EP3364036A1 - Logement de palier à fente axiale et machine rotative - Google Patents

Logement de palier à fente axiale et machine rotative Download PDF

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Publication number
EP3364036A1
EP3364036A1 EP17156696.1A EP17156696A EP3364036A1 EP 3364036 A1 EP3364036 A1 EP 3364036A1 EP 17156696 A EP17156696 A EP 17156696A EP 3364036 A1 EP3364036 A1 EP 3364036A1
Authority
EP
European Patent Office
Prior art keywords
housing part
end cover
bearing housing
bearing
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP17156696.1A
Other languages
German (de)
English (en)
Inventor
Jake Wharton
Ryan Wheen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sulzer Management AG
Original Assignee
Sulzer Management AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sulzer Management AG filed Critical Sulzer Management AG
Priority to EP17156696.1A priority Critical patent/EP3364036A1/fr
Publication of EP3364036A1 publication Critical patent/EP3364036A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D1/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D1/06—Multi-stage pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/0462—Bearing cartridges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/0563—Bearings cartridges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/624—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/60—Mounting; Assembling; Disassembling
    • F04D29/62—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps
    • F04D29/628—Mounting; Assembling; Disassembling of radial or helico-centrifugal pumps especially adapted for liquid pumps

Definitions

  • the invention relates to an axially split bearing housing for receiving the non-drive end of a shaft of a rotary machine and to a rotary machine for acting on a fluid in accordance with the preamble of the respective independent claim.
  • Rotary machines for acting on a fluid typically comprise a stationary machine casing enclosing a rotor, e.g. an impeller, for interacting with the fluid and a shaft for rotating the rotor about an axial direction.
  • the shaft can be driven by a drive unit.
  • the end of the shaft that is connected to the drive unit is also referred to as the drive end of the shaft, whereas the other end of the shaft is referred to as non-drive end of the shaft.
  • the rotary machine further comprises at least one bearing unit with a radial and/or an axial (thrust) bearing for supporting the shaft and the rotor.
  • the bearing has a separate housing which is fixedly connected to the casing of the rotary machine. Since the bearings usually require lubrication and/or cooling a lubricant, for example an oil or any other suited fluid, is supplied to the bearing unit. In many applications this lubricant shall neither leak from the bearing unit into the environment nor get into contact with the fluid the rotary machine is acting on to avoid any contamination of this fluid or the environment with the lubricant.
  • a lubricant for example an oil or any other suited fluid
  • the invention is related to this between bearing design and in particular to the bearing housing arranged at the non-drive end of the shaft.
  • This bearing housing has an inboard end facing the rotary machine and an outboard end facing away from the rotary machine.
  • the shaft enters the bearing housing through the inboard end and ends within the bearing housing, meaning that the outboard end of the bearing housing has to be closed with respect to the axial direction.
  • an axially split bearing housing for receiving the non-drive end of a shaft of a rotary machine, the bearing housing extending in an axial direction from an inboard end to an outboard end, and comprising an upper housing part and a lower housing part designed for being fixedly connected to each other, and further comprising a disk-shaped end cover for closing the bearing housing at the outboard end in the axial direction, wherein the upper housing part, the lower housing part and the end cover are designed to engage with each other for fixedly connecting the end cover to the upper and the lower housing part in a boltless manner.
  • the outer rim of the end cover comprises a tongue extending in a radial direction
  • the upper housing part and/or the lower housing part comprise a groove for engaging with the tongue.
  • both the upper and the lower housing part are each provided with a groove that extends along the entire respective housing part with respect to the circumferential direction.
  • said two grooves form an essentially annular groove for receiving the tongue of the end cover.
  • the tongue or the tongues at the upper and/or the lower housing part and to provide the outer rim of the end cover with a groove adapted for receiving said tongue(s).
  • the tongue comprises a notch
  • the upper housing part or the lower housing part comprise a pin for engaging with the notch to prevent a relative rotational movement between the end cover and the upper and the lower housing part.
  • the outer rim of the end cover comprises a slot for receiving a sealing element, said slot extending along the entire circumference of the end cover.
  • a sealing element such as an O-ring is inserted into the slot for providing the sealing action.
  • the slot for the sealing element is provided on that side of the tongue that faces away from the outboard end of the bearing housing, i.e. the tongue is located between the slot and the outboard end.
  • the end cover comprises a centrally arranged hole for receiving a locking device for the shaft.
  • a locking device for the shaft for example, a locking device for the shaft.
