• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The axial bearing arrangement comprises a first axial bearing plate (12) and a second axial bearing plate (13) each having an annular ring shape, the first axial bearing plate (12) having a first surface (12.1). axially oriented towards the second axial bearing plate (13) and a second surface (12.2) opposite to the respective first surface (12.1), the second axial bearing plate (13) having a first surface (13.1) oriented axially towards the first axial bearing plate (12) and a second surface (13.2) opposite the respective first surface (13.1); a spacer ring (14) clamped between the first surfaces (12.1, 13.1) of the first and second axial bearing plates (12, 13), the spacer ring (14) defining an axial distance between the first and second plates axial bearing (12, 13); and a bearing sleeve (15) abutting against the second surface (13.2) of the second axial bearing plate (13) and being attached to a compressor block (16). The axial bearing arrangement comprises a resilient element (22) axially biasing the first and second axial bearing plates (12, 13) and the spacer ring (14) with a predetermined force against an abutment surface (17) of the bearing sleeve (15).
    公开号:FR3055678A1
    申请号:FR1658168
    申请日:2016-09-02
    公开日:2018-03-09
    发明作者:Yves Rosson；Patrice Bonnefoi；Arnaud Daussin；Mihai Dobrica
    申请人:Danfoss Silicon Power GmbH；
    IPC主号:
    专利说明:

    ® FRENCH REPUBLIC
    NATIONAL INSTITUTE OF INDUSTRIAL PROPERTY © Publication number:
    (to be used only for reproduction orders)
    ©) National registration number
    055 678
    58168
    COURBEVOIE © Int Cl 8 : F04 D 29/056 (2017.01)
    PATENT INVENTION APPLICATION
    A1
    ©) Date of filing: 02.09.16. © Applicant (s): DANFOSS SILICON POWER GMBH (© Priority: - OF. @ Inventor (s): ROSSON YVES, BONNEFOI PATRICE, DAUSSIN ARNAUD and DOBRICA MIHAI. (43) Date of public availability of the request: 09.03.18 Bulletin 18/10. ©) List of documents cited in the report preliminary research: Refer to end of present booklet (© References to other national documents ® Holder (s): DANFOSS SILICON POWER GMBH. related: ©) Extension request (s): © Agent (s): CABINET GERMAIN & MAUREAU.
    COMPRESSOR DRIVE SHAFT
    PA AXIAL BEARING ARRANGEMENT FOR A CENTRIFUGAL.
    FR 3 055 678 - A1 (PT) The axial bearing arrangement comprises a first axial bearing plate (12) and a second axial bearing plate (13) each having an annular ring shape, the first axial bearing plate ( 12) having a first surface (12.1) oriented axially towards the second axial bearing plate (13) and a second surface (12.2) opposite the respective first surface (12.1), the second axial bearing plate (13) having a first surface (13.1) oriented axially towards the first axial bearing plate (12) and a second surface (13.2) opposite the respective first surface (13.1); a spacer ring (14) sandwiched between the first surfaces (12.1, 13.1) of the first and second axial bearing plates (12, 13), the spacer ring (14) defining an axial distance between the first and second plates axial bearing (12, 13); and a bearing sleeve (15) abutting against the second surface (13.2) of the second axial bearing plate (13) and being fixed to a compressor block (16). The axial bearing arrangement comprises an elastic element (22) axially biasing the first and second axial bearing plates (12, 13) and the spacer ring (14) with a predetermined force against a stop surface (17) of the bearing sleeve (15).

    Field of the invention
    The present invention relates to an axial bearing arrangement for a drive shaft of a centrifugal compressor.
    Background of the invention
    In known manner, an axial bearing arrangement for a drive shaft of a centrifugal compressor can include:
    - a first axial bearing plate and a second axial bearing plate, also called first and second stop plates, being parallel and each having an annular ring shape, the first axial bearing plate having a first surface oriented axially towards the second axial bearing plate and a second surface opposite the first surface of the first axial bearing plate, the second axial bearing plate having a first surface oriented axially towards the first axial bearing plate and a second surface opposite the first surface of the second axial bearing plate,
    a spacer ring sandwiched between the first surfaces of the first and second axial bearing plates at the level of radial outer parts of the first and second axial bearing plates, the spacer ring defining an axial distance between the first and second plates axial bearing, and
    - a bearing sleeve being fixed to a compressor block and abutting against the second surface of the second axial bearing plate, so as to clamp the first and second axial bearing plates and the spacer ring against a contact surface provided on the compressor block.
