AU2016299064A1

AU2016299064A1 - Gearbox and vibration generator having a lubricating-fluid distributor

Info

Publication number: AU2016299064A1
Application number: AU2016299064A
Authority: AU
Inventors: Herman DE JONG; Robert Weinand
Original assignee: Schenck Process Europe GmbH
Current assignee: Sandvik Rock Processing Australia Pty Ltd
Priority date: 2015-07-30
Filing date: 2016-07-28
Publication date: 2018-02-01
Anticipated expiration: 2036-07-28
Also published as: DE102015009697B4; AU2016299064B2; DE102015009697A1; WO2017016665A1

Abstract

The invention relates to a gearbox, comprising a housing (3), which supports at least one shaft (5) by means of at least one bearing (12), wherein the housing (3) has a bearing housing (9), in which the bearing (12) is inserted, and in which bearing housing (9) at least one lubricating-fluid collecting and conducting pocket (10) formed as a cut-out or recess is present, wherein the lubricating-fluid collecting and conducting pocket (10) and a lubricating-fluid distributor in the form of a distributor ring (19) are in an operative relation with each other in such a way that targeted guidance of lubricating fluid to the bearing (12) is forced. The invention further relates to a vibration generator (2) for a vibration machine (1), such as a vibratory conveyor and/or a vibratory sieve, comprising such a gearbox of the type according to the invention.

Description

Gearset and Vibration Exciter With a Lubricating Fluid Distributor

The invention relates to a gearset, including a housing which supports at least one shaft with the aid of at least one bearing, the housing including a bearing bell, in which the bearing, designed for example as a roller or friction bearing, is fas-tened/inserted, for example pressed in, and at least one lubricating fluid collecting and conducting pocket, designed as a recess or indentation, being provided in the bearing bell.

The invention generally relates to gearsets, in which toothed wheels, such as spur wheels, are supported on shafts. In particular, gearsets of this type are used in vibration exciters for vibration machines which are designed as vibrating conveyors or vibrating screens. The invention therefore also relates to vibration exciters for vibration machines of this type, namely vibrating conveyors and/or vibrating screens and a vibrating machine of this type.

Compared to the use of unbalance motors, vibration exciters, preferably linear exciters or circular exciters, have the advantage that defined flows of force and defined mechanical stresses may be introduced into a vibration machine. The vibration data is dependent on loads applied by the bulk material.

The roller bearing and toothed wheels of a vibration exciter supported in a cast housing are usually oil-lubricated, for example oil immersion-lubricated. Maintenance is usually limited to an occasional oil level check or an oil change at stipulated time intervals. When at a standstill, the unbalance masses/unbalance weights may be changed by installing and removing additional masses. Unbalances made of steel or lead may be balanced out. The vibration exciter is usually driven externally by a standard electric motor via a propeller shaft. Suitable maintenance-free propeller shafts are available for vibration exciters. If necessary, brake devices for reducing the rundown vibrations and frequency converters for the stepless variation of centrifugal forces, and thus the conveying power, may be used.

Vibration exciters in the form of linear exciters generate a force F having a sinusoidal characteristic, which acts along a line. A linear exciter has two shafts aligned with unbalance masses. These unbalance masses are synchronized for counterclockwise rotation at the same speed due to the built-in toothed-wheel gearset. The components of the centrifugal forces of the unbalance masses acting in the direction of the aforementioned line add up to a resulting force. The components occurring perpendicularly to the aforementioned line cancel each other out.

In contrast, the unbalance masses of a vibration exciter in the form of a circular exciter, also known as an exciter cell, rotate around the one center axis of a circular housing of the circular exciter or exciter cell and generate centrifugal forces whose vectors rotate at the operating frequency.

On the whole, vibration exciters are economical and offer a powerful drive even at high power demand. They have a long excitation life and a good running smoothness. They result in only a small amount of maintenance effort. The noise level that they produce is very low. It is advantageous that devices of this type have a 98-percent availability, which makes them ideal for use during continuous operation.

For example, a gearset from the automotive industry is disclosed in US 2 368 963 A, in which the shaft is supported in a bearing bell with the aid of two bearings, and in which a channel is provided in the housing for supplying the lubricating fluid to the bearings from a lubricating fluid sump, this channel being provided with a radial bore, and a sleeve being provided, in turn, to limit the lubricating fluid inflow to the bearings.

For example, a gearset is also known from US 2011/0064344 A1, in which the shaft is supported in a bearing bell with the aid of two bearings, and in which the corresponding bearing element includes a lubricating fluid reservoir having two legs, which have an opening in the area of the bearing elements for supplying the lubricating fluid to the bearing.

