are screwed into the
Die Buchse 27a ist ringförmig geschlossen und ist mit engen Toleranzen an den Innendurchmesser des Gießzylinders 7a angepasst. Die Buchse 27a besteht zweckmäßigerweise aus einer Kupferlegierung, während zumindest der Kolbenteil 3a, vorzugsweise aber auch der Kolbenteil 11a aus Stahl besteht. Auf der Hochdruckseite des Kolbens kann zwischen einem Überstand 45a der Stirnwand 15a und dem Gießzylinder 7a ein Spalt 47a gebildet sein, in welchem zur Verbesserung der Dichtwirkung die Schmelze erstarren kann. Auch der Kolben 1a ist entsprechend dem Kolben der Fig. 1 gekühlt und ist durch eine Bajonettverbindung 5a mit der Kolbenstange 9a lösbar verbunden.The bush 27a is closed annularly and is adapted with close tolerances to the inner diameter of the
Fig. 3 zeigt einen als Kappe ausgebildeten Kolben 1b, der sich durch die Art der Fixierung seines Dichtrings 27b von den Kolben der Fig. 1 und 2 unterscheidet. Der Dichtring 27b ist entsprechend dem in
Die Teilungsfläche 33b ist gegenüber dem Dichtring 27b mit Abstand von diesem zur Niederdruckseite hin versetzt und in dem zwischen der Teilungsfläche 33b und dem Dichtring 27b verbleibenden Materialbereich des Kolbenteils 11b ist in einer Bohrung 55 ein formschlüssig in eine nicht näher dargestellte Aussparung des Dichtrings 27b eingreifender Sicherungsstift 57 eingesetzt, der den Dichtring 27b gegen Verdrehen sichert. Auf diese Weise werden gleichbleibende Einlaufeigenschaften des Dichtrings 27b sichergestellt.The dividing
Fig. 4 zeigt einen für den Metallguss unter Hochvakuum geeigneten, besonders gut abdichtenden, als Kappe ausgebildeten Kolben 1 c mit einem hochdruckseitigen, in Form eines Stufenschlitzes geschlitzten Dichtring 27c, der entsprechend der Beschreibung zu Fig. 3 mit einer inneren Ringnut 49c auf einen äußeren Ringsteg 51c des hochdruckseitigen Kolbenteils 11c aufgeschnappt ist. Zur Erläuterung wird auf die Beschreibung entsprechender Bezugszahlen in Fig. 3 verwiesen.Fig. 4 shows a suitable for metal casting under high vacuum, particularly good sealing, designed as a cap piston 1 c with a high pressure side, slotted in the form of a stepped slot sealing ring 27c, which is snapped according to the description of FIG. 3 with an inner annular groove 49c on an outer annular web 51c of the high-pressure side piston part 11c. For explanation, reference is made to the description of corresponding reference numerals in Fig. 3.
Während der hochdruckseitige Dichtring 27c an dem Kolbenteil 11c fixiert ist, sitzt ein niederdruckseitiger Dichtring 59 in einer Ringaussparung 61 des wiederum über eine Bajonettverbindung 5c mit der Kolbenstange 9c lösbar verbundenen Kolbenteils 3c. Zur Niederdruckseite hin bildet die Aussparung 61 für die axiale Fixierung des Dichtrings 59 eine Schulter 63. Auf der Hochdruckseite wird der Dichtring 59 durch eine Stirnfläche 65 fixiert, die in dieser Position der Teilungsfläche 33c folgt.While the high pressure side seal ring 27c is fixed to the piston part 11c, a low pressure
Der Dichtring 59 ist radial federnd ausgebildet und hat außerhalb des Gießzylinders 7c ein radiales Übermaß, so dass er beim Einführen des Kolbens 1 c in den Gießzylinder 7c radial gespannt wird. An seinem hochdruckseitigen Rand hat der Dichtring 59 eine konische Einfädelschräge 67, so dass er auch im Dauerbetrieb der Kaltkammer-Druckgießmaschine bei zurückgezogenem Kolben 1 c aus dem Gießzylinder 7c austreten kann. Dies verkürzt die für ein vorgegebenes Gießvolumen erforderliche Baulänge des Gießzylinders.The sealing
