Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21B—ROLLING OF METAL
  • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
  • B21B31/07—Adaptation of roll neck bearings
  • B21B31/076—Cooling; Lubricating roller bearings
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
  • B21B—ROLLING OF METAL
  • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
  • B21B31/07—Adaptation of roll neck bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
  • F16C13/02—Bearings
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
  • F16C33/02—Parts of sliding-contact bearings
  • F16C33/04—Brasses; Bushes; Linings
  • F16C33/06—Sliding surface mainly made of metal
  • F16C33/10—Construction relative to lubrication
  • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
  • F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
  • F16C33/1065—Grooves on a bearing surface for distributing or collecting the liquid
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16N—LUBRICATING
  • F16N7/00—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated
  • F16N7/38—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems
  • F16N7/40—Arrangements for supplying oil or unspecified lubricant from a stationary reservoir or the equivalent in or on the machine or member to be lubricated with a separate pump; Central lubrication systems in a closed circulation system
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2322/00—Apparatus used in shaping articles
  • F16C2322/12—Rolling apparatus, e.g. rolling stands, rolls
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16N—LUBRICATING
  • F16N13/00—Lubricating-pumps
  • F16N13/20—Rotary pumps
  • F16N2013/205—Screw pumps

Definitions

• the invention relates to a chock, d. H. a bearing housing for supporting a roll in a roll stand of a roll stand.
• the rolling stand has a main bore for receiving a pin of the roller.
• the chock has an inlet for supplying lubricant, typically under pressure, to the interior of the chock and a drain for returning the lubricant from the chock.
• the lubricant is used to lubricate the roll neck bearing during rolling of rolling stock, e.g. B. slabs.
• the chock may be associated with a pump means for conveying the lubricant flowing back through the return from the chock.
• the pump device then has a housing, an inlet channel and an outlet channel, wherein the inlet channel communicates fluidically in the pump device with the inlet in the chock and the drainage channel in the pump device with the outlet for the lubricant in the chock.
• the pump device can be driven by the flow of lubricant in the inlet.
• Such chocks with pumping devices to support the return of the lubricant are basically known in the art, for. From European patents EP 1 078 172 B1 or EP 1 497 048 B1. Furthermore, in the prior art various types of pumping devices, for. B. circulating pumps, hydrodynamic screws or screw pumps, z.
• screw conveyor are, for. B. known from the patent US 1, 434.138.
• the invention has for its object to provide a chock with an alternative pumping device for supporting the return of lubricant from the chock.
• This object is solved by the subject matter of patent claim 1.
• the pumping device comprises in its housing a screw pump with a screw conveyor in the discharge channel for conveying the returning lubricant and a driven by the pressurized tapered lubricant turbine in the inlet channel for driving the screw pump.
• the inlet and the outlet are arranged in the chock.
• the inlet channel and the outlet channel also referred to below as the return channel, are arranged outside the chock in the pump device.
• the inlet is at least largely aligned with the inlet channel at its junction.
• the drainage channel is at least largely aligned with the drainage channel at its junction.
• the screw pump is formed from a tubular base body which carries on the outside a screw conveyor, and the housing of the pump device has a bore in which the screw pump is rotatably mounted in bearings.
• the space between the outside of the body and the inside of the bore forms the drainage channel, wherein the screw conveyor protrudes into the return channel for conveying the returning lubricant and wherein the bearings - and thus the auger - stationarily positioned by means of holding means inside the bore are rotatably mounted.
• the individual helix of the screw conveyor are each at an acute angle ⁇ - in the flow direction of the lubricant in Return - inclined relative to the tubular body. This inclination advantageously increases the efficiency of the screw conveyor.
• the holding means for the bearings are exemplified in the form of spoked wheels or perforated plates, which each extend in a plane perpendicular to the longitudinal axis of the bore in the housing. At their periphery they are each connected to the inside of the bore to the housing. On their inside they carry - preferably coaxial with the bore - each one of the bearings for the screw pump.
• the formation of the holding means in the form of spoke wheels or perforated plates is absolutely necessary at least below the longitudinal axis of the bore in order to ensure the permeability of the return passage for the lubricant.
• the interior of the tubular body forms the inlet channel.
• the turbine for driving the screw pump is arranged.
• the ratio of the cross-sectional area of the return channel to the cross-sectional area of the inlet channel is between 2 and 10.
• the return occurs on the drain side of the chock in the form of a single hole from the chock and the single inlet is guided inside the bore for the return to the chock.
• the Pumping device is preferably placed as a separate unit outside on the discharge side of the chock so that the inlet channel of the pump device with the inlet of the chock and the return channel of the pump device communicates fluidically with the return of the chock.