    During operation, a radial flange part of the drive shaft extends in a space defined between the inner surface of the spacer ring and radial inner parts of the first surfaces of the first and second axial bearing plates, and cooperates with the first surfaces of the first and second axial bearing plates in order to limit an axial movement of the drive shaft.
    In such a compressor, especially when operating at very high speed, high temperature conditions can occur, causing thermal stresses and deformations in compressor components, for example when components of materials of different thermal expansion are attached. to each other and / or when there is a high thermal gradient in the solid parts.
    Axial bearing arrangements are particularly important, where the radial flange portion of the drive shaft rotates between the first and second axial bearing plates, with very small clearances between the rotating and stationary portions.
    Mechanical stresses introduced into the axial bearing arrangement by mounting and assembly tolerances of the compressor or due to the aforementioned non-uniform thermal expansion can deteriorate the parallel positioning of the first and second axial bearing plates. This can lead to seizure of the axial bearing arrangement and shortening the life of the centrifugal compressor.
    Summary of the invention
    The object of the present invention is to provide an improved axial bearing arrangement which can overcome the drawbacks encountered in conventional axial bearing arrangements.
    Another object of the present invention is to provide an axial bearing arrangement which is reliable, and which is particularly not subject to the abovementioned deformations.
    According to the invention, such an axial bearing arrangement comprises:
    a first axial bearing plate having the shape of an annular ring, the first axial bearing plate having a first surface and a second surface opposite to the respective first surface,
    - a spacer ring abutting against the first surface of the first axial bearing plate at a radial outer part of the first axial bearing plate,
    - A bearing sleeve being fixed to a compressor block, characterized in that the axial bearing arrangement further comprises an elastic element arranged between the second surface of the first axial bearing plate and the compressor block, and in that the the elastic element axially biases the first axial bearing plate and the spacer ring with a predetermined force against an abutment surface of the bearing sleeve.
    Such a configuration of the axial bearing arrangement, and in particular the presence of the elastic element, allows, when thermal expansion occurs, axial sliding of the first bearing plate and of the spacer ring relative to to the compressor block, and thus prevents deformations of said parts which could lead to seizure of said parts and to the reduction of the life of the centrifugal compressor.
    The axial bearing arrangement may also include one or more of the following characteristics, taken alone or in combination.
    According to one embodiment of the invention, the abutment surface of the bearing sleeve extends transversely, and for example essentially perpendicularly, to a longitudinal axis of the bearing sleeve.
    According to one embodiment of the invention, the abutment surface is located at an axial end of the bearing sleeve.
    According to one embodiment of the invention, the elastic element is an annular elastic washer, preferably of the Belleville type.
    According to one embodiment of the invention, the predetermined force exerted by the elastic element on the first axial bearing plate is in the range from 1000 to 2000 N, preferably about 1500 N.
    According to one embodiment of the invention, the elastic element is in contact with a radial outer part of the second surface of the first axial bearing plate.
    According to one embodiment of the invention, the elastic element is in contact with a radial outer part of the second surface of the first axial bearing plate, at a radius close to the mean radius of the spacer ring.
    According to one embodiment of the invention, the elastic element is arranged in an annular recess formed in an axial surface of the compressor block.
    According to one embodiment of the invention, an axial clearance is provided between the second surface of the first axial bearing plate and the axial surface of the compressor block.
    According to one embodiment of the invention, the axial clearance between the second surface of the first axial bearing plate and the axial surface of the compressor block is in the range of 20 µm.
    According to an embodiment of the invention, the bearing sleeve is configured to rotatably support the drive shaft.
    According to an embodiment of the invention, the bearing sleeve comprises at least one part of radial bearing, and for example at least one part of radial gas bearing.
    According to one embodiment of the invention, the bearing sleeve is configured to surround the drive shaft and to cooperate with the outer surface of the drive shaft.
    According to one embodiment of the invention, the compressor unit has an annular shoulder against which the bearing sleeve bears, and for example the abutment surface of the bearing sleeve.