Due to the limited installation space for the present gearset, it is not possible to provide lubricating fluid reservoirs of this type in the area of the bearing.

The object of the invention is to provide an improvement here. The disadvantages of the prior art are to be eliminated or at least mitigated. In particular, the object is to induce a forced guidance of oil, which is frequently used as the lubricating fluid, which results in a durable vibration exciter design, gearsets per se are intended to be durable and yet cost-effective to manufacture.

According to the invention, this object is achieved in a generic device in such a way that the lubricating fluid collecting and conducting pocket and a lubricating fluid distributor in the form of a distributor ring are in active relationship with each other in such a way that a targeted lubricating fluid guidance to the bearing is forced. A gearset of a vibration exciter usually comprises a bearing housing, a shaft and two bearings, which are usually provided with the same design, i.e. are both designed as roller or friction bearings. Of course, a combination of a roller bearing with a friction bearing is also conceivable. A lubricating fluid sump is also situated in the housing, with which a rotating driver engages and distributes the lubricating fluid within the bearing housing during the operation of the gearset.

In linear exciters, in particular, toothed wheels, such a spur wheels, for example straight-toothed or helically toothed wheels, are mounted on the shafts. These toothed wheels are used as drivers and take up the lubricating fluid from the lubricating fluid sump and fling it onto the underside of a housing cover, from which it drips onto the shaft, the housing sides or the bearings. Toothed wheels of this type are usually inserted between the two bearings. In linear exciters, it is customary to use two shafts, which are each supported via two bearings of the same type, a spur wheel being mounted on each shaft between these two bearings, which meshes with the spur wheel mounted on the other shaft. Since linear exciters are frequently fastened to vibration machines in an inclined position, only the lower of the two toothed wheels engages with the lubricating fluid sump. The lubrication of the upper toothed wheel and the shaft and bearing connected thereto must take place by suitable lubrication fluid guidance in the housing.

By inserting the lubricating fluid distributor ring in a suitable location, dripping lubricating fluid is transported in a targeted manner past parts of the bearing which are not to be lubricated and into an area of the bearing to be lubricated. A failsafe operation of the gearset or the vibration exciter is thus ensured over a long period of use.

Since the installation space of the housing or gearset is very limited in the longitudinal direction of the shaft, it is extremely advantageous to use a distributor ring of a limited thickness. This means that the dimensions of the distributor ring in the longitudinal direction of the shaft are very small compared to the dimensions of the bearing.

The distributor ring advantageously has one or multiple recesses on its outer diameter, which form an opening between the outer race of the bearing and a securing ring in the lubricating fluid collecting and conducting pockets. Advantageous exemplary embodiments are claimed in the subclaims and are explained in greater detail below.

It is advantageous if a large number of lubricating fluid collecting and conducting pockets are disposed distributed over the circumference of the bearing bell. Dripping lubricating fluid may then be efficiently transported to the bearing. In order to use proven lubricants, it is advantageous if oil, for example mineral oil, is used as the lubricating fluid.

It is furthermore advantageous if the lubricating fluid distributor ring is designed as a component which is separate from the bearing and from the bearing bell. The assembly is simplified thereby.

The lubricating action and a forced conduction is improved if the lubricating fluid distributor ring is disposed within the lubricating fluid collecting and conducting pocket or abuts the latter or opens thereinto. This means that the recesses disposed on the distributor ring are radially aligned with the lubricating fluid collecting and conducting pockets. Or in another manner, that the edges of the recesses of the distribution ring are disposed within the recesses defined by the housing wall for the lubricating fluid collecting and conducting pockets. The lubricating fluid distributor ring is situated at a distance of more than double, preferably three times, its thickness from an edge of the lubricating fluid collecting and conducting pocket which is spaced an axial distance from the bearing. A targeted oil conduction is simplified thereby.

To be able to secure the bearing and simultaneously design the lubricating fluid guidance efficiently, it is advantageous if the lubricating fluid distributor ring is disposed between an outer race of the bearing, for example a bearing outer shell/a bearing outer race, and a securing ring/retaining ring.

Here again it has proven to be advantageous if the securing ring is disposed in or on the lubricating fluid collecting and conducting pocket, for example adjacent thereto. One advantageous exemplary embodiment is also characterized in that the distributor ring has a lubricating fluid conducting surface, inclined toward the longitudinal axis of the bearing, on its side facing away from the bearing. An one-sided or two-sided wedge surface is advantageous. A spherical, curved, convex or concave design of the lubricating fluid conducting surface may also be sensible.

