Abstract:
Apparatus for blow molding hollow plastic bodies ( 7 ) comprising a plurality of pairs of mutually joinable half-molds ( 2, 4 ) capable of being opened and closed, associated to an appropriate rotary apparatus ( 10 ) carrying said half-molds ( 2, 4 ), a retrieval device adapted to remove the finished container ( 7 ) from the respective pair of half-molds ( 2 ) after the opening thereof, an opening and closing mechanism adapted to close the half-molds ( 2, 4 ) after the passage thereof through the position of the preform feeding mechanism, and to open them before the passage thereof through the position of the finished-container removal mechanism, in which said pairs of half-molds ( 2, 4 ) are constituted by a fixed half-mold ( 2 ) and a moving half-mold ( 4 ) that is capable of being opened from and closed against said fixed half-mold ( 2 ). In a preferred manner, said fixed half-molds ( 2 ) are linked to said rotary apparatus ( 10 ) and are arranged in a substantially vertical position, with the respective moving half-mold ( 4 ) adapted to be closed by accomplishing a substantially rotary movement about a horizontal axis of rotation.

Description:
BACKGROUND OF THE INVENTION 
     The present invention refers to an improved apparatus for the production of containers made of thermoplastic material, in particular polyethylene terephthalate (PET) and polypropylene (PP), intended for use in applications employing them being filled with liquids at elevated temperatures and/or containing CO 2  (carbon dioxide) gas, provided with devices that enable the productivity of moulds during the blow moulding phase to be increased. 
     In particular, the present invention is particularly advantageous when the described devices are associated with a preform manufacturing apparatus included in a so-called single-stage plant, but can be advantageously used also in conjunction with apparatuses that are supplied with previously manufactured preforms and are solely intended to carry out a final blow moulding phase (ie. two-stage plants). 
     In a two-phase process, a previously produced preform or parison, which is in a substantially amorphous state, is heated up again to its preferred molecular orientation temperature, at which it is then blow-moulded into the desired shape. As used in this context, the term “two-stage process”, or “double-stage process”, shall be understood to cover any process that produces a preform or parison which must then be heated up from ambient temperature to the related blow-moulding temperature. 
     In contrast therewith, single-stage processes are so defined in that they are capable of forming the so-called preform, or parison, and transferring the preform from the injection mould or extrusion die (upon it having been allowed to cool down to some appropriate temperature) to a conditioning station, where it is allowed to level evenly at a temperature of preferred molecular orientation. The preform or parison is then transferred to a blow-moulding mould, in which it is finally moulded into its desired form. According to a prior-art technique, the cavities in which the preforms are injection moulded and the preform transferring and conditioning devices are arranged in an on-line configuration along with the blow-moulding moulds, so as to ensure an easier, more convenient handling of the preforms, the containers and the various members therewith associated. 
     According to such a construction principle, both preforms and finished containers are processed in successive groups, with the same processing and/or transferring operations occurring at the same time. 
     In particular, the blow moulding tools, the the moulds, are particularly critical in this connection, since with the increasing blow moulding pressure and the increase in the number of cavities contained in each pair of blow moulding platens, more rapid and powerful pumping stations are required. Furthermore, the increased total pressure produced by the bottles during blow moulding must be opposed by a corresponding greater mould clamping pressure. 
     Such a greater pressure, which can be estimated to amount to a clamping force exerted on the moulds in excess of 100,000 kgf, would require all mechanical and pneumatic organs intended to produce and withstand such a pressure to be sized accordingly, which generally means to a very burdensome extent. 
     Such a huge and, what&#39;s more, pulsating pressure, however, has a negative effect also on the resistance of the moulds themselves, which are not only exposed to a greater pressure, but have, at the same time, to be capable of withstanding such pressure over a much greater period, owing to the greater number of blow moulding gates, and this of course causes the rigidity thereof to become a critical factor. It also makes it easier for the moulds to warp outwardly, thereby affecting the bottle blow-moulding results in an easily understandable manner. 