  • the hole in the end cover may be sealingly closed by a plug or any other appropriate means.
  • the outer rim of the end cover comprises a plurality of tongues extending in the radial direction
  • the upper housing part and/or the lower housing part comprise a plurality of grooves, each groove being adapted for engaging with one of the tongues.
  • the individual tongues are aligned with respect to the circumferential direction of the end cover.
  • a respective groove is provided in the upper or the lower housing part for receiving the tongue.
  • the length of the respective groove as measured in the circumferential direction corresponds to the length of the individual tongue in the circumferential direction, so that each tongue closely fits into the respective groove.
  • the length of the individual tongues in the circumferential direction may be the same for all tongues but may also be different for the individual tongues.
  • the upper housing part and the lower housing part each comprise a flange at its respective outboard end, each of said flanges extending radially inwardly, meaning that the diameter of the end cover is smaller than the diameter of the outboard end of the bearing housing.
  • This design enables a particularly safe and reliable connection between the end cover and the two housing parts.
  • the flanges may be used as support for a thrust bearing arranged in the bearing housing, i.e. the flanges may absorb the mechanical forces acting upon the thrust bearing during operation.
  • each flange is integrally formed in one piece with the respective housing part.
  • the bearing housing comprises a first annular chamber for receiving a radial bearing for the shaft.
  • the bearing housing comprises a second annular chamber for receiving a thrust bearing for the shaft.
  • the bearing housing has both the first chamber for receiving the radial bearing and the second chamber for receiving the thrust bearing.
  • This is a very compact design for housing the radial (or journal) bearing as well as the thrust (or axial) bearing for the shaft of a rotary machine.
  • the second chamber is arranged behind the first chamber such that the first chamber is closer to the inboard end of the bearing housing and the second chamber is closer to the outboard end of the bearing housing.
  • the second annular chamber is delimited by the flange of the upper housing part and by the flange of the lower housing part.
  • a rotary machine for acting on a fluid, comprising a shaft having a drive end as well as a non-drive end, and further comprising an axially split bearing housing in accordance with the invention for receiving the non-drive end of the shaft.
  • the rotary machine is a pump, in particular a centrifugal pump.
  • the centrifugal pump may be designed for example as a boiler feed pump or as a booster pump or as an injection pump for seawater or water injection or as a pump for moving oil or crude oil through a pipeline.
  • Fig. 1 shows a cross-sectional view of an embodiment of a rotary machine according to the invention which is designated in its entity with reference numeral 100.
  • the embodiment of the rotary machine 100 is a centrifugal pump 100 for conveying a fluid, for example water or crude oil or a multiphase fluid.
  • the invention is neither restricted to the centrifugal pump 100 illustrated in Fig. 1 nor to centrifugal pumps as such but is related to rotary machines 100 in general.
  • the rotary machine 100 may also be another type of pump, a compressor, a blower, an expander or a turbine.
  • the centrifugal pump 100 comprises a casing 101 that may consist of a plurality of casing parts, which are connected to each other to form the casing 101.
  • the casing 101 of the centrifugal pump 100 comprises an inlet 102, through which the fluid to be conveyed enters the pump 100 and an outlet 103 for discharging the fluid.
  • Inside the casing 101 at least one impeller 104 is provided for acting on the fluid.
  • the embodiment shown in Fig. 1 is designed as a multistage pump having a plurality of impellers 104, here five impellers 104. All impellers 104 are mounted in series on a shaft 110 in a torque proof manner.
  • the impellers 104 are driven during operation of the pump 100 for a rotation about an axial direction A that is defined by the longitudinal axis of the shaft 110.
  • the flow of the fluid is indicated by the arrows without reference numeral.
  • a direction perpendicular to the axial direction A is referred to as 'radial direction'.
  • the term 'axial' or 'axially' is used with the common meaning 'in axial direction' or 'with respect to the axial direction'.
  • the term 'radial' or 'radially' is used with the common meaning 'in radial direction' or 'with respect to the radial direction'.
  • the shaft 110 is driven by means of a drive unit (not shown), for example an electric motor or any other type of motor, to which the shaft 110 is coupled.
  • a drive unit for example an electric motor or any other type of motor
  • the end of the shaft 110 that is coupled to the drive unit is designated as drive end 111 of the shaft, whereas the other end of the shaft 110 is designated as non-drive end 112.
  • the drive end 110 that is connected to the drive unit (not shown) is located on the left side.