Fig. 5 zeigt eine Draufsicht auf den verglichen mit dem Dichtring 27c axial vergleichsweise langen Dichtring 59, der im dargestellten Ausführungsbeispiel nahezu die gesamte axiale Länge des Kolbenteils 3c einnimmt. Der Dichtring 59 ist aus einer federnden Kupferlegierung hergestellt und trägt an jeder der sich in Umfangsrichtung gegenüberliegenden Kanten 69, 71 in Umfangsrichtung vorstehende Zungen 73, denen jeweils Aussparungen 75 des anderen Schlitzrands gegenüberliegen. Die Zungen 73 greifen in axialer Richtung eng passend, jedoch beweglich in jeweils eine der Aussparungen 75 ein, so dass sich insgesamt eine mäanderförmige axiale Dichtung ergibt.Fig. 5 shows a plan view of the compared with the sealing ring 27c axially comparatively long sealing
Fig. 6 zeigt einen wiederum als Kappe ausgebildeten Kolben 1d gemäß der Erfindung, der sich von dem Kolben 1c der Fig. 4 im Wesentlichen nur dadurch unterscheidet, dass der dort als breiter Ring ausgebildete Dichtring 59 axial mittig in zwei voneinander gesonderte Dichtringe 67, 69 aufgeteilt ist, von denen jeder einen Stufenschlitz hat und die gemeinsam in der Ringaussparung 61d des ersten Kolbenteils 3d geführt sind. Um die radiale Anpresskraft der Dichtringe 67, 69 zu erhöhen, sind in Umfangsrichtung des ersten Kolbenteils 3d verteilt mehrere radiale Sacklöcher 71 vorgesehen, in die vorgespannte Schraubendruckfedern 73 eingesetzt sind (Fig. 7). Die Schraubendruckfedern 73 liegen über Druckkörper 75, hier in Form von Kugeln, am Innenumfang der Dichtringe 67 bzw. 69 an. Die Sacklöcher 71 sind in Umfangsrichtung mittig zu den Durchgangslöchern 35d der Befestigungsschrauben 37d versetzt.FIG. 6 shows a piston 1d in turn embodied as a cap according to the invention, which essentially differs from the piston 1c of FIG. 4 only in that the sealing
Der Dichtring 27d kann, wie dies bereits anhand von Fig. 3 erläutert wurde, im Bereich seines hochdruckseitgen Außenrands einen, verglichen mit der axialen Ringbreite schmalen Auflagebereich haben, der sich im übrigen zur Niederdruckseite hin verjüngen kann. Im übrigen ist die Kolbenstange 9d mittels eines sie umschließenden Abdichtrings 77 gegen den ersten Kolbenteil 3d abgedichtet. Ein solcher Abdichtring kann auch bei den vorangegangen erläuterten Varianten vorgesehen sein.The sealing
Der in den Fig. 8 bis 10 dargestellte, wiederum als Kappe ausgebildete Kolben 1e unterscheidet sich von dem anhand von Fig. 1 erläuterten Kolben 1 in erster Linie dadurch, dass die Ringaussparung 25e sich nahezu über die gesamte axiale Länge des Kolbens 1e erstreckt und zusätzlich zu dem hochdruckseitig im Bereich der Stirnwand 1e des zweiten Kolbenteils 11e angeordneten Dichtrings 27e ein zweiter Dichtring 79 in der Ringaussparung 25e angeordnet ist. Die Dichtringe 27e und 79 werden durch die Stirnflächen 29e des zweiten Kolbenteils 11e einerseits und die Stirnfläche 31 e des ersten Kolbenteils 3e andererseits axial fixiert. Der hochdruckseitige Dichtring 27e ist, wie Fig. 9 zeigt, mit einem axial und radial durchgehenden Stufenschlitz 81 versehen und sitzt mit radialem Spiel radial beweglich in der Ringaussparung 25e. Der niederdruckseitige Dichtring 79 ist als geschlossener Dichtring ausgebildet, dessen Außendurchmesser engpassend dem Gießzylinder 7e angepasst ist.The illustrated in FIGS. 8 to 10, again designed as a
Durch das Radialspiel zwischen dem Innenumfang des Dichtrings 27e und dem Ringboden der Ringaussparung 25e wird ein Ringspalt 53e gebildet, der über mehrere in Umfangsrichtung verteilte Kanäle 83 mit der Schmelze der Gießkammer in Verbindung steht. Die Kanäle 83 haben im dargestellten Ausführungsbeispiel die Form axialer Nuten am Umfang des von der Stirnwand 15e radial nach außen abstehenden, die Ringschulter 29e der Ringaussparung 25e bildenden Vorsprungs 45e. In den Ringspalt 53e eindringende Schmelze erstarrt aufgrund der Kühlung des Kolbens 1e in dem Ringspalt 53e und sorgt für eine verbesserte Abdichtung.Due to the radial clearance between the inner circumference of the sealing
