CLOSING FORCE UNIT

Abstract

A closing force unit for the treatment space of a tire vulcanization machine, having a base plate and at least one linear drive for the displacement and force application of a mold pressure plate, wherein the at least one linear drive is an integral part of the base plate so that a compact and stringent structure of the closing force unit is supported. A tire vulcanization machine having such a closing force unit.

Claims

1-20. (canceled)

21. A closing force unit for a treatment chamber of a tire vulcanization machine, comprising: a base plate; and at least one linear drive for displacement of and exertion of force on a mold pressure plate, wherein the at least one linear drive is an integral constituent part of the base plate, such that a compact stringent structure of the closing force unit is supported.

22. The closing force unit according to claim 21, wherein the at least one linear drive is a piston that is received in movable fashion in a bore of the base plate.

23. The closing force unit according to claim 22, wherein the piston is a plunger piston.

24. The closing force unit according to claim 22, wherein the piston is a piston-piston rod combination having a piston region and a piston rod region.

25. The closing force unit according to claim 24, wherein a transition between the piston region and the piston rod region is formed by a concentric diameter step.

26. The closing force unit according to claim 22, wherein the bore is a blind bore.

27. The closing force unit according to claim 22, wherein the bore is a through bore.

28. The closing force unit according to claim 22, wherein the bore and the piston are formed so that a clearance fit gap is realized between them, so that the piston is received in movable fashion in the bore of the base plate.

29. The closing force unit according to claim 28, wherein the clearance fit gap is a concentric ring-shaped gap.

30. The closing force unit according to claim 28, further comprising at least one seal assigned to the linear drive so that an escape of fluid from the clearance fit gap is reduced.

31. The closing force unit according to claim 30, wherein the at least one seal is an O-ring or a shaft seal.

32. The closing force unit according to claim 28, further comprising at least one wiper assigned to the linear drive so as to wipe fluid from a region of a wall of the piston that extends from the bore.

33. The closing force unit according to claim 30, wherein the at least one seal is assigned to the piston wail and/or to a wall of the bore and/or to a ring.

34. The closing force unit according to claim 30, wherein the at least one wiper is assigned to the piston wall and/or to a wall of the bore and/or to a ring.

35. The closing force unit according to claim 22, wherein a first fluid chamber is defined and delimited at a base plate side by walls of the bore, and the piston has a crown as a displaceable element that closes off the fluid chamber with a thereby variable volume.

36. The closing force unit according to claim 35, wherein the fluid chamber has at least one opening for an introduction and/or discharge of fluid into and/or from the fluid chamber.

37. The closing force unit according to claim 34, wherein the fluid is a hydraulic oil or water.

38. The closing force unit according to claim 25, wherein an introduction of fluid into the fluid chamber is performed under low-pressure conditions.

39. The closing force unit according to claim 38, wherein the low-pressure condition lies below 100 MPa.

40. The closing force unit according to claim 39, wherein the low-pressure condition is 40 MPa.

41. The closing force unit according to claim 22, further comprising a temperature insulation dement on a face side of the piston.

42. A tire vulcanization machine, comprising a closing force unit according to claim 21.

Description

[0038] One of the possible embodiments of the closing force unit according to the invention for tire vulcanization machines, having at least one linear drive integrated into the base plate, is illustrated in figures, in which:

[0039] FIG. 1 shows an exemplary embodiment of the closing force unit (1) according to the invention for tire vulcanization machines (200) in a perspective overall illustration of the tire vulcanization machine (200) with a partial section in the x-z plane,

[0040] FIG. 2 shows the perspective sectional illustration of the vulcanization chamber or of the tire mold (30) with closing force unit (1), and

[0041] FIG. 3 shows the perspective sectional illustration of the closing force unit (1) in a detail view.

[0042] FIG. 1 illustrates a tire vulcanization machine (200) with an exemplary embodiment of the closing force unit (1) according to the invention in a three-dimensional overall view. The tire vulcanization machine (200), which is also referred to as tire heating press, is in this example constructed as a column-type press and, in its load-bearing overall construction, has a machine bed (100) with columns (110), a crossmember (80) and a base plate (10).

