• 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 centrifugal compressor has an airtight housing; a drive shaft (4); first and second compression stages (8, 9) configured to compress a refrigerant, the first and second compression stages (8, 9) respectively having first and second wheels (18, 19), the first and second wheel ( 18, 19) being connected to the drive shaft (4) and arranged in a back-to-back configuration; a radial annular groove (27) formed between the rear sides (25, 26) of the first and second wheels (18, 19); an interstage seal arrangement (35) provided between the first and second compressor stages (8, 9) and in the radial annular groove (27); a radial bearing arrangement configured to rotatably support the drive shaft (4); and a thrust bearing arrangement configured to limit axial displacement of the drive shaft (4) during operation. The diameter of the interstage seal arrangement (35) is configured to minimize the magnitude of the axial load applied to the thrust bearing arrangement during operation of the centrifugal compressor (2).
    公开号:FR3038665A1
    申请号:FR1556410
    申请日:2015-07-07
    公开日:2017-01-13
    发明作者:Patrice Bonnefoi；Nicolas Nouyrigat；Arnaud Daussin
    申请人:Danfoss Commercial Compressors SA；
    IPC主号:
    专利说明:

    Field of the invention
    The present invention relates to a centrifugal compressor, and in particular to a two-stage centrifugal compressor.
    Background of the invention
    The document WO2012124293 describes a two-stage centrifugal compressor including in particular: - a hermetic housing, - a drive shaft rotatably arranged inside the hermetic housing, - first and second compression stages configured to compress a refrigerant the first and second compression stages respectively having first and second wheels, the first and second wheels being connected to the drive shaft and being arranged in a back-to-back configuration, - a radial annular groove formed between rear sides of the first and second wheels, - an inter-stage sealing arrangement provided between the first and second compressor stages and in the radial annular groove, - a radial bearing arrangement configured to rotatably support the drive shaft. and a thrust bearing arrangement configured to limit axial displacement of the drive shaft during operation.
    During the operation of such a two-stage centrifugal compressor, the axial loads applied to the thrust bearing arrangement are high, which necessitates the provision of a large thrust bearing arrangement to withstand the axial loads applied thereto. latest. This results in a centrifugal compressor having a high power consumption. Summary of the invention
    An object of the present invention is to provide a centrifugal compressor which can overcome the disadvantages encountered with conventional centrifugal compressors.
    Another object of the present invention is to provide a centrifugal compressor having a thrust bearing arrangement of reduced size and thus having a low power consumption.
    According to the invention, such a centrifugal compressor comprises: - a hermetic housing, - a drive shaft rotatably arranged inside the hermetic housing, - first and second compression stages configured to compress a refrigerant, the first and second compression stages having respective first and second impellers, each of the first and second impellers having a front side and a rear side, the first and second impellers being connected to the drive shaft and being arranged in a back configuration; at the back, - a radial annular groove formed between the rear sides of the first and second wheels, - a circular interstage sealing arrangement provided between the first and second compressor stages and in the radial annular groove, - an arrangement radial bearing configured to rotatably support the drive shaft, and - a bearing arrangement of stopper configured to limit axial displacement of the drive shaft during operation, wherein the diameter of the interstage seal arrangement is configured to minimize the magnitude of the axial load applied to the bearing arrangement of stop during the operation of the centrifugal compressor.
    Such a configuration of the interstage sealing arrangement, and in particular its diameter, allows the provision of a thrust bearing arrangement of reduced size, and thus reduce the energy consumption of the centrifugal compressor. These provisions therefore make it possible to increase the efficiency of the centrifugal compressor.
    The centrifugal compressor may also include one or more of the following features, taken alone or in combination.
    According to one embodiment of the invention, the diameter of the interstage seal arrangement is configured such that the absolute value of the axial thrust load occurring during any operating conditions of the centrifugal compressor is minimal. .
    According to one embodiment of the invention, the minimum diameter of the inter-stage sealing arrangement is less than half the outer diameter of the first wheel and is less than half the outer diameter of the second wheel.
    According to one embodiment of the invention, the ratio between the outside diameter of the first wheel and the minimum diameter of the inter-stage seal arrangement is greater than 2.5, and the ratio of the outside diameter of the second wheel and the minimum diameter of the interstage seal arrangement is greater than 2.5.