    According to one embodiment of the invention, the axiai bearing arrangement further comprises a fixing element fixed to the compressor block and axially clamping the bearing sleeve against the compressor block, and for example against the annular shoulder of the compressor block.
    According to one embodiment of the invention, the bearing sleeve has an annular shoulder against which the fixing element bears.
    According to one embodiment of the invention, the bearing sleeve has a part sandwiched between the compressor block and the fixing element.
    According to one embodiment of the invention, the fixing element is fixed by screwing to the compressor block.
    According to one embodiment of the invention, the elastic element and the bearing sleeve are arranged coaxially.
    According to one embodiment of the invention, the axial bearing arrangement further comprises a second axial bearing plate having an annular ring shape, the second axial bearing plate having a first surface oriented axially towards the first bearing plate axial and a second surface opposite the first surface of the second axial bearing plate, the spacer ring being clamped between the first surfaces of the first and second axial bearing plates at the level of radial outer parts of the first and second bearing plates axial, the spacer ring defining an axial distance between the first and second axial bearing plates, the bearing sleeve abutting against the second surface of the second axial bearing plate, the elastic element axially biasing the first and second axial bearing plates and the spacer ring with the predetermined force against the abutment surface of the bearing sleeve.
    According to an embodiment of the invention, the first and second axial bearing plates are parallel to each other.
    According to an embodiment of the invention, the second axial bearing plate is formed as an integral part of the bearing sleeve.
    The present invention also relates to a centrifugal compressor comprising a drive shaft and an axial bearing arrangement according to the invention.
    According to one embodiment of the invention, the drive shaft has a radial flange portion extending in a space between radial interior portions of the first surfaces of the first and second axial bearing plates.
    According to one embodiment of the invention, the spacer ring surrounds the radial flange portion of the drive shaft.
    According to one embodiment of the invention, an axial clearance is provided between the radial flange portion of the drive shaft and the first surfaces of the first and second axial bearing plates.
    According to one embodiment of the invention, the axial clearance between the radial flange portion of the drive shaft and the first surfaces of the first and second axial bearing plates is in the range of 10 µm.
    According to one embodiment of the invention, the centrifugal compressor is configured to introduce gaseous fluid between the radial flange portion of the drive shaft and the first surfaces of the first and second axial bearing plates to form a bearing axial gas for the drive shaft.
    These advantages and others will become apparent from reading the following description taking into account the attached drawing representing, by way of nonlimiting examples, embodiments of a centrifugal compressor comprising an axial bearing arrangement according to the invention .
    Brief description of the drawings
    The following detailed description of two embodiments of the invention is better understood when read in conjunction with the accompanying drawings, it being understood, however, that the invention is not limited to the specific embodiments disclosed.
    FIG. 1 is a schematic view in longitudinal section of a centrifugal compressor comprising an axial bearing arrangement according to a first embodiment of the invention.
    FIG. 2 is a view in partial longitudinal section of the centrifugal compressor of FIG. 1.
    Figure 3 is an enlarged view of a detail of Figure 2.
    Figure 4 is an enlarged view of a detail of Figure 3.
    Figure 5 is a perspective view of an elastic member of the axial bearing arrangement of Figure 1.
    FIG. 6 is a schematic view in longitudinal section of a centrifugal compressor comprising an axial bearing arrangement according to a second embodiment of the invention.
    Detailed description of the invention
    FIG. 1 represents a centrifugal compressor 2 which can for example be a two-stage centrifugal compressor. The centrifugal compressor 2 comprises a drive shaft 3 extending along a longitudinal axis A.
    According to the embodiment shown in the figures, the drive shaft 3 comprises an intermediate bearing part 4, a wheel part 5 arranged at a first axial end part of the intermediate bearing part 4, and a drive part 6 arranged at a second axial end part of the intermediate bearing part 4. In particular, the intermediate bearing part 4 comprises a cylindrical bearing part 7 and a radial flange part 8 extending radially outwards from the cylindrical bearing part 7. The radial flange part 8 has the shape of a flat disc, and has a first axial end face 8.1 and a second axial end face 8.2 opposite to the first axial end face 8.1.
    The drive shaft 3 can be made, for example, of high-strength steel, ceramic materials, or combinations thereof.
