Classifications

• • 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
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
  • F16C19/545—Systems comprising at least one rolling bearing for radial load in combination with at least one rolling bearing for axial load
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
  • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
  • F01C21/02—Arrangements of 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
  • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
  • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
  • F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
• • 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
  • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
  • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
  • F16C35/042—Housings for rolling element bearings for rotary movement
• • 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
  • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
  • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
  • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
  • F16C35/07—Fixing them on the shaft or housing with interposition of an element
  • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
  • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
  • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
  • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
  • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
• • 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
  • F16C2360/00—Engines or pumps
  • F16C2360/43—Screw compressors

Definitions

• Rolling Bearing Carrier Module and Compressor relate to a rolling bearing support module for a machine such as a compressor or a screw compressor and a compressor.
• a face gap existing between a housing of such a compressor and one of the surfaces of a rotor is essential to the efficiency of such a compressor.
• other dimensions and positions of components with each other also determine the performance, efficiency and cost-effectiveness of machines with precisely positioned bearings and corresponding contact surfaces on their housing or on other components. It is so often the task of creating a bearing assembly that allows a more accurate alignment of a shaft to another components with an end face.
• roller bearing carrier module according to claim 1 or a compressor according to claim 10.
• the rolling bearing support module thus further comprises a rolling bearing assembly having a first rolling bearing and a second rolling bearing, which is arranged in the axial direction directly or indirectly adjacent to the first rolling bearing, wherein the rolling bearing assembly is adapted to over the first rolling bearing axial forces in at least one axial direction, but to transmit substantially no radial forces.
• the rolling bearing assembly is further configured to receive radial forces but substantially no axial forces in the at least one axial direction via the second rolling bearing and deliver them to the carrier, wherein a side surface of the first rolling bearing with one of the end face of the machine or the abutment surface of the shaft corresponding level is aligned.
• the first rolling bearing is further configured to deliver the axial forces in the at least one direction across the side surface to a component in a corresponding plane of the other surface of the end surface and the abutment surface of the shaft.
• the second rolling bearing is in this case arranged on a side of the first rolling bearing facing away from the first bearing of the first bearing.
• a compressor comprises a first component having a bore in an end face of the first component, a shaft extending substantially in the axial direction parallel to the bore into the latter and having a contact surface which extends substantially extends in the radial direction and substantially parallel to the end face of the first component, and a rolling bearing assembly having a first rolling bearing and a second rolling bearing, which in the axial direction directly or indirectly adjacent to the first rolling bearing angeord- is net.
• the rolling bearing arrangement is in this case further designed to receive axial forces in at least one axial direction, but substantially no radial forces, via the first rolling bearing.
• the rolling bearing assembly is further configured to receive over the second rolling bearing radial forces, but substantially no axial forces in the at least one axial direction and deliver to the first component.
• a side surface of the first rolling bearing is in this case with the end face or the contact surface of the shaft in contact.
• the first rolling bearing is designed to transmit the axial forces in the at least one direction via the side surface to the other surface of the end face and the contact surface of the shaft.
• the second rolling bearing is arranged on a side of the first rolling bearing facing away from the side surface of the first rolling bearing.
• Embodiments of the present invention is based on the finding that a tolerance chain can be shortened by arranging it on the shaft in the case of a bearing arrangement with at least two rolling bearings on the first rolling bearing, which absorbs the axial forces in at least one direction. that only this contributes to the tolerance chain for the axial direction.
• this is achieved in that the first rolling bearing is arranged on the shaft or on the first component, the first rolling bearing with its side surface directly with the end face of the first component or the contact surface of the shaft in contact during the axial force is delivered from the side surface of the first rolling bearing directly to the other surface to the associated component, ie the shaft or the first component.
• this arrangement of the first rolling bearing of the rolling bearing assembly is chosen so that - after assembly - results in a corresponding arrangement.
• the first rolling bearing is an angular contact ball bearing, which has, for example, a width tolerance of the class PA4 or PA7 or finer.