• the drainage side of the chock is the side opposite the ball side of the chock.
• the bale side of the chock is that side which, when the roll is installed, is directly opposite the bale of the roll.
• the bore for the return side of the chock with respect to the main bore for receiving the roll neck is positioned such that the upper apex of the bore for the return a vertical distance s to the lower vertex of the action hole arranged in the main bore has annular sealing lip with 0 ⁇ s ⁇ r1, where r1 corresponds to the radius of the bore for the return.
• the upper vertex of the bore for the return is preferably above the lower apex of the radius of action of the sealing lip.
• the annular sealing lip is placed on the journal of the roller and seals it against the main bore of the chock.
• the effective opening of the sealing lip means that opening which results when the sealing lip is slightly radially compressed when the roll neck is inserted.
• the radius of this effect opening is called the radius of action of the sealing lip.
• the diameter of the bore for the return in the chock and the return passage in the pump means is advantageously only between 40 and 80 mm.
• the chock may be an upper chock for supporting an upper back-up roll or a lower chock for supporting a lower back-up roll in the roll stand.
• the underside of the upper chock can be flat.
• d2 between the lower vertex UB of the main bore (1 10) of the chock and the flat bottom of the upper chock, d2 ⁇ 20 mm, preferably d2 ⁇ 10 mm.
• the present invention offers the following advantages:
• the pump device increases the volume flow of the lubricant in the drain. This has the advantage that in the chocks according to the invention, a smaller cross-sectional area or a smaller radius for the bore of the drain can be selected in comparison to chocks without the pump device according to the invention.
• the provision of a second bore for the return of the lubricant as is typically used in traditional chocks, can be completely dispensed with; d. h., When using the pump device according to the invention, only one (number word) hole for the flow on the discharge side of the chock needs to be provided.
• a predetermined maximum distance between the lower vertex (UB) of the main bore (1 10) and the preferably flat underside of the chock can be maintained or even undershot, in particular in compliance with the claimed horizontal distance d1 and the vertical distance s.
• the invention is a total of five figures attached, wherein
• Figure 1 is a perspective view of the chock according to the invention; 2 shows a longitudinal section through the chock with attached
• FIG. 3 shows a longitudinal section through the pump device according to the invention
• FIG. 4 shows a schematic cross section through the discharge side of FIG
• FIG. 5 shows a cross section through the pump device according to the invention; shows.
• FIG. 1 shows by way of example a perspective view of the chock 100 according to the invention, in particular with regard to its discharge side 105.
• a chock refers to a bearing housing for receiving a roll neck (not shown here). The chock is typically mounted vertically displaceable in the window of a roll stand. In the chock, a main bore 1 10 is provided for receiving the roll neck, preferably also a bearing bush and a pin bushing, which, however, will not be discussed here.
• the roll or the roll neck is mounted in the bore of the chock, one side of the chock is associated with the bale of the roll. This side of the chock is called the bale side.
• the already mentioned drainage side 105 of the chock lies opposite the bale side.
• the name is due to the fact that on this side the lubricant, which is supplied during operation, ie during the rotation of the roller, the chock on the bale side exits and is discharged from there.
• an inlet 120 can be seen, through which the lubricant 200 is guided into the chock 100 to the inlet opening 120-1 in the space between the bore of the chock and the roll neck, or more precisely in the Gap between a bearing bush and a pin bush, to enter, there to form a lubricating film.
• the lubricant is regularly circulated, ie it is regularly fed lubricant under pressure via the inlet 120 and discharged via the discharge side.
• the lubricant collects in the lower region of the chock on the bale side and the discharge side in a lubricant collecting space 142 of the chock. From there, it is typically pumped off and fed back to the lubricant circuit.
• the pump which serves to maintain the lubricant circuit and which pumps the lubricant with a pressure p in the inlet 120, is not the subject of the invention and therefore not shown in the figures. It is important, however, that this pump is not to be confused with the pumping device 130, which is the subject of the invention.
• the outer coaxial ring represents the drain 140 within the chock and the drainage channel 136 typically aligned therewith in the pump means of the present invention for removing the lubricant accumulated in the lubricant plenum 142.
• the vertical center plane LM of the main bore 1 10 indicated.
• the pump device according to the invention described below allows the distance d2 between the lower vertex UB of the main bore 110 and the preferably planar underside of the upper chock to be kept comparatively small: the upper limit lies at d2 ⁇ 20mm, preferably d2 ⁇ 10mm.
• the lower limit is defined by safety reasons or by the required load.
• FIG. 2 shows a longitudinal section through the chock 100 with its discharge side 105 and the pump device 130. It can be seen that the pump device 130 is placed on the discharge side 105 of the chock and that the inlet 120 for the lubricant 200 inside the chock 100 with the inlet channel 134 in the interior of the pump device 130 communicates fluidically. Likewise, the drain 140 in the interior of the chock is aligned with the drain passage 136 within the pump means. According to the invention, the inlet channel 134 and the outlet channel 136 are arranged coaxially with one another.
