Assembly with an elastically mounted bearing with an oil damper and a method of manufacturing thereof

Field of the Invention

0001This invention relates to a bearing assembly for a rotor and method for constructing the same, and, more particularly, to a bearing assembly and method involving a bearing cage that extends between the rotating member and a bearing housing.

Background Art

0002In many bearing designs of the above type, it is necessary to have a fairly precise engagement between the bearing cage and the bearing housing that will be sufficient through the range of manufacturing clearances of these components, yet will maintain a positive seal at the joint between the housing and cage. Also, it is important that the bearing geometry be controlled and that the clamping force not be high enough to cause bending or deformity.

0003<patcit id="pcit0001" dnum="EP1300600A"><text>EP 1 300 600 A</text></patcit>, an earlier application by the applicant of the present instance published after the priority date of the present application, discloses exemplary bearings related to those shown in <figref idref="f0001">Figures 1 and 2</figref> of the present instance.

0004<patcit id="pcit0002" dnum="US3473853A"><text>US 3 473 853 A</text></patcit> discloses vibration damping devices, and bearings incorporating the same, in which a hydrodynamic squeeze film is produced in a gap containing a liquid between two dished members. <b>Summary of the Invention</b>

0005According to a first aspect of the present invention, there is provided a bearing assembly for a rotor, the assembly comprising: a cage surrounding the rotor and defining a recess therein, a series of tilt pads disposed within the recess and adapted to engage the rotor, a housing surrounding the cage, and at least one axially-extending groove formed in the outer periphery of the housing and spaced radially outwardly from the inner radial surface of the housing to form a cantilevered portion extending between the groove and the corresponding surface of the cage to form a mechanical spring.

0006According to a second aspect of the present invention, there is provided a method comprising: surrounding a rotor with a cage defining a recess therein, the recess having a series of tilt pads adapted to engage the rotor, surrounding the cage with a housing, and forming at least one axially-extending groove in the outer periphery of the housing and spaced radially outwardly from the inner radial surface of the housing to form a cantilevered portion extending between the groove and the corresponding surface of the cage to form a mechanical spring.

Brief Description of the Drawings

0007To enable a better understanding of the present invention, and to show how the same may be carried into effect, reference will now be made, by way of example only, to the accompanying drawings, in which: <ul id="ul0001" list-style="none" compact="compact"><li><figref idref="f0001">Fig. 1</figref> is a cross-sectional view of an exemplary bearing assembly as described in <patcit id="pcit0003" dnum="EP1300600A"><text>EP 1 300 600 A</text></patcit> and not according to the present invention, shown in operative engagement with a rotor, which is shown in elevation.</li><li><figref idref="f0001">Fig. 2</figref> is an enlarged cross-sectional view of a portion of the bearing assembly of <figref idref="f0001">Fig. 1</figref>.</li><li><figref idref="f0002">Figs. 3 and 4</figref> are views, similar to <figref idref="f0001">Figs. 1 and 2</figref>, respectively, but depicting an embodiment of the present invention.</li><li><figref idref="f0003">Figs. 5 and 6</figref> are views, similar to <figref idref="f0001">Figs. 1 and 2</figref>, respectively, but depicting an alternate embodiment of the present invention.</li></ul>

Detailed Description

0008Referring to <figref idref="f0001">Fig. 1</figref> of the drawings, the reference numeral 10 refers in general to an exemplary bearing assembly not according to the present invention which surrounds a rotor 12. It is understood that the rotor 12 is rotated about its axis and forms part of an assembly that includes a driving system for imparting torque to the rotor, in a conventional manner.

0009An annular bearing cage 16 extends around the rotor 12 and has an internal recess formed therein for receiving a series of tilt pads 18, one of which is shown, which form the bearing members. Since the tilt pads 18 are conventional, they will not be described in detail.

0010Two axially-extending grooves 16a and 16b are formed in the outer periphery of the cage 16 with each extending for approximately 180 degrees. The grooves 16a and 16b are spaced radially inwardly from the outer radial surface of the cage 16 a predetermined amount to form cantilevered portions 16c and 16d that extend radially outwardly from the respective grooves. The thickness of each cantilevered portion 16c and 16d is such that it functions as a mechanical spring. It is understood that the thickness of each portion 16c and 16d, and therefore the stiffness of the mechanical spring formed by each portion, can be adjusted relative to the bearing stiffness of the tilt pads 18.

0011A radially-extending passage 16e is formed through the center of the cage 16 for supplying lubricating oil to the tilt pad 18, in a manner to be explained.