    According to one embodiment of the invention, the minimum diameter of the inter-stage seal arrangement is smaller than the outside diameter of the portion of the drive shaft rotatably supported by the radial bearing arrangement. .
    According to one embodiment of the invention, the centrifugal compressor further comprises a separating element connected to the hermetic housing, the separating element having a disc shape and being at least partially arranged inside the radial annular groove. the interstage sealing arrangement being formed by an inner peripheral surface of the separating element and a circumferential bottom surface of the radial annular groove.
    According to one embodiment of the invention, the separating element has a first axial wall surface and a second axial wall surface opposite to the first axial wall surface, the first axial wall surface and the rear side of the first axial wall surface. wheel defining a first axial space and the second axial wall surface and the rear side of the second wheel defining a second axial space.
    According to one embodiment of the invention, the inner peripheral surface of the separating element and the circumferential bottom surface of the radial annular groove define a radial space. The presence of a certain axial space (and therefore a certain volume) between the separating element and the first and second wheels ensures stable pressure conditions inside the radial annular groove, especially if the absolute dimensions are very small.
    According to one embodiment of the invention, the width of the first axial space is at least twice the width of the radial space, and the width of the second axial space is at least twice the width of the radial space.
    According to one embodiment of the invention, each of the first and second axial spaces may be between 1 and 10% of the outer diameter of the first wheel, and may be between 1 and 10% of the outer diameter of the second wheel.
    According to one embodiment of the invention, each of the first and second axial spaces may be between 140 and 150 μm, and is for example about 150 μm.
    Advantageously, each of the first and second axial spaces is larger than the maximum allowed axial displacement of the drive shaft during operation of the centrifugal compressor.
    According to one embodiment of the invention, the radial space can be between 0.1 and 2% of the outer diameter of the first wheel, and can be between 0.1 and 2% of the outer diameter of the second wheel.
    According to one embodiment of the invention, the radial space may be between 40 and 50 μm.
    According to one embodiment of the invention, the hermetic housing comprises a low pressure chamber located upstream of the first compression stage, a high pressure chamber located downstream of the second compression stage, and an intermediate pressure chamber provided between an outlet of fluid of the first compression stage and a fluid inlet of the second compression stage.
    According to one embodiment of the invention, the circular inter-stage sealing arrangement is configured to minimize or regulate fluid flow from the high pressure chamber to the intermediate pressure chamber.
    According to one embodiment of the invention, the radial bearing arrangement and the thrust bearing arrangement are arranged in the low pressure chamber.
    According to one embodiment of the invention, the circular inter-stage sealing arrangement is a labyrinth sealing arrangement.
    According to one embodiment of the invention, the outer diameters of the first and second wheels are substantially equal.
    Advantageously, the ratio between the outer diameter of the first wheel and the outer diameter of the second wheel is between 0.8 and 1.2 or between 0.9 and 1.1.
    According to one embodiment of the invention, the drive shaft comprises a first axial end portion, a second axial end portion and an intermediate portion arranged between the first and second axial end portions.
    According to one embodiment of the invention, the first and second wheels are connected to the first axial end portion of the drive shaft.
    According to one embodiment of the invention, the centrifugal compressor further comprises a driving device configured to rotate the drive shaft about an axis of rotation, the radial bearing arrangement and the arrangement thrust bearing being located between the drive device and the first compression stage.
    According to one embodiment of the invention, the drive device is an electric motor comprising a stator and a rotor. Advantageously, the rotor is connected to the second axial end portion of the drive shaft.
    According to one embodiment of the invention, the drive device comprises at least one turbine blade.
    According to one embodiment of the invention, the drive device is arranged in the low pressure chamber.
    According to one embodiment of the invention, the thrust bearing arrangement can be provided on a fixed part or on a rotating part of the centrifugal compressor, with any shape including chevrons, oscillating pads, a bearing-sheet, grooves ...
    According to one embodiment of the invention, the thrust bearing arrangement comprises a thrust bearing element arranged on the outer surface of the drive shaft, the thrust bearing element extending substantially radially towards the thrust bearing. outside relative to the drive shaft.
    According to one embodiment of the invention, the thrust bearing element is annular.
