EP2729293A2 - Machine de moulage par soufflage pourvue d'un vérin pneumatique à compensation de force pour compresseur à piston - Google Patents

Machine de moulage par soufflage pourvue d'un vérin pneumatique à compensation de force pour compresseur à piston

Info

Publication number
EP2729293A2
EP2729293A2 EP12732834.2A EP12732834A EP2729293A2 EP 2729293 A2 EP2729293 A2 EP 2729293A2 EP 12732834 A EP12732834 A EP 12732834A EP 2729293 A2 EP2729293 A2 EP 2729293A2
Authority
EP
European Patent Office
Prior art keywords
pressure
force
cylinder
fluid
blow molding
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.)
Withdrawn
Application number
EP12732834.2A
Other languages
German (de)
English (en)
Inventor
Jochen Hirdina
Heinrich Bielmeier
Konrad Senn
Günter Winkler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Krones AG
Original Assignee
Krones AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Krones AG filed Critical Krones AG
Publication of EP2729293A2 publication Critical patent/EP2729293A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
    • B29C49/42—Component parts, details or accessories; Auxiliary operations
    • B29C49/58—Blowing means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
    • B29C49/42—Component parts, details or accessories; Auxiliary operations
    • B29C49/4284—Means for recycling or reusing auxiliaries or materials, e.g. blowing fluids or energy
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C2949/00—Indexing scheme relating to blow-moulding
    • B29C2949/07—Preforms or parisons characterised by their configuration
    • B29C2949/0715—Preforms or parisons characterised by their configuration the preform having one end closed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
    • B29C49/02—Combined blow-moulding and manufacture of the preform or the parison
    • B29C49/06—Injection blow-moulding
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
    • B29C49/08—Biaxial stretching during blow-moulding
    • B29C49/10—Biaxial stretching during blow-moulding using mechanical means for prestretching
    • B29C49/12—Stretching rods
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
    • B29C49/42—Component parts, details or accessories; Auxiliary operations
    • B29C49/4236—Drive means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
    • B29C49/42—Component parts, details or accessories; Auxiliary operations
    • B29C49/4284—Means for recycling or reusing auxiliaries or materials, e.g. blowing fluids or energy
    • B29C49/42845—Recycling or reusing of fluid, e.g. pressure
    • B29C49/42855—Blowing fluids, e.g. reducing fluid consumption
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
    • B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
    • B29C49/00—Blow-moulding, i.e. blowing a preform or parison to a desired shape within a mould; Apparatus therefor
    • B29C49/42—Component parts, details or accessories; Auxiliary operations
    • B29C49/78—Measuring, controlling or regulating
    • B29C49/783—Measuring, controlling or regulating blowing pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
    • Y02P70/10—Greenhouse gas [GHG] capture, material saving, heat recovery or other energy efficient measures, e.g. motor control, characterised by manufacturing processes, e.g. for rolling metal or metal working