• the second rolling bearing may be formed for example by a cylindrical roller bearing. It is also possible to provide in embodiments of the present invention, one or more further angular contact ball bearings or radial bearings, which are arranged in the rolling bearing assembly and are to be found for example between the first and the second rolling bearing. In the case of a roller bearing support module according to an embodiment of the present invention, this can be connected to the machine, for example, by providing a cohesive or non-positive connection.
• FIG. 1 shows a sectional view of an embodiment of a roller bearing support module
• FIG. 2 is a cross-sectional view of a compressor with a mounted rolling bearing support module according to embodiments of the present invention
• FIG. Fig. 3 shows a sectional view of a screw compressor
• Fig. 4 shows a cross section of a conventional bearing assembly with an intermediate ring to be ground
• 5 shows a cross-sectional view of a compressor with a mounted roller bearing support module according to embodiments of the present invention for 2 shafts;
• FIG. 6 shows a cross-sectional view of a roller bearing support module according to an embodiment of the present invention for a fixed-lot bearing
• Fig. 7 shows a cross-sectional view of a compressor according to an embodiment of the present invention.
• FIGS. 1-7 Before, in connection with FIGS. 1-7, embodiments of the present invention and comparative constructions are described and explained with respect to their mode of operation, it is useful to first of all point out that in the context of the present application, summary reference numbers are used to simplify the description.
• Machine elements, components, assemblies and other elements which are referred to by means of reference numerals, can hereby be executed identically and / or dimensioned. With regard to their dimensioning and design, however, they can also deviate from each other in any constructively meaningful dimensions or be executed differently.
• 1 shows a roller bearing support module 100 according to an embodiment of the present invention with a carrier 110 and a roller bearing assembly 120, which comprises a first roller bearing 130 and a second roller bearing 140.
• the rolling bearing arrangement 120 further comprises, in the region of the second rolling bearing 140, a bearing cup 150, which in a radial direction creates a mechanical connection between the carrier 110 and the second rolling bearing 140 via the radial forces from an inner ring 140a of the second rolling bearing via the rolling elements 140n and an outer ring 140c to the carrier 110 are transferable.
• a corresponding bearing cup is missing from the first roller bearing 130.
• a line of symmetry 160 which also represents a center line of a shaft to be connected to the roller bearing carrier module 100
• a recess 170 which adjoins the first roller bearing 130 in the axial direction, so that at least 80% of a peripheral surface of an outer ring 130c of the first rolling bearing 130 is exposed.
• a roller bearing support module 100 may be included in the recess 170, for example, a structure which allows for storage and / or assembly purposes, a fixation of the first roller bearing 130 in the roller bearing support module 100.
• the corresponding structure not shown in FIG. 1 may, for example, be a multi-part plastic honeycomb structure which, after the rolling bearing carrier module 100 has been mounted on a shaft, is easily removable due to the multi-part design.
• this may also optionally remain in the built-in rolling bearing support module 100, provided that it is ensured that essentially no radial forces can be transmitted to the support 110 by these.
• This can be achieved by a choice of material, for example plastic or by a corresponding geometric design, in which at least 80% of the peripheral surface of the outer ring 130 of the first rolling bearing 130 are exposed.
• it may also be advisable to choose a higher proportion, about 90% or 95%, to further reduce the level of power transmission.
• a transmission becomes radial Kräfle via an inner ring 130a, the rolling elements 130b and the outer ring 130c of the first rolling bearing on the support 110 at least so far reduced that a corresponding radial power transmission essentially takes place only over the wide roller bearing 140.
• the first and second rolling bearings 130, 140 in the axial direction in the embodiment shown in FIG. 1, they are aligned such that a side surface of the first rolling bearing 130 formed by a side surface of the outer ring 130c of the first rolling bearing 130, is aligned with a plane 180, which also represents the plane of an end face of the machine for which the rolling bearing support module 100 is designed and designed.
• a plane 180 which also represents the plane of an end face of the machine for which the rolling bearing support module 100 is designed and designed.
• the plane 180 moreover coincides with the plane of the contact surface of the shaft of the corresponding machine.