0012An annular housing 20 surrounds the cage 16 and has an internal annular recess 20a which communicates with the passage 16e of the cage 16 and with a radially-extending through passage 20b. Oil can thus be introduced to the passage 20b and passes through the latter passage, the recess 20a and the passage 16e for supplying oil to the tilt pads 18.

0013A majority of the radial inner surface of the housing 20 is slightly spaced from the radial outer surface of the cage 16, including the cantilevered portions 16c and 16d, to form an annular clearance C which communicates with the recess 20a of the housing 20 and thus receives some of the above-mentioned oil.

0014As better shown in <figref idref="f0001">Fig. 2</figref>, the axial end portion of the radial outer surface of each cantilevered portions 16c and 16d is enlarged as shown by the reference numeral 16f in connection with the cage portion 16c. The enlarged portions, including the portion 16f, project radially outwardly from the plane of the latter portions. Although the enlarged portion 16f is shown slightly spaced from the corresponding inner surfaces of the housing 20 in <figref idref="f0001">Fig. 1</figref> in the interest of clarity, the enlarged portions actually engage the latter surfaces in an interference fit to prevent the leakage of oil from the clearance C. Also, the axial lengths of the enlarged portions, including the portion 16f are designed to minimize contact stresses between the cage 16 and the housing 20.

0015The system 10 thus has the following advantages: <ol id="ol0001" compact="compact" ol-style=""><li>1. A relatively low clamping force acts on the bearing housing 20 to eliminate the risk of deformation and leakage.</li><li>2. No deformation of the inside of the cage 16 occurs where the tilt pads 18 contact the cage, allowing a much better control of the tilt pad bearing geometry.</li><li>3. There is less sensitivity to temperature effects on the housing 20 resulting in minimum deleterious effects on the interference fit between the enlarged portions, including portion 16f, of the cantilevered portions 16c and 16d and the corresponding surfaces of the housing 20.</li><li>4. The presence of the oil in the clearance C provides additional damping of the bearing assembly 10 in general, thus significantly increasing the damping provided to the rotor 12.</li></ol>

0016Referring to <figref idref="f0002">Fig. 3</figref>, the reference numeral 30 refers, in general, to the bearing assembly according to an embodiment of the invention. The bearing assembly 30 surrounds a rotor 32 which is rotated about its axis and forms part of an assembly that includes a driving system for imparting torque to the rotor, in a conventional manner.

0017An annular bearing cage 36 extends around the rotor 32 and has an internal recess formed therein for receiving a series of tilt pads 38, one of which is shown, which form the bearing members. Since the tilt pads 38 are conventional they will not be described in detail. A radially-extending passage 36a is formed through the center of the cage 36 for supplying lubricating oil to the tilt pad 38, in a manner to be explained.

0018An annular housing 40 surrounds the cage 36 and has an internal annular recess 40a which communicates with the passage 36a of the cage 36 and with a radially-extending through passage 40b. Oil can thus be introduced to the passage 40b and passes through the latter passage, the recess 40a and the passage 36a for supplying oil to the tilt pads 38.

0019Two axially-extending grooves 40c and 40d are formed in the outer periphery of the housing 40 and each extends for approximately 180 degrees. The grooves 40c and 40d are spaced radially outwardly from the inner radial surface of the housing 40 a predetermined amount to form cantilevered portions 40e and 40f that extend radially inwardly from the respective grooves. The thickness of each cantilevered portion 40e and 40f is such that it functions as a mechanical spring. It is understood that the thickness of each cantilevered portion 40e and 40f, and therefore the stiffness of the mechanical spring formed by each portion, can be adjusted relative to the bearing stiffness of the tilt pads 38.

0020A majority of the radial inner surface of the housing 40, including the cantilevered portions 40e and 40f, is radially spaced from the radial outer surface of the cage 36 to form an annular clearance C which communicates with the recess 40a of the housing 40 and thus receives some of the above-mentioned oil.

0021As better shown in <figref idref="f0002">Fig. 4</figref>, an axial end portion 36b of the radial outer surface of the cage 36 is enlarged so as to project radially outwardly from the plane of the latter portion. Although <figref idref="f0002">Fig. 3</figref> depicts the end portion 36b slightly spaced from the corresponding inner surfaces of the housing 40 in the interest of clarity, it actually engages the latter surfaces in an interference fit to prevent the leakage of oil from the clearance C. Also, the axial length of the enlarged end portion 36b is designed to minimize contact stresses between the cage 36 and the housing 40.