Definitions

  • the invention relates to a blow molding machine for blow molding plastic containers with at least one blowing unit for stretch blow molding of preforms by means of compressed air according to the preamble of patent claim 1, and to a corresponding method for blow molding containers according to the preamble of claim 16.
  • the container In blow molding machines for stretch blow molding of plastic containers, the container is formed from a preform and formed into a container by means of compressed air.
  • compressed air is required at pressures of for example 25 to 40 bar.
  • This compressed air is typically generated by means of one or more high pressure compressors.
  • This compressed air is in the value chain of a container production, for example, in addition to polyethylene terephthalate (PET) a major energy consumers.
  • PET polyethylene terephthalate
  • Various compressed air recycling systems and special bottle shapes are a reaction on the part of the blowing technology with regard to a possible reduction of energy consumption.
  • DE 10 2009 019 008 A1 shows a method for blow-molding containers, in which a preform is thermoformed in the container after thermal conditioning within a blow mold of a blow molding machine by blowing pressure. At least one Part of the stored within the blown container pneumatic pressure energy converted into mechanical drive energy.
  • the invention provides a blow molding machine for blow molding plastic containers with at least one blowing unit for preforms by means of compressed air, wherein the blowing unit has a force equalization, so that at least part of the occurring compression force is compensated, wherein the blowing unit comprises a pressure piston and a pressure cylinder includes.
  • the blow molding machine as described above may further include a fluid pressure accumulator.
  • the fluid pressure accumulator can also be referred to in short form as a fluid reservoir.
  • the fluid pressure accumulator can be compared for example with a compression spring which releases its force during the gas compression / compression and is mechanically tensioned again during the piston return stroke.
  • the blow molding machine described above may further comprise in its fluid pressure accumulator a second pressure piston in a second pressure cylinder, wherein the second pressure cylinder may be at least partially filled with a fluid, for example a hydraulic fluid or compressed air.
  • a fluid for example a hydraulic fluid or compressed air.
  • the second pressure piston thus moves in the second pressure cylinder and biases or relaxes the fluid.
  • a compressive force can also be provided to the force balance via the fluid.
  • a force can be absorbed by means of the second pressure piston or made available to the force compensation again. This happens, for example, by the second pressure piston is moved in the second pressure cylinder.
  • the blow molding machine described above may further include in the force balance, a wheel, such as a flywheel, wherein on the wheel, a connecting rod is attached, which receives the force of the pressure piston.
  • a wheel such as a flywheel
  • the force is typically stretched to stretch blow molding of the preform and, after the preform is inflated to its predetermined size of the ram, "is released again, so can up on the wheel or be discharged.
  • the construction with the wheel has the advantage that the clock movement of the pressure piston can be converted into a circular motion of the wheel.
  • the wheel of the force balance of the blow molding machine, as described above, can also be connected to the fluid pressure accumulator. Through this connection, the wheel can take on one side, the force of the pressure piston or vice versa give power to the pressure piston and also tension the piston of the fluid pressure accumulator respectively relax. It is understood that optionally between the pressure piston and the force balance, such as the wheel, a drive can be provided.
  • the above-described blowing machine in the force balance may comprise a surge tank, which is connected to the second pressure cylinder.
  • the expansion tank may be configured to at least partially receive the fluid from the second pressure cylinder.
  • the surge tank can therefore typically be connected to the second pressure cylinder.
  • the surge tank allows storage of the fluid when the second pressure piston is tensioned in the second pressure cylinder.
  • the fluid from the surge tank can run back into the second pressure cylinder, for example, be sucked when the second pressure piston is relaxed again. This has the advantage that storage of pressure energy can be possible by means of the fluid and the expansion tank.
  • the fluid pressure cylinder within the force balance of the blow molding machine may be formed as a water hydraulic system, wherein substantially water is used as the hydraulic fluid.
  • substantially water is used as the hydraulic fluid.
  • it may thus be possible to be able to provide a particularly simple hydraulic fluid which is harmless within the scope of the system.
  • other liquids or mixtures for example an oil-water mixture, as a hydraulic fluid within the blow molding machine described above.
  • the printing cylinder in the expanded state can be pressurized.
  • the size of the impression cylinder can be controlled and the impression cylinder does not have to be too large.