• a disintegration of these two levels may be constructive.
• the second roller bearing 140 connects to one of the side surface of the first rolling bearing opposite side surface of the above described. This may, but need not, be directly in contact with the first roller bearing 130. Nor is it necessary that the second rolling bearing 140 directly in the axial direction with a surface of the carrier 110 is in contact.
• the rolling bearing support module 100 as shown in Fig. 1, in this case, as the first roller bearing 130 a universally mating angular contact ball bearings, whose high shoulder on its outer ring 130c of the plane 180 faces. Accordingly, the inner ring 130 a does not have a high shoulder on the side facing away from the plane 180.
• the rolling bearing module 100 shown in FIG. 1 the second rolling bearing 140 is designed as a cylindrical roller bearing, in which the outer ring 140c has Borden, while the inner ring 140a is designed bordenok.
• FIG. 2 shows a compressor 200 according to an exemplary embodiment of the present invention, in which the roller bearing support module 100 shown in FIG. 1 and described there is mounted on an end face 210 of a housing 220 of the compressor (housing end face).
• the compressor 200 represents an example of a machine on which carrier modules 100 according to embodiments of the present invention can be used.
• the roller bearing support module 100 agrees with the roller bearing support module 100 shown in FIG. 1, which is why reference is made at this point to the description there.
• the rolling bearing module 100 shown in FIG. 2 is not only connected to the end surface 210 of the compressor 200, but the rolling bearing assembly 120 is further mechanically coupled to a shaft 230.
• FIG. 1 shows a compressor 200 according to an exemplary embodiment of the present invention, in which the roller bearing support module 100 shown in FIG. 1 and described there is mounted on an end face 210 of a housing 220 of the compressor (housing end face).
• the compressor 200 represents an example of a machine on which carrier modules 100 according to embodiments of the present
• the respective inner rings 130a, 140a of the two rolling bearings 130, 140 are frictionally connected by corresponding fits with the shaft 230.
• the shaft 230 also has an abutment surface 240, which is a shaft shoulder.
• the contact surface 240 is in this case mechanically directly in contact with the inner ring 130 a of the first rolling bearing 130, while a side surface of the outer ring 130 c of the first rolling bearing 130 has an axial force of the shaft 230 directed to the left in FIG. 2 via the ball 130 b via the high Shoulder of the outer ring 130c transmits directly to the end face 210 of the housing 220.
• the housing 220 has an additional recess or recess 250 in the region of the end face.
• the shaft 230 is in this case part of a rotor 260 and extends through a bore 270 of the housing over the end face 210 of the housing 220 of time.
• the rotor 260 in this case has a rotor end face 280, which directly opposite a housing end face 290 and forms a front gap 300 between them.
• the first component 310-1 of the tolerance chain 310 results from the distance between the housing end face 290 in the interior of the housing 220 and the end face 210 to which the roller bearing support module 100 is attached.
• the second component 310-2 results from the bearing of the shaft 230 mediated by the first bearing 130, and is thus strongly dependent on the width tolerance of the first rolling bearing 130 or the tolerance of the outer ring 130c and the inner ring 130a of the first rolling bearing 130.
• the third component 310-3 of the tolerance chain 310 is then essentially given by the tolerance of the distance from the contact surface 240 to the rotor end face 280.
• the tolerance chain 310 can be significantly shortened compared to previous conventional solutions, so either a lower tolerance is achieved or the assembly process can be simplified can. Of course, compromise solutions can also be implemented.
• one or more universally paired angular contact ball bearings 130 are brought into abutment axially against the compressor housing face 210 and radially captured in the carrier module 100.
• the universally mating angular contact ball bearings 130 have been chosen in the embodiments shown in FIGS. 1 and 2, since they can be provided with defined, narrow width tolerances, so that they allow a more precise adjustment of the front gap 300.
• angular contact ball bearings with a width tolerance of the class PA4 or PA7 or finer can be used in embodiments of the present invention.
• it may also be advisable to use better or finer classes with regard to width tolerance for example classes PA9A or P9.