    According to one embodiment of the invention, the thrust bearing element is formed in one piece with the drive shaft.
    According to one embodiment of the invention, the thrust bearing member has a first thrust bearing surface and a second thrust bearing surface opposite to the first thrust bearing surface.
    According to one embodiment of the invention, the first abutment bearing surface of the abutment bearing element is configured to cooperate with a first abutment bearing surface defined by a first abutment bearing element connected to the hermetic housing, and the second abutment bearing surface of the abutment bearing member is configured to cooperate with a second abutment bearing surface defined by a second abutment bearing member connected to the hermetic housing.
    According to one embodiment of the invention, the first and second abutment bearing elements are annular.
    According to one embodiment of the invention, the first and second wheels are formed integrally with the drive shaft. According to another embodiment of the invention, the first and second wheels are provided on a wheel element attached to the drive shaft, and for example to the first axial end portion of the drive shaft. .
    According to one embodiment of the invention, the front side of each of the first and second wheels comprises a plurality of blades configured to accelerate during the rotation of the drive shaft, the refrigerant entering the stage of respective compression. According to one embodiment of the invention, the plurality of blades of each of the first and second wheels are configured to route the accelerated refrigerant to a diffuser arranged at the radial outer edge of the respective wheel.
    According to one embodiment of the invention, each of the first and second compression stages comprises a fluid inlet and a fluid outlet, the fluid outlet of the first compression stage being fluidly connected to the fluid inlet of the second compression stage.
    According to one embodiment of the invention, the radial bearing arrangement is configured to cooperate with an outer surface of the drive shaft.
    According to one embodiment of the invention, at least one of the radial bearing arrangement and the thrust bearing arrangement comprises a gas bearing. Therefore, compressed gas at an intermediate or high pressure is conveyed to a space provided between the corresponding adjacent bearing surfaces of the thrust bearing arrangement and / or the radial bearing arrangement. Hereby, the use of a lubricating oil and the problems associated with the oil supply, the oil temperature or the oil circulation in the refrigerant compression can be avoided.
    According to one embodiment of the invention, the radial bearing arrangement is a radial gas bearing arrangement.
    According to one embodiment of the invention, the thrust bearing arrangement is a thrust bearing arrangement.
    According to one embodiment of the invention, the centrifugal compressor is configured such that at least a portion of the refrigerant compressed in the first and second compression stages is used as a lubricating fluid in the radial gas bearing arrangement. and / or the fluid thrust bearing arrangement. According to said embodiment of the invention, the centrifugal compressor can be considered as a monofluid compressor. This configuration of the centrifugal compressor avoids a separate supply of lubricating fluid and thus reduces costs.
    According to one embodiment of the invention, the first and second wheels are non-closed wheels.
    According to one embodiment of the invention, the input diameter of the first wheel is different from the input diameter of the second wheel.
    According to one embodiment of the invention, the input diameter of the first wheel is greater than the input diameter of the second wheel.
    According to one embodiment of the invention, the inlet diameter of the first wheel is greater than the minimum diameter of the inter-stage seal arrangement, and the minimum diameter of the inter-stage seal arrangement is greater than to the input diameter of the second wheel.
    According to one embodiment of the invention, the input diameter of the second wheel is greater than the input diameter of the first wheel.
    These and other advantages will become apparent on reading the following description with reference to the drawing attached thereto showing, by way of nonlimiting examples, embodiments of the centrifugal refrigerating compressor according to the invention.
    Brief description of the drawings
    The following detailed description of several embodiments of the invention will be better understood when read in conjunction with the accompanying drawings, it being understood, however, that the invention is not limited to the specific embodiment described.
    Figure 1 is a partial longitudinal sectional view of a centrifugal compressor according to the invention.
    Figures 2 to 5 are enlarged sectional views of details of the centrifugal compressor of Figure 1.
    Detailed description of the invention
    Figures 1 to 5 show a centrifugal compressor 2, in particular a two-stage centrifugal refrigeration compressor.
