Continuous dryer

Abstract: In addition to blades (16), the rotor (9) is provided with at least one centrifuging element extending along the entire axis of the rotor advantageously in a helical pattern in the product discharge direction, said centrifuging element being shaped in the form of a rib (13) with a height less than the height of said blades (16) and so calculated as to act as a device for limiting the product layer present on the heated surface of said cylinder (2).

Description: This invention relates to a continuous dryer of the substantially horizontal axis type especially designed and constructed for drying products in general and in particular pasty and pulverulent liquid products. The continuous dryer is of the kind illustrated in the preamble of the attached main claim. Various types of horizontal axis dryers are known, consisting substantially of a cylinder having a heated surface and within which a possibly heated rotor is rotated, this being provided with a plurality of blades the purpose of which is to keep the product to be treated in a state of agitation so that it is brought turbulently into contact with the heated surface while at the same time being advanced along the cylinder axis towards discharge, concurrently or countercurrently fed hot gas possibly being used. British Patent 1 401 195 discloses an example of a continuous dryer of the kind above comprising: a horizontal or substantially horizontal static cylinder provided with means for the direct and indirect heating of the surface which is to come into contact with the product under treatment and a rotor within said static cylinder. The rotor comprises in a first portion a continuous helical perforated band, in a second portion a continuous helical unperforated band, in a third portion axial blade arrangements, and in the fourth portion a continuous helical unperforated band. The rotor structure is a bulky one and the dryer cannot be easily modified as concerns the thrust exerted on the product under treatment. In fact if need arises the whole rotor has to be changed. These types of conventional dryer do not always achieve satisfactory drying of all types of products, particularly thermolabile or rheologically critical products, because the thickness, turbulence, dynamic and contact conditions of the layer of product under treatment lying at the cylinder heating surface are such as not to produce correct heat transfer and in particular result in the formation of a deposit at said surface by virtue of the different treatment times which the product undergoes. This deposit results in soiling and in particular deterioration of the product, with consequent fall-off of heat transfer. In these known dryers the product must never be statically at rest on the hot wall and the distance therefrom of the agitation element must tend to zero in order to act on the entire layer, with the result that a further problem encountered is that the difference in thermal expansion due to the temperature difference between the cylinder and rotor results in a variation in the position of the blades relative to the heated surface of the cylinder. This obviously results in irregular or incorrect and non-constant turbulence of the product under treatment, resulting in a loss of dynamicity of the system. A further drawback of conventional dryers is that the centrifuging of the product under treatment and its distribution over the heated surface is partial, random and limited and depends on the blade inclination, with consequent poor contact with the cylinder. Again, in conventional dryers gas-product separation takes place externally with consequent problems of cost, space requirement and handling. An object of the present invention is to provide a continuous dryer in which the drawbacks encountered in conventional continuous dryers are overcome. This object is achieved by a dryer having the features of claim 1. The dryer of the invention is illustrated by way of non-limiting example in the figures of the accompanying drawings, in which: Figure 1 is a longitudinal section through the overall dryer; Figure 2 is an enlarged schematic cross-section on the line II-II of Figure 1; Figures 2a and 2b are schematic illustrations of two preferred embodiments of the ribs; Figures 3 and 3' show a detail of the expansion mounting of a blade; Figure 4 is a cut-away view of a part of the rotor showing its blades mounted on a single block and a rib; Figure 5 is a schematic section on the line V-V of Figure 1. With reference to said figures, the dryer indicated overall by 1 consists of a cylinder 2 of horizontal axis provided with closure heads 3 and 4. The cylinder 1 is supported by elements 5 resting on a common surface. Circumferentially about said cylinder there is provided a chamber 6 for the passage of diathermic oil, which is fed and discharged through ports 7 and 8 provided along said cylinder 2. In the illustrated example the chamber 6 is divided into several compartments, each compartment being provided with an inlet and discharge port 7 and 8, to obtain differential heating of the cylinder 2 if desired. A rotor 9 is arranged axially within the cylinder 2 and is provided with hubs 10, 10' which pass through the heads 3 and 4 and are supported by bearing systems 11, 11' each supported by its own structure 12, 12', which is independent of the elements 5 supporting the cylinder 2. The reason for providing separate and independent support elements for the cylinder 2 and rotor 9 is basically that as these latter two components are at different temperatures, they undergo different degrees of expansion, which could affect the correct operation of the unit. A further reason for separate supports is the extent of the dynamic forces in play when the rotor rotates at high speed. As can be seen from Figure 2, the rotor 9 comprises a plurality of ribs 13 arranged variously relative to the rotor and extending substantially along the entire length of the roller and arranged helically in the direction of the discharge aperture 14 for the product, which is fed through a loading aperture 15. The shape of the ribs 13 can be suitably designed to prevent dynamic return with depression, and material deposition on them, together with prolonged centrifugal moments. Schematic examples of possible arrangements of the ribs 13 are shown in Figures 2a and 2b, What is essential is that the outer edge 13' of each rib 13, independently of its configuration, is spaced from the heated inner surface 2' of the cylinder 2 by a distance d equal to the required thickness of the layer of material under treatment in the interspace between the surface 2' and the edge 13'. On the rotor 9 there is also provided a plurality of blades 16 in a prevalently helical arrangement with one or more starts, their particular structure being such that the end edge 16' is maintained always substantially tangential to or scraping the heated surface 2' when the rotor is moving. As shown in Figures 3, 3' each blade is fixed onto the rotor 9 via a cup spring 17 or like elements. Such a structure enables the position of the edge 16' relative to the surface 2' to be controlled independently of the state of the rotor 9. When the rotor 9 is at rest (Figure 3) the spring 17 is in an expanded state and the end 16' is distant from the heated surface 2'. This obviously has no influence on operation as the dryer 1 is inoperative. When the rotor 9 is moving (Figure 3') the centrifugal force compresses the spring 17 and the edge 16' is brought into the vicinity of the heated surface 2'. The required travel of the edge 16' of the blade 16 is calculated on the basis of various factors, the strength of the springs 11 also being calculated on the basis of these factors. The purpose of the blades 16, as is well known, is to maintain the treated product in a stage of agitation throughout the entire cross-section of the layer while at the same time urging the product towards discharge. This is achieved in conventional dryers by inclining the blade by between 0° and 45° to provide an identical thrust throughout the entire layer. As there may be accumulations of product and therefore an undesirable layer increase in progressing along the longitudinal axis of the dryer, the blade must be able to automatically handle this product accumulation. This is achieved by giving the individual blades 16 different inclinations and different heights as illustrated schematically in Figure 4 in which the blades are given a twist or fixing angle which is different for different blade heights so as to generate both a propulsive force and a sustentation force. As is well known, the product turbulence is a function of the number of blades, which when viewed in development during rotation must ideally cover the entire heated surface. In current dryers this turbulence is achieved with individual blades each requiring its own mounting and adjustment, thus creating a limitation on the number of blades. A large number of blades can be formed by blanking and bending them from a single element 18 (Figure 4) fixed to the rotor 9 either by way of the expansion system already described with reference to Figures 3 and 3', or not. With particular reference to Figure 1, a thrust and centrifuging blade 19 is fixed rigidly to the rotor 9 in proximity to the head 4, to provide air/product separation and discharge the air through an aperture 20 provided in the bottom of the head 4. If the dryer 1 is to be used with supplementary hot air, an aperture 21 is provided in the head 3 for feeding this air into a distribution channel 22 which feeds said air into the cylinder in a radial direction. With particular reference to Figure 5, barrier blades 23 are provided on the rotor 9 in the same plane immediately upstream of the discharge aperture 14 to hinder the product exit by obliging it to pass over the top of these blades. In practice these blades can also consist of a single ring. To reduce mechanical work due to the cutting and impact force, the blades have a sharpened working edge. In addition, to increase the product heat transfer surface, in combination with the blades there are provided preferably corner-section grinding elements 24 or cam-shaped devices (not shown), mounted in any manner on the rotor and arranged to hammer against the heat transfer wall by centrifugal force.