  • a drive end bearing housing 115 accommodating a radial (or journal) bearing 116; a mechanical seal 117 for sealing the pump 100 against leakage of the fluid along the shaft 110; the plurality of impellers 104; a balancing drum 118 for balancing the axial thrust generated by the impellers 104; another mechanical seal 119 for sealing the non-drive side of the shaft 110 against leakage of the fluid to be pumped; and a non-drive end bearing housing 1 accommodating a further radial (or journal) bearing 120 and a thrust (or axial) bearing 121 for supporting the non-drive end 112 of the shaft 110 with respect to the radial direction and the axial direction A, respectively.
  • the centrifugal pump 100 is designed as a between bearing pump having bearings 116, 120, 121 on both sides of the plurality of impellers 104, i.e. at the drive end 111 of the shaft 110 as well as at the non-drive end 112 of the shaft 110.
  • the bearing housing 1 arranged at the non-drive end 112 of the shaft 110 is designed according to the invention.
  • the bearing housing 1 will now be explained in more detail referring to embodiments of the bearing housing 1 for receiving the non-drive end 112 of the shaft 110.
  • Fig. 2 shows a perspective view of a first embodiment of the bearing housing 1 according to the invention for receiving the non-drive end 112 of the shaft 110 of the rotary machine 100.
  • Fig. 3 shows this bearing housing 1 in a perspective cross-sectional view.
  • the bearing housing 1 that is designated in its entity with reference numeral 1 has an essentially cylindrical shape for surrounding the shaft 110 of the centrifugal pump 100.
  • the bearing housing 1 is designed as an axially split bearing housing 1 having an upper housing part 2 and a lower housing part 3.
  • axially split means that the bearing housing 1 is divided along the axial direction A or in other words, divided parallel to the shaft 110, which is surrounded by the bearing housing 1 during operation.
  • Each of the upper housing part 2 and the lower housing part 3 extends in the axial direction A from an inboard end 41 to an outboard end 42 of the bearing housing 1.
  • the inboard end 41 of the bearing housing 1 is that end of the bearing housing 1, which faces the centrifugal pump 100 when the bearing housing 1 is attached to the centrifugal pump 100 (see Fig. 1 ).
  • the outboard end 42 of the bearing housing 1 is that end of the bearing housing 1, which faces away from the centrifugal pump 100 when the bearing housing 1 is attached to the centrifugal pump 100.
  • the upper housing part 2 and the lower housing part 3 are configured for being fixedly connected to each other.
  • each of the upper housing part 2 and the lower housing part 3 comprises a lateral flange 21 and 31, respectively, having a plurality of pairwise aligned bores 23 for receiving bolts or nuts 231 by means of which the upper housing part 2 and the lower housing part 3 are securely fixed to each other.
  • Both the upper housing part 2 and the lower housing part 3 have an essentially semicylindrical shape.
  • the inboard end 41 of the bearing housing 1 is configured as a mounting flange 5 for fixing the bearing housing 1 to the casing 101 of the centrifugal pump 100 (see Fig. 1 ).
  • the mounting flange 5 comprises a plurality of bores 51 for receiving screws or bolts by means of which the bearing housing 1 may be secured to the casing 101 of the centrifugal pump 100.
  • the upper housing part 2 comprises a flange 24 extending radially inwardly such that the flange 24 forms a part of the outboard end 42 of the bearing housing 1.
  • the lower housing part 3 comprises a flange 34 extending radially inwardly such that the flange 34 forms a part of the outboard end 42 of the bearing housing 1. Both flanges 24 and 34 are preferably formed integrally in one piece with the respective housing part 2, 3.
  • the bearing housing 1 further comprises a generally disk-shaped end cover 6 for closing the circular opening 7 in the outboard end 42 of the bearing housing 1.
  • the disk-shaped end cover 6 is arranged perpendicular to the axial direction A at the outboard end 42, such that it closes the bearing housing 1 with respect to the axial direction A.
  • the upper housing part 2, the lower housing part 3 and the end cover 6 are designed to engage with each other for fixedly connecting the end cover 6 to the upper housing part 2 and the lower housing part 3 in a boltless manner.
  • FIG. 4 shows a plan view of the end cover 6 of the bearing housing 1.
  • Fig. 5 shows a cross-sectional view of the end cover 6 in a cut taken along cutting line V-V in Fig. 4 .
  • the essentially disk-shaped end cover 6 has an outer rim 61 delimiting the end cover 6 with respect to the radial direction.