     Furthermore, when use is made of blow moulding moulds provided with a large number of cavities, the time needed for all preforms to be transferred into the respective cavities increases in a proportional manner with a corresponding increase in the cycle time and a resulting reduction in the overall productivity of the plant. 
     In order to do away with such drawbacks, a largely known solution lies in the replacement of blow moulding moulds provided with a plurality of on-line cavities with a smaller number of individual moulds, ie. comprising a single respective blow moulding cavity, which are arranged along the periphery of a rotating carousel-like structure, such as for instance illustrated in WO 95/05933, WO 89/01400, U.S. Pat. Nos. 4,850,850 and 4,313,720. 
     In particular, WO 89/01400 teaches that the blow moulding half-moulds are adapted to open and close in a book-like manner about respective axes of rotation that are orthogonal to the plane on which the preforms and the finished containers move. 
     Such a solution, although effective in solving the afore cited problems, does not however go without some drawbacks that are summarized below: 
     a) the need arises for two half-moulds to be handled and driven, and this, of course, adds to the complexity of the structures and causes costs to rise; 
     b) the lateral rotary movement of both the half-moulds requires, of course, the availability of adequate lateral space, and this, of course, puts a penalty on the compactness of the plant; 
     c) the handling means provided must be able to introduce the preforms from the front zone of the half-moulds, as well as to again remove the respective finished containers from the same front zone, and this of course understandably adds significantly to the complexity of both construction and operation of the plant. 
     However, during operating tests carried out on some types of plants having the characteristics as recited in the appended claims, and made with the use of known techniques of more obvious and immediate choice, such as the use of a direct pneumatic control or electromagnetic actuators or means like a lever joint generally known as a toggle joint in the art, it has been observed that a number of problems tend to a arise in connection with the opening and closing, or clamping, of the moving half-mould, ie.: 
     the final closing and opening movement of the moving half-mould is an abrupt, not adequately slowed-down one, so that it may give rise to blows and clattering; 
     owing to the rapid wear-down of the mechanical organs and parts concerned (it should be noted that these must be able to operate on a contmuous-duty basis over very long periods of time), the duration of the machine life is significantly affected, ie. reduced, thereby giving rise to immediate problems of planned maintenance and/or repair work; 
     the noise generated by the entire system controlling and actuating the movement of the moving half-mould is in general quite high and tends to further increase owing the the above cited wear-down effect; 
     since the moving half-mould must perform an alternating opening and closing movement at a relatively high rate, vibrations are generated which tend to be transferred to the entire structure of the plant, and this has obviously a negative impact on the duration and the operation of the machine organs involved; furthermore, the final opening and closing phase of the moulds is an extremely short and therefore strongly accelerated phase, and this of course contributes to an increased level of the so induced vibrations; and 
     for such accelerations to be obtained, over-sized movement control and driving organs must be used, but this fact not only has a negative effect on the level of the vibrations, but also, due to the greater extent of wear-down caused, to the ability of ensuring the desired precision standards over adequately long periods of time. 
