Method for screening paper fiber stock

Abstract

A method of screening paper fiber stock incorporating a screen member having generally circular perforations and a rotor supporting vanes movable in the supply chamber, the rotor vanes are spaced from the screen member by a substantial distance (3/16"-1/2") to establish a tubular layer of stock of corresponding radial thickness adjacent the screen member, the rotor is operated at high speed to develop strong hydraulic shear forces in the tubular layer of stock causing tangential orientation of predominantly two-dimensional contaminant particles, and ribs on the inlet side of the screen member cause the stock to be continuously recirculated in the supply chamber to prevent undue increase in the consistency of the stock in the tubular layer, thereby enabling the screen to operate effectively at high capacity and high stock consistencies.

Description

BACKGROUND OF THE INVENTION

Paper mills have for many years made extensive use, for the screening of paper making stock, of screen apparatus embodying a cylindrical perforate screen member defining supply and accepts chambers on the opposite sides thereof in a closed housing and provided with a rotor member which operates in one of the chambers to keep the screen perforations open and free from solid material tending to cling to the screen surface. Commonly, the stock or furnish is delivered to the supply chamber adjacent the end of the screen member, and the material rejected by the screen member is collected and discharged from the opposite end of the screen member.

The assignee of this invention has manufactured and sold many such screens, originally in accordance with Staege U.S. Pat. No. 2,347,716, and more recently in accordance with Martindale U.S. Pat. No. 2,835,173, the latter construction being characterized by a rotor comprising bars or vanes of air-foil section in closely spaced but non-contacting relation with the surface of the screen member. More specifically, these vanes have been moved along the screening surface at relatively low speeds, e.g. in the range of 1,250-2,500 feet per minute, with the clearance between the supply side of the screen member and the nearest portion of the vanes being in the range of 0.030-0.060 inch.

The art has experimented widely with detailed variations in screens of the above type, including variations in the vane shape and other forms of rotor, and also in the size, spacing and configuration of the perforations in the screen member. In recent years, such screens have been offered to the trade wherein the rotor is a wall member provided with multiple bumps or other offset portions over its surface for the purpose of creating localized changes in volume, and resulting agitation effects, in the annular space between the rotor and the screen member, a typical such construction being shown in Clarke-Pounder U.S. Pat. No. 3,363,759.

SUMMARY OF THE INVENTION

The present invention is directed to the provision of a screen of the type outlined above wherein the screen member has multiple generally circular perforations and which will offer important practical advantages over the previously available similar screens, particularly in the following respects:

a. High throughput rate per unit area of screen cylinder surface, e.g. as high as 40 tons per day per square foot; b. high feed consistencies, e.g. as high as 5%; c. relative insensitivity to fluctuations of feed consistency, furnish type and/or flow rate; d. the ability to screen out the predominantly two-dimensional types of contaminant particles, e.g. slivers and flakes, otherwise capable of passing through the perforations; e. effective screening action over the entire perforate area of the screen member, with minimum tendency to undesirable thickening of the furnish adjacent the end of the screen member nearest to the reject outlet; f. economy of maintenance and operation, especially from the standpoint of the power requirements with relation to throughput; and g. mechanical reliability, especially from the standpoint of minimum damage to working parts.

In general it appears immaterial to the practice of the invention whether the supply chamber be on the inside or outside of the screen member, but it is essential that the rotor include bars or vanes which are located on the supply side of the screen member. It is also essential to this invention that the speed of the rotor be substantially increased as compared with conventional practice, to establish a correspondingly high peripheral speed for the vanes. For example, and in contrast to the range of approximately 1,250-2,200 feet per minute prescribed in the Martindale patent, outstanding results in the practice of the invention have been obtained with the vanes traveling at speeds of the order of 5,000 feet per minute. This is a practical limit for economic reasons although in principle, considerably higher speeds (e.g. 12,000 rpm) can be used and will permit operation at correspondingly higher consistencies and throughput rates.

Another particularly important characteristic of the invention is that the rotor vanes should be spaced substantially further from the adjacent surface of the screen member than in the prior practice. To illustrate, in contrast with the range of 0.030-0.060 inch specified in the Martindale patent, optimum results have been obtained in the practice of the invention with this spacing in the range of 3/16 to 1/2 inch, and in contrast with the range of 0.5-1.0% consistencies conventionally used with screens constructed in accordance with the Martindale patent, the invention makes it possible to handle feed consistencies as high as 5% solids. In general, optimum results from the standpoint of screening effectiveness with high consistencies and throughput rates have been obtained with the maximum rotor speed and vane spacings noted herein. Decreased vane to screen spacings can be used successfully at lower vane speeds, with corresponding reduction in capacity and throughput while still obtaining effective screening.