• Other types of bearings than the angular contact ball bearings shown here often have coarser width tolerances, so they are not shown here in describing embodiments of the present invention. In principle, however, they can also be used, provided that they can be manufactured or obtained with appropriate width tolerances.
• the module 100 can be assembled and fastened as a unit together with its bearings 130, 140. As will be explained in more detail in connection with FIG. 6, it is additionally possible to additionally insert additional bearings depending on the load in the carrier module 100.
• the compressor 200 in the context of the carrier module 100 comprises a securing ring 320, which is connected to the shaft 230 on a side surface of the inner ring 140a of the second rolling bearing 140 on the side facing away from the first rolling bearing 130.
• This ring 320 can be, for example, a shaft nut, a glued ring or a snap ring, which can be used for holding and / or securing the bearing assembly.
• the ring 320 may serve, for example, to secure the inner ring 140a of the second rolling bearing 140.
• the roller bearing support module 100 is connected to the end face 210 of the housing 220 in a force-locking or cohesive manner.
• a non-positive connection for example, by a suitable clamping of the Rolling bearing support module 100 are created.
• a cohesive connection can be created for example by gluing, soldering or welding.
• Fig. 3 shows a cross-sectional view of a compressor 400 with a conventional bearing assembly comprising two intermediate rings to be ground.
• the compressor 400 in this case comprises two mechanically positively coupled screw shafts 410, 420, of which the screw shaft 410 projects beyond a housing 430 of the compressor 400 and can be driven by an external power source.
• the screw shaft 410 is supported by a fixed-loose bearing arrangement in the housing 430.
• the propeller shaft 410 is drive side via a floating bearing 440 in the form of a cylindrical roller bearing with ribs on the outer ring, but without having to exhibit borders on the inner ring.
• the screw shaft 410 is mounted on the side facing away from the drive side via a fixed bearing assembly 450 in the housing 430.
• the rolling bearing assembly 450 here comprises an intermediate ring 460, to which a cylindrical roller bearing 470 adjoins, which has ribs exclusively on the outer ring, so that this transmits radial forces of the screw shaft 410 to the housing 430.
• the cylindrical roller bearing 470 is adjoined by a four-point bearing 480, which has a rearward rotation of the housing 430, so that only axial forces on the outer ring of the four-point bearing 480 or on both outer rings of the four-point bearing 480 and the cylindrical roller bearing 470 on the Housing 430 to be transferred.
• the second screw shaft 420 is mounted in the housing 430 with a corresponding fixed-loose mounting.
• the compressor 400 has on the drive side for the second screw shaft 420, a floating bearing 490 in the form of a cylindrical roller bearing, which comprises only on the outer ring Borden.
• the compressor also has a fixed bearing assembly 500 for the second screw shaft 420 on the drive side facing away from the side, which also contains an intermediate ring 510 to be ground, a cylindrical roller bearing 520 and a four-point bearing 530.
• the cylindrical roller bearings 470, 520 (radial bearings) responsible for receiving the radial forces are seated on the side of the rotor shafts 410, 420 facing the housing, so that its inner and outer rings are part of the tolerance chain of the components to be positioned axially.
• the adjustment of the axial position takes place only after a trial installation and a corresponding measurement.
• a component of the tolerance chain so for example a sleeve or one of the two intermediate rings 460, 510, ground after the first trial assembly of the compression stage of the compressor 400 and the measurement of the face gap for adjustment and compensation of the resulting tolerances to the required level before then the compressor 400 is finally mounted a second time.
• FIG. 4 shows a further example of a conventional bearing arrangement 600 with an intermediate ring 610 to be ground.
• a cylindrical roller bearing 630 On a shaft 620, on the side facing the rotor, first of all a cylindrical roller bearing 630 is arranged, which transmits the radial forces from the shaft 620 to the bearing arrangement 600.
• the cylindrical roller bearing 630 in turn has ribs only on its outer ring, so that the cylindrical roller bearing 620 basically does not receive any axial forces.