     SUMMARY OF THE INVENTION 
     Based on these considerations, it therefore is a main purpose of the present invention to provide a blow-moulding apparatus of a plant for producing hollow bodies allowing for the productivity thereof to be increased through an accelerated handling of both preforms and finished containers, without incurring any of the afore mentioned drawbacks, which is capable of being easily implemented with the aid of readily available techniques and means and therefore is reasonably low-cost, reliable and preferably capable of being integrated with a preform production stage arranged upstream. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     This above arm, along with further features of the present invention, is reached in a blow-moulding apparatus having the characteristics as recited in the appended claims, and embodies itself in definite parts and arrangements of parts, as can be more readily understood from the detailed description of a preferred embodiment that is given below by way of non-limiting example with reference to the accompanying drawings, in which: 
     FIG. 1 is a side vertical-section view of a pair of half-moulds according to the present invention, shown at a closing angle enabling the preforms to be introduced therein; 
     FIG. 2 is a side view similar to FIG. 1, however with the same half-moulds shown in a minimum opening position thereof enabling the blow-moulded container to be removed therefrom; 
     FIG. 3 is a schematic view of a path, as seen from above, followed by a preform to enter and to come out of a pair of half-moulds in a book-like open arrangement according to the prior air; 
     FIG. 4 is again a schematic view of the path, as seen from above, followed by a preform to enter and to come out of a pair of half-moulds according to the present invention: 
     FIG. 5 is a vertical front view of the half-moulds in their opened state, at the exact moment when the blow-moulded container starts to be removed therefrom; 
     FIG. 6 is a schematic top view of the geometry and mutual arrangement of a plurality of moulds according to the present invention; 
     FIG. 7 synthetically illustrates a comparison between two diagrams representing on a horizontal scale the time requirements for carrying out a preform moulding phase according to the prior art and the present invention, respectively; 
     FIGS. 8 through 12 are views of positions of the moving half-mould, and the related actuation organs, from a fully open to a fully closed position thereof: 
     FIGS. 8A through 12A are schematic views of the locations on which forces concentrate, as well as the axes along which the forces acting on the actuation organs of FIGS. 8 through 12 concentrate; 
     FIG. 13 is a schematic view of the positions of fundamental point vectors and force vectors acting on the actuation organs of FIG. 8, with the mould in an open state; and 
     FIG. 14 is a diagrammatic view of position characteristics of the moving half-mould with respect to the position of an actuation pin from a reference position thereof. 
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT 
     A main feature of the present invention lies in the use of pairs of half-moulds adapted to blow mould preforms  1  in view of converting them into finished containers  7 . The half-moulds are essentially arranged as illustrated in FIGS. 1,  2  and  6  showing, respectively, a schematic side vertical-section view of a pair of half-moulds in a partially open state, a schematic side vertical-section view of the same half-moulds in an almost fully open state, and a schematic top view of the arrangement of moulds  24 ,  25 ,  26  according to the present invention, in a fully open state in the case of the moulds  24  and  25 , and a fully closed state, in the case of the mould  26 . 
     On an outer periphery of a per se known rotating carousel  10  there are applied a plurality of pairs of half-moulds, wherein 
     one of such half-moulds  2  is fixed and firmly joined to the carousel, and is further arranged on a vertical plane, with its respective half-cavity facing outwardly and radially oriented with respect to the carousel  10 , and 
     the other half-mould  4  is movable with a rotary motion about an axis X arranged on the horizontal plane and hinged on a rotation device (not shown) so that, when raised into its closed position, it is moved into coupling exactly with the matching fixed half-mould  2  that is firmly joined to the carousel. In this way, therefore, the need actually arises for only the moving half-mould  4  to be actuated into closing and opening, since the other half-mould  2  is fixed and substantially firmly joined to the carousel. 
     In this connection, a look should be taken at the illustrations appearing in FIGS. 3 and 4. In particular, the illustration in FIG. 3 can be seen to show, in an extremely schematic manner, a top view of a path a followed by the preform, which is then moulded into a finished container, with respect to two half-moulds  21  and  22  according to the prior art (and therefore both movable) as shown in an open state thereof. From this Figure it can be readily noticed that path a must include a deep sloping pattern in order to enable the preform to first slide into the half-moulds and then move out therefrom as a finished container. 
     As compared with such a situation, the illustration appearing in FIG. 4 shows, again in a schematic manner, a corresponding top view of a path b followed by the preform, which is then moulded into a finished container, with respect to the fixed half-mould  2  and the moving half-mould  4 . Although sketched in a rather simplified form, this illustration does not fail to immediately stress the point that the path b of the preform runs along an arc of circumference without any apparent diversion, or anyway a curvilinear trajectory without any point of inflection that is likely to slow down the movement of the preform/container along the path thereof or to add to the complexity of the construction of the motion control organs. 
     The line portions indicated at H, L, M, P and R in the diagram of FIG. 7 respectively show the preform insertion time, the half-mould closing time, the blow moulding time (dashed line), the half-mould re-opening time, and the finished container removal time, according to the prior-art. 