  • a blow molding machine may include a second blowing unit connected to the force balance, wherein the second blowing unit may substantially have the characteristics as described above with reference to the first blowing unit.
  • At least part of the occurring compression force can be used alternately in or from the first and the second blowing unit.
  • excess compression force can be used by the first blowing unit in the second blowing unit and vice versa.
  • This process can be done by mediating the pressure equalization as described above, so that in particular force peaks can be avoided. This makes it possible to match two blowing units exactly to each other and to ensure a particularly efficient operation by the vote.
  • the force balance may comprise a passive and an active actuator, wherein the passive actuator may comprise a spring and / or a pneumatic cylinder and / or a hydraulic cylinder and wherein the active actuator an electromechanical cylinder and / or may comprise a linear motor and / or a hydraulic cylinder, wherein the active actuator can be combined with a threaded spindle or a ball screw.
  • the passive actuator may comprise a spring and / or a pneumatic cylinder and / or a hydraulic cylinder and wherein the active actuator an electromechanical cylinder and / or may comprise a linear motor and / or a hydraulic cylinder, wherein the active actuator can be combined with a threaded spindle or a ball screw.
  • the force required for blow molding in the blow molding machine can be divided into two force components.
  • the passive actuator can absorb the greater part of the force.
  • a smaller, variable force component can typically be dispensed with on the active actuator.
  • the active actuator can be used for compression, whereby energy can be saved.
  • the force balance as described above may include a toggle mechanism.
  • the active and / or the passive actuator can be incorporated in the toggle mechanism.
  • the force balance may include a scissors joint.
  • the active and / or the passive actuator can be incorporated in the scissors joint.
  • the scissors joint can also be connected to the toggle mechanism.
  • the invention also provides a method of blow molding containers comprising the steps of: docking a preform to a blowing unit comprising a pressure piston and a pressure cylinder, stretch blow molding the preform into a finished container by means of compressed air, undocking the finished container; wherein at least a part of the compression force is compensated by a force balance.
  • blowing machine and the method as described above thus offer the advantages of more even utilization of the piston drive and thus the energy savings and also a possible smaller dimensions of the piston drive. As a result, force peaks when driving can be reduced or even avoided.
  • FIG. 2 sketch of a blowing unit according to the invention with a force balance.
  • FIG. 3 sketch of a fluid pressure accumulator according to the invention.
  • FIG. 4 Sketch of the force compensation as a function of the compression according to the
  • FIG. 5A sketch of a further development of the force balance with fluid pressure accumulator according to the invention.
  • FIG. 5B Sketch of the force balance with fluid pressure accumulator in a relaxed state of the fluid pressure accumulator.
  • FIGS. 5A and 5B shows a sketch of the resulting force as a function of the travel of the printing cylinder according to the embodiment of FIGS. 5A and 5B,
  • FIG. 7 sketch of a blow molding machine blow molding of plastic containers with two blowing units according to a development of the invention.
  • Fig. 8A u. 8B Sketch of a further development of the force compensation with a passive and an active actuator with a lever mechanism, wherein different stages of the compression are shown.
  • 9A and 9B sketch of a further development of the force compensation with a passive and an active actuator and a lever mechanism, wherein different stages of compression are shown.
  • FIG. 10A Sketch of a further development of the force compensation with a passive and an active actuator and a lever mechanism, whereby different stages of the compression are shown.
  • Figs. 1A to 1F show a blowing cycle such as occurs in a blow molding machine for blow molding plastic containers with at least one blower unit.
  • a preform 10A is docked to the blowing unit.
  • the preform 10A may be made of PET or other suitable material.
  • the blowing unit shown further comprises a pressure cylinder 4, in which a pressure piston 5 can be moved.
  • a feed pump 9 compressed air / compressed air can be conducted into the pressure piston 5 with a relaxed pressure piston 5.
  • a valve 2A On the side of the feed pump 9 is a valve 2A.
  • a valve 2B On the side of the docked preform 10A.
  • the valve 2A can be opened and the pressure cylinder can be filled with pre-pressure.
  • the pre-pressure can be about 4 to 12 bar.
  • Fig. 1B shows the next step.
  • the valve 2B is opened and, by the pre-pressure in the pressure cylinder, the preform 10A inflated to Vorblasflasche 10B.
  • FIGS. 1A to 1F no pre-blow molds for forming the preforms 10A to be blown are shown.
  • the units shown in these figures are pre-blow bottles.
  • FIGS. "IC shows the next step of the blowing cycle.