    The centrifugal compressor 2 comprises a hermetic housing 3, and a drive shaft 4 rotatably arranged in the hermetic housing 3 and extending along a longitudinal axis A. The drive shaft 4 comprises a first part axial end portion 5, a second axial end portion 6 opposite the first axial end portion 5, and an intermediate portion 7 arranged between the first and second axial end portions 5, 6. drive 4 can be made of high-strength steel, ceramic materials, or combinations thereof.
    The centrifugal compressor 2 further comprises a first compression stage 8 and a second compression stage 9 configured to compress a refrigerant. The first compression stage 8 comprises a fluid inlet 11 and a fluid outlet 12, while the second compression stage 9 comprises a fluid inlet 13 and a fluid outlet 14, the fluid outlet 12 of the first compression stage 8 being fluidly connected to the fluid inlet 13 of the second compression stage 9.
    The hermetic housing 3 thus comprises a low pressure chamber 15 located upstream of the first compression stage 8, a high pressure chamber 16 located downstream of the second compression stage 9, and an intermediate pressure chamber 17 provided between the fluid outlet 12 the first compression stage 8 and the fluid inlet 13 of the second compression stage 9.
    The first and second compression stages 8, 9 respectively comprise a first wheel 18 and a second wheel 19. The first and second wheels 18, 19 are connected to the first axial end portion 5 of the drive shaft 4. According to the embodiment shown in the figures, the first and second wheels 18, 19 are provided on a wheel element 20 fixed to the first axial end portion 5 of the drive shaft 4. However, according to another embodiment of the invention, the first and second wheels 18, 19 can be formed integrally with the drive shaft 4.
    The first and second wheels 18, 19 are arranged in a back-to-back configuration, so that the fluid flow directions at the flow inlet 11, 13 of the first and second compression stages 8, 9 are opposed to each other.
    Each of the first and second wheels 18, 19 has a front side equipped with a plurality of blades 23, 24 configured to accelerate, during the rotation of the drive shaft 4, the refrigerant entering the respective stage among the first and second stages of compression 8, 9, and for conveying the accelerated refrigerant to a diffuser arranged at the radial outer edge of the respective wheel among the first and second wheels 18, 19. Each of the first and second wheels 18, 19 also comprises a rear side 25, 26 extending advantageously substantially perpendicularly to the drive shaft 4.
    According to the embodiment shown in the figures, the outer diameters D01, D02 of the first and second wheels 18, 19 are substantially equal. It should be noted that the outer diameters D01, D02 correspond respectively to the outlet diameters of the first and second wheels 18, 19, that is to say the maximum outside diameters of the first and second wheels 18, 19.
    In addition, according to the embodiment shown in the figures, the input diameter DU of the first wheel 18 is greater than the input diameter DI2 of the second wheel 19. It should be noted that the input diameter DM corresponds to the diameter blade root at the front ends of the blades 23, and thus at the hub diameter at the front ends of the blades 23. It should also be noted that the inlet diameter DI2 corresponds to the root diameter of the blade at level of the front ends of the vanes 24, and thus to the hub diameter at the front ends of the vanes 24.
    The centrifugal compressor 2 also has a radial annular groove 27 formed between the rear sides 25, 26 of the first and second wheels 18, 19. According to the embodiment shown in the figures, the radial annular groove 27 is provided on the wheel element 20.
    The centrifugal compressor 2 comprises a separating element 28 connected to the hermetic housing 3, and having a disc shape. The separating element 28 is at least partially arranged within the radial annular groove 27, and extends substantially perpendicularly to the drive shaft 4. The separating element 28 has an inner peripheral surface 29, an outer peripheral surface 31, a first axial wall surface 32 and a second axial wall surface 33 opposed to the first axial wall surface 32.
    The first axial wall surface 32 and the rear side 25 of the first wheel 18 define a first axial space GA1 and the second axial wall surface 33 and the rear side 26 of the second wheel 19 define a second axial space GA2. The inner peripheral surface 29 of the separating element 28 and a circumferential bottom surface 34 of the radial annular groove 27 define a radial space GR.
    Advantageously, the width of the first axial space GA1 is at least twice the width of the radial space GR, and the width of the second axial space GA2 is at least twice the width of the radial space GR. According to one embodiment of the invention, each of the first and second axial spaces GA1, GA2 may be between 140 and 150 pm, and is for example about 150 pm. Advantageously, each of the first and second axial spaces GA1, GA2 is larger than the maximum allowed axial displacement of the drive shaft 4 during the operation of the centrifugal compressor. According to one embodiment of the invention, the radial space GR may be between 40 and 50 μm.