     On the contrary, with the process according to the present invention, owing essentially to the closing phase of the moving half-mould occurring partially at the same time as the preform insertion phase, as well as the opening phase of the same moving half-mould occurring partially at the same time as the finished container removal phase, a reduction in the overall cycle-time of the blow moulding tools can be obtained. 
     Since the above cited improvement allows for preform insertion phase H′ to partially overlap closing phase L′ of the sole moving half-mould, such a time during which the two phases are carried out simultaneously is identified as time T 0  which must necessarily be deducted from the overall cycle time. Furthermore, after the related blow moulding phase M′, which has necessarily an unaltered duration, the opening phase P′ of the moving half-mould is carried out. Even in this case, the possibility exists for the subsequent removal phase R′ of the finished container to be caused to start earlier, by a tune T′, before the mould is fully open, so that this partial overlapping of the opening phase P′ of the moving half-mould and the removal phase R′ of the finished blow-moulded container again brings about a further reduction in the overall cycle time by such period during which the phases are overlapping, ie. by the above cited time T′. 
     In practice, the total cycle time is reduced from a value T x  indicated in FIG. 7 to a lower value T c , since T c =T x −T 0 −T 1 . 
     Only a slight mention is made here of the fact that the actual blow moulding time T s , which is also identified by a dashed portion in both diagrams of FIG. 7, is common to and unaltered for both blow moulding processes, so that it is not affected, ie. modified, by the present invention. 
     However, the advantages brought about by the present invention do not end here. In fact, a further improvement of the invention itself can be easily obtained in the manner that is described below with particular reference to FIGS. 1 and 2. 
     Referring to FIG. 1, it can be noticed that the introduction of the preforms in the blow moulding half-moulds, ie. the exclusive movement of the preforms towards the half-moulds, can be accomplished through just a partial opening of the moving half-mould  4 , ie. when the opening angle is an angle  that is smaller than the maximum opening angle. On the contrary, this is not possible in those cases in which both half-moulds are movable, owing to the particular kinematic mechanisms that would be needed, as anyone skilled in the art is well aware of. 
     This furthermore leads to the advantage of the overall plant being capable of adjustment to the length of the preforms, since it can be easily appreciated that shorter preforms require a smaller opening angle and, therefore, shorter mould insertion times. Similarly, as better illustrated in FIG. 2, the movement for the removal of the finished blow-moulded container can be started before the moving half-mould is fully opened, provided that the trajectory S of the lower edge of the same container does not interfere with the moving half-mould. 
     A further advantageous improvement of the present invention lies in providing an appropriately curved guide element  15 , illustrated in FIGS. 4 and 5, arranged in a stable manner in such position as to be able to intercept the path of the preform neck from the trajectory b, and to assist it in its movement of insertion in the respective cavity of the corresponding fixed half-mould  2 . 
     As far as the technical improvements in the organs controlling the movement of the moving half-mould are concerned, reference should be made to FIGS. 8 through 12, as well as the corresponding schematics appearing in FIGS. 8A through 12A. The latter can be seen to symbolically represent the fundamental points of application of the action and reaction forces on the organs of the plant, the vectors representing such forces, and the direction of action thereof. 
     From the illustrations in the above cited Figures it can be noticed that the actuation organs of the moving half-mould  4  comprise: 
     a first class lever provided with arms  52  and  53  separated by a fulcrum F 1 , whose power and resistance points are located at the extreme ends of said two arms, ie. at P 1  and R 1 , respectively; 
     a third class lever provided with respective arms  55  and  56 , a respective fulcrum F 2 , and respective power and resistance points at P 2  and R 2 ; 
     a rigid connecting member  54  that links the resistance point R 1  of said first class lever with the power point P 2  of the third class lever, the resistance and power points being pivotally connected to the extreme ends of the connecting member  54 ; 
     an actuating member  51  provided with two end portions, the first one of which is connected to the power point P 1  of the first class lever. 
     The fulcra F 1  and F 2  of the first class lever and the third class lever, respectively, are applied pivotally on respective distinct points of a structure  60  that is integral with or firmly joined to the fixed half-moulds. Furthermore, the moving half-mould  4  is applied on the arm  56  of the third class lever opposite to the related fulcrum F 2  with respect to the corresponding power point P 2 . 