  • the valve 2A is closed, so that no further pressure by the supply pump is more filled into the pressure cylinder 4, the piston of the pressure cylinder 4 is tensioned, whereby the pressure in the system is increased.
  • the valve 2B is opened, the pressure in the pre-blowing bottle 10B is further increased so that it expands to the pre-blowing bottle 10C.
  • Fig. 1 D is shown that the pressure cylinder 4 is almost completely tensioned with pressure piston 5.
  • the Vorblasflasche is now inflated to a bottle with Fertigblastik. This bottle with finished blowing pressure is designated by the reference numeral 10D.
  • Fig. 1 F the valve 2B is closed.
  • the pressure piston 5 has returned to its starting position in the pressure cylinder 4.
  • the finished bottle 10F is undocked by the blowing unit and can be transferred to further manufacturing steps.
  • FIG. 2 shows a preform 1A in a blow mold 1 on a blowing unit 30A.
  • the blow mold 1 is held by a holder (not shown) with a valve 2.
  • a stretching unit 3 Above the valve 2 is a stretching unit 3.
  • the stretching unit 3 with the valve 2 and the holder with the preform 1A are connected to a pressure cylinder 4 with pressure piston 5.
  • Pressure cylinder 4 and pressure piston 5 can correspond to the pressure cylinder 4 and pressure piston 5 of Fig. 1 A to 1 F.
  • the impression cylinder 4 of the blowing unit 30A has a low-pressure air passage 8.
  • the low-pressure passage 8 has a valve 8A.
  • the valves 2 and 8A may correspond in their operation to the valves 2A and 2B of FIGS. 1A to 1F.
  • the 2 also shows a drive 6 for the pressure cylinder 4 with pressure piston 5.
  • the drive 6 may be a suitable motor drive, which is able to exert a force on the pressure piston 5 in pressure cylinder 4, ie the pressure piston 5 in the pressure cylinder 4 to tension or the pressure piston 5 in the pressure cylinder 4 to relax again.
  • the drive 6 is further connected to a force compensation 7, which is adapted to receive or compensate for a compression force which is received via the pressure piston 5.
  • Fig. 3 shows a fluid pressure accumulator 50.
  • This is exemplified as a hydraulic pressure accumulator.
  • This hydraulic accumulator 50 may be included in the force balance 7. Furthermore, it is possible for the hydraulic accumulator 50 to be connected separately to the force compensator 7.
  • the hydraulic pressure accumulator 50 as shown in Fig. 3, comprises a filling valve 51 for a filling gas such. Nitrogen.
  • a nitrogen filling 52 forms a gas bundle 52.
  • the gas bundle 52 such as nitrogen gas, may move the hydraulic pressure piston 53, which additionally has seals 53A, inside the hydraulic pressure accumulator 50.
  • the hydraulic pressure piston 53 operates against a hydraulic fluid 54, which is shown in Fig. 3 in the lower part.
  • the hydraulic accumulator 50 has a hydraulic connection 55. Via the hydraulic side of the hydraulic likdruckpeicher 50 with hydraulic pressure cylinder 56, a force can be transmitted. The pressure is provided via the nitrogen bundle 52.
  • FIG. 4 shows, by way of example, the force required in relation to the compression for the normal case 11 for the development as shown in FIG.
  • the fields 112a and 112b can be compensated in accordance with the force compensation indicated by the reference numeral 11.
  • the resulting force is typically a force that represents a uniform drive load and contains significantly less or no force peaks.
  • the curve 11 is cycled many times. Without compensation, large force fluctuations, ie force peaks, would occur.
  • the curve 1 1 1 would therefore for example heavily jagged.
  • the force compensation can "the force peaks are heavily smoothed as the curve 1 13 shown by way of example, and a uniform force as a function of compression can be provided.
  • FIGS. 5A and 5B show a further development of the force compensation 7 with a fluid pressure accumulator 16.
  • FIGS. 5A and 5B show different compression phases, ie voltage phases, of a pressure cylinder 15, which is referred to as a second pressure cylinder, and of the fluid pressure accumulator 16
  • the fluid pressure accumulator is exemplified as a hydraulic pressure accumulator.
  • the fluid pressure accumulator 16 may, for example, at least partially filled with a hydraulic fluid as fluid. However, it is also possible to fill the fluid pressure accumulator 16 with another fluid, for example with compressed air.
  • Fig. 5A shows a wheel 11, which may be for example a flywheel.
  • This wheel 1 1 can be connected via a connecting rod 12 with the blowing unit, as outlined in Figure 2. That is, the connecting rod 12 may be suitably connected to the drive 6 in order to be able to deliver a force to the pressure cylinder 4 with its pressure piston 5 via the drive 6.
  • the connecting rod 12 may be one or more parts.
  • the connecting rod 12 is sketched in two parts, for example.
  • the connecting rod 1 is typically fastened near the circumference of the wheel 11.
  • the attachment of the connecting rod 12 or at least the first element of the connecting rod 12 is formed, for example, movable.
  • the wheel 11 is connected to the fluid pressure accumulator 16.
  • the fluid pressure accumulator 16 includes the pressure piston 13, which is referred to as a second pressure piston.
  • the second pressure piston 13 can move in the second pressure cylinder 15.
  • the second pressure cylinder 15 may be a hydraulic pressure cylinder.