In order for the lubricating fluid to become easily detached from the distributor ring, it is advantageous if a drip edge for the lubricating fluid is formed on the distributor ring.

The distributor ring may then also form a drip edge at a distance from the end, although it is particularly advantageous if the drip edge is formed by the radial inner edge of the distributor ring. A manufacture of the ring may then be easily carried out, in particular if it is manufactured from metal, such as a steel alloy.

If the drip edge is disposed at the radial height of rolling elements or a bearing gap, i.e. preferably axially adjacent to the rolling elements or the bearing gap, due to two sliding members, the lubricating fluid may be supplied as quickly as possible to the members to be lubricated, so that a damage to the members is avoided. The drip edge then ends next to the rolling elements or the bearing gap.

Webs and/or drip edges may furthermore be provided in the housing, which induces the targeted guidance of the lubricating fluid, which is flung against the housing inner wall by a driver and flows back on the housing inner wall in the direction of the lubricating fluid sump. A drip edge is advantageously provided on the underside of the housing cover. This causes the lubricating fluid flowing along the underside of the housing cover and in the direction of the lubricating fluid sump to drip or be introduced into an area of the bearing bell facing away from the lubricating fluid sump.

Webs are also disposed inside the bearing housing, which prevent the lubricating fluid from flowing back directly into the lubricating fluid sump and induce a forced guidance of the lubricating fluid in the direction of the shaft or bearing.

In particular, the invention relates to a vibration exciter for a vibration machine, such as a vibrating conveyor and/or a vibrating screen, which includes a gearset according to the invention.

The invention also relates to a vibration machine of this type, which includes a vibration exciter of this type.

The special feature of the invention is that an angle-independent approach is provided, i.e. a good lubricating action is always achieved independently of the installation situation, due to the arrangement of the lubricating fluid distributor ring. While holes have otherwise been relied on, which are used for draining rather than supply, in a corresponding rotation or inclined arrangement of the gearset or the vibration exciter, an always uniform, good, and efficient supply of lubricating fluid is now ensured.

Linear exciters may be disposed in any position on a vibration machine, preferably at an angle of approximately 45°to the horizontal, al though perpendicular and overhead positions are also customary. As a result, bearings known according to the prior art, which are supplied with lubricating fluid, should not be used. This is apparent, for example, in rolling element bearings, which ensure the supply of lubricating fluid via a groove in the outer race and radial bores disposed therein. These measures are namely used to ensure a lubricating fluid supply. Due to the arbitrary arrangement of the linear exciter, the lubricating fluid would drain into the bottom bores, which is, however, undesirable. Approaches of a conventional design—which then close these bores according to the arrangement position of the exciter—are, however, extremely complex. Due to the invention, however, it is possible to dispense with complex approaches which would otherwise be necessary, such as the use of pumps and nozzles. A second race is advantageously disposed on the side of the bearing opposite the distributor ring and/or between the outer race of the bearing and a side cover. An additional lubricating fluid sump is formed thereby with the aid of the second race, the distributor ring and the outer race of the bearing. This additional lubricating fluid sump remains in the lower area of the bearing while the vibration exciter is at a standstill.

The invention is explained in greater detail below with the aid of a drawing, in which a first exemplary embodiment is illustrated in greater detail, where:

Figure 1 shows a side view of a vibration machine, which includes a vibration exciter according to the invention;

Figure 2 shows an enlargement of area II from Figure 1, including a vibration exciter;

Figure 3 shows a perspective representation of the vibration exciter;

Figure 4 shows an enlarged representation of the vibration exciter with the cover removed;

Figure 5 shows another perspective view, including the schematically illustrated clockwise direction of toothed wheels mounted on shafts and meshing with each other;

Figure 6 shows a housing extension, illustrated in a partial sectional, perspective view;

Figure 7 shows a side view of the vibration exciter, mounted on the vibration machine during operation, including a lubricating fluid sump contained in its housing;

Figure 8 shows an enlarged, partial sectional and perspective representation of the transition area of the housing to the bearing supporting the shafts, including lubricating fluid collecting and conducting pockets;

Figure. 9 shows a side view of the area of some of the lubricating fluid collecting and conducting pockets; and

Figure 10 shows a longitudinal sectional representation in the area of a roller bearing, which is disposed between a bearing bell and a shaft, viewed in the radial direction, and between a side cover and a toothed wheel, viewed in the axial direction, including a lubricating fluid distributor ring mounted near the bearing;

Figure 11 shows a partial section of the vibration exciter, along a section line XI-XI illustrated in Figure 10.