• To the cylindrical roller bearing 630 close immediately on the side facing away from the rotor two angular contact ball bearings 640-1, 640-2, in which each have the outer rings on the side facing the rotor high shoulders, while their inner rings on the opposite side, ie on the having a shaft end facing side corresponding high shoulders.
• the bearing arrangement 600 can transmit axial forces in the direction of the motor via the two angular contact ball bearings 640-1, 640-2 and the outer ring of the cylindrical roller bearing 630 to the bearing order or dissipate the housing of the compressor.
• Both angular contact ball bearings 640 are each turned behind, so that radial forces are not transmitted substantially.
• the angular contact ball bearing 640-2 is adjoined by the previously mentioned intermediate ring 610, which is arranged between the inner ring of the angular contact ball bearing 640-2 and an inner ring of a ball bearing 650.
• the resulting arrangement of the cylindrical roller bearing 630, the two angular contact ball bearings 640 and the ball bearing 650 is connected to the shaft 620 via a shaft nut 660 and a screw 670.
• the outer ring of the ball bearing 650 is in contact with a surface 680 of the bearing assembly 600 via a side surface such that the ball bearing 650 can transfer axial forces in the direction of the shaft end via the surface 680 to the bearing assembly 600 and thus to the housing of the compressor.
• the ball bearing 650 is laterally rotated to avoid a power transmission in Radialerraumsessgebliuse.
• FIG. 5 shows a further exemplary embodiment of a compressor 200 with a roller bearing carrier 100, which differs from the exemplary embodiment shown in FIG. 2 only in that, via the rolling bearing module 100, not only a single shaft 230 (as in FIG. 2), but rather 2 shafts 230, 230 'are stored.
• the roller bearing support module 100 in addition to the rolling bearing assembly 120 already described in connection with FIG. 2 with the first roller bearing 130 and the second roller bearing 140 for the first shaft 230, a second rolling bearing assembly 120 'with a corresponding first roller bearing 130' and a corresponding second rolling bearing 140 'on.
• the components of the second rolling bearing assembly 120 ' correspond to those of the rolling bearing assembly 120.
• the first roller bearing 130' of the second rolling bearing assembly 120 ' communicates with the contact surface 240' of Shaft 230 'in contact, while the outer ring of the first rolling bearing 130' with a side surface axially occurring forces in the direction of the motor 260 'on the common end face 210 of the housing 220 transmits.
• the second rolling bearing arrangement 120 ' likewise has a bearing cup 150', via which the second rolling bearing 140 ', which in turn acts as a cylinder bearing roller bearing is executed, radial forces from the second shaft 230 'transmits to the carrier 110.
• the first and second bearings of the two rolling bearing assembly 120, 120 ' can be designed differently, but also with regard to the further structural features they can be adapted according to the actual conditions. This is indicated in FIG. 5, for example in the region of the bearing cup 150 ', which is shown clearly larger than the bearing cup 150 of the first rolling bearing arrangement 120.
• the two rolling bearing arrangements 120, 120' can also differ with regard to other structural features. Thus, it is far from necessary that the alignment of the contact surfaces 140, 140 'in the ratio of or the end faces 210 for both rolling bearing assemblies 120, 120' match.
• the planes of the contact surfaces 140, 140 'for a rolling bearing arrangement coincide with the plane of the end face 210, while a different, parallel shifted plane and thus contact surface is used for the other contact surface.
• both a compressor 200 and a roller bearing support module 100 can have a second rolling bearing arrangement with a further first rolling bearing and a further second rolling bearing, which is arranged in the axial direction directly or indirectly adjacent to the first further rolling bearing.
• the second rolling bearing arrangement is then designed to transmit axial forces in at least one axial direction but substantially no radial forces via the first further rolling bearing, wherein the second rolling bearing arrangement is further configured to generate radial forces via the second further rolling bearing. it is essential to absorb no axial forces in the at least one axial direction and to deliver them to the carrier.
