Abstract
An adapting sleeve for flexographic printing machines defines an exterior surface appropriate for the mounting of a printing sleeve. The adapting sleeve has an outer cylindrical member made of a rigid material and surrounding an inner cylindrical member that defines a cylindrical passage for mounting of the adapting sleeve on a rotary core of a flexographic printing machine. The adapting sleeve has some ring separators that are mounted between the outer cylindrical member and the inner cylindrical member and spaced longitudinally from each other. The adapting sleeve has a hydraulic device that includes hydraulic pads arranged between the inner surface of the inner cylindrical member and the ring separators and connected by a hydraulic circuit to a pressurization element that is actionable manually from the exterior of the adapting sleeve.
Claims
1. Adapting sleeve for a flexographic printing machine having at least one cylindrical rotary core that can be rotatably driven about a rotational axis, the adapting sleeve comprising: an outer cylindrical member made of a rigid material and defining a cylindrical inner surface, the outer cylindrical member defining a first end and a second end disposed longitudinally spaced apart from the first end; an inner cylindrical member defining a cylindrical, diametrically-expandable inner surface having a diameter larger than the diameter of the rotary core of the printing machine for slidably mounting the inner cylindrical member on the rotary core of the printing machine, the inner cylindrical member defining a first end and a second end disposed longitudinally spaced apart from the first end; a first ring separator mounted between the first end of the outer cylindrical member and the first end of the inner cylindrical member; a second ring separator mounted between the second end of the outer cylindrical member and the second end of the inner cylindrical member, wherein a hollow compartment is defined between the ring separators, the outer cylindrical member and the inner cylindrical member; and wherein the inner cylindrical member defines a first gripping region substantially coextensive with a recess defined in the first ring separator, the first gripping region defining a first cavity therein; and a first selectively expandable and compressible hydraulic element is disposed in the first cavity of the first gripping region of the inner cylindrical member.
2. Adapting sleeve, as per claim 1, wherein the selectively expandable and compressible hydraulic element includes a hydraulic pad.
3. Adapting sleeve, as per claim 1, wherein the selectively expandable and compressible hydraulic element includes an annular-shaped hydraulic pad arranged circumferentially around the first ring separator.
4. Adapting sleeve as per claim 1, further comprising a hydraulic cylinder connected to the selectively expandable and compressible hydraulic element and including a piston having a coupling, wherein the piston is configured for axial movement by rotational movement of a threaded rod that is selectively manually attachable to and detachable from the coupling of the piston.
5. Adapting sleeve, as per claim 4, wherein the first ring separator defines an access conduit through which the threaded rod is afforded access for selectively manually attaching to and detaching from, the coupling of the piston.
6. Adapting sleeve, as per claim 4, wherein hydraulic fluid fills the hydraulic cylinder, which is configured for changing its volume commensurate with axial movement of the piston.
7. Adapting sleeve as per claim 1, wherein the selectively expandable and compressible hydraulic element forms part of a hydraulic circuit that includes a hydraulic pressure line connected to the selectively expandable and compressible hydraulic element and formed of relatively thin and flexible hollow tubing that defines an internal hollow passage and is lightweight.
8. Adapting sleeve, as per claim 7, further comprising an hydraulic distributor connecting the hydraulic pressure line and the hydraulic cylinder.
9. Adapting sleeve as per claim 1, wherein the inner cylindrical member defines a second gripping region substantially coextensive with a recess defined in the second ring separator, the second gripping region defining a second cavity therein, and wherein a second selectively expandable and compressible hydraulic element is disposed in the second cavity of the second gripping region of the inner cylindrical member.
10. Adapting sleeve, as per claim 9, further comprising a first hydraulic pressure line connecting the hydraulic cylinder to the first the selectively expandable and compressible hydraulic element, and a second hydraulic pressure line connecting the hydraulic cylinder to the second the selectively expandable and compressible hydraulic element.
11. Adapting sleeve, as per claim 10, further comprising an hydraulic distributor that is disposed equidistant between and connecting the first hydraulic pressure line and the second hydraulic pressure line.
12. Adapting sleeve, as per claim 11, further comprising a hydraulic cylinder connected to the hydraulic distributor.
13. Adapting sleeve, as per claim 1, further comprising a pressure limiter that is configured and disposed to prevent overpressurization of the first selectively expandable and compressible hydraulic element.