The figures are only of a schematic nature and are used only for the sake of understanding the invention. Identical elements are provided with identical reference numerals.

Figure 1 shows a vibration machine 1, on which a vibration exciter is fastened in the form of a linear exciter 2, which includes a housing 3. Vibration exciter 2 causes an excitation to be produced in the direction of an arrow 4. Figure 2 illustrates vibration exciter 2, including its housing 3, in an enlarged representation. It is apparent that two shafts 5 are used, on which unbalance weights/unbalance masses 6 are mounted, which may also be referred to as vibrating segments.

The overall structure of vibration exciter in a perspective representation is apparent from Figure 3, which visualizes the fact that four unbalance weights 6 are present on each shaft 5, two of which are each present on one side of housing 3. Housing 3 is closed by a cover 7, so that a toothed wheel 8 assigned to each shaft 5 is removed from view.

With regard to toothed wheel 8, reference is made to Figure 5. However, a view of the interior is already facilitated in Figure 4. Housing 3 is thus divided into two parts in such a way that each part of housing 3 includes two bearing bells 9, which may also be referred to as bearing flanges. Lubricating fluid collecting and conducting pockets 10 are formed in bearing bells 9. Webs 11 formed by housing 3 may abut lubricating fluid connecting and conducting pockets 10.

Areas which are free of lubricating fluid collecting and conducting pockets exist on bearing bell 9, i.e., such areas in which some of lubricating fluid collecting and conducting pockets 10 are missing in the uniform distribution of lubricating fluid collecting and conducting pockets 10. Lubricating fluid collecting and conducting pockets 10 are designed in the form of channels and thus form grooves which are oriented in the radial direction and are open in the axial direction. They are shaped by the casting material of housing 3. They are primary-formed but may also be introduced by milling.

Shafts 5 are supported via bearings 12, as is also indicated in Figure 5. Particular bearing 12 is designed as a roller bearing, in particular a (self-aligning) roller, spherical or ball bearing. The rolling elements are identified by reference numeral 13.

Bearing bells 9 for accommodating bearing 12 are clearly apparent in Figure 6. Lubricating fluid conducting channels 14, which penetrate them axially and are designed as through-holes, in particular in the manner of bores, are also apparent. They are used to check a lubricating fluid balance. Enough lubricating fluid, namely (mineral) oil, is contained in housing 3 in such a way that a lubricating fluid sump 15 is formed.

The two toothed wheels 8 are in active meshing relationship with each other, toothed wheels 8 have a toothing 16 on their outside, namely a straight-toothed or helically toothed outer toothing. Lubricating fluid is distributed in the interior of housing 3 by the rotation of shafts 5 and toothed wheels 8, which act as drivers.

The lubricating fluid may then enter the interior of bearing bell 9 through lubricating collecting and conducting pockets 10, as are easily apparent in Figure 8, for example conducted by webs 11 or by force of gravity or due to centripetal force. Lubricating fluid collecting and conducting pockets 10 open onto circumferential surface 17 of a lubricating fluid distributor ring 19 and onto circumferential surface 18 of a securing ring 20. It is advantageous if a web 11 opens centrally into a lubricating collecting and conducting pocket 10, i.e. is disposed in the center thereof, i.e. defines an axially oriented projection in the interior of the channel. Lubricating fluid may then enter lubricating fluid collecting and conducting pocket 10 from both sides.

As is clearly apparent in Figure 9 as well as in Figure 10, lubricating fluid distributor ring 19 has a radially inner edge 21, which acts as a drip edge 22. A radially outer circumferential surface of lubricating fluid distributor ring 19 is disposed farther to the inside than a circumferential surface of securing ring 20. Roll or barrel-shaped rolling elements 13 are disposed between a bearing outer race 23 and a bearing inner race 24 of bearing 12. On an outside of housing 3, a side cover 25 interacts with a seal 26, for example a labyrinth seal, and a felt ring 27 in a sealing manner, a splash disk 28 being provided axially farther on the bearing side. On the side of bearing 12 facing away from the splash disk, a spacer sleeve 29 is also disposed radially between toothed wheel 8 and bearing inner race 24 within distributor ring 19 and securing ring 20. Radial inner edge 21 of distributor ring 19 is disposed radially farther to the inside than a radial inner edge of securing ring 20.

Lubricating fluid thus runs along lubricating fluid collecting and conducting pocket 10, penetrates between securing ring 20 and bearing outer race 23 along the toothed wheel-side surface of partially wedge-shaped lubricating fluid distributor ring 19 and drips in the area of drip edge 22 to supply rolling elements 13.

