Assembly assembly with adjustable axial installation distance

Abstract

The utility model provides an assembling component with an adjustable axial mounting distance. The fitting assembly defines a central axis and includes: a first component and a second component coaxially positioned along the central axis, one of the first component and the second component being rotatable about the central axis relative to the other of the first component and the second component; the floating seal assembly is arranged between the first component and the second component to provide floating seal between the first component and the second component, and a floating seal gap is defined between the floating seal assembly and the first component. The second component is configured to be capable of axially moving along the central axis relative to the first component under the condition that the axial size of the floating seal gap is kept unchanged. By means of the assembling assembly with the adjustable axial installation distance, the use flexibility of the assembling assembly can be improved, the phenomenon that error gaps and even cannot be assembled is avoided, the assembling flexibility is improved, and the axial installation distance can be adjusted under the condition that the floating seal gap is kept unchanged.

Description

Technical Field

[0001] This application relates to a mechanical assembly structure, and more particularly to a mechanical assembly structure with adjustable assembly. Background Technology

[0002] In finished gearboxes, the axial installation distance between the mating spindle and the ring gear is usually fixed. This means that the axial dimensions of the tooling components using the gearbox (also known as a reducer), such as winches, are fixed after leaving the factory. During the actual installation of the winch, manufacturing and assembly tolerances are unavoidable in each component, often leading to non-compliance during assembly. For example, an undesirable (axial) error clearance may occur between the winch delivered to the site and the support frame to be assembled with, subjecting the gearbox or other components to harmful axial loads and shortening the service life of components such as bearings. More seriously, the winch's axial dimension may be too large to properly match the support frame on site. Therefore, after the winch (especially the gearbox) is assembled, it is obviously more convenient to have some adjustability in the axial installation distance between the spindle and the ring gear in the gearbox.

[0003] In the configuration of a transmission, a floating seal assembly is typically used between the spindle and the ring gear to achieve sealing. However, in existing transmissions, changes in the axial installation distance between them often alter the floating seal clearance formed by the assembly. A fixed floating clearance ensures the floating seal is in its optimal state, unaffected by adjustments to the dimensions or tolerances of other assembly components. An excessively large floating seal clearance increases the risk of oil leakage, while an excessively small clearance leads to excessive wear on the contact sealing surfaces, reducing the lifespan of the floating seal assembly and thus affecting the overall stress distribution and sealing performance of the transmission. This is clearly an undesirable situation in practical operation.

[0004] Therefore, the industry needs an assembly component with a certain degree of adjustability in axial installation distance, while this dimensional adjustment will not affect the sealing effect of the floating seal assembly, that is, it will not change the axial dimension of the floating seal gap. Utility Model Content

[0005] To achieve the above objectives, this application provides an assembly assembly with adjustable axial mounting distance.

[0006] According to one embodiment of the present invention, the assembly defines a central axis and includes: a first component and a second component coaxially positioned along the central axis, one of the first component and the second component being rotatable relative to the other about the central axis; a floating seal assembly disposed between the first component and the second component to provide a floating seal between them, and defining a floating seal gap between the floating seal assembly and the first component; wherein the second component is configured to be axially movable relative to the first component along the central axis while maintaining a constant axial dimension of the floating seal gap.

[0007] Furthermore, an actuating portion is provided on the radial side of the second component facing the first component, the actuating portion being configured to realize the axial movement of the second component relative to the first component. The actuating portion is in the form of an actuating surface extending radially from the radial side of the second component.

[0008] Furthermore, the assembly also includes a bearing configured to be axially fixed relative to the first component, the bearing having: a first bearing ring configured to be fixed relative to or integrally formed with the first component, and a second bearing ring configured to engage with the second component and to remain axially fixed as the second component moves axially relative to the first component, and to selectively abut or move away from the action surface.

[0009] According to another embodiment of the present invention, the working surface is configured as an axial sidewall of a recess (212G) extending radially from the radial side of the second component away from the central axis, the recess having an axial dimension; and at least a portion of the second bearing ring is disposed within the recess, and the at least a portion is configured to selectively abut or move away from the axial sidewall of the recess.

[0010] Alternatively, the working surface is configured as an axial sidewall of a protrusion (212P) extending radially from the radial side of the second component toward the central axis, the protrusion having an axial dimension; and the second bearing ring is configured to selectively abut or move away from the axial sidewall of the protrusion.