• one side face of the further first rolling bearing can be in alignment with or in contact with a plane corresponding to the end face of the machine or compressor or another contact face of a further shaft, while the first further rolling bearing is configured, axial forces in of the at least one direction over the end face to a component in a further corresponding plane of the other surface of the end face and the further contact surface of the further wave, wherein the second further rolling bearing is arranged on one of the side surface of the first further antifriction bearing facing away from the first further rolling bearing.
• FIG. 6 shows a further exemplary embodiment of a roller bearing carrier module 100, which is very similar to that of FIG.
• the roller bearing support module 100 via a carrier 110 and a rolling bearing assembly 120 with a first roller bearing 130, a second roller bearing 140 and a bearing cup 150, as has already been described in more detail in connection with FIG.
• the rolling bearing module 100 of FIG. 6 differs from that of FIG. 1 in two aspects.
• the roller bearing support module 100 from FIG. 6 has a further angular contact ball bearing 700, which is arranged between the first roller bearing 130 and the second roller bearing 140.
• this further angular contact ball bearing 700 can also be replaced by another radial bearing, that is, for example, a ball bearing, a four-point bearing, a shoulder ball bearing, a self-aligning ball bearing or other rolling bearing.
• the roller bearing support module 100 shown in FIG. 6 further differs from that shown in FIG. 1 in that it has another rolling bearing assembly 710 with a third rolling bearing 720, the further rolling bearing assembly 710 being adapted to receive axial forces in the other axial Direction, so take the opposite direction and deliver to the carrier 110.
• the third rolling bearing 720 is an angular contact ball bearing which is installed in mirror symmetry to the first rolling bearing 130 in such a way that this is in contact with the support 110 with a side surface. If an axial force is exerted to the right by a shaft, not shown in FIG. 6, via the inner ring of the third rolling bearing 720, it is transmitted directly to the carrier 110 via the mirror-inverted high shoulders of the inner and outer rings of the third rolling bearing.
• the further rolling bearing arrangement can be supplemented by a fourth rolling bearing 730, which, similar to the second rolling bearing 140, is designed to transmit substantially radial forces to the carrier 110, but not axial forces.
• the third rolling bearing 720 can be supplemented by a cylindrical roller bearing as the fourth rolling bearing 730 such that it adjoins the third rolling bearing directly or indirectly.
• between the further roller bearing assembly 710 and the rolling bearing assembly 120 forms a free area such that at least one side surface of the other rolling bearing assembly is two. This side surface of the rolling bearing assembly is opposite to the side surface of the further rolling bearing assembly 710, which is in contact with the carrier 110 and exerted on these forces.
• FIG. 7 shows another compressor 200 according to an exemplary embodiment of the present invention, which differs from the compressor shown in FIG. 2 only in that in the compressor shown in FIG. 7, no roller bearing support module 100 is used, but rather the first and second second rolling bearings 130, 140 are inserted directly into a corresponding bore in the housing 220 of the compressor 200.
• the end face 210 results in the region of the bore into which the rolling bearing assembly 120 is introduced.
• the corresponding bore 800 can be closed by a lid 810.
• the contact surface of the shaft can not be formed only by a shaft shoulder, as has been described in the present application, but are also formed by other methods. It is for example possible to create a corresponding contact surface by introducing a collar or other projection with a defined geometry.
• Embodiments of the present invention are not limited to compressors and screw compressors, but in many places also applicable to other machines in which thrust bearings and corresponding contact surfaces are to be positioned as accurately as possible. In addition to machines in the compressor area and in the field of promotion of other liquids and gases, embodiments of the present invention can therefore also be used in other areas of mechanical engineering.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Rolling Contact Bearings (AREA)

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• 2010
  • 2010-11-12 DE DE102010043807A patent/DE102010043807A1/de not_active Withdrawn
• 2011
  • 2011-11-03 US US13/884,833 patent/US20140314358A1/en not_active Abandoned
  • 2011-11-03 CN CN2011800648837A patent/CN103328837A/zh active Pending
  • 2011-11-03 EP EP11778873.7A patent/EP2638301A1/de not_active Withdrawn
  • 2011-11-03 WO PCT/EP2011/069273 patent/WO2012062642A1/de active Application Filing

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