14. Adapting sleeve, as per claim 1, wherein the inner cylindrical member is composed of material that is elastically deformable radially due to the action of the selectively expandable and compressible hydraulic element.
15. Adapting sleeve, as per claim 1, wherein the inner cylindrical member is formed of fiber glass.
16. A method of fastening an adapting sleeve as per claim 1 non-rotatively relative to a cylindrical rotary core of a flexographic printing machine, the method comprising the steps of: sliding adapting sleeve onto the cylindrical rotary core; and selectively expanding the selectively expandable and compressible hydraulic element so as to displace the inner cylindrical member radially inwardly to press the inner surface of the inner cylindrical member against the rotary core of the printing machine with the consequent fastening of the adapting sleeve to the rotary core of the flexographic printing machine.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
(1) Aspects and advantages of the invention are set forth below in the following description, or may be obvious from the description, or may be learned through practice of embodiments of the invention. Those of ordinary skill in the art will better appreciate the features and aspects of such embodiments, and others, upon review of the specification. A full and enabling disclosure of the present invention, including the best mode thereof to one skilled in the art, is set forth more particularly in this specification, including reference to the accompanying figures, in which:
(2) FIG. 1 shows a schematic view in perspective of an exemplary configuration of the adapting sleeve for flexographic printing machines, fitted in this case with hydraulic pads arranged between the inner surface, with greater diameter, of the inner cylinder and the ring separators of the adapting sleeve.
(3) FIG. 2 shows in perspective view an enlarged portion of one end of the adapting sleeve of FIG. 1, in which components are disassembled to reveal the circumferential arrangement of the hydraulic pads.
(4) FIG. 3 shows a frontal view of one of the ends of the adapting sleeve of the previous figures.
(5) FIG. 4 shows a cross-sectional view of the adapting sleeve of the previous figures sectioned by a longitudinal median plane through the central rotational axis of the adapting sleeve, with components in the background outlined in dashed line.
(6) FIG. 5 shows an expanded close-up of the section of FIG. 4 in which one of the depressurized hydraulic pads is seen. In this FIG. 5, the portion of the adapting sleeve mounted on a portion of a rotary core of the flexographic printing machine is shown, expanding the separation between the surfaces across from each other in order to render them more readily discernible.
(7) FIG. 6 shows a view similar to FIG. 5, but with the pressurized hydraulic pads in an operating position causing an elastic deformation radially of the inner surface of the inner cylindrical member and its consequent action against the exterior surfaces of the rotary core of a flexographic printing machine.
(8) FIG. 7 shows a perspective view of an alternative embodiment of the adapting sleeve in which the hydraulic device includes a ring shaped hydraulic pad arranged between the inner surface of the inner cylinder and each one of the ring separators of this adapting sleeve.
DETAILED DESCRIPTION OF EXEMPLARY EMBODIMENTS OF THE INVENTION
(9) In FIG. 1, the adapting sleeve is generally designated (1a) for flexographic printing machines (not shown) and includes a rigid outer cylindrical member (2) that is defined about a central axis of rotation and extends along the central axis from one end of the outer cylindrical member (2) longitudinally to the opposite end of the outer cylindrical member (2). The outer cylindrical member (2) is configured to carry on its exterior surface (22) (FIGS. 5 and 6), a printing sleeve (not shown) that carries the media that transfers ink to the substrate being drawn through the printing machine at very high rates of as much as 1,200 meters per minute. As the mechanism for mounting and dismounting printing sleeves on the exterior surface (22) of the adapting sleeve (1a) is not the focus of this disclosure, it suffices to say that at least one of the conventional mechanisms for accomplishing these functions can be applied to the adapting sleeve (1a). Among them is connecting the adapting sleeve (1a) to a source of pressurized air at 80 to 90 psi, which typically would be available in the printing facility, to expand the cylindrical internal diameter of the printing sleeve sufficiently to slide the printing sleeve onto the exterior surface (22) of the adapting sleeve (1a).