  • the outer rim 61 comprises a tongue 62 extending in the radial direction as a protrusion.
  • the tongue 62 is extending in the circumferential direction essentially along the entire circumference of the end cover 6.
  • the tongue 62 is provided with a notch 63 forming a small gap in the tongue 62 for receiving a pin 81 (see Fig. 3 ) engaging with the notch 63 to prevent rotation of the end cover 6.
  • the outer rim 61 is further provided with a slot 64 for receiving a sealing element, preferably an O-ring, which seals the end cover 6 with respect to the upper and lower housing part 2, 3 in a liquid tight manner, so that no liquid can leak between the end cover 6 and the upper or lower housing part 2, 3, respectively.
  • the slot 64 is designed as an annular slot 64 extending along the entire circumference of the end cover 6.
  • the slot 64 is extending essentially parallel to the tongue 62 and located with respect to the axial direction A more inwardly than the tongue 62, such that the tongue 62 is located between the slot 64 and the outboard end 42 in the assembled state.
  • both the upper housing part 2 and the lower housing part 3 respectively comprise a groove 8 for engaging with the tongue 62 of the end cover 6. More particularly, the grooves 8 are provided in that surface of the respective flange 24, 34 of the upper and the lower housing part 2, 3, which delimits the central opening 7. In the assembled state of the upper and the lower housing part 2, 3 the grooves 8 complement one another to form an annular groove 8 extending along the entire circumference of the bounding surface delimiting the central opening 7.
  • the pin 81 is provided for engaging with the notch 63 in the tongue 62 of the end cover 6.
  • the tongue 62 and the annular groove 8 are designed to closely fit into one another in the assembled state.
  • the end cover 6 further comprises a centrally arranged hole 65 for receiving a locking device (not shown) for the shaft 110.
  • the circular hole 65 is arranged in the center of the end cover 6 so that the locking device may be inserted through the end cover 6 for contacting the non-drive end of the shaft 110 when the bearing housing 1 is mounted to the non-drive end 112 of the shaft 110.
  • the locking device shall prevent any undesired motion of the shaft 110 in particular during transportation, assembly or installation of the centrifugal pump 100.
  • the locking device as such is well known in the art and therefore does not require additional explanations. It is inserted through the hole 65 and engages the shaft 110 within the bearing housing 1 for securing the shaft.
  • the locking device is removed prior to putting the pump 100 into operation.
  • the hole 65 in the end cover is sealingly closed, for example by a plug or a cover or a similar means.
  • the bearing housing 1 comprises a first annular chamber 11 for accommodating the radial bearing 120 ( Fig. 1 ) that supports the non-drive end 112 of the shaft 110 with respect to the radial direction.
  • the radial bearing 120 is also referred to as journal bearing.
  • the bearing housing 1 comprises a second annular chamber 12 for receiving the thrust bearing 121 ( Fig. 1 ) that supports the shaft 110 with respect to the axial direction A.
  • the thrust bearing 121 is also referred to as axial bearing.
  • the first annular chamber 11 and the second annular chamber 12 are arranged in series inside the bearing housing 1 with respect to the axial direction A in such a way that the first annular chamber 11 is closer to the inboard end 41 and the second annular chamber 12 is closer to the outboard end 42 of the bearing housing 1.
  • the second annular chamber 12 for receiving the thrust bearing 121 is arranged such that it is delimited by the flanges 24 and 34 of the upper and lower housing part 2, 3. Thereby the flanges 24 and 34 provide support to the thrust bearing 121 with respect to the axial direction A and may absorb the axial forces acting on the thrust bearing 121.
  • the end cover 6 is not loaded with axial forces from the thrust bearing 121. According to said known designs the end cover is usually used to position and to support the side of the thrust bearing facing the outboard end. According to the preferred embodiment shown in Fig. 2 and Fig.
  • the second annular chamber 12 for the thrust bearing 121 is arranged in such a manner, for example by machining it into the bearing housing 1, that the second annular chamber 12 is delimited at the outboard end 42 by the flanges 24 and 34.
  • the flanges 24 and 34 provide support to the thrust bearing 121
  • the end cover 6 has the main function to sealingly close the outboard end 42 of the bearing housing 1, but has not to provide any essential support to the thrust bearing 121.
  • the bearing housing 1 may comprise other components which are as such known in the art, for example a breather 9 ( Fig. 2 ), or internal channels 91 for a lubricant or a coolant such as a lubricating oil.