Claims: A continuous dryer for a product, said dryer comprising: a substantially horizontal static cylinder (2) having product loading (15) and discharge (14) apertures, and heating means (6) associated with said static cylinder for heating a cylindrical inner surface (2') of said static cylinder; a substantially cylindrical rotor (9) in said static cylinder, defining a substantially cylindrical gap with said inner surface (2'); two blade arrangements (16; 13) on the rotor, the first arrangement comprising a plurality of rows of spaced blades (16), each such row being connected to the rotor (9) by means of an element and extending within said gap, and the second arrangement comprising a plurality of ribs (13) of differing shape configuration with respect to the spaced blades (16); said two blade arrangements being angularly displaced on said rotor (9); said ribs (13) alternating with said rows of blades (16) along the periphery of the rotor (9) and acting as centrifuging elements; characterized in that the two blade arrangements (16, 18; 13) extend along the whole length of the rotor (9); in that the ribs (13) are arranged helically in the direction of the discharge aperture (14); and in that the blades (16) are inclined with respect to a plane perpendicular to the rotor in a prevalently helical arrangement for urging the product towards the discharge aperture (14). A continuous dryer according to Claim 1, wherein the heating means (6) includes means (7, 8) for differential heating of the cylindrical inner surface (2'). A continuous dryer according to Claim 1, wherein the cylinder (2) and the rotor (9) are supported by independent support means (5, 11). A continuous dryer according to Claim 1, wherein the blades of the rows of blades (16) are resiliently urged away from the heated surface (2') by springs (17). A continuous dryer according to Claim 1, wherein the rows of blades (16) are formed from a single piece structure (18). A continuous dryer according to Claim 1, further comprising aperture means (21) for feeding hot air into the cylindrical gap countercurrent to the product advancement. A continuous dryer according to Claim 1, further comprising gas separating means (19) located on the rotor (9) in proximity to the loading aperture (15) for separating gases from the product. A continuous dryer according to Claim 1, further comprising on the rotor (9) barrier means (23) immediately upstream of the discharge aperture (14) partially intercepting the cylindrical gap. A continuous dryer according to Claim 1, wherein the blades (16) have a sharpened edge (16') facing the product layer. A continuous dryer according to Claim 1, further comprising grinding means (24), in association with the rows of blades (16).

Inventors: GARBAGNATI GIBERTO, SPADA MASSIMILIANO, GARBAGNATI, GIBERTO, SPADA, MASSIMILIANO
Applicants: VRV S P A, VRV S.P.A.
Application year: 1991
Main classification: F26B17
IPC codes: F26B25, F26B17