     The second extreme end  57  of said actuating member  51  is adapted to be movably actuated by a moving member  58  on a plane that is orthogonal to the axis of rotation of the fulcrum F 1  of the first class lever. 
     The whole assembly of levers, connecting members and actuating members is adapted to move, clearly in a synchronous and coherent manner, since each moving member is linked to another member, between two respective extreme positions, in which one of such extreme positions corresponds to the full-open position (FIGS. 8,  8 A and  12 ) of the moving half-mould, whereas the other one of said extreme positions corresponds to the full-closed position (FIG. 12,  12 A and  16 ) of the same half-mould. 
     Referring now to FIG. 13, which illustrates the condition of the mould assembly in its fully open position, it can be noticed that when the second extreme end  57  of the actuating member  51  is urged to start moving in the direction in which the moving half-mould  4  is caused to close, the vector V 1  of the force transmitted from the point of resistance R 1  of the first class lever to the rigid connecting member  54  has a component V 2  in the direction of action on the connecting member, ie, along the straight line joining R 1  with P 2 , wherein the component V 2 , if considered as being applied on the point of power P 2  of the third class lever, indicated at V 2 , 1  in the Figure, may be in turn broken down into two mutually orthogonal components, one of which, ie, the one indicated at V 2 , 2  in the Figure, is oriented towards F 2  and acts so as to only compress the related arm  55 , with practically no effect at all within the overall geometry, whereas the other component V 2 , 3  is radial with respect to the arm  55  and therefore acts on the arm  56  supporting the half-mould  4 , in such a manner as to cause the third class lever to rotate, thereby causing the moving half-mould to close. 
     As far as the spatial configuration and the possible components of the force vectors, the lever arms and the other connecting/actuating members, it has practically been found that the most effective and logical arrangement thereof is obtained when all of them are provided on a same plane, in particular on the plane shown in the FIGS. 8 through 12. However, as anyone skilled in the art is capable of readily understanding, the vectors, members and components may also be arranged three-dimensionally, provided that they meet the pre-condition of their projections or components on a given, suitable plane reflecting the subsequent conditions illustrated in the Figures. 
     FIGS. 9 through 11 illustrate subsequent dispositions of the whole assembly of levers and connecting and actuating members, along with the respective vectors, corresponding to some subsequent positions of the moving half-mould  4  as it is moved into closing. They are, anyway, readily understandable by those skilled in the art, so that no further explanation needs to be given here in this connection. 
     FIGS. 12 and 12A represent the situation when the moving half-mould is fully closed. This is a quite particular situation since, further to representing a kind of end-of-stroke point it also represents the condition in which the “toggle effect” shows up in all of its effectiveness. In other words, this is the condition in which the clamping force of the half-mould reaches its peak, ie, is maximized, while the angular displacement of the half-mould is at a minimum. Use is anyway made also of other means, further to this fact, in order to ensure a fully stable clamping of the half-mould. 
     Reference should be made now to FIG.  12 : the point of resistance R 1  of the lever  52 ,  53  is in an articulated arrangement with respect to the connecting member  54 , so that the arm  53  and the connecting member  54  are capable of rotating with respect to each other. However, a further rotation thereof beyond a pre-established position is prevented by the presence of a mechanical or positive retainer (not shown) that really acts as a toggle, ie. enables two levers hinged on an extreme end thereof to rotate with respect to each other only up to a certain angle and not any further. 
     The geometric configurations and the dimensions of the various members and components involved are so defined as to make sure that, when such a limit stop position is reached, this position also coincides with both 
     the full-closed condition of the moving half-mould against the respective fixed half-mould and 
     the particularly favourable condition created by the three geometrical sites identified by P 2 , R 1  and F 1  being aligned, as is shown in FIG.  12 A. 