  • a breather 9 Fig. 2
  • internal channels 91 for a lubricant or a coolant such as a lubricating oil.
  • a sealing element preferably an O-ring seal
  • the disk-shaped end cover 6 is inserted in one of the upper or lower housing part 2, 3 for example in the lower housing part 3, such that the tongue 62 engages with the groove 8 in the lower housing part 2, i.e. the tongue 62 is inserted into the groove 8 which tight-fittingly receives the tongue 62.
  • the pin 81 engages with the notch 63 in the tongue 62.
  • the upper housing part 2 is laid upon the lower housing part 3 such that the tongue 62 is inserted into the groove 8 in the upper housing part 2 and that the lateral flanges 21 and 31 of the upper and lower housing part 2, 3 are facing each other.
  • screws or bolts 231 into the bores 23 in the lateral flanges 21, 31 and tightening said screws or bolts the bearing housing 1 is closed and the upper housing part 2 is fixedly connected with the lower housing part 3.
  • the end cover 6 is fixedly connected to the bearing housing 1 in a boltless manner, meaning that there are no bolts or screws provided at the end cover 6 or passing through the end cover 6 for the fixation of the end cover 6 to the bearing housing.
  • the end cover 6 is clamped between these two housing part 2, 3 and there is no need to provide any screws or bolts or similar fixing means at the end cover 6.
  • the axial position of the end cover 6 is restrained by the engagement of the tongue 62 with the groove 8.
  • any rotation of the end cover 6 relative to the bearing housing 1, i.e. relative to the upper and the lower housing part 2, 3 is prevented through the pin 81 in the groove 8 that engages with the notch 63 in the tongue 8.
  • the sealing element for example the O-ring, inserted into the slot 64 of the end cover 6 provides a reliable sealing action between the end cover 6 and the housing parts 2, 3, so that no liquid, for example the lubricant or the coolant for the radial bearing 120 or the thrust bearing 121, can leak between the end cover 6 and the upper and lower housing part 2, 3.
  • FIG. 6 shows the end cover 6 in the mounted state with the tongue 62 of the end cover 6 engaging with the groove 8 in the upper housing part 2, more particular in the flange 24 of the upper housing part 2.
  • a sealing element namely an O-ring 641 is inserted into the slot 64.
  • a screw 81' or a dowel screw 81' or a similar element is provided at the axial end surface delimiting the flange 24 at the outboard end 42.
  • the screw 81' is arranged in such a manner that it extends into the tongue 62 engaging with the groove 8 in the flange 24.
  • the screw 81' preferably ends within the tongue 62 and performs essentially the same function as the pin 81 described above. The engagement of the screw 81' with the tongue 62 prevents any rotation of the end cover 6 about the axial direction.
  • Fig. 67 illustrates a second embodiment of the bearing housing 1 according to the invention.
  • the explanations with respect to the first embodiment are also valid in analogously the same way for the second embodiment shown in Fig. 7 .
  • the reference numerals have the same meaning as already explained hereinbefore.
  • Fig. 7 shows a plan view of the end cover 6 and (partially) the upper and lower housing part 2, 3.
  • Fig. 7 illustrates the state where the housing parts 2, 3 and the end cover 6 are not yet assembled.
  • the housing parts 2, 3 are only indicated schematically.
  • the outer rim 61 of the end cover 6 of the second embodiment comprises a plurality of tongues 62, each extending in the radial direction.
  • the individual tongues 62 have a lengths L in the circumferential direction of the end cover 6. All the tongues 62 are aligned with respect to the circumferential direction of the end cover 6.
  • the outer rim 61 of the end cover 6 is provided with four tongues 62. It has to be understood that the number of four tongues 62 is only an example.
  • the number of tongues 62 may be smaller than four, for example only two or three tongues 62 may be provided at the outer rim 61, or the number of tongues 62 may be larger than four, for example six or eight or even more tongues 62 may be provided at the outer rim 61.
  • the length L of the tongues 62 in circumferential direction may be the same for each of the tongues 62, or the length L may be different for different tongues 62.
  • the distance between adjacent tongues 62 measured in the circumferential direction may be the same for each pair of adjacent tongues 62, or said distance may be different for different pairs of adjacent tongues 62.
  • the embodiment shown in Fig. 7 has four tongues 62 at the outer rim 61, which are equidistantly distributed along the circumference of the outer rim 61. All tongues 62 have the same length L in the circumferential direction.