    The centrifugal compressor 2 further comprises at least one wheel 9 connected to the wheel part 5 of the drive shaft 3, and configured to compress a refrigerant. The centrifugal compressor 2 can for example comprise two wheels 9 arranged in a back-to-back configuration.
    The centrifugal compressor 2 also comprises an electric motor 11 configured to rotate the drive shaft 3 around the longitudinal axis A. The electric motor 11 is advantageously arranged in a low pressure chamber, and comprises a stator 11.1 and a rotor 11.2. According to one embodiment of the invention, the rotor 11.2 is connected to the drive part 6 of the drive shaft 3. For this purpose, the drive part 6 may include an axial bore in which the rotor 11.2 is arranged. The rotor 11.2 can for example be firmly adjusted, as adjusted by pressure or adjusted by contraction, in the axial bore.
    The centrifugal compressor 2 further comprises an axial bearing arrangement, also called a thrust bearing arrangement, arranged in the low pressure chamber and configured to limit axial movement of the drive shaft 3 during operation. The axial bearing arrangement can be a fluid axial bearing arrangement, and for example a gas axial bearing arrangement.
    According to the embodiment shown in the figures, the axial bearing arrangement comprises a first axial bearing plate 12 and a second axial bearing plate 13 each having an annular ring shape, and being arranged in parallel. The first axial bearing plate 12 has a first surface 12.1 oriented axially towards the second axial bearing plate 13 and a second surface 12.2 opposite the first surface 12.1, while the second axial bearing plate 13 has a first surface 13.1 oriented axially towards the first axial bearing plate 12 and a second surface 13.2 opposite the first surface 13.1.
    The radial internal parts of the first surfaces 12.1, 13.1 of the first and second axial bearing plates 12, 13 define a space in which the radial flange part 8 of the drive shaft 3 extends. In particular, the first surfaces 12.1, 13.1 of the first and second axial bearing plates 12, 13 are respectively configured to cooperate with the first and second axial end faces 8.1, 8.2 of the radial flange part 8.
    According to one embodiment of the invention, an axial clearance is provided between the radial flange part 8 of the drive shaft 3 and the first surfaces
    12.1, 13.1 of the first and second axial bearing plates 12, 13. Such an axial clearance is advantageously in the range of 10 μm.
    The axial bearing arrangement further comprises a spacer ring 14 surrounding the radial flange portion 8 of the drive shaft 3, and being sandwiched between the first surfaces 12.1, 13.1 of the first and second axial bearing plates 12 , 13 at the level of radial external parts of the first and second axial bearing plates 12, 13. The spacer ring 14 defines an axial distance between the first and second axial bearing plates 12, 13, said axial distance being slightly greater than the width of the radial flange portion 8.
    The axial bearing arrangement also comprises a bearing sleeve surrounding the drive shaft, and being fixed to a compressor block 16 of the centrifugal compressor 2. Advantageously, the bearing sleeve 15 extends along the part of intermediate bearing 4 of the drive shaft.
    The bearing sleeve 15 has an abutment surface 17 which abuts against the second surface 13.2 of the second axial bearing plate
    13. The abutment surface 17 is located at an axial end of the bearing sleeve 15, and extends transversely, and advantageously perpendicularly, to the longitudinal axis A of the drive shaft 3 .
    According to the embodiment shown in the figures, the compressor unit has an annular shoulder 18 against which the bearing sleeve 15 bears, and more precisely the abutment surface 17 of the bearing sleeve 15.
    In addition, the axial bearing arrangement includes a fastening element 19 fixed, for example by screwing, to the compressor block 16 and axially clamping the bearing sleeve 15 against the compressor block 16, and more particularly against the annular shoulder 18 of the compressor block 16.
    According to the embodiment shown in the figures, the bearing sleeve 15 has an annular shoulder 21 against which the fastening element 19 is supported, and the bearing sleeve 15 is partly sandwiched between the compressor block 16 and the fastening element 19.
    The axial bearing arrangement also comprises an elastic element 22 arranged between the second surface 12.2 of the first axial bearing plate 12 and the compressor block 16. The elastic element 22 axially biases the first and second axial bearing plates 12, 13 and the spacer 14 with a predetermined force, for example in the range of 1000 to 2000 N, and preferably about 1500 N, against the abutment surface of the support sleeve 15. Advantageously, the elastic element 22 is an annular elastic washer, preferably of the Belleville type, arranged coaxially with the bearing sleeve 15 and the drive shaft 3.