  • the second pressure cylinder 15 comprises a pneumatic pressure cylinder.
  • the force direction of the second pressure piston 13 inside half of the second pressure cylinder 15 is exemplified by an arrow with the letter F H indicated.
  • the direction of force indicated by the arrow F H in FIG. 5A is decisive, for example, for relaxing the second pressure cylinder 15. Accordingly, the opposite direction with respect to the arrow F H is decisive for the tensioning of the second pressure cylinder 15.
  • the second pressure cylinder 15 further includes a fluid, such as a hydraulic fluid 14a.
  • the hydraulic fluid 14 a can be compressed by the second pressure piston 13 within the second pressure cylinder 15 of the fluid pressure accumulator 16.
  • the second pressure cylinder 15 is connected to a surge tank 14.
  • the surge tank 14 is formed, for example, " during clamping of the second pressure cylinder 15, the fluid, so for example to be able to receive the hydraulic fluid 14A from the second pressure cylinder 15.
  • FIG. 5B shows the development of FIG. 5A in the state in which the fluid pressure cylinder 15 has received a maximum amount of fluid, for example hydraulic fluid 14a, from the expansion tank 14.
  • a maximum amount of fluid for example hydraulic fluid 14a
  • the second pressure piston 13 is practically maximally withdrawn, i. the second pressure piston 13 is in the end position with respect to the second pressure cylinder 15. At the same time, the maximum force in the direction of the blowing unit (not shown here) is given off, as indicated by the vertical arrow F.
  • the connecting rod 12 is substantially stretched.
  • the connecting rod 12 may also be multi-part. In the case of a multi-piece connecting rod 12 all parts of the connecting rod 12 form a substantially straight line.
  • the second pressure piston 13 is movably mounted on the side facing away from the second pressure cylinder 15 on the wheel 1 1.
  • the second pressure piston 13 is also attached near the circumference of the wheel 1 1. This attachment is similar to the attachment of the connecting rod 12, but may typically be made at a point far from the attachment of the connecting rod 12 near the circumference of the wheel 11.
  • the fluid pressure member 16 has another suspension 19.
  • the suspension 19 may be provided on the closed side of the second pressure cylinder 15, for example. With the help of the suspension 19, the fluid pressure cylinder 16 can follow the movement of the wheel 1 1 in a suitable manner. It is understood that other movable suspensions of the elements sketched in FIGS. 5A and 5B are possible.
  • FIG. 6 shows by way of example the force as a function of the path according to the development of FIGS. 4, 5A and 5B.
  • Curve 101 of FIG. 6 shows, by way of example, the uncompensated compression force in pressure cylinder 4.
  • Curve 102 shows by way of example the force provided by force compensation 7. It should be noted in the illustration in Fig. 6 that the ordinate sketched here carries a double arrow and the zero point is located approximately in the middle of the ordinate.
  • the force compensation 7 corresponding to the curve 102 compensates the compression force of the pressure cylinder 101.
  • the resulting force ie the sum of the forces corresponding to the curves 101 and 102, is represented by the curve 103 by way of example.
  • the resulting force as exemplified in Fig. 6, for example, be kept below 2% of the maximum force of the pressure piston 5.
  • the maximum force of the pressure piston 5 is shown in FIG. 6 by way of example by the maximum of the curve 101 at the right edge of the graph. Accordingly, the drive of the embodiment of FIGS. 4 to 6 may no longer have to be designed for a force of, for example, 40 kN, but, for example, a force of only about 1 kN would suffice.
  • FIG. 7 shows a further development of the blow molding machine with a second blowing unit 30B in addition to the first blowing unit 30A.
  • the blowing units 30A and 30B are connected to a force balance 17.
  • the force balance 17 may be configured similar to the force balance 7, which has already been described above.
  • the blowing units 30A and 30B may be substantially the same, Fig. 7 shows that in the blowing unit 30A, a preform 1 A is not yet blown. On the other hand, in the unit 30B, a finished bottle 1B is blown in the tuyere 1.
  • the pressure piston 5 of the pressure cylinder 4 of the unit 30B is substantially completely tensioned.
  • a portion of the compression force released in one unit, here 30A, can be provided to the other unit 30B via the drive 6 of the unit 30A and the corresponding drive 6, and vice versa.
  • the force balance 17 ensures a further smoothing of the force that can be provided alternately between the two blowing units 30A and 30B. It would also be conceivable that the two blowing units 30A and 30B are connected to a pressure connection, for example a pipe, but each of the units 30A and 30B has its own force balance (not shown here).
  • FIGS. 8A and 8B show a further development of the blow molding machine.
  • the increase in force in compression and blow molding is direct Drive very high. That is, at the end of the compression, a very high force would have to be applied, which would require a very large drive.
  • the total force "shown in Figures 4 and 6, can be divided into two force components.