(10) Moreover, as schematically shown in FIG. 2 for example, the outer cylindrical member (2) circumferentially surrounds an inner cylindrical member (3). As schematically shown in FIGS. 2, 5 and 6 for example, inner cylindrical member (3) is hollow and has an inner cylindrical surface (31) that defines a longitudinally extending interior passage. The diameter of the inner cylindrical surface (31) of the inner cylindrical member (3) is configured to be larger than the exterior diameter of the rotary core (N) (FIGS. 5 and 6) of the flexographic printing machine for which the adapting sleeve (1a) is intended. Thus, the interior passage defined by the inner cylindrical surface (31) of the inner cylindrical member (3) comfortably receives therein the rotary core (N) of the printing machine. Accordingly, it is possible to slide the adapting sleeve (1a) by hand over the rotary core (N) of the printing machine to mount the adapting sleeve (1a) onto the rotary core (N) of the printing machine or dismount the adapting sleeve (1a) from the rotary core (N) of the flexographic printing machine. To facilitate the sliding movements of adapting sleeves (1a) of relatively longer lengths, the assistance of pressurized air introduced between the inner cylindrical surface (31) of the inner cylindrical member (3) and the rotary core (N) of the printing machine might be required.
(11) As schematically shown in FIG. 4, at each opposite end of the adapting sleeve (1a) there is a rigid ring separator (4). As schematically shown in FIGS. 3 and 4, each ring separator (4) defines a cylindrical hole through the center thereof. As schematically shown in FIG. 3 for example, each ring separator (4) is mounted between the interior surface (21) of the outer cylindrical member (2) and the exterior surface (32) of the inner cylindrical member (3) and rigidly resists any expansion of the exterior surface (32) of the inner cylindrical member (3).
(12) In this example, the outer cylindrical member (2) and the ring separators (4) are made of carbon fiber, which is both rigid and light in weight, but other similarly rigid materials can be used for the outer cylindrical member (2). However, the inner cylindrical member (3) must be composed of material that is elastically deformable when it is subject to a predetermined amount of pressure greater than normal atmospheric pressure. This elastically deformable material must resume its original shape when the predetermined pressure is removed. A suitable elastically deformable material the inner cylindrical member (3) is provided by fiber glass for example or another material of similar characteristics.
(13) In accordance with the present invention, the adapting sleeve (1a) includes a hydraulic device (5) that the user can manually activate in order to selectively apply or remove, as the operator chooses, the predetermined amount of pressure greater than normal atmospheric pressure for elastically deforming the inner cylindrical member (3). By operating the hydraulic device (5) to apply the predetermined amount of pressure, the inner cylindrical member (3) becomes elastically deformed so as to reduce the diameter of the inner cylindrical surface (31) of the inner cylindrical member (3), at least in the end region coextensive with the adjacent ring separator (4) as schematically shown in FIG. 6, by an amount sufficient to clamp tightly around the exterior surface (N2) of a rotary core (N) of a flexographic printing machine, represented schematically in FIGS. 5 and 6. When the hydraulic device (5) removes the predetermined amount of pressure, the inner cylindrical member (3) elastically returns to its original shape in which the diameter of the inner cylindrical surface (31) is again slightly larger than the diameter of the exterior surface (N2) of the rotary core (N) and accordingly permits the user to manually slide the adapting sleeve (1a) off of the rotary core (N) of the flexographic printing machine.
(14) As embodied herein, the hydraulic device (5) in charge of fastening the adapting sleeve (1a) to the rotary core (N) includes at least one selectively expandable and compressible hydraulic element. As explained more fully below, the selectively expandable and compressible hydraulic element can take the form of a plurality of discrete hydraulic pads (51) that are circumferentially spaced apart from one another as schematically shown in FIG. 1, or alternatively an annular hydraulic pad (56) as schematically shown in FIG. 7.
(15) As schematically shown in FIG. 5 for example, each hydraulic pad (51) is housed in a respective cavity (33) that is defined internally of a gripping region (34) of the inner cylindrical member (3). As schematically shown in FIG. 5 for example, the end region (35) of the inner cylindrical member (3) is substantially coextensive with the adjacent ring separator (4), and the gripping region (34) desirably is disposed within the end region (35) of the inner cylindrical member (3). Moreover, the gripping region (34) desirably is provided with about twice the radial thickness of the rest of the length of the end region (35) of the inner cylindrical member (3) as well as about twice the radial thickness of portion of the inner cylindrical member (3) that extends axially over most of the length of the inner cylindrical member (3).