  • the upper housing part 2 and/or the lower housing part 3 comprise a plurality of grooves 8, each groove 8 being adapted for engaging with one of the tongues 62.
  • the grooves 8 are indicated in Fig. 7 by dashed lines because they are not visible in this plan view.
  • the total number of grooves 8 in the upper housing part 2 and in the lower housing part 3 equals the number of tongues 62 at the outer rim 6.Thus, for each of the individual tongues 62 a respective groove 8 is provided in the upper or the lower housing part 2, 3 for receiving the respective tongue 62.
  • the length of the respective groove 8 as measured in the circumferential direction preferably corresponds to the length L of the individual tongue 62 that engages with the groove in the assembled state. Thus, each tongue 62 closely fits into the respective groove 8.
  • the design with a plurality of tongues 62 engaging with a plurality of grooves 8 prevents a rotation of the end cover 6 about the axial direction A in the mounted state.
  • the optional pin 81 e.g. a dowel pin, engaging with the notch 63 in one of the tongues 62 or the screw 81' ( Fig. 6 ) for securing the end cover 6 against rotation may be dispensed with. Due to the plurality of tongues 62 and grooves 8 the end cover 6 is reliably prevented from a rotation relative to the upper and lower housing part 2, 3.
  • a variant which is applicable for both the first and the second embodiment of the bearing housing 1 is to interchange the location of the tongue(s) 62 and the groove(s) 8, meaning that in an analogous manner the tongue or the tongues 62 may be provided at the upper and/or lower housing part 2, 3, in particular at the flanges 24 and 34 on the surface delimiting the opening 7, whereas the groove or the grooves 8 may be provided in the outer rim 61 of the end cover 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mounting Of Bearings Or Others (AREA)
EP17156696.1A 2017-02-17 2017-02-17 Logement de palier à fente axiale et machine rotative Withdrawn EP3364036A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP17156696.1A EP3364036A1 (fr) 2017-02-17 2017-02-17 Logement de palier à fente axiale et machine rotative

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Application Number Priority Date Filing Date Title
EP17156696.1A EP3364036A1 (fr) 2017-02-17 2017-02-17 Logement de palier à fente axiale et machine rotative

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EP3364036A1 true EP3364036A1 (fr) 2018-08-22

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EP17156696.1A Withdrawn EP3364036A1 (fr) 2017-02-17 2017-02-17 Logement de palier à fente axiale et machine rotative

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110454399A (zh) * 2019-08-21 2019-11-15 沈阳启源工业泵制造有限公司 一种无止推轴承多级离心泵
USD897383S1 (en) * 2017-05-02 2020-09-29 Itt Manufacturing Enterprises Llc Sleeve-ball split bearing housing

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2056553A (en) * 1934-06-11 1936-10-06 Micro Westco Inc Pump
US5655845A (en) * 1995-09-27 1997-08-12 Skf Usa Inc. Bearing housing seal
US20120156012A1 (en) * 2010-12-16 2012-06-21 Sulzer Pumpen Ag Flow machine for a fluid having a radial sealing gap and a stationary wear ring
US20140178119A1 (en) * 2011-08-08 2014-06-26 Mitsubishi Heavy Industries Compressor Corporation Fixture used in rotary machine and method for transporting rotary machine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2056553A (en) * 1934-06-11 1936-10-06 Micro Westco Inc Pump
US5655845A (en) * 1995-09-27 1997-08-12 Skf Usa Inc. Bearing housing seal
US20120156012A1 (en) * 2010-12-16 2012-06-21 Sulzer Pumpen Ag Flow machine for a fluid having a radial sealing gap and a stationary wear ring
US20140178119A1 (en) * 2011-08-08 2014-06-26 Mitsubishi Heavy Industries Compressor Corporation Fixture used in rotary machine and method for transporting rotary machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
SCHAEFFLER TECHNOLOGIES AG & CO. KG: "Split Plummer Block Housings SNS", 30 November 2015 (2015-11-30), XP055392085, Retrieved from the Internet <URL:http://www.schaeffler.com/remotemedien/media/_shared_media/08_media_library/01_publications/schaeffler_2/tpi/downloads_8/tpi_231_de_en.pdf> [retrieved on 20170719] *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USD897383S1 (en) * 2017-05-02 2020-09-29 Itt Manufacturing Enterprises Llc Sleeve-ball split bearing housing
CN110454399A (zh) * 2019-08-21 2019-11-15 沈阳启源工业泵制造有限公司 一种无止推轴承多级离心泵

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