[0043] If the tire heating press is constructed for example as a frame-type or stand-type press, the closing force unit (1) may be integrated into the machine frame or, as in the case of the column-type construction shown in FIG. 1, into a base plate (10). In this way, the closing force unit (1) according to the invention can be realized independently of the type of construction of the press and in any desired tire vulcanization machine (200).

[0044] A functional core element of the tire vulcanization machine (200) is the treatment chamber or the vulcanization chamber/tire mold (30), the spatial extent of which is delimited by the mold pressure plate (40) and by the mold counterpressure plate (60) and by a preferably cylindrical tension casing (50). Aside from the delimitation of the vulcanization space (30), the tension casing (50) is assigned two further functional tasks: owing to the pressure forces within the vulcanization chamber (30) during the vulcanization of the green tire, the tension casing (50) accommodates the resultant (tensile) forces in an axial direction, and has an insulating action with regard to the vulcanization temperatures of up to 160 degrees Celsius, in some cases even higher, which prevail in the vulcanization chamber (30).

[0045] The mold pressure plate (40) can be linearly axially both displaced and also subjected to force, both being introduced into the mold pressure plate (40) by the closing force unit (1), such that a pressing force can be built up in the vulcanization chamber (30) and the volume thereof can be set. The mold counterpressure plate (60) practically constitutes the counterbearing, with respect to the mold pressure plate (40), for the closing and pressing forces, wherein the tension casing (50) produces the force-transmitting connection between the plates (10, 40, 60).

[0046] The tension casing (50) is preferably fixed to the mold counterpressure plate (60) and axially movable as a common structural unit. The mold counterpressure plate (60) is guided together with the tension casing (50), via a crossmember (80), by two columns (110). The axial movement drive for the structural unit of mold counterpressure plate (60) with tension casing (50) is realized by means of two fluid cylinders (90) which produce an operative connection of crossmember (80) to machine bed (100) and which are preferably of double-acting form.

[0047] FIG. 2 shows, in a perspective sectional illustration, the region of the vulcanization chamber (30). Essential constituent parts of the vulcanization chamber (30) are the mold pressure plate (40), the mold counterpressure plate (60) and the tension casing (50). Optional adapter plates (70) may be provided for fixing tire mold halves to the mold pressure plate (40) and/or to the mold counterpressure plate (60).

[0048] The closing force unit (1) is positioned adjacent to the vulcanization chamber (30) such that both the closing force and the axially directed displacement travel can be introduced into the mold pressure plate (40). The example shown in FIG. 2 realizes the positioning of the closing force unit (1) adjacent to the treatment chamber (30) by means of the concentric position vertically below the mold pressure plate (40).

[0049] If devices for internal pressurization and applying heat energy to the green tire to be vulcanized are required in the tire mold or the vulcanization chamber (30), passage regions (11, 41, 61) may be provided for the leadthrough of the mechanical components.

[0050] To realize the closing force unit (1) according to the invention in the embodiment and arrangement example shown, at least one piston (20) is arranged in the base plate (10) such that said piston, as an integrated linear drive (5), can displace and exert force on the mold pressure plate (40). It is particularly advantageous for multiple pistons (20) to be used in a manner distributed symmetrically or asymmetrically on the face side of the base plate (10). It is possible for four or more pistons (20) to be installed such that, [0051] firstly, the available base plate area is optimally utilized, and/or [0052] a highly uniform contact pressure and introduction of force can be introduced by the multiple pistons (20) into the mold pressure plate (40), and/or [0053] the axially linear displacement can be introduced substantially uniformly into the mold pressure plate (40), and in this way, misalignment or tilting of the base plate (10) during the displacement is reduced, and/or [0054] a large effective total piston surface area is provided across the pistons (20) used, such that a reduced contact pressure prevails between the respective piston face surfaces and the mold pressure plate (40), and the temperature insulation means required at said locations are subjected to lower mechanical load, and/or even the low pressure range of the fluid results in adequately high pressing forces.

[0055] FIG. 3 shows the exemplary embodiment of the closing force unit (1) from FIG. 1 and FIG. 2 in a perspective sectional illustration. The base plate (10) is equipped with each case one blind bore (12) for accommodating the piston (20). The bore diameter realizes a clearance fit with the piston diameter, such that the piston (20) is displaceable in its axial direction in the blind bore (12) when a fluid, such as for example water or hydraulic oil, is introduced into the fluid chamber (13). The fluid chamber (13) is defined and delimited at the base plate side by the blind bore base and by the bore wall, and the piston crown (21) as a displaceable element closes off the fluid chamber (13) with a thereby variable volume.