(16) As schematically shown in FIG. 5 for example, the inner surface (42) of the ring separator (4) defines a recess that is configured to receive therein the gripping region (34) of the inner cylindrical member (3). This recess desirably extends axially so that it is substantially coextensive with the axial dimension of the gripping region (34) of the inner cylindrical member (3). As schematically shown in FIG. 5 for example, the inner surface (42) of the ring separator (4) rests directly in contact with and firmly against the exterior surface (32) of the gripping region (34) of the inner cylindrical member (3). Moreover, the rigidity of the material composing the ring separator (4) precludes any expansion of the gripping region (34) in the direction of the inner surface (42) of the ring separator (4).
(17) As schematically shown in FIGS. 1 and 2 for example, six hydraulic pads (51) are spaced equidistantly apart around the circumference of each end region of the inner cylindrical member (3). One of these six hydraulic pads (51) is schematically depicted in cross-section in each of FIGS. 5 and 6 for example. Thus, each hydraulic pad (51) is arranged circumferentially between the inner surface (31) of the inner cylindrical member (3) and each of the ring separators (4) arranged near the respective free end of the adapting sleeve (1a).
(18) The manner of generating the inner cylindrical member (3) by the successive buildup of layers of elastically deformable material is well understood and accordingly will not need to be described herein in any great detail. As merely one example, US Patent Application Publication No. 2008-0011173 A1, which is hereby incorporated herein by this reference for all purposes, describes embedding a transponder in a printing cylinder. Embedding each hydraulic pad (51) in a respective cavity (33) of the gripping region (34) of the inner cylindrical member (3) can be accomplished in a similar fashion.
(19) As schematically shown in FIGS. 5 and 6 for example, each hydraulic pad (51) desirably is formed from a top sheet (51a) that overlays a bottom sheet (51b). Each of the top sheet and the bottom sheet desirably is provided by a generally rectangular steel sheet of the same area disposed one on top of the other and length of each sheet desirably is at least twice the width of each sheet. The two opposing longer edges of the overlaid sheets on each of the longer sides of the sheets are welded together to define a respective side edge, and a slight curvature about the longitudinal axis is imposed before welding together the two opposing front edges and the two opposing rear edges of the overlaid top sheet (51a) and bottom sheet (51b). The degree of this curvature will depend on the diameter of the adapting sleeve (1a) in which the hydraulic pad (51) is to be embedded. Each of the hydraulic pads (51) is designed to withstand an internal static pressure of as much as 100 bar, which is more than adequate to provide the desired forces for locking and unlocking the adapting sleeve 1a from the exterior surface N2 of the rotary core N. As is apparent from this description, the different gripping requirements of different adapting sleeves 1a of differing sizes can be obtained by adjustments between the surface area of the top sheet (51a) of each hydraulic pad (51), the number of hydraulic pads (51) and the internal static pressure within each hydraulic pad (51). The total surface area occupied by these four edges of each hydraulic pad (51) is very much diminished compared to the surface area occupied by either the top sheet (51a) or the bottom sheet (51b). Thus, the total force exerted from the pressure within each hydraulic pad (51) amounts to much less force transferred through these four edges than the total force that is transferred through either the top sheet (51a) or the bottom sheet (51b). As schematically shown in FIG. 6, the gauge of the steel sheet that forms the top sheet (51a) is much thinner (e.g., 0.02 mm to 1 mm) than the gauge of the steel sheet that forms the bottom sheet (51b) in order that the top sheet (51a) is more resiliently flexible than the bottom sheet (51b) of each hydraulic pad (51). While it is desirable that the top sheet (51a) with the thinner gauge of steel should be disposed closer to the inner cylindrical surface (31) of the inner cylindrical member (3), the opposite disposition also can be employed.