     The advantageous character of such a circumstance has already been hinted at above and lies essentially in the fact that, in the final portion of the closing path covered by the moving half-mould, the force that is produced and can therefore be used to close and clamp the half-mould, is at its maximum, ie. reaches a peak. In this case in fact, as is most clearly shown in FIG. 14 illustrating the opening or closing angle of the moving half-mould in accordance with the progressive displacement of the moving member  58 , or rolling pin, the most favourable condition is obtained in -new of making the best possible use of the so-called “toggle effect”, the condition being reached through the illustrated combination and association of the described leverages. In a more detailed manner, FIG. 14 can be noticed to emphasize how, in correspondence of the portion of curve indicated at M, at a certain progressive displacement of the device or rolling pin  58 , whose scale in the lower portion of the Figure is a linear one, a rotation is obtained with a progressively decreasing increment of the angle between the members  54  and  55  until an angle of 0° is eventually reached between the members  54  and  55  in correspondence of a value of approx. 1 in the abscissa. 
     The particular pattern followed by the curve in correspondence of the above cited point M, which corresponds to the moving half-mould being closed, and also of the point H at the opposite end of the same curve, which corresponds to the full-open position of the half-mould, ensures a movement of the same half-mould with progressively slowed-down accelerations and decelerations towards the respective end-of-stroke positions thereof, until practically a condition of zero acceleration is reached when the half-mould approaches the respective end-of-stroke positions thereof. 
     Such a moving pattern of the half-mould translates into a number of significant practical advantages, ie. a noticeable reduction in vibrations, the prevention of the moving half-mould from bumping when moving into its end-of-stroke positions, and the possibility for the moving device to be actuated with the help of simple, reliable and accurate means that are furthermore durable, ie. well resistant to wear-down since they are not subject to the action of “forces”. 
     This condition is further strengthened by the fact that, immediately upon the moving half-mould having so been moved into its fully closed position, the same half-mould is automatically clamped in such a position with the help of such supplementary external means as readily conceivable by all those skilled in the art, the means being linked to the pins  41 ,  42  that are firmly joined with the fixed half-mould and the moving half-mould, respectively. 
     It will of course be appreciated that when it is stated that the geometrical sites identified by P 2 , R 1  and F 1  are aligned, as is shown in FIG. 12A, this is meant to be understood in the broadest sense of the word, since this is actually intended to mean that, in order to ensure the desired “toggle effect”, it is sufficient for the axes of rotation of the pins centered on P 2 , R 1  and F 1  to be not only parallel, but also arranged on the same plane. 
     The continuous operation of the described assembly for alternatingly opening and closing the moving half-mould can be obtained through a corresponding to-and-fro movement of the moving device or roiling pin  58 . Such a movement can be easily obtained by means of a continuously rotating cam device adapted to control the movement and the position of the rolling pin in full synchronization with all other devices, mechanisms and actuators that altogether ensure the various phases for opening the half-mould, introducing the preform, closing the half-mould, blow moulding the preform, opening the half-mould and simultaneous removal of the finished container. 
     A further advantage of the present invention, as exemplified in the illustrated embodiment thereof, derives from the fact that if, as just stated above, the alternating to-and-fro movement of the moving device or rolling pin  58  is actuated by two rotating cams, preferably on the same vertical axis of rotation of the carousel  10  in FIG. 6, the limited weardown effect that unavoidably takes place between the actuating surfaces of the rotating cams and the rolling pin has only a very limited impact on the opening and closing accuracy of the moulds. This fact brings about the remarkable benefit deriving from the possibility for the maintenance or re-adjustment of the cams and therewith associated organs to be carried out at quite extended intervals, without incurring any loss in processing precision. 
     A confirmation of the fact that the weardown effect of the cams, and possibly also of the associated rolling pin or moving device, has only a very limited impact on the precision of the end-of-stroke positions of the moving half-mould, can be simply obtained by again having a look at FIG. 14, in which it can in fact be observed that the condition actually occurs in which, in front of a certainly non-negligible displacement, ie. oscillation of the rolling pin about the points M and H, the angle of rotation of the moving half-mould is almost nil and practically negligible. As a result, if such an oscillation is due to weardown, this practically has no significant effect on the precision of the end-of-stroke positions of the moving half-mould.