    The elastic element 22 is advantageously arranged in an annular recess 23 formed in an axial surface of the compressor block 16, and is in contact with a radial external part of the second surface 12.2 of the first axial bearing plate 12, at a close radius the mean radius of the spacer ring 14.
    The elastic element allows, in particular when thermal expansion occurs in the centrifugal compressor, an axial sliding of the first and second axial bearing plates 12, 13 and of the spacer ring 14 relative to the compressor block 16, and avoids thus the deformations of said parts which could lead to a reduction in the life of the centrifugal compressor.
    According to one embodiment of the invention, an axial clearance C is provided between the second surface 12.2 of the first axial bearing plate 12 and the axial surface of the compressor block 16 provided with the annular recess 23. Said axial clearance C is advantageously lies in the range of 20 pm.
    According to the embodiment shown in the figures, the bearing sleeve 15 is configured to rotatably support the drive shaft 3. In particular, the bearing sleeve 15 comprises a radial bearing part 24 having an interior surface configured to cooperate with the outer surface of the cylindrical bearing part 7 of the drive shaft 3. Consequently, the bearing sleeve 15 forms a radial sleeve bearing, and for example a gas radial sleeve bearing.
    According to one embodiment of the invention, the centrifugal compressor 2 is configured so that the gaseous fluid is introduced between the radial flange part 8 of the drive shaft 3 and the first surfaces 12.1, 13.1 of the first and second axial bearing plates 12,13 to form an axial gas bearing for the drive shaft 3. The centrifugal compressor 2 is also configured so that the gaseous fluid is introduced between the cylindrical bearing part 7 of the shaft d drive 3 and the inner surface of the radial bearing portion 24 to form a radial gas bearing for the drive shaft 3.
    According to another embodiment of the invention shown in FIG. 6, the second axial bearing plate 13 can be formed as an integral part of the bearing sleeve 15.
    Of course, the invention is not limited to the embodiments described above by way of nonlimiting examples, but on the contrary, it encompasses all of the embodiments thereof.
    ίο
    权利要求:
    Claims (15)
    [1" id="c-fr-0001]
    1. Axial bearing arrangement for a drive shaft (3) of a centrifugal compressor (2), the axial bearing arrangement comprising:
    - a first axial bearing plate (12) having an annular ring shape, the first axial bearing plate (12) having a first surface (12.1) and a second surface (12.2) opposite to the first surface (12.1) of the first axial bearing plate (12),
    - a spacer ring (14) abutting against the first surface (12.1) of the first axial bearing plate (12) at a radial outer part of the first axial bearing plate (12),
    - a bearing sleeve (15) being fixed to a compressor block (16), characterized in that the axial bearing arrangement also comprises an elastic element (22) arranged between the second surface (12.2) of the first plate axial bearing (12) and the compressor block (16), and in that the elastic element (22) biases the first axial bearing plate (12) and the spacer ring (14) with a predetermined force against a abutment surface (17) of the bearing sleeve (15).
    [2" id="c-fr-0002]
    2. Axial bearing arrangement according to claim 1, wherein the elastic element (22) is an annular elastic washer.
    [3" id="c-fr-0003]
    3. Axial bearing arrangement according to claim 1 or 2, wherein the predetermined force exerted by the elastic element (22) on the first axial bearing plate (12) is in the range from 1000 to 2000 N.
    [4" id="c-fr-0004]
    4. Axial bearing arrangement according to any one of claims 1 to 3, wherein the elastic element (22) is in contact with a radial outer part of the second surface (12.2) of the first axial bearing plate (12 ).
    [5" id="c-fr-0005]
    5. Axial bearing arrangement according to claim 4, in which the elastic element (22) is in contact with a radial external part of the second surface (12.2) of the first axial bearing plate (12), at a close radius. the average radius of the spacer ring (14).
    [6" id="c-fr-0006]
    6. Axial bearing arrangement according to any one of claims 1 to 5, wherein the elastic element (22) is arranged in an annular recess (23) formed in an axial surface of the compressor block (16).