(20) Because the exterior surface (32) of the inner cylindrical member (3) is constrained against expansion by the rigid interior surface (42) of the coextensive ring separator (4), any expansion of the hydraulic pad (51) when the adapting sleeve (1a) is mounted on the rotary core (N) of the printing machine, causes the inner surface (31) of the inner cylindrical member (3) to undergo a reduction in its diameter that eliminates any gap between the inner surface (31) of the inner cylindrical member (3) and the exterior surface (N2) of the rotary core (N). This is schematically indicated in FIG. 6 by the three parallel arrows pointing away from the hydraulic pad (51) that is expanding so that the top sheet (51a) presses the inner surface (31) of the inner cylindrical member (3) against the exterior surface (N2) of the rotary core (N). Given the coefficient of static friction at the interface between the inner surface (31) of the inner cylindrical member (3) and the exterior surface (N2) of the rotary core (N), the total area occupied by the hydraulic pads (51) suffices to generate a substantial clamping force. Moreover, the number of hydraulic pads (51) and the dimensions of each can be engineered so that adequate clamping force can be generated even at relatively low pressures within the hydraulic pads (51). Thus, the inner surface (31) of the inner cylindrical member (3) tightly grips the exterior surface (N2) of the rotary core (N) when the hydraulic pads (51) undergo expansion as schematically depicted in FIG. 6.
(21) As embodied herein and schematically shown by the dashed lines in FIG. 1, the hydraulic device (5) includes a hydraulic circuit that includes a plurality of hydraulic pressure lines (52) that are connected to the hydraulic pads (51) and configured to carry hydraulic fluid to pressurize the hydraulic pads (51) and alternatively carry hydraulic fluid away from the hydraulic pads (51) to depressurize the hydraulic pads. Each of the hydraulic pressure lines (52) desirably is a relatively thin and flexible hollow tube that is lightweight and can follow a curved path without kinking or constricting the internal hollow passage. Each of the hydraulic pressure lines (52) desirably is a stainless steel capillary tube defining a lumen with a diameter in the range of about 0.6 mm to 1.4 mm, which minimizes the amount of hydraulic fluid required to fill the hydraulic circuit, and the exterior diameter of these stainless steel capillary tubes forming the hydraulic pressure lines (52) desirably ranges between about 0.9 mm to 1.7 mm.
(22) As schematically shown in the cross-sectional view of FIG. 4, desirably a hydraulic pad (51) at one end of the adapting sleeve is directly connected via a hydraulic pressure line (52) to a hydraulic pad (51) at the opposite end of the adapting sleeve. Desirably, these two connected hydraulic pads (51) are aligned with each other so that the connecting hydraulic pressure line (52) runs in a straight line and thus is minimized in length and avoids any kinks that otherwise would introduce additional pressure drops in the hydraulic circuit. Moreover, as schematically shown in FIG. 4, the hydraulic pressure lines (52) are carried within the hollow, annular shaped compartment (60) that is defined between the ring separators (4), the outer cylindrical member (2) and the inner cylindrical member (3).
(23) As embodied herein and schematically shown in FIGS. 1 and 4 for example, the hydraulic device (5) includes a pressurization element (53). When the pressurization element (53) is activated manually, it is configured to cause the pressurization or depressurization of this hydraulic circuit and the contraction (deflation) or expansion (inflation) of the hydraulic pads (51) as schematically represented in FIGS. 5 and 6 respectively. The pressurization element (53) desirably is constituted in this exemplary embodiment by a hydraulic cylinder that is fitted with a piston that is moved axially in a longitudinal direction by a threaded rod (54), which is actionable manually from the outside of the adapting sleeve (1a) and via an appropriate tool (not shown) that can be inserted through a hole (41) defined for this purpose through one of the ring separators (4). The hydraulic fluid chamber of the hydraulic cylinder is connected via the hydraulic pressure lines (52) to the hydraulic pads (51). Use of the tool to effect manual rotation of the threaded rod (54) in one direction moves the piston to reduce the volume in the hydraulic chamber, thus commensurately increasing the pressure in the hydraulic circuit and expanding the hydraulic pads (51), as schematically indicated by the three vertical arrows depicted in FIG. 6. Similarly, manual rotation of the threaded rod (54) in the opposite direction moves the piston to increase the volume in the hydraulic chamber, thus commensurately decreasing the pressure in the hydraulic circuit and depressurizing the hydraulic pads (51) to resume their neutral volume schematically shown in FIG. 5. However, the pressurization element (53) can be any other type that allows pressurizing and depressurizing the hydraulic circuit and the hydraulic pads (51) within the space constraints imposed by the configuration of the adapting sleeve (1a) and thereby effecting in any case an autonomous operation of the hydraulic device (5).