Der Vorsprung 45e kann wiederum so ausgebildet sein, dass er zur Innenfläche des Gießzylinders 7e einen Ringspalt 47e bildet, wie dies anhand von Fig. 1 erläutert wurde. Die Komponenten 43 und 44 des Kolbens der Fig. 1 können an dem hochdruckseitigen Dichtring 27e gleichfalls vorhanden sein.The
Fig. 11 zeigt eine Variante des Kolbens der Fig. 8-10, die sich von diesem Kolben im Wesentlichen dadurch unterscheidet, dass die Ringaussparung 25f, die die beiden axial nebeneinander angeordneten Dichtringe 27f und 79f führt, hochdruckseitig durch eine konvex-konische, d.h. zur Niederdruckseite hin sich verjüngende Stirnfläche 29f begrenzt ist, während die hochdruckseitige Stirnfläche 85 des hochdruckseitigen, geschlitzten Dichtrings 27f konkav-konisch ausgebildet ist. Die beiden Konusflächen 29f und 85 haben gleichen Konuswinkel und damit zueinander parallele Erzeugende.Fig. 11 shows a variant of the piston of Figs. 8-10, which differs from this piston substantially in that the annular recess 25f, which leads the two axially adjacent sealing rings 27f and 79f, high pressure side by a convex-conical, i. to the low pressure side is tapered end face 29 f is limited, while the high-pressure side end face 85 of the high-pressure side, slotted sealing ring 27 f is concave-conical. The two
Der Dichtring 27f ist radial elastisch und mit radialem Spiel in der Ringaussparung 25f gehalten, so dass zwischen den Konusflächen 29f und 85 ein konischer Ringspalt 87 verbleibt, durch den wiederum Schmelze in den Ringspalt 53f eintreten kann, die aufgrund der Kühlung in den Ringspalten 53f und 87 erstarrt und für eine Abdichtung des Dichtrings 27f relativ zum Kolben 1f sorgt. Mit wachsender Abnutzung des Dichtrings 27f wird der Ringspalt 87 breiter, womit mehr Schmelzematerial in den Ringspalt 87 eindringen kann, das nach dem Erstarren die Abdichtwirkung verbessert.The sealing ring 27f is held radially elastic and with radial play in the annular recess 25f, so that between the conical surfaces 29f and 85 a conical
Die konische Gestaltung der hochdruckseitigen Stirnfläche läßt sich auch bei niederdruckseitig angeordneten Dichtringen, wie z.B. dem Dichtring 67 des Kolbens der Fig. 6, nutzen.The conical design of the high pressure side end face can also be used in low pressure side sealing rings, such as. the sealing
Die anhand der Fig. 1 erläuterten Komponenten 43 und 44 können auch bei dem Dichtring 27f vorgesehen sein. Darüber hinaus können, wie bei 83f in Fig. 11 angedeutet, zusätzlich als Nuten ausgebildete Kanäle am Umfang des Vorsprungs 45f verteilt vorgesehen sein, die zusätzliche Schmelze in den Ringspalt 53f einführen.The explained with reference to FIG. 1
Bei den vorstehend erläuterten Kolben sind die beiden Kolbenteile durch Schrauben miteinander verbunden. Die Fig. 12 und 13 zeigen eine Variante, bei welcher der erste Kolbenteil 3g mit dem zweiten Kolbenteil 11g über eine Bajonettverbindung mit mehreren, in Umfangsrichtung verteilt angeordneten Bajonettvorsprüngen 89 und 91 an jedem der beiden Kolbenteile 3g und 11 g. Die Bajonettvorsprünge 89, 91 sind jeweils durch Lücken 93 voneinander getrennt, so dass die Kolbenteile 3g, 11 g axial ineinander gesteckt und durch Verdrehen relativ zueinander in eine Eingriffstellung gebracht werden können. Zwischen einander axial benachbarten Stirnflächen der über die Bajonettvorsprünge 89, 91 hinweg verlaufenen Teilungsfläche 33g ist wiederum ein Abdichtring 41 g angeordnet. Die Bajonettverbindung der Fig. 12 und 13 kann bei jeder der vorangegangenen Ausgestaltungen des Kolbens eingesetzt werden.In the above-explained piston, the two piston parts are connected by screws. 12 and 13 show a variant in which the first piston part 3g with the second piston part 11g via a bayonet connection with a plurality of circumferentially distributed