The arrangement of distributor ring 19 opposite lubricating fluid collecting and conducting pockets 10 and opposite bearing 12 is apparent from Figure 11. Distributor ring 19 illustrated here has recesses 30 distributed over its circumference, which correspond to collecting/conducting pockets 10 in bearing bell 9. The edges of recesses 30 are situated within the boundaries of collecting/conducting pockets 10 so that a targeted guidance of lubricating fluid in the direction of recesses 30 is ensured. The lower boundary of recesses 30, in turn, corresponds with the opening of the bearing, preferably the opening between bearing outer race 17 and rolling elements 13, into which the lubricating fluid is to be introduced for the purpose of optimally lubricating the bearing. Alternatively, a distributor ring 19 having circumferential, interrupted edge could also be provided. However, it would then end at the height of the aforementioned opening, so that it may, in turn, act as a drip edge.

List of Reference Numerals 1 vibration machine 2 vibration exciter 3 housing 4 excitation direction 5 shaft 6 unbalance weight/unbalance mass 7 cover 8 toothed wheel 9 bearing bell 10 lubricating fluid collecting and conducting pocket 11 web 12 bearing 13 rolling element 14 lubricating fluid conducting channel 15 lubricating fluid sump 16 toothing 17 circumferential surface of the lubricating fluid distributor ring 18 circumferential surface of the securing ring 19 distributor ring 20 securing ring 21 radially inner edge of the lubricating fluid distributor ring 22 drip edge 23 bearing outer race 24 bearing inner race 25 side cover 26 seal 27 felt ring 28 splash disk 29 spacer sleeve 30 recess on the lubricating fluid distributor ring 31 drip edge on the housing

Claims

Patent Claims

1. A gearset, including a housing (3), which supports at least one shaft (5) with the aid of at least one bearing (12), the housing (3) including a bearing bell (9), into which the bearing (12) is inserted, at least one lubricating fluid collecting and conducting pocket (10), designed as a recess or indentation, being present in the bearing bell (9), characterized in that a lubricating fluid distributor in the form of a distributor ring (19) is provided, which is in an active relationship with the lubricating fluid collecting and conducting pocket in such away that a targeted lubricating fluid guidance is forced in the direction of the bearing (12).
2. The gearset according to Claim 1, characterized in that the distributor ring (19) is provided with one or multiple recesses on its outer diameter, which form an opening between the outer race of the bearing (12) and a securing ring (20) in the lubricating fluid collecting and conducting pockets (10) and thus ensure a lubricating fluid guidance to the bearing (12).
3. The gearset according to one of the preceding claims, characterized in that a large number of lubricating fluid collecting and conducting pockets (10) are disposed, distributed over the circumference of the bearing bell (9).
4. The gearset according to one of the preceding claims, characterized in that the distributor ring (19) is designed as a component which is separate from the bearing (12) and from the bearing bell (9).
5. The gearset according to one of Claims 2 through 4, characterized in that the recess of the distribution ring (19) is aligned with the lubricating fluid collecting and conducting pocket (10) in the radial direction.
6. The gearset according to one of the preceding claims, characterized in that the distributor ring (19) is disposed between an outer race of the bearing (12) and a securing ring (20).
7. The gearset according to one of the preceding claims, characterized in that a second race is disposed on the side of the bearing (12) opposite the distributor ring (19) and/or between the outer race (23) of the bearing (12) and a side cover (25).
8. The gearset according to Claim 7, characterized in that an additional lubricating fluid sump is formed by the second race, the distributor ring (19) and the outer race (23) of the bearing (12).
9. The gearset according to one of the preceding claims, characterized in that the securing ring (20) is disposed within the lubricating fluid collecting and conducting pocket (10) in the axial direction, or an annular groove for the securing ring (20) is provided in the bearing bell (9) in the area of the lubricating fluid collecting and conducting pocket (10).
10. The gearset according to one of the preceding claims, characterized in that the distributor ring (19) has a lubricating fluid conducting surface, inclined toward the longitudinal axis of the bearing (12), on its side facing away from the bearing.
11. The gearset according to one of the preceding claims, characterized in that a drip edge (22) for lubricating fluid is formed on the distributor ring (19), and/or a drip edge (22) is formed by the radially inner edge of the lubricating fluid distributor ring (19).
12. The gearset according to Claim 10, characterized in that the drip edge (22) is disposed at the radial height of rolling elements (13) or at the radial height of a bearing gap.
13. A vibration exciter (2) for a vibration machine (1), including a gearset according to one of Claims 1 through 12.