(24) During printing operations of the flexographic printing machine, various external printing pressures can be transmitted to the adapting sleeve (1a, 1b). When these external printing pressures are transmitted from the exterior surface (22) of the adapting sleeve (1a) to the gripping region (34) of the inner cylindrical member (3), these external printing pressures can generate pressure pulses that can travel through the hydraulic circuit via the pressure lines (52). In order to eliminate or minimize any adverse effects from such pressure pulses, as schematically shown in FIGS. 1 and 4, the hydraulic circuit includes a plurality of connectors (52a), which are hydraulic distributors welded into the hydraulic pressure lines (52). Each hydraulic distributor (52a) in each connector line (52) is disposed centrally between both opposite ends of the connector line (52), and thus equidistant between each of the hydraulic pads (51) at each opposite end of the pressure line (52). By this arrangement, pressure pulses that originate at opposite ends of the adapting sleeve (1a) will arrive simultaneously at the centrally located hydraulic distributor (52a) in each connector line (52), where the oppositely traveling pressure pulses will cancel out one another. The pressurization element (53) is connected to each of the hydraulic pressure lines (52) via a respective hydraulic distributors (52a), which are connected to the pressurization element (53) via one of the individual hydraulic feeder lines (52b) that forms part of the hydraulic circuit. Thus, as schematically shown in FIG. 4, one hydraulic pad (51) at one end of the adapting sleeve (1a) is paired with an hydraulic pad (51) at the opposite end of the adapting sleeve (1a), and these two paired hydraulic pads (51) are connected via an hydraulic pressure line (52) that includes one of the hydraulic distributors (52a), which in turn is connected to the pressurization element (53) via one of the individual hydraulic feeder lines (52b) that forms part of the hydraulic circuit.
(25) As embodied herein and schematically shown in FIG. 1 for example, the hydraulic device (5) also includes a pressure limiter (55) that impedes the pressurization of the hydraulic circuit (52) above a predetermined value to guard against damage to the components of the hydraulic device (5) if the pressurization element (53) should be activated uncontrollably. The pressure limiter (55) desirably is provided by a relief valve with a bellows that yields when subjected to a pressure greater than the predetermined pressure indicative of the pressurization element (53) having been uncontrollably activated. As embodied herein and schematically shown in FIG. 1 for example, the pressure limiter (55) is disposed between the pressurization element (53) and the hydraulic pressure lines (52) that connect to the hydraulic pads (51). Moreover, as schematically shown in FIG. 4, the hydraulic pressure lines (52), the pressurization element (53), the threaded rod (54) and the pressure limiter (55) are carried within the hollow, annular shaped compartment that is defined between the ring separators (4), the outer cylindrical member (2) and the inner cylindrical member (3).
(26) Because the adapting sleeves (1a) of the present invention are designed to be clamped onto rotary cores (N) that are driven at very high rotational speeds, the pressurization element (53), threaded rod (54), and the pressure limiter (55) must be rigidly fastened to the exterior surface (32) of the inner cylindrical member (3). As schematically shown in FIG. 4, this desirably is accomplished by providing an axially formed channel as part of the exterior surface (32) of the inner cylindrical member (3) and adhesively cementing the pressurization element (53), threaded rod (54), and the pressure limiter (55) in this first channel. Moreover, in order to dynamically compensate for the weight of the hydraulic device (5), and in particular the pressurization element (53), threaded rod (54), and the pressure limiter (55), there desirably is provided in the exterior surface (32) of the inner cylindrical member (3), a mirror channel that is displaced 180 circumferentially from the first channel. A compensating dead weight desirably is cemented in this mirror channel so that the adapting sleeve (1a) is dynamically balanced.
(27) After the hydraulic device (5) and the compensating dead weight have been attached to the exterior surface (32) of the inner cylindrical member (3), the inner cylindrical member (3) is dynamically balanced before being inserted into the hollow chamber defined by the interior surface (21) of the outer cylindrical member (2). A respective rigid ring separator (4) closes off each opposite end of the outer cylindrical member (2). Conventional adhesives then are applied to permanently affix each ring separator (4) to the interior surface (21) of the outer cylindrical member (2) and the exterior surface (32) of the inner cylindrical member (3).
(28) As schematically shown in FIG. 5, the hydraulic circuit (52) is depressurized and the hydraulic pads (51) are deflated to resume their unexpanded shape. The inner surface (31) of the inner cylindrical member (3) defines a continuous hollow passage defining a diameter that is constant and slightly greater than the exterior surface (N2) of the rotary core (N) of the printing machine, thereby allowing the mounting and dismounting of the adapting sleeve (1a) on this rotary core (N).