    The centrifugal compressor 2 comprises a circular interstage sealing arrangement 35 provided between the first and second compressor stages 8, 9 and in the annular radial groove 27. The circular interstage sealing arrangement 35 is configured to reduce at least or regulate a flow of fluid from the high pressure chamber 16 to the intermediate pressure chamber 17. The interstage seal arrangement 35 is formed by the inner peripheral surface 29 of the separating element 28 and the surface circumferential bottom 34 of the radial annular groove 27.
    The minimum diameter Ds of the interstage sealing arrangement 35 is advantageously less than half the outer diameter D01 of the first wheel 18 and is advantageously less than half the outer diameter D02 of the second wheel 19.
    According to the embodiment shown in the figures, the circular interstage seal arrangement 35 is a labyrinth seal arrangement. To this end, the wheel element 20 has a circumferential projection 36 extending from the circumferential bottom surface 34 of the radial annular groove 27, the circumferential projection 36 being received in an annular recess 37 provided in the peripheral surface. inside 29 of the separating element 28.
    The centrifugal compressor 2 comprises an electric motor 38 configured to drive the drive shaft 4 in rotation about the longitudinal axis A. The electric motor 38 comprises a stator 39 and a rotor 41. The electric motor 38 is advantageously arranged in the low pressure chamber 15 defined by the hermetic housing 3.
    The rotor 41 is connected to the second axial end portion 6 of the drive shaft 4. For this purpose, the second axial end portion 6 of the drive shaft 4 may comprise a central axial bore 42 The rotor 41 may for example be firmly fitted, as adjusted with clamping, within the central axial bore 42.
    The centrifugal compressor 2 comprises a radial bearing arrangement arranged in the low pressure chamber 15 and configured to rotatably support the drive shaft 4. The radial bearing arrangement comprises a radial bearing 43 surrounding the drive shaft 4 and configured to cooperate with the outer surface of the drive shaft 4. The radial bearing 43 may be a radial fluid bearing, and for example a radial gas bearing. According to the embodiment shown in the figures, the radial bearing 43 extends along the second axial end portion 6 and along a portion of the intermediate portion 7 of the drive shaft 4. Advantageously , the minimum diameter Ds of the interstage seal arrangement 35 is smaller than the outside diameter D3 of the portion of the drive shaft 4 rotatably supported by the radial bearing arrangement.
    According to another embodiment of the invention, the radial bearing arrangement may comprise a plurality of radial bearings distributed over the axial length of the drive shaft 4.
    The centrifugal compressor 2 further comprises a thrust bearing arrangement arranged in the low pressure chamber 15 and configured to limit axial displacement of the drive shaft 4 during operation. The thrust bearing arrangement may be a fluid thrust bearing arrangement, and for example a thrust bearing arrangement. The thrust bearing arrangement comprises an annular abutment bearing element 44 arranged on the outer surface of the intermediate portion 7 of the drive shaft 7, and located between the electric motor 38 and the first compression stage 8. The thrust bearing member 44 may be formed integrally with the drive shaft 4, or may be attached thereto. The thrust bearing member 44 extends radially outwardly relative to the intermediate portion 7 of the drive shaft 4, and has a first thrust bearing surface 45 and a second thrust bearing surface. 46 opposite the first abutment bearing surface 45. The first abutment bearing surface 45 of the abutment bearing member 44 is configured to cooperate with a first abutment bearing surface defined by a first abutment bearing member. annular 47 connected to the hermetic housing 3, while the second bearing bearing surface 46 of the thrust bearing element 44 is configured to cooperate with a second annular thrust bearing surface defined by a second thrust bearing element 48 connected to the hermetic housing 3.
    According to one embodiment of the invention, the centrifugal compressor 2 is configured such that a portion of the refrigerant compressed by the first and second compression stages 8, 9 is used as a lubricating fluid in the radial bearing arrangement fluid and the fluid thrust bearing arrangement.