Claims (23)
- Piston in the form of a cap (1d), which can be detachably fastened to the end on the high pressure side of a piston rod (9d) that is axially displaceable in a casting cylinder (7d) of a cold-chamber diecasting machine, said cap having a peripheral wall and an end wall (15d) that seals the cap (1d) on the high pressure side, at least one sealing ring (27d, 67, 69) being arranged on the outer periphery of the peripheral wall,
the cap (1d) comprising two piston parts (3d, 11d), which butt axially against each other in a separating surface (33d), are detachably fastened to each other to form a structural unit and of which a first piston part (3d) is formed as a bush that forms at least a portion of the peripheral wall and a second piston part (11d) forms at least the end wall (15d) and seals the bush on the high pressure side, characterized in that the sealing ring (67, 69) is formed as a slit sealing ring and a number of radially acting spring elements (73), which press the sealing ring (67, 69) radially outwards, are arranged distributed in the peripheral direction on the outer periphery of the first piston part (3d). - Piston according to Claim 1, characterized in that the first piston part (3d) has fastening elements, in particular bayonet fastening elements (5d), for the detachable fastening of the piston to the piston rod (9d).
- Piston according to Claim 1 or 2, characterized in that the first piston part (3d) has a number of axial through-holes (35d) which are arranged distributed in the peripheral direction and through which the second piston part (11d) is screwed onto the first piston part (3d) by means of fastening screws (37d), in that the axial through-holes (35d) for the fastening screws (37d) are provided in the wall of the bush.
- Piston according to Claim 1 or 2, characterized in that the first piston part (3g) and the second piston part (11g) are detachably fastened to each other by means of a bayonet coupling (89, 91).
- Piston according to one of Claims 1 to 4, characterized in that arranged between end faces of the first piston part (3d) and the second piston part (11d), which lie axially opposite each other and form the separating surface (33d), is a sealing ring (41d), which seals the end faces with respect to each other.
- Piston according to one of Claims 1 to 5, characterized in that the second piston part (11d) forms in the region of its piston face (15d) a space (19d) that can be charged with coolant.
- Piston according to one of Claims 1 to 6, characterized in that the sealing ring (27c, d) is formed as a slit sealing ring enclosing the second piston part (3c, d), in particular a sealing ring provided with a stepped slit, and the separating surface (33c, d) between the first piston part (3c, d) and the second piston part (11c, d) is offset by an axial distance towards the low pressure side in relation to the edge of the sealing ring (27c, d) on the low pressure side.
- Piston according to Claim 7, characterized in that a securing pin (57c, d), running axially and engaging in the sealing ring (27c, d) to secure it against rotation is arranged on the low pressure side of the sealing ring (27c, d).
- Piston according to Claim 8, characterized in that the securing pin (57c, d) is held in the second piston part (11c, d).
- Piston according to one of Claims 7 to 9, characterized in that the first-mentioned sealing ring (27c, d) is axially fixed on the second piston part (11c, d), in that the separating surface (33c, d) ends in an annular relief (61; 61d) enclosing the outer periphery of the first piston part (3c, d) and overlapping at least part of its axial extent, and in that at least a second sealing ring (59; 67, 69) is arranged in the annular relief (61; 61d).