    [7" id="c-fr-0007]
    7. Axial bearing arrangement according to claim 6, in which an axial clearance is provided between the second surface (12.2) of the first axial bearing plate (12) and the axial surface of the compressor block (16).
    [8" id="c-fr-0008]
    8. An axial bearing arrangement according to any one of claims 1 to 7, wherein the bearing sleeve (15) is configured to rotatably support the drive shaft (3).
    [9" id="c-fr-0009]
    9. Axial bearing arrangement according to any one of claims 1 to 8, further comprising a fixing element (19) fixed to the compressor block (16) and axially clamping the bearing sleeve (15) against the compressor block (16 ).
    [10" id="c-fr-0010]
    10. Axial bearing arrangement according to any one of claims 1 to 9, further comprising a second axial bearing plate (13) having an annular ring shape, the second axial bearing plate (13) having a first surface ( 13.1) oriented axially towards the first axial bearing plate (12) and a second surface (13.2) opposite the first surface (13.1) of the second axial bearing plate (13), the spacer ring (14) being clamped between the first surfaces (12.1, 13.1) of the first and second axial bearing plates (12, 13) at the level of radial outer parts of the first and second axial bearing plates (12, 13), the spacer ring (14) defining an axial distance between the first and second axial bearing plates (12 13), ie bearing sleeve (15) abutting against the second surface (13.2) of the second axial bearing plate (13), the elastic element (22) acting axially the first and second axial bearing plates (12, 13) and the spacer ring (14) with the predetermined force against the abutment surface (17) of the bearing sleeve (15).
    [11" id="c-fr-0011]
    11. An axial bearing arrangement according to claim 10, wherein the second axial bearing plate (13) is formed as an integral part of the bearing sleeve.
    [12" id="c-fr-0012]
    12. Centrifugal compressor (2) comprising a drive shaft (3) and an axial bearing arrangement according to any one of claims 1 to
    11.
    [13" id="c-fr-0013]
    13. Centrifugal compressor (2) according to claim 12, in which the drive shaft (3) comprises a radial flange part (8) extending in a space between the radial internal parts of the first surfaces (12.1,13.1 ) first and second axial bearing plates (12,13).
    [14" id="c-fr-0014]
    14. Centrifugal compressor according to claim 13, in which an axial clearance is provided between the radial flange part (8) of the drive shaft (3) and the first surfaces (12.1, 13.1) of the first and second plates. axial bearing (12, 13).
    5
    [0015]
    15. Centrifugal compressor (2) according to claim 13 or 14, wherein the centrifugal compressor (2) is configured to introduce gaseous fluid between the radial flange portion (8) of the drive shaft (3) and the first surfaces (12.1, 13.1) of the first and second axial bearing plates (12, 13) to form an axial gas bearing for the drive shaft (3).
    1/3
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    同族专利:
    公开号 | 公开日
    CN109790868B|2020-10-27|
    CN109790868A|2019-05-21|
    WO2018041949A1|2018-03-08|
    US20190226489A1|2019-07-25|
    US10760583B2|2020-09-01|
    FR3055678B1|2020-09-18|
    DE112017004420T5|2019-06-27|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US20080181546A1|2003-05-13|2008-07-31|Burgmann Automotive Gmbh|Axial plain bearing assembly|
    EP1770811A2|2005-09-29|2007-04-04|JTEKT Corporation|Fuel-cell apparatus with coupled compressor and turbine|
    WO2010142633A1|2009-06-09|2010-12-16|Oerlikon Leybold Vacuum Gmbh|Vacuum pump|
    WO2013142461A1|2012-03-20|2013-09-26|Flowserve Management Company|Dry gas thrust bearing for use in rotating equipment|