    It should be noted that, during use, the volume delimited between the rear side 26 of the second wheel 19 and the second axial wall surface 33 of the separating element 28 is at high pressure (P2), while the volume Delimited between the rear side 25 of the first wheel 18 and the first axial wall surface 32 of the separating element 28 is at intermediate pressure (Pi). As the outer diameters D01, D02 of the first and second spinning wheels 18, 19 are approximately equal, the gas force acting on the rear side 26 of the second wheel 19 (due to the high pressure volume) exceeds the force acting on the rear side 25 of the first wheel 18 (due to the volume of intermediate pressure). Thus the resultant force Fs acting on the shaft / wheel unit due to the interstage sealing arrangement 35 acts in a first direction away from the electric motor 38. The resulting force Fs is calculated using the following formula:
    Fs = P2 * π / 4 * (D022 - Ds2) - Pi * tt / 4 * (D012 - Ds2), where D01 is the outside diameter of the first wheel 18; D02 is the outside diameter of the second wheel 19; and
    Ds is the minimum diameter of the interstage seal arrangement 35.
    In addition, gas forces F1 acting on the front side 21 of the first wheel 18 and gas forces Fm acting on an axial end face of the rotor 42 also act in the first direction.
    The forces acting in a second direction opposite to the first direction, that is to say towards the electric motor 38, are the gas forces Fi2 acting on the front side 22 of the second wheel 19 and the gas forces Fr acting on other axial surfaces of the drive shaft 4 towards the electric motor 38.
    For each operating point of the centrifugal compressor 2, the stop force Ft acting on the thrust bearing surfaces 45, 46 of the thrust bearing element 44 can be calculated by:
    Ft = Fs + Fi1 + Fm - Fi2 - Fr.
    The stop force Ft can act in two axial directions, depending on the pressure conditions at different points of the operating board of the centrifugal compressor.
    Since the stop force Ft can be calculated on the basis of the resultant force Fs which can be calculated on the basis of the minimum diameter of the interstage seal arrangement 35, the Applicant has identified that, by optimizing the minimum diameter As from the interstage seal arrangement 35, it is possible to minimize the magnitude of the axial load applied to the thrust bearing arrangement during the operation of the centrifugal compressor 2. Such an optimization of the minimum diameter As a result of the interstage sealing arrangement 35, the size of the thrust bearing element 44 and thus the energy consumption of the centrifugal compressor 2 can be reduced.
    Of course, the invention is not limited to the embodiments described above by way of non-limiting examples, but on the contrary it encompasses all the corresponding embodiments.
    权利要求:
    Claims (16)
    [1" id="c-fr-0001]
    Centrifugal compressor (2) comprising: - a hermetic housing (3), - a drive shaft (4) rotatably arranged inside the hermetic housing (3), - first and second compression stages ( 8, 9) configured to compress a refrigerant, the first and second compression stages (8, 9) respectively having first and second wheels (18, 19), each of the first and second wheel (18, 19) having a side front (21, 22) and a rear side (25, 26), the first and second wheels (18, 19) being connected to the drive shaft (4) and arranged in a back-to-back configuration, - a radial annular groove (27) formed between the rear sides (25, 26) of the first and second wheel (18, 19), - a circular inter-stage sealing arrangement (35) provided between the first and second stages of compressor (8, 9) and in the radial annular groove (27), a radial bearing arrangement con shown for rotatably supporting the drive shaft (4), and - a thrust bearing arrangement configured to limit axial displacement of the drive shaft (4) during operation, wherein the diameter of the drive shaft interstage seal arrangement (35) is configured to minimize the magnitude of the axial load applied to the thrust bearing arrangement during operation of the centrifugal compressor (2).
    [2" id="c-fr-0002]
    The centrifugal compressor (2) according to claim 1, wherein the minimum diameter (Ds) of the interstage seal arrangement (35) is less than half the outer diameter (D01) of the first wheel (18). and is less than half the outer diameter (DO2) of the second wheel (19).
    [3" id="c-fr-0003]
    3. Centrifugal compressor (2) according to claim 1 or 2, wherein the minimum diameter (Ds) of the inter-stage seal arrangement (35) is smaller than the outside diameter (D3) of the part of the drive shaft (4) rotatably supported by the radial bearing arrangement.