- Piston according to Claim 10, characterized in that the second sealing ring (59; 67, 69) is arranged at an axial distance from the first sealing ring (27c, d).
- Piston according to Claim 10 or 11, characterized in that the second sealing ring (59; 67, 69) is formed as a slit sealing ring, resiliently opening out radially to an oversize outside the pressure cylinder (7c).
- Piston according to Claim 12, characterized in that the second sealing ring (59) has an insertion taper (67) on its outer edge on the high pressure side.
- Piston according to one of Claims 10 to 13, characterized in that the second sealing ring (59) is formed as a slit sealing ring, the edges (69, 71) of which that form the slit forming at least a tongue (73) projecting in the peripheral direction and a relief (25) lying opposite the tongue (73) in the peripheral direction, in which relief the tongue (23) engages in an axially close-fitting manner but movably in the peripheral direction.
- Piston according to Claim 14, characterized in that each of the two edges (69, 71) of the second sealing ring that form the slit forms at least one tongue (73) each.
- Piston according to one of Claims 1 to 15, characterized in that the cap (1) can be cooled at least in the region of the end wall (15) of the second piston part (11) by a cooling medium that can be introduced into the cap (1),
in that the sealing ring (27) is arranged such that it is fixed but movable with play in an annular relief (25) in the region of the end wall (15) on the outer periphery of the cap (1),
in that the second piston part (11) projects axially beyond the sealing ring (27) on the high pressure side and reaches radially over the sealing ring (27), over part of its radial thickness, on the high pressure side with a projection (45), the radially outer peripheral surface of which that is adjacent to the sealing ring (27) on the high pressure side bounding between itself and the casting cylinder (7) an annular gap (47) that can be cooled to solidifying temperature in the casting operation. - Piston according to one of Claims 1 to 16, characterized in that the sealing ring (27) has a radially elastic annular body with a slit that is continuous both axially and radially, in particular a slit that is stepped in the peripheral direction, in that the outer peripheral surface of the annular body has near its axial end on the high pressure side an outer contact-making annular surface (44), which is intended for making contact with the inner peripheral surface of the casting cylinder (7) and the axial length of which is less than the axial length of an inner annular surface on the inner periphery of the annular body that axially overlaps this outer contact-making annular surface (44) and can be exposed to the molten material, in particular molten metal material, and
in that, on the low pressure side of the outer peripheral surface of the annular body, the outer contact-making annular surface (44) is adjoined at least over a partial region of the remaining axial length of the annular body by an annular surface portion (43) of which the diameter is less than the diameter of the outer contact-making annular surface (44). - Piston according to Claim 17, characterized in that the annular surface portion (43) of reduced diameter has an at least approximately frustoconical form and tapers towards the axial end of the annular body on the low pressure side.
- Piston according to one of Claims 1 to 18, characterized in that the sealing ring (27b, c, d, e) is fixed in the region of the end wall (15d) on the outer periphery of the cap (1d), and
in that an annular gap (53d) that is open on the high pressure side of the sealing ring (27d) at least over part of its peripheral surface towards the high pressure side of the casting cylinder (7d) is provided between the inner peripheral surface of the sealing ring (27d) and the outer peripheral surface of the cap (1d). - Piston according to Claim 19, characterized in that the sealing ring (27e) is arranged in an annular relief (25e) on the outer periphery of the cap (1e),
in that the second piston part (11e) reaches radially over the sealing ring (27e) over part of its radial thickness on the high pressure side with a projection (45e), and
in that the projection (45e) has distributed in the peripheral direction a number of axial channels (83), which are formed in particular as grooves and connect the high pressure side of the casting cylinder (7e) to the annular gap (53e). - Piston according to one of Claims 1 to 20,
characterized in that the sealing ring (27f) is arranged in an annular relief (25f) on the outer periphery of the cap (1f), the side faces (29f, 31f) of which run with approximately the same contour as the axial end faces of the sealing ring (27f), and
in that the axial end face (85) of the sealing ring (27f) on the high pressure side and the axially adjacent side face (29f) of the annular relief (25f) are formed as conical surfaces. - Piston according to one of Claims 1 to 21, characterized in that at least the second piston part (3) consists of steel.