[0011] Furthermore, the assembly also includes a stop (R2, R3) that axially abuts against the bearing, the stop having a boss (R21, R31) extending radially outward from the central axis, the boss being configured to selectively abut and move away from the working surface axially.

[0012] According to another embodiment of the present invention, the floating seal assembly includes: two sealing members configured to axially abut against each other; and a floating seal seat configured to accommodate at least a portion of one of the two sealing members and to define the floating seal gap between the floating seal seat and the first member.

[0013] Furthermore, the floating seal seat is configured to be fixed relative to the second bearing ring. The floating seal seat (213s) is configured to be disposed on the same side of the sealing member as the second bearing ring. Alternatively, the floating seal seat (313s) is configured to be disposed on opposite sides of the sealing member as the second bearing ring, and a portion of the floating seal seat extends along the central axis through the sealing member to the second bearing ring.

[0014] According to another embodiment of the present invention, at least one of the first component and the second component is capable of rotating relative to each other about the central axis.

[0015] The axially adjustable mounting distance assembly component provided in this application expands the matching assembly range, improves the flexibility of using the mating dimensions and tolerances of other assembly components or parts, avoids the aforementioned improper error gaps or even assembly failures, and enhances assembly flexibility. Furthermore, it allows adjustment of the axial mounting distance while maintaining the floating seal gap (axial dimension) constant. In actual design and production processes, the mating tolerances of its components or parts can be increased, reducing processing costs and scrap rates. Attached Figure Description

[0016] The accompanying drawings of this application illustrate, by way of example, several embodiments of the axially adjustable mounting assembly according to this application. The embodiments shown in the drawings are merely exemplary and are not intended to limit the subject matter of this application to these embodiments. In the drawings, similar or identical reference numerals are used to refer to similar or identical elements or components. In the drawings,

[0017] Figure 1 This is an installation diagram of an assembly component based on existing technology, wherein a partial sectional view shows a portion of the structure of the assembly component to better illustrate the assembly relationship between its constituent parts.

[0018] Figure 1A It shows Figure 1 The image shown is a partial enlarged view of an assembly component according to the prior art, illustrated in cross-section.

[0019] Figure 2This is a cross-sectional view of a winch using an axially adjustable mounting assembly according to the present application, taken through its central axis CC, wherein, for the purpose of simplification, the axial dimension of the drum is shortened and the bearing assembly is omitted.

[0020] Figure 2A yes Figure 2 An enlarged view of the structure shown in box A.

[0021] Figure 2B It is similar to Figure 2A The view that shows Figure 2A Alternative embodiments of the structure shown are described.

[0022] Figure 2C Similarly Figure 2A The view that shows Figure 2A Another alternative embodiment of the structure shown.

[0023] Figure 3 It is similar to Figure 2 The view that shows Figure 2 An alternative embodiment of the structure of the winch shown.

[0024] Figure 3A yes Figure 3 An enlarged view of the structure shown in box A. Detailed Implementation

[0025] The following detailed description, in conjunction with the accompanying drawings, will be provided. It should be noted that, for the purposes of brevity and ease of understanding, the following descriptive notes focus primarily on structures relevant to the improvements of this application, and do not describe all the structures of the components or parts involved. However, this does not imply that the component or part does not have or cannot have the undescribed structures. For structures not described in detail, those skilled in the art can and readily obtain their details.

[0026] Figure 1 A schematic diagram of the assembly according to the prior art is shown. As shown in the figure, the gearbox assembly (also called the reducer) 11, shown in a partial sectional view, is bolted axially to the drum 12 (shown in blue lines) and the bearing assembly 13 (shown in yellow lines), thereby forming the winch 10. It should be noted that the blue and black dashed lines indicate that the component may have a certain axial dimension (i.e., the left-right direction shown in the figure), that is, extending axially. For the purpose of simplicity, only the structure of the two ends of the component is shown here.

[0027] After the pre-assembled winch 10 is transported to the site, it is assembled onto the support frame 14 set up on site (shown as a thick black line in the figure). Generally speaking, the axial dimension of the support frame 14 is selected according to the specific application and remains fixed once selected.

[0028] As described above, due to unavoidable machining and assembly errors in the various components 11, 12, and 13 of the winch 10, the axial dimension of the winch 10 often exhibits dimensional errors. This results in an error gap G0 between the winch 10 and the support frame 14 after the winch 10 is installed, due to the existence of axial dimensional errors. To ensure the stability of the winch 10's operation, this error gap G0 often needs to be compensated for using additional bolts AB. In more serious cases, the winch 10 may be too large to be assembled onto the support frame 14.