  • the distribution is such that the largest possible proportion corresponds to a force curve of a passive actuator and only a small variable force component must be applied by a drive.
  • the greater part of the total force can be applied by means of a passive actuator, for example a spring and / or a pneumatic cylinder and / or a hydraulic cylinder. It is understood that these elements can also be used in any combination as a passive actuator. For this purpose, only a drive with low power is required as an active actuator for compacting.
  • FIG. 8A shows a toggle mechanism 70 with which the force on the pressure cylinder 4 can be deflected into a uniform course for the drive mechanism 70, for example shown in FIG.
  • the greater proportion of the driving force is applied by a passive actuator, such as a hydraulic cylinder / pneumatic cylinder 75 or a spring.
  • the remaining, variable component can be realized by an active actuator, for example by an electromechanical cylinder, a drive M in the form of a rotary or servomotor 71, or by another hydraulic cylinder.
  • the drive M can be combined with a threaded spindle or ball screw 73.
  • the reference numeral 73 denotes a threaded spindle or ball screw with associated (motion) thread.
  • Figure 8A shows posts / fixtures 72L, 72R and 72T.
  • the pneumatic cylinder / hydraulic cylinder 75, the threaded spindle 73 and a rotary or servomotor 71 are fixed between the pillars 72L and 72R.
  • FIG. 8A also shows by reference numeral 76 a plain bearing. The sliding bearing serves to guide a rod 76S.
  • the toggle mechanism 70 is shown in Figure 8A in the start position, in which the pneumatic piston / hydraulic piston of the pneumatic cylinder / hydraulic cylinder is pushed out completely.
  • Figure 8B shows the same elements as in Figure 8A. In this case, however, the toggle mechanism 70 is shown in the position in which the piston 5 is pushed maximum downward in the pressure cylinder 4, so the highest pressure is generated for blow molding.
  • FIG. 9A shows a further development of the drive mechanism 70, as has already been discussed with reference to FIGS. 8A and 8B.
  • the mechanism 80 shown in Figure 9A is characterized in that lower supporting forces are introduced into the surrounding housing.
  • the hydraulic / pneumatic cylinder 75 and the actuator for the drive are here between a Scherengelenk 80.
  • the passive actuator in the form of the pneumatic cylinder or hydraulic cylinder 75 is located between the points C and D of the scissors linkage 80.
  • the active actuator is located between the points A and B of the scissors linkage 80.
  • the drive M may take the form of another hydraulic cylinder / Pneumatic cylinder 79 or in the form of a motor, for example a linear motor can be realized.
  • the reference numeral 74 denotes a threaded spindle or ball screw, which can be combined with the drive M.
  • Fig. 9A shows the toggle mechanism 80 in the start position, in which the pneumatic piston / hydraulic piston of the pneumatic cylinder / hydraulic cylinder 75 is pushed out completely. In this case, the piston 5 is biased in the pressure cylinder 4.
  • Fig. 9B shows the mechanism 80 in the position in which the piston 5 is pushed completely down in the pressure cylinder 4, so the highest blowing pressure is generated for blow molding. In this case, the punch of the pneumatic piston / hydraulic piston 75 is pushed in maximum.
  • Figs. 8A, 8B, 9A and 9B The principle of the examples shown in Figs. 8A, 8B, 9A and 9B is as follows.
  • a drive is described, which is designed to control the movement of the piston 4 significantly alone. Without force compensation depending on the compression of the blowing air in the cylinder 4 a lot of power (power) needed for compression. This would be dependent on the position of the piston 5.
  • the maximum required force can be reduced because the transferable moment is greatest at the time of greatest compression due to the leverage laws. If the toggle lever is at a very large angle, only minor moments (forces) can be transmitted by the lever laws. However, these are then not needed, because at this time less compression of the piston 5 must be made.
  • the passive actuator may also be a spring, but would provide a non-uniform force.
  • a weight would also be suitable as a replacement for the piston 75, but the size of the weight would have to be maintained in relation to the size of the device.
  • FIGS. 10A and 10B show a further development compared to the variants as shown in FIGS. 8A, 8B and 9A and 9B.
  • the active part of the actuator is respectively realized by a cam roller 77 and a cam track 78.
  • FIG. 10A again shows the state in which the pneumatic piston / hydraulic piston 75 is pushed out completely while the piston 5 is pretensioned in the pressure cylinder 4.
  • FIG. 10B shows the state in which the piston 5 in the pressure cylinder 4 is pushed completely down, that is to say the highest blowing pressure is generated. In this case, the punch of the pneumatic piston / hydraulic piston 75 is pushed in maximum.
  • the cam roller 77 following the cam track 78 has arrived at a lowest point.
  • valves of the blowing units can have an emergency stop especially when starting up.
  • This emergency stop must guarantee that, where appropriate, the pressure can be released from the system by opening the valves, in particular if, for example, a pressure piston in a pressure cylinder can not move away.