- Piston according to one of Claims 1 to 22, characterized in that two sealing rings (67, 69) that are pressed radially outwards by radially acting spring elements (73) are provided.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE20309181U DE20309181U1 (en) | 2003-06-13 | 2003-06-13 | Multi-part piston for a cold chamber die casting machine |
PCT/EP2004/006321 WO2004110679A1 (en) | 2003-06-13 | 2004-06-11 | Piston for a cold chamber die casting machine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1635973A1 EP1635973A1 (en) | 2006-03-22 |
EP1635973B1 true EP1635973B1 (en) | 2007-08-15 |
Family
ID=33395152
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04739812A Expired - Lifetime EP1635973B1 (en) | 2003-06-13 | 2004-06-11 | Piston for a cold chamber die casting machine |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP1635973B1 (en) |
AT (1) | ATE369929T1 (en) |
DE (2) | DE20309181U1 (en) |
ES (1) | ES2293275T3 (en) |
WO (1) | WO2004110679A1 (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005048717A1 (en) | 2005-10-12 | 2007-04-19 | Allper Ag | Multi-part piston for a cold chamber casting machine |
WO2008123009A1 (en) * | 2007-04-05 | 2008-10-16 | Italpresse Industrie S.P.A. | Sealing device for injection system of die-casting machines |
BRPI0703362A2 (en) * | 2007-08-15 | 2009-03-31 | W Fischer Tecnica Ltda | cast metal injection piston |
DE202010008596U1 (en) | 2010-09-21 | 2010-12-02 | Schmelzmetall (Deutschland) Gmbh | Die-cast pistons |
DE102011052446A1 (en) | 2011-08-05 | 2013-02-07 | Schmelzmetall Ag | Die-cast piston head |
CN106623839B (en) * | 2015-11-03 | 2020-01-14 | 广东科达洁能股份有限公司 | Casting forming machine |
WO2018119517A1 (en) * | 2016-12-30 | 2018-07-05 | Exco Technologies Limited | Die-casting piston, and die-casting apparatus incorporating same |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3300822A (en) * | 1965-05-03 | 1967-01-31 | Gen Motors Corp | Die casting plunger piston ring |
DE3305594C1 (en) * | 1983-02-18 | 1984-07-19 | Friedrich 8192 Geretsried Glas | Casting piston for die casting machines |
SU1225680A2 (en) * | 1984-11-06 | 1986-04-23 | Yagin Vasilij P | Pressing plunger of die=casting machine |
JPH0246961A (en) * | 1988-08-04 | 1990-02-16 | Hitachi Metals Ltd | Plunger tip |
EP0525229B1 (en) * | 1991-07-29 | 1996-11-06 | Allper Ag | Piston, especially for pushing out liquid metal from a pouring cylinder |
EP0901852B1 (en) * | 1997-09-09 | 2002-07-17 | André Müller | Plunger for a hot-chamber die-casting machine |
JP3793646B2 (en) * | 1998-07-17 | 2006-07-05 | 修 山本 | Die-casting machine plunger device and die-casting machine |
AU2002257612A1 (en) * | 2002-03-04 | 2003-09-16 | Allper Ag | Sealing ring and piston for a pressure die casting cylinder |
-
2003
- 2003-06-13 DE DE20309181U patent/DE20309181U1/en not_active Expired - Lifetime
-
2004
- 2004-06-11 WO PCT/EP2004/006321 patent/WO2004110679A1/en active IP Right Grant
- 2004-06-11 DE DE502004004662T patent/DE502004004662D1/en not_active Expired - Fee Related
- 2004-06-11 EP EP04739812A patent/EP1635973B1/en not_active Expired - Lifetime
- 2004-06-11 AT AT04739812T patent/ATE369929T1/en not_active IP Right Cessation
- 2004-06-11 ES ES04739812T patent/ES2293275T3/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
DE20309181U1 (en) | 2004-10-28 |
WO2004110679A1 (en) | 2004-12-23 |
EP1635973A1 (en) | 2006-03-22 |
DE502004004662D1 (en) | 2007-09-27 |
ATE369929T1 (en) | 2007-09-15 |
ES2293275T3 (en) | 2008-03-16 |
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