[0029] Therefore, it is convenient and preferred to make the axial dimension of the winch 10 (i.e., the axial mounting distance L of the gearbox assembly 11) somewhat adjustable.

[0030] In the prior art transmission assembly 11, such as Figure 1A As shown, the transmission assembly 11 includes components along the axial direction (i.e., along the central axis CC, denoted as...). Figure 2 A mandrel 111 and a ring gear 112 are coaxially fitted together. A floating seal assembly 113 is provided between them to space them axially and form a floating seal gap G1 between the mandrel 111 and the ring gear 112. The ring gear 112 is configured to rotate relative to the mandrel 111 about a central axis CC. The ring gear 112 and the mandrel 111 are radially spaced apart by bearings. Figure 1A As shown, the bearing comprises a pair of roller bearings B11 and B12. Although the use of paired roller bearings is described herein, this application is not limited thereto. As will be appreciated by those skilled in the art, other numbers and / or bearings with other configurations may be used where applicable.

[0031] The outer rings of these roller bearings are configured to rotate synchronously and at the same speed as the ring gear 112 rotates about the central axis CC, and the inner rings are configured to rotate (if present) as the spindle 111 rotates about the central axis CC. Alternatively, the inner ring can be configured to be integrally formed with the spindle 111. In other words, the bearing has only one outer ring and no separate inner ring. At least one retaining ring R1 is provided between these roller bearings, at least a portion of which (away from the central axis CC) is disposed within a groove 112G formed on the radially inner surface of the ring gear 112, and the axial dimension of the groove 112G is slightly larger than the total axial dimension of the at least one retaining ring R1 (when there is one retaining ring R1, the total axial dimension is the axial dimension of a single retaining ring R1; when there are two or more retaining rings R1, the total axial dimension is the maximum axial dimension of the axial space occupied by all retaining rings R1). As those skilled in the art will understand, the structure and axial dimension of each retaining ring R1 may vary. Although two seemingly identical annular retaining rings R1 are shown in the figure, this application does not limit the specific structure and number of retaining rings R1. This arrangement allows the annular gear 112 to move axially relative to the spindle 111 along the central axis CC. The difference between the axial dimension of the groove 112G and the total axial dimension of at least one retaining ring R determines the maximum axial displacement of the annular gear 112.

[0032] However, as Figure 1A As clearly shown, the axial movement of the ring gear 112 relative to the spindle 111 changes the axial mounting distance L of the transmission assembly 11, and inevitably alters the axial dimension of the floating seal clearance G1. This is clearly not desirable in this field. Although... Figure 1A As shown in the illustration, in this application, the axial mounting distance L is defined as the distance between two axially opposite sides of the corresponding flanges of the mandrel and the ring gear. However, this application is not limited to this, as the axial mounting distance is only intended to indicate the relative positional relationship between the mandrel and the ring gear, and it can also be defined, for example, as the distance between two axially facing sides of the corresponding flanges of the mandrel and the ring gear.

[0033] To address the issue that the axial dimension of the floating seal clearance changes with the relative positions of the spindle and the ring gear, this application makes improvements based on the aforementioned structure, as detailed below. Figure 2 and Figure 2A .in, Figure 2 This is a cross-sectional view of a winch using an axially adjustable mounting assembly according to the present application, taken through its central axis CC, wherein, for the purpose of simplification, the axial dimension of the drum is shortened and the bearing assembly is omitted. Figure 2A yes Figure 2 An enlarged view of the structure shown in box A.

[0034] See Figure 2A , and Figure 1A The differences in the structures shown are mainly in the following aspects.

[0035] exist Figure 2A In the transmission assembly 21 shown, the spindle 211 has the same structure as the spindle 111 in the transmission assembly 11, so its structure will not be described in detail here. The ring gear 212 is coaxially fitted with the spindle 211 and radially spaced apart from each other by bearings. The bearings are similar in structure to those used in the transmission assembly 11, and also include a pair of roller bearings B21 and B22. The specific structure and configuration of this pair of roller bearings will not be described in detail here. A protrusion 212P extending from its radial inner surface toward the central axis CC is provided on the radially inner side of the ring gear 212. This protrusion 212P interacts with a retaining ring R2 disposed between the roller bearings B21 and B22 to restrict the axial movement of the ring gear 212 along the central axis CC relative to the spindle 211.