[0056] As an alternative to the blind bore (12) shown in FIG. 3, the piston receptacle in the base plate (10) may also be realized by a passage bore which is closed off on one side by a plate after the production process. In this case, the fluid chamber (13) is defined and delimited by the plate and by the bore wall.

[0057] To introduce the fluid into and/or discharge said fluid from the fluid chamber (13), the invention provides at least one opening in the base plate (10), which opening is preferably formed as a bore at the blind hole base (not shown) and supports the connection to a fluid apparatus. Alternatively or in addition, the at least one opening may be arranged on the bore wall or on the piston (20).

[0058] Owing to the considerable utilizable piston surfaces, the closing forces that result from the contact pressures may, even in the case of fluid pressures in the low pressure range, be high enough that the fluidic linear drives (5) and fluid apparatuses do not have to be realized in the expensive high-pressure variants.

[0059] According to the invention, the piston construction may be realized optionally as a plunger-type piston or as a piston-piston rod unit.

[0060] In terms of geometry, the plunger-type piston is a prismatic, preferably cylindrical piston with a continuous shell without a shoulder. In other words: the plunger-type piston has no piston rod, and the piston extends over the entire axial length and functionally also performs the task of the piston rod. Owing to this design, the plunger-type piston can be produced very easily and, together with the receiving bore in the base plate (10), forms a clearance fit gap which, owing to its very large meridian length, both has excellent sealing characteristics and guides the plunger-type piston in a very exact manner.

[0061] The piston structure of the piston-piston rod unit has a piston region (20) and a piston rod region (20) with an interposed shoulder in the form of a concentric diameter step. The diameter in the piston region (20) is larger than the diameter in the piston rod region (20), such that only the meridian length of the piston region (20) forms a clearance fit gap together with the receiving bore (12) in the base plate (10). Owing to the second fluid chamber which is thus formed and which is bordered by the bore wall, the concentric diameter step and the outer wall of the piston rod region (20), the linear drive (5) can be of double-acting design.

[0062] To reduce the escape of fluid from the clearance fit gap, the invention provides at least one seal (14), assigned in each case to a linear drive (5) of the closing force unit (1). The seal (14) may for example be an O-ring or a Simmerring. Furthermore, a stripper ring (15) may be provided which interacts with the seal (14).

[0063] The positioning of the seal (14) and of the stripper (15) may be realized in a variety of configurations: in the example shown, a ring (16) is reversibly fixed to the base plate (10) at the piston outlet side of the bore (12) and is equipped, on the inside, with corresponding ring-shaped grooves for receiving the seal (14) and the stripper (15). If no ring (16) is used, the grooves, and thus the positioning of the seal (14) and the stripper (15), may be arranged for example within the bore (12) and/or in the piston side surface.

[0064] The ring (16) may optionally have further structural and functional features. For example, a collar may be formed thereon, which collar projects into the bore (12) and is formed as a bushing. Furthermore, the ring (16) may functionally act as a stop with the shoulder of the piston (20) between the piston region (20) and the piston rod region (20) and thereby limit the linear deployment movement of the piston (20).

[0065] On the face side of the piston (20) and adjacent to the mold pressure plate (40), there is normally a need for temperature insulation measures for reducing the heat transfer into the at least one piston (20) and base plate (10) from the vulcanization chamber (30).

[0066] Owing to the very large piston face surface provided by means of the teaching according to the invention, and the altogether large contact surfaces of the multiple pistons (20) that are preferably used, the contact pressure that acts on the contact surfaces is relatively low, despite high closing forces that can be realized by the closing force unit (1). The reduced contact pressure in said regions supports the use of temperature insulation elements (17) with low compressive strength characteristics. As a result, use may be made of insulation materials which are less expensive and/or exhibit improved insulation characteristics.

[0067] The temperature insulation elements (17) may, by means of different thicknesses, simultaneously be utilized for compensating shape and dimensional tolerances and thereby leveling height differences in the case of multiple linear drives (5) being used.