(29) As schematically shown in FIG. 6, when the hydraulic circuit (52) is pressurized, the hydraulic pads (51) are inflated. Such inflation causes a radial deformation of the inner surface (31) of the inner cylindrical member (3) that reduces the diameter of the inner surface (31) sufficiently to press against the perimeter areas of the exterior surface (N2) of the rotary core (N), thereby establishing the fastening of the adapting sleeve (1a) with respect to the rotary core (N) so that the adapting sleeve (1a) and the rotary core (N) rotate together as a single unit without an relative movement between them.
(30) This deformation of the inner cylinder (3) toward its interior due to the action of the hydraulic pads (51) is facilitated by the elasticity of the material forming this inner cylinder (3) and to the rigidity both of the ring separators (4) and the outer cylinder (2).
(31) A perspective view of an alternative embodiment of an adapting sleeve (1b) is schematically shown in FIG. 7. Only the variance of adapting sleeve (1b) from the adapting sleeve (1a) of the previous figures need be described. The essential difference is the substitution of an annular hydraulic pad (56) for a plurality of the hydraulic pads (51) arranged circumferentially. The annular hydraulic pad (56) desirably is formed from a top cylindrical sheet that concentrically overlays a bottom cylindrical sheet. Each of the top cylindrical sheet and the bottom cylindrical sheet desirably is provided by a steel cylinder open at both opposite ends. The overlaid edges of the open ends of the overlaid cylindrical sheets are welded together to define a respective end edge. In this alternative embodiment of adapting sleeve (1b), the cross-sectional portions of the views of FIGS. 4, 5 and 6 would be applicable for illustrative purposes. The cavity (33) that is defined internally of a gripping region (34) of the inner cylindrical member (3) forms a continuous circumferentially extending channel instead of the separate individual compartments arranged circumferentially as in the embodiment of the adapting sleeve 1a shown in FIG. 1. Thus, in this embodiment of the adapting sleeve (1b) schematically shown in FIG. 7, the hydraulic device (5) of the adapting sleeve (1b) includes an annular hydraulic pad (56) mounted between the inner cylindrical member (2) and each of the ring separators (4). Each an annular hydraulic pad (56) performs the function of the plurality of discrete hydraulic pads (51) distributed circumferentially at each opposite end of the embodiment of the adapting sleeve (1a) shown in FIGS. 1-6.
(32) Additional alternative embodiments of an adapting sleeve (1a, 1b) can include either a third plurality of hydraulic pads (51) or a third annular hydraulic pad (56) mounted in the central region of the adapting sleeve (1a, 1b) essentially intermediate between the two ends thereof. Such an embodiment is particularly desirable when additional clamping force between the adapting sleeve (1a, 1b) and the rotary core (N) is desired, such as might be warranted by the length or diameter of the adapting sleeve (1a, 1b). In such embodiments, each of the third plurality of hydraulic pads (51) or a third annular hydraulic pad (56) can form a terminus point of the hydraulic circuit as schematically depicted in FIGS. 5 and 6 for example. Alternatively, in such embodiments, the third plurality of hydraulic pads (51) or a third annular hydraulic pad (56) can form a pass through component of the hydraulic circuit such that the hydraulic pressure lines (52) connect to them from the first plurality of hydraulic pads (51) or first annular hydraulic pad (56) at one end of the adapting sleeve (1a, 1b) and also connect from them to the second plurality of hydraulic pads (51) or annular hydraulic pad (56) at the opposite end of the adapting sleeve (1a, 1b).
(33) Each example is provided herein by way of explanation of the invention, not limitation of the invention. As the nature of the invention is described sufficiently, as well as an example of the presently preferred configuration, the materials, shape, size and disposition of the elements described may be modified, as long as it does not involve an alteration of the essential characteristics of the invention that are claimed. In fact, it will be apparent to those skilled in the art that modifications and variations can be made in the present invention without departing from the scope or spirit thereof. For instance, features illustrated or described as part of one embodiment may be used on another embodiment to yield a still further embodiment. Thus, it is intended that the present invention covers such modifications and variations as come within the scope of the appended claims and their equivalents.