Under these dimensional and operational conditions, several important results are accomplished. The first is to establish an annular layer of furnish immediately adjacent the supply side of the screen member which is of substantial thickness, corresponding to the spacing between the rotor vanes and the screen member. Movement of fiber through the screen perforations will take place from this layer, but due to a number of factors, including particularly the frictional resistance of the edges of the holes to the passage of fiber therethrough, water will flow through the holes faster than the fibers, and since this water will be replaced by furnish at the feed consistency, the layer will be generally of a higher consistency than the balance of the furnish in the supply chamber. This increase in consistency will of course also be contributed to by the presence of reject particles in the annular layer.

A particularly significant result of the conditions outlined above is the creation of a substantially tangentially oriented steady field of hydraulic shear in the tubular layer of furnish between the path of the rotor vanes and the inlet side of the slotted screen member. Thus, that portion of this tubular layer contiguous to the surface of the screen member will have a circumferential velocity which approaches zero, because substantial portions thereof will pass through the slots, and their velocity will be essentially radial. Additionally, this layer will be subject to skin friction with respect to the imperforate surface portions of the screen member. On the other hand, the portion of the layer nearest to the vane path will travel circumferentially at a high velocity, approaching that of the vanes themselves. The intermediate portion will therefore travel at this velocity, varying from a maximum near the vane path to a minimum near the relatively zero velocity portion next to the screen member.

The importance of the shear forces created as just described derives from the effect which they have on the predominantly two-dimensional contaminant particles in the furnish, namely the slivers and flakes. These particles are induced to align themselves generally tangentially of the screen surface. The tangential alignment of such elongated particles will cause them to travel past the holes and to remain on the reject side of the screen member, whereas if they were randomly oriented, many would pass through the holes.

It is important to the practice of the invention to assure minimum disturbance of the shear field in the tubular layer of stock between the vane path and the screen member. Thus contrary to the principle of localized agitation effects emphasized in the Clarke-Pounder patent, optimum results are obtained if the vanes are smooth and extend the full axial length of the screen member to produce a uniform wave action instead of localized turbulance such as would result from the ends of shorter vanes. Similarly, the surface of the inlet side of the screen member should be smooth and free of flow-disrupting protrusions.

A further desirable result provided by this invention can best be explained by noting first that in the conventional practice according to the Martindale patent, with the rotor vanes moving in closely spaced relation to the surface of the screen member, the pressure pulse between the leading edge of each vane and the adjacent surface of the screen member tends to create excessive flow through the perforations, which can result in an undesirable extent of dewatering of the fiber in that immediate vicinity and mechanical smearing of the fiber over the screening surface. The large increase in the spacing of the vanes from the screen surface in accordance with the invention eliminates these undesirable effects, but at the same time, the high speed for the vanes prescribed by the invention creates a sufficient suction pulse between the trailing end of each vane and the screen member to keep the screen surface clean.

In connection with the point just discussed, it is pertinent that in screens of this general type wherein rotor vanes operate in closely spaced relation to the screen member, as in the Martindale patent, there is a tendency for the screen member to fracture, apparently because of the pressure pulses produced by the traveling vanes. It would seem likely that at the substantially higher rotor speeds prescribed by this invention, increased screen breakage problems could result, but the contrary has ocurred, apparently because the substantial increase in spacing between the vanes and the screen member significantly reduces 900000000000000000000000000000000000000000000000000000000000000000

RELATED APPLICATION

This application is a continuation of application Ser. No. 496,160, now abandoned filed Aug. 9, 1974 as a continuation of Ser. No. 288,293, now abandoned filed Sept. 12, 1972.

US Referenced Citations (12)

Number	Name	Date	Kind
1856176	Trimbey	May 1932
2900077	Sandison	Aug 1959
2975899	Cannon	Mar 1961
2983379	Cram	May 1961
3080696	Morin	Aug 1972
3363759	Clarke-Powder	Nov 1968
3394809	Hunter	Jul 1968
3581893	Rich	Jun 1971
3581903	Holz	Jun 1971
3586172	Hunter	Jun 1971
3726401	Bolton	Apr 1973
3849302	Seifert	Nov 1974

Foreign Referenced Citations (3)

Number	Date	Country
203353	May 1959	ATX
727010	Feb 1966	CAX
735273	May 1966	CAX

Continuations (2)

	Number	Date	Country
Parent	496160	Aug 1974
Parent	288293	Sep 1972