[0036] Specifically, such as Figure 2A As shown, a retaining ring R2 extends a boss R21 from its radially outer side away from the central axis CC. One axial side of the boss R21 (hereinafter referred to as the working surface) is configured to abut against a first axial side of the protrusion 212P. The distance S1 between the working surface of the boss R21 and the axial side of the opposing roller bearing B21 (hereinafter referred to as the working surface, which is configured to abut against a second axial side of the protrusion 212P opposite to the first axial side) is slightly greater than the axial dimension S0 of the protrusion 212P. Thus, this arrangement allows the protrusion 212P to move axially between a first position and a second position, in which the first axial side of the protrusion 212P abuts against the working surface of the boss R21, and in the second position, in which the second axial side of the protrusion 212P abuts against the working surface of the roller bearing B21, thereby defining the maximum axial displacement of the protrusion 212P (and thus the ring gear 212) relative to the spindle 211. In this case, the maximum axial displacement is approximately equal to the axial distance S1 between the working surface of the roller bearing B21 and the working surface of the boss R21 minus the axial dimension S0 of the protrusion 212P.

[0037] although Figure 2AThe boss R21 is shown abutting against one side of the roller bearing B22. The protrusion 212P is configured to switch between abutting against the roller bearing B21 and abutting against the boss R21, but this is not limiting. For example, the boss R21 may be configured not to abut against the roller bearing B22, or it may be configured to be closer to the roller bearing B22. In the latter case, the protrusion 212P may be configured to switch between abutting against the roller bearing B22 and abutting against the boss R21 (the axial side facing the roller bearing B22).

[0038] Alternatively, although the working surfaces of the protrusion 212P, the bearing, and the boss R21 are shown as planes in the figures, they can also be curved surfaces (convex or concave), as long as the possible interaction between any two surfaces can stop the axial movement of the ring gear 212.

[0039] In the transmission assembly 21, a floating seal assembly 213 is also provided between the spindle 211 and the ring gear 212. Unlike the floating seal assembly 113 of the prior art, which includes only two sealing components, the floating seal assembly 213 in this embodiment includes two sealing components (e.g., O-rings) and a floating seal seat 213s for accommodating at least a portion of one of the sealing components in the axial direction. A floating seal gap G2 is defined between the floating seal seat 213s and the spindle 211. It is noteworthy that the formation of the floating seal gap G2 differs from the floating seal gap G1 of the prior art (which is defined by the spindle 111 and the ring gear 112). The floating seal seat 213s is positioned radially outward by a sidewall extending axially from one side of the ring gear 212, and a seal (e.g., an O-ring) is provided between them to achieve a seal. This arrangement allows the ring gear 212 to move axially relative to the floating seal seat 213s along the central axis CC, but there is no relative rotation between them about the central axis CC. In other words, once the ring gear 212 rotates around the central axis CC, it will drive the floating seal seat 213s to rotate synchronously and at the same speed. This configuration is further achieved by a bearing disposed between the spindle 211 and the ring gear 212.

[0040] like Figure 2A As shown, the axial movement of the floating seal seat 213s is restricted by the roller bearing B21, preventing it from moving axially relative to the spindle 211. This ensures that the axial dimension of the floating seal clearance G2 between the spindle 211 and the floating seal seat 213s remains constant. Preferably, the floating seal seat 213s is attached to the outer ring of the roller bearing B21 by means such as an interference fit or adhesive bonding, so that the rotational movement of the ring gear 212 can drive the outer ring of the roller bearing B21, and in turn, drive the floating seal seat 213s to rotate synchronously and at the same speed.

[0041] Similar to the structure of the prior art transmission assembly 11, the outer rings of the roller bearings B21 and B22 of the transmission assembly 21 are both configured to allow the ring gear 212 to move axially relative to the roller bearing along the central axis CC, but not to allow circumferential relative movement between them around the central axis CC (i.e., they are limited to rotating synchronously and at the same speed).

[0042] See further Figure 2B , Figure 2B It is similar to Figure 2A The view that shows Figure 2A Alternative embodiments of the structure shown are described.

[0043] and Figure 2A The structure shown is different in that, Figure 2B In the structure shown, the outer rings of roller bearings B21 and B22 have different outer diameters. The actuating portion (interacting with the bearing) of the ring gear 212 is also in the form of a protrusion 212Q extending radially inward from the ring gear 212 toward the central axis CC, and is configured to move between a first position and a second position. In the first position, the first actuating surface of the protrusion 212Q abuts against the axial side (i.e., the actuating surface) of the float seal seat 213s; in the second position, the second actuating surface of the protrusion 212Q, opposite to the first actuating surface, abuts against the axial side (i.e., the actuating surface) of the boss R21 of the retaining ring R2. The difference between the distance S2 between the actuating surface of the float seal seat 213s and the actuating surface of the boss R21 and the axial dimension S0 of the protrusion 212Q determines the maximum axial displacement of the actuating portion (i.e., the protrusion 212P) relative to the spindle 211.