• FIG. 3 shows a longitudinal section through the pump device 130 according to the invention.
• the pump device has a housing 132 in which a screw pump 137 is rotatably mounted.
• a tubular main body 137-1 of the screw pump 137 is rotatably supported in bearings 137-2.
• the bearings 137-2 and thus also mounted therein screw pump 137 are inside the Housing 132 held by means of holding means 132 a.
• the holding means 132a are formed for example in the form of spoked wheels or perforated plates.
• the holding means preferably each extend in a plane perpendicular to the longitudinal axis L of the bore in the housing 132.
• the holding means are at its periphery on the inside of the bore with the housing 132 z. B. integrally connected.
• the rohrformige main body 137-1 of the screw pump 137 carries on its outside a screw conveyor 138.
• the screw conveyor 138 protrudes with their helices in the space between the outside of the rohrformigen body 137-1 of the screw pump 137 and the inside of the bore in the housing 132, wherein this space forms the drain passage 136 for the lubricant 200.
• the helix of the screw conveyor is set at an angle ⁇ relative to the outside of the rohrformigen body 137-1 in the flow direction.
• the flow direction of the supplied through the inlet channel 134 and the running out of the lubricant collection chamber 142 lubricant 200 is shown in Figure 3 by arrows.
• the outlet channel 136 extends coaxially to an inlet channel 134, which is formed by the interior of the rohrformigen body 137.
• a turbine 139 Inside the rohrformigen body is a turbine 139, which is rotatably connected on its outside with the rohrformigen body 137-1.
• the turbine 139 is driven by the pressurized and via the inlet channel 134 of the circulation pump (not shown here) supplied lubricant, which flows through the inlet channel 134 from right to left in Figure 3.
• the turbine does not require its own drive device and no external or additional energy supply.
• the turbine due to its fixed connection with the tubular body 137-1, drives the auger pump 137 and thus rotates the auger 138.
• Figure 4 shows a cross section through the discharge side of the chock 100.
• the cross section is shown only highly schematic. It serves to illustrate the essential constructive relationships for the present invention.
• the center or the longitudinal axis of the pump device 130 according to the invention With respect to the lubricant collection chamber 142 so that during rolling operation, the maximum level PH of the lubricant 200 in the interior of the lubricant collecting chamber 142 does not rise higher than the center axis or the longitudinal axis L of the pump device 130.
• the upper vertex OS of the bore for the drain 140 in the vertical direction is always above the lower vertex US of the action opening of a arranged in the main bore 1 10 annular sealing lip.
• the distance should be greater than 0 and less than the radius r1 of the bore for drain 140.
• the horizontal distance d1 between the center of the main bore 110 and the center of the bore for the outlet 140 should be: R1 ⁇ d1 ⁇ R1 + 100 mm, where R1 denotes the radius of action of the annular sealing lip.
• R1 denotes the radius of action of the annular sealing lip.
• FIG. 5 shows a cross section through the pump device 130 according to the invention.
• the outer hatched area shows the pump housing 132 with a circular or cylindrical bore into which the screw pump 137 is inserted. It can be seen the tubular body 137-1, which extends coaxially with the bore in the housing 132. Inside the tubular body 137-1, the turbine 139 with its paddle wheels is shown schematically.
• the inner cross section of the tubular base body represents the cross-sectional area A 2 of the inflow channel 134.
• the cross-sectional area of this coaxial annular space represents the cross-sectional area A1 of the drainage channel.
• the cross-sectional area of the inlet channel 134 may be formed substantially smaller than the cross-sectional area of the drain channel 136.
• the ratio of the cross-sectional area A1 of the discharge channel to the cross-sectional area A2 of the inlet channel is between 2 and 10. This ratio is made possible above all by the pump device 130 according to the invention, which serves as a support for the faster Discharge of the Schnniernstoffs 200 from the lubricant collection chamber 142 is used under atmospheric pressure.
• the pump device 130 makes it possible to dispense with a second drainage bore on the discharge side of the chock.
• the radius r1 of the bore 133 in the housing 132 of the pump device or the drainage channel 136 can be kept so low that the constructive spacing ratios described above with reference to FIG. 4 can be maintained.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Oil, Petroleum & Natural Gas (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Rolling Contact Bearings (AREA)

Priority Applications (5)

Applications Claiming Priority (2)

Publications (1)

Family

ID=49880744

Family Applications (1)

Country Status (7)

Families Citing this family (5)

Citations (2)

Family Cites Families (17)

• 2012
  • 2012-12-28 DE DE102012224511.1A patent/DE102012224511A1/de not_active Withdrawn
• 2013
  • 2013-12-18 RU RU2015131098A patent/RU2609192C1/ru active
  • 2013-12-18 CN CN201380074034.9A patent/CN105121046B/zh not_active Expired - Fee Related
  • 2013-12-18 EP EP13811899.7A patent/EP2938446B1/de not_active Not-in-force
  • 2013-12-18 US US14/758,365 patent/US9623458B2/en not_active Expired - Fee Related
  • 2013-12-18 WO PCT/EP2013/077091 patent/WO2014102109A1/de not_active Ceased
  • 2013-12-18 JP JP2015550029A patent/JP5932166B2/ja not_active Expired - Fee Related

Patent Citations (2)

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