    [4" id="c-fr-0004]
    4. Centrifugal compressor according to any one of claims 1 to 3, further comprising a separating element (28) connected to the hermetic housing (3), the separating element (28) having a disc shape and being at least partially arranged within the annular radial groove (27), the interstage sealing arrangement (35) being formed by an inner peripheral surface (29) of the separating element (28) and a surface of circumferential bottom (34) of the radial annular groove (27).
    [5" id="c-fr-0005]
    Centrifugal compressor (2) according to claim 4, wherein the separating element (28) has a first axial wall surface (32) and a second axial wall surface (33) opposite the first axial wall surface. (32), the first axial wall surface (32) and the rear side (25) of the first wheel (18) defining a first axial space (GA1) and the second axial wall surface (33) and the rear surface (26). ) of the second wheel (19) defining a second axial space (GA2).
    [6" id="c-fr-0006]
    Centrifugal compressor (2) according to claim 4 or 5, wherein the inner peripheral surface (29) of the separating element (28) and the circumferential bottom surface (34) of the radial annular groove (27) define a radial space (GR).
    [7" id="c-fr-0007]
    Centrifugal compressor (2) according to claims 5 and 6, wherein the width of the first axial space (GA1) is at least twice the width of the radial space (GR), and the width of the second axial space (GA2). ) is at least twice the width of the radial space (GR).
    [8" id="c-fr-0008]
    8. Centrifugal compressor according to any one of claims 1 to 7, wherein the hermetic housing (3) comprises a low pressure chamber (15) located upstream of the first compression stage (8), a high pressure chamber (16). located downstream of the second compression stage (9), and an intermediate pressure chamber (17) provided between a fluid outlet (12) of the first compression stage (8) and a fluid inlet (13) of the second stage of compression (9).
    [9" id="c-fr-0009]
    Centrifugal compressor according to claim 8, wherein the circular interstage seal arrangement (35) is configured to minimize or regulate fluid flow from the high pressure chamber (16) to the intermediate pressure chamber (17). ).
    [10" id="c-fr-0010]
    Centrifugal compressor (2) according to claim 8 or 9, wherein the radial bearing arrangement and the thrust bearing arrangement are arranged in the low pressure chamber (15).
    [11" id="c-fr-0011]
    Centrifugal compressor according to any one of claims 1 to 10, wherein the circular interstage seal arrangement (35) is a labyrinth seal arrangement.
    [12" id="c-fr-0012]
    12. Centrifugal compressor according to any one of claims 1 to 11, wherein the outer diameters (D01, D02) of the first and second wheel (18, 19) are substantially equal.
    [13" id="c-fr-0013]
    13. Centrifugal compressor (2) according to any one of claims 1 to 12, further comprising a drive device (38) configured to rotate the drive shaft (4) about an axis of rotation. the radial bearing arrangement and the thrust bearing arrangement being located between the drive device (38) and the first compression stage (8).
    [14" id="c-fr-0014]
    Centrifugal compressor (2) according to any one of claims 1 to 13, wherein the thrust bearing arrangement comprises a thrust bearing element (44) arranged on the outer surface of the drive shaft ( 4), the thrust bearing member (44) extending substantially radially outwardly relative to the drive shaft (4).
    [15" id="c-fr-0015]
    The centrifugal compressor (2) according to any one of claims 1 to 14, wherein at least one of the radial bearing arrangement and the thrust bearing arrangement comprises a gas bearing.
    [16" id="c-fr-0016]
    16. Centrifugal compressor (2) according to any one of claims 1 to 15, wherein the input diameter (DM) of the first wheel (18) is greater than the inlet diameter (DI2) of the second wheel (19). .