0022Thus, the embodiment of <figref idref="f0002">Figs. 3 and 4</figref> enjoys all the advantages of the examples of <figref idref="f0001">Figs. 1 and 2</figref> set forth above. A bearing assembly according to another embodiment of the invention is shown, in general by the reference numeral 50 in <figref idref="f0003">Figs. 5 and 6</figref>. As shown in <figref idref="f0003">Fig. 5</figref>, the bearing assembly 50 surrounds a rotor 52 which is rotated about its axis and forms part of an assembly that includes a driving system for imparting torque to the rotor, in a conventional manner.

0023An annular bearing cage 56 extends around the rotor 52 and has an internal recess formed therein for receiving a series of tilt pads 58, one of which is shown, which form the bearing members. Since the tilt pads 58 are conventional, they will not be described in detail.

0024Two axially-extending grooves 56a and 56b are formed in the outer periphery of the cage 56 with each extending for approximately 180 degrees. The grooves 56a and 56b are spaced radially inwardly from the outer radial surface of the cage 56 a predetermined amount to form cantilevered portions 56c and 56d that extend radially outwardly from the respective grooves. The thickness of each cantilevered portion 56c and 56d is such that it functions as a mechanical spring. The thickness of each cage portion 56c and 56d, and therefore the stiffness of the mechanical spring formed by each portion, can be adjusted relative to the bearing stiffness of the tilt pads 58.

0025A radially-extending passage 56e is formed through the center of the cage 56 for supplying lubricating oil to the tilt pad 58, in a manner to be explained.

0026An annular housing 60 surrounds the cage 56 and has an internal annular recess 60a which communicates with the passage 56e of the cage 56 and with a radially-extending through passage 60b. Oil can thus be introduced to the passage 60b and passes through the latter passage, the recess 60a, and the passage 56e for supplying oil to the tilt pads 58.

0027A majority of the radial inner surface of the housing 60 is slightly spaced from the radial outer surface of the cage 56, including the cantilevered portions 56c and 56d, to form an annular clearance C which communicates with the recess 60a of the housing 60 and thus receives some of the above-mentioned oil.

0028As better shown In <figref idref="f0003">Fig. 6</figref>, the axial end portion of the radial outer surface of each cantilevered portions 56c and 56d is enlarged as shown by the reference numeral 56f in connection with the cage portion 56c. The enlarged portions, including the portion 56f, project radially outwardly from the plane of the latter portions and engages the corresponding inner surfaces of the housing 60 in an interference fit. Although the enlarged portions, including the portion 56f, are shown slightly spaced from the corresponding inner surfaces of the housing 60 in <figref idref="f0003">Figs. 5 and 6</figref> in the interest of clarity, they actually engage the latter surfaces in an interference fit to prevent the leakage of oil from the clearance C. Also, the axial lengths of the enlarged portions, including the portion 56f, are designed to minimize contact stresses between the cage 56 and the housing 60.

0029Two axially-extending grooves 60c and 60d are formed in the outer periphery of the housing 60 and each extends for approximately 180 degrees. The grooves 60c and 60d are spaced radially outwardly from the inner radial surface of the housing 60 a predetermined amount to form cantilevered portions 60e and 60f that extend radially inwardly from the respective grooves. The thickness of each cantilevered portion 60e and 60f is such that it functions as a mechanical spring. The thickness of each cantilevered portion 60e and 60f, and therefore the stiffness of the mechanical spring formed by each portion, can be adjusted relative to the bearing stiffness of the tilt pads 58.

0030Thus, the embodiment of <figref idref="f0003">Figs. 5 and 6</figref> enjoys all the advantages of the example of <figref idref="f0001">Figs. 1 and 2</figref>, and the embodiment of <figref idref="f0002">Figs. 3 and 4</figref>.

0031It is understood that variations may be made in each of the above embodiments without departing from the scope of the invention. For example, the number of angularly-spaced grooves formed in the cage and the housing in each of the above embodiments can vary and, in fact, there can be only one groove that is continuous in an angular direction. Also, the radial and axial lengths of the cage portions, including the enlarged portions, can vary from those shown in the drawings. Also, the sealing between the housings and their respective cages can be done by other means than metal-to-metal contact as shown on the drawings. Further, the cages and/or the housings can be formed by two split arcuate sections that are attached at their respective ends, in a conventional manner.

0032Since other modifications, changes, and substitutions are intended in the foregoing disclosure, it is appropriate that the scope of the invention be construed broadly and in a manner consistent with the appended claims.