    WO2014038080A1|2012-09-10|2014-03-13|株式会社日立製作所|Thrust bearing device and rotating machine using same|
    US20160146248A1|2014-11-25|2016-05-26|General Electric Company|Compliant hybrid gas lubricated thrust bearing|
    US4892469A|1981-04-03|1990-01-09|Arthur D. Little, Inc.|Compact scroll-type fluid compressor with swing-link driving means|
    US4465446A|1983-05-11|1984-08-14|Frick Company|Radial and thrust bearing mountings providing independent loading|
    US4828403A|1987-04-03|1989-05-09|Schwartzman Everett H|Resiliently mounted fluid bearing assembly|
    DE4230037A1|1991-09-09|1993-03-11|Aisin Seiki|CENTRIFUGAL RECHARGE BLOWER|
    US5528976A|1993-11-24|1996-06-25|Kabushiki Kaisha Toyoda Jidoshokki Seisakusho|Swash plate type compressor with bearing assembly|
    JP2937040B2|1994-11-18|1999-08-23|株式会社豊田自動織機製作所|Double head swash plate type compressor|
    JPH08144945A|1994-11-22|1996-06-04|Toyota Autom Loom Works Ltd|Double head cam plate type compressor|
    EP2325489B1|2008-10-27|2016-11-30|Panasonic Corporation|Sealed compressor|
    JP4961485B2|2010-03-30|2012-06-27|本田技研工業株式会社|Dynamic pressure type foil type gas bearing|
    JP4932921B2|2010-03-31|2012-05-16|本田技研工業株式会社|Electric centrifugal compressor|
    JP2017089384A|2014-03-19|2017-05-25|株式会社豊田自動織機|Electric turbo type compressor|
    DE102015218428A1|2014-10-03|2016-04-07|Borgwarner Inc., Patent Department|DEVICES AND METHOD FOR ADJUSTING THE BALANCE OF THE ROTATION ARRANGEMENT OF A TURBOCHARGER|FR3085189B1|2018-08-22|2020-12-25|Danfoss As|A TURBOCHARGER CONTAINING AN ENGINE COOLING ARRANGEMENT|
    FR3085191B1|2018-08-22|2020-12-25|Danfoss As|A TURBOCHARGER HAVING A BEARING SLEEVE WITH AXIAL END SLOTS|
    FR3085188B1|2018-08-22|2020-12-25|Danfoss As|A TURBOCHARGER PROVIDED WITH AN AXIAL BEARING COOLING SYSTEM|
    FR3085187B1|2018-08-22|2020-09-18|Danfoss As|A TURBOCHARGER HAVING A FLEXIBLE CONTACT ZONE BETWEEN A BEARING SLEEVE AND A FIXED COMPRESSOR PART.|
    FR3085190B1|2018-08-22|2020-12-25|Danfoss As|A TURBOCHARGER HAVING A BEARING SLEEVE PROVIDED WITH A CROSS-SECTION REDUCTION|
    CN111365256A|2018-12-25|2020-07-03|珠海格力电器股份有限公司|Centrifugal compressor and air conditioning equipment|
    CN111536055A|2020-04-30|2020-08-14|北京动力机械研究所|High-efficient compressor arrangement of inert gas mixture bearing|
    法律状态:
    2017-08-24| PLFP| Fee payment|Year of fee payment: 2 |
    2018-03-09| PLSC| Publication of the preliminary search report|Effective date: 20180309 |
    2018-08-23| PLFP| Fee payment|Year of fee payment: 3 |
    2019-08-29| PLFP| Fee payment|Year of fee payment: 4 |
    2019-12-27| TP| Transmission of property|Owner name: DANFOSS A/S, DK Effective date: 20191119 |
    2020-08-26| PLFP| Fee payment|Year of fee payment: 5 |
    2021-08-26| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1658168A|FR3055678B1|2016-09-02|2016-09-02|AXIAL BEARING ARRANGEMENT FOR A CENTRIFUGAL COMPRESSOR DRIVE SHAFT|
    FR1658168|2016-09-02|FR1658168A| FR3055678B1|2016-09-02|2016-09-02|AXIAL BEARING ARRANGEMENT FOR A CENTRIFUGAL COMPRESSOR DRIVE SHAFT|
    DE112017004420.0T| DE112017004420T5|2016-09-02|2017-08-31|Thrust bearing arrangement for a drive shaft of a centrifugal compressor|
    CN201780059341.8A| CN109790868B|2016-09-02|2017-08-31|Axial bearing arrangement for a drive shaft of a centrifugal compressor|
    PCT/EP2017/071874| WO2018041949A1|2016-09-02|2017-08-31|Axial bearing arrangement for a drive shaft of a centrifugal compressor|
    US16/329,313| US10760583B2|2016-09-02|2017-08-31|Axial bearing arrangement for a drive shaft of a centrifugal compressor|
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