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    FR3063776A1|2018-09-14|BEARING ARRANGEMENT FOR A DRIVE SHAFT OF A TURBOMACHINE, AND A TURBOMACHINE HAVING SUCH A BEARING ARRANGEMENT
    FR3030648A1|2016-06-24|COMPRESSOR WITH SEALING SYSTEM
    FR2983539A1|2013-06-07|PUMP AND PALLET TURBINE
    同族专利:
    公开号 | 公开日
    WO2017005477A1|2017-01-12|
    US20180142694A1|2018-05-24|
    US10619645B2|2020-04-14|
    CN107850080A|2018-03-27|
    FR3038665B1|2017-07-21|
    CN107850080B|2019-11-05|
    WO2017005477A8|2018-01-04|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE1803958A1|1967-10-18|1969-06-19|Materiels Hispano Suiza Sa Soc|Compression system with two compression stages and intermediate heat exchanger|
    DE3041093A1|1980-10-31|1982-06-09|Atlas Copco AB, Nacka|Rotor for radial compressor - has integral rotor disc arrangement with groove for seal between discs |
    WO2012124293A1|2011-03-16|2012-09-20|川崎重工業株式会社|Multistage centrifugal compressor and turbo refrigeration machine using same|WO2018162660A1|2017-03-08|2018-09-13|Robert Bosch Gmbh|A double-stage impeller arrangement for a double-stage centrifugal turbo-compressor|JPS5722673B2|1978-12-26|1982-05-14|
    CN1042758A|1988-11-18|1990-06-06|列宁联合企业涅弗斯克工厂|Centrifugal compressor with horizontal dismountable plane|
    US6834501B1|2003-07-11|2004-12-28|Honeywell International, Inc.|Turbocharger compressor with non-axisymmetric deswirl vanes|
    US7407364B2|2005-03-01|2008-08-05|Honeywell International, Inc.|Turbocharger compressor having ported second-stage shroud, and associated method|
    US7568883B2|2005-11-30|2009-08-04|Honeywell International Inc.|Turbocharger having two-stage compressor with boreless first-stage impeller|
    IT1396885B1|2009-12-17|2012-12-20|Nuovo Pignone Spa|INTERMEDIATE GAS BEARING|
    CN202937467U|2012-11-30|2013-05-15|沈阳鼓风机集团安装检修配件有限公司|Multi-level efficient centrifugal compressor with axial air feed|
    WO2014197343A1|2013-06-06|2014-12-11|Dresser-Rand Company|Compressor having hollow shaft|
    JP2015178866A|2014-03-19|2015-10-08|株式会社豊田自動織機|turbo type fluid machine|
    US10605160B2|2014-11-17|2020-03-31|Mitsubishi Heavy Industries Engine & Turbocharger, Ltd.|Turbomachine|US10718346B2|2015-12-21|2020-07-21|General Electric Company|Apparatus for pressurizing a fluid within a turbomachine and method of operating the same|
    FR3063778A1|2017-03-08|2018-09-14|BD Kompressor GmbH|CENTRIFUGAL TURBOCHARGER|
    FR3085188B1|2018-08-22|2020-12-25|Danfoss As|A TURBOCHARGER PROVIDED WITH AN AXIAL BEARING COOLING SYSTEM|
    法律状态:
    2016-06-13| PLFP| Fee payment|Year of fee payment: 2 |
    2017-01-13| PLSC| Search report ready|Effective date: 20170113 |
    2017-06-23| PLFP| Fee payment|Year of fee payment: 3 |
    2017-07-21| TP| Transmission of property|Owner name: DANFOSS SILICON POWER GMBH, DE Effective date: 20170621 |
    2018-06-25| PLFP| Fee payment|Year of fee payment: 4 |
    2019-06-26| PLFP| Fee payment|Year of fee payment: 5 |
    2019-12-27| TP| Transmission of property|Owner name: DANFOSS A/S, DK Effective date: 20191119 |
    2020-06-25| PLFP| Fee payment|Year of fee payment: 6 |
    2021-06-24| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1556410A|FR3038665B1|2015-07-07|2015-07-07|CENTRIFUGAL COMPRESSOR HAVING INTER-STAGE SEALING ARRANGEMENT|FR1556410A| FR3038665B1|2015-07-07|2015-07-07|CENTRIFUGAL COMPRESSOR HAVING INTER-STAGE SEALING ARRANGEMENT|
    PCT/EP2016/064160| WO2017005477A1|2015-07-07|2016-06-20|A centrifugal compressor having a inter-stage arrangement|
    US15/735,301| US10619645B2|2015-07-07|2016-06-20|Centrifugal compressor having an inter-stage sealing arrangement|
    CN201680036568.6A| CN107850080B|2015-07-07|2016-06-20|Centrifugal compressor with interstage seal arrangement|
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