Abstract

Machine de moulage par soufflage pour le soufflage de récipients en plastique, comportant au moins une unité de soufflage pour le moulage par soufflage avec étirage de préformes à l'aide d'air comprimé, ladite unité de soufflage présentant une compensation de force de telle sorte qu'au moins une partie de la force de compression produite est compensée, et comportant un piston de compression et un vérin pneumatique.
EP12732834.2A 2011-07-05 2012-07-02 Machine de moulage par soufflage pourvue d'un vérin pneumatique à compensation de force pour compresseur à piston Withdrawn EP2729293A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011106652A DE102011106652A1 (de) 2011-07-05 2011-07-05 Blasmaschine mit Druckzylinder mit Kraftausgleich für Kolbenkompressor
PCT/EP2012/062820 WO2013004657A2 (fr) 2011-07-05 2012-07-02 Machine de moulage par soufflage pourvue d'un vérin pneumatique à compensation de force pour compresseur à piston

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EP2729293A2 true EP2729293A2 (fr) 2014-05-14

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EP12732834.2A Withdrawn EP2729293A2 (fr) 2011-07-05 2012-07-02 Machine de moulage par soufflage pourvue d'un vérin pneumatique à compensation de force pour compresseur à piston

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US (1) US9314957B2 (fr)
EP (1) EP2729293A2 (fr)
CN (1) CN103917354B (fr)
DE (1) DE102011106652A1 (fr)
WO (1) WO2013004657A2 (fr)

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DE102015110204A1 (de) 2015-06-25 2017-01-12 Krones Ag Adiabate Hochdruckerzeugung
EP3374148B1 (fr) * 2017-02-03 2019-06-26 KHS Corpoplast GmbH Procédé et dispositif de fabrication de récipients remplis d'un produit de remplissage liquide à partir de préformes, grâce à une matière de remplissage introduite sous pression dans la préforme
US10723060B2 (en) 2017-03-30 2020-07-28 Graham Packaging Company, L.P. HVAC, pump, and dehumidifier combined utilities skid supporting blow-molding machines
EP3656532B1 (fr) 2017-07-21 2023-06-28 Nissei Asb Machine Co., Ltd. Unité de matrice pour moulage par soufflage, et dispositif de moulage par soufflage
DE102018105229A1 (de) * 2018-03-07 2019-09-12 Krones Ag Vorrichtung und Verfahren zum Expandieren und gleichzeitigen Befüllen von Behältnissen
DE102018105228A1 (de) * 2018-03-07 2019-09-12 Krones Ag Vorrichtung und Verfahren zum Expandieren und gleichzeitigen Befüllen von Behältnissen
CN109732880A (zh) * 2019-02-20 2019-05-10 广州达意隆包装机械股份有限公司 一种吹瓶机抽芯装置压力控制机构
CN110240106B (zh) * 2019-06-24 2021-01-05 宁夏绿健源生物科技有限公司 一种节能连续性液体饲料灌装机
EP3990250A1 (fr) * 2019-06-27 2022-05-04 Discma AG Traitement à haute pression de formation et de remplissage d'un récipient et système correspondant
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Also Published As

Publication number Publication date
WO2013004657A3 (fr) 2014-01-30
US9314957B2 (en) 2016-04-19
DE102011106652A1 (de) 2013-01-10
US20140124988A1 (en) 2014-05-08
CN103917354A (zh) 2014-07-09
WO2013004657A2 (fr) 2013-01-10
CN103917354B (zh) 2017-03-08

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