[0044] although Figure 2A and Figure 2B In all cases, the retaining ring is configured to interact with an actuating portion that extends from the radial inner wall of the ring gear 212 toward the central axis CC, but this application is not limited thereto. Figure 2C As shown, the actuating part can also take the form of a recess 212G that is recessed from the radial inner wall of the ring gear 212 (i.e., extending away from the central axis CC), which can be configured to work with the boss R31 of the retaining ring R3 extending therein.

[0045] like Figure 2C As shown, gaps are formed between the two opposite axial surfaces of the boss 31 and the corresponding axial sidewalls of the recess 212G. This is preferred in some cases because this arrangement allows the axial dimension of the initially assembled winch to be increased or decreased by the axial movement of the ring gear 212 relative to the spindle 211 (that is, this change is bidirectional), thus providing greater assembly flexibility and application adaptability.

[0046] Furthermore, regarding the mating relationship between the retaining ring and the ring gear, which has protruding or recessed actuating parts, those skilled in the art can conceive of various modified structures to achieve the same function. This application does not impose any limitations on this. In other words, this stopping function is not necessarily achieved through a retaining ring disposed between the bearings.

[0047] The following is combined with Figure 3 and Figure 3A Please provide an explanation. Figure 3 It is similar to Figure 2 The view that shows Figure 2 An alternative embodiment of the winch structure shown is presented. Figure 3A yes Figure 3 An enlarged view of the structure shown in box A.

[0048] exist Figure 2-Figure 2C In the illustrated embodiment, the ring gear 212 is configured to be axially movable relative to the spindle 211 along the central axis CC. In contrast, in Figure 3 and Figure 3A In the illustrated embodiment, unlike the previous one, the spindle 311 is configured to be axially movable relative to the ring gear 312 along the central axis CC. The spindle 311 and the ring gear 312 are radially spaced apart by ball bearings B3. This application does not impose excessive limitations on the structure and arrangement of the ball bearings B3. Although the use of ball bearings is described herein, this application is not limited thereto. As will be understood by those skilled in the art, other numbers or bearings with other structures may be used where applicable.

[0049] like Figure 3A As shown, the outer ring of ball bearing B3 is attached to ring gear 312 via a mounting method such as an interference fit, thereby enabling it to rotate synchronously and at the same speed around the central axis CC without any axial relative movement between them. In other words, ring gear 312 restricts the axial movement of the outer ring of ball bearing B3, and consequently its inner ring. The inner ring of ball bearing B3 can be fitted onto spindle 311 via a method such as an transition fit, thereby enabling it to rotate synchronously and at the same speed around the central axis CC, while allowing axial relative movement between them along the central axis CC.

[0050] Furthermore, a floating seal assembly 313 is provided between the spindle 311 and the ring gear 312, which includes two sealing components and a floating seal seat 313s for accommodating at least a portion of one of the sealing components. Figure 2-Figure 2CThe illustrated embodiment differs in that a floating seal gap G3 is formed between the floating seal seat 313s and the ring gear 312 (rather than with the spindle 311). The floating seal seat 313s is positioned radially outward by a radial sidewall of the spindle 311, and a seal (e.g., an O-ring) is placed between them to achieve a seal. This arrangement allows the spindle 311 to move axially relative to the floating seal seat 313s along the central axis CC, but there is no relative rotation between them about the central axis CC. In other words, once the spindle 311 rotates about the central axis CC, it causes the floating seal seat 313s to rotate synchronously and at the same speed.

[0051] like Figure 3A As shown, a portion of the floating seal seat 313s extends axially through the sealing member of the floating seal assembly 313 to reach the inner ring of the bearing B3, and is fixed thereto by means such as an interference fit or adhesive, so that there is no axial relative movement between the floating seal seat 313s and the bearing B3 (the inner ring of the bearing). Therefore, although the spindle 311 is configured to be axially movable relative to the ring gear 312 along the central axis CC, this axial movement will not have any effect on the floating seal seat 313s (and the entire floating seal assembly 313), thereby ensuring that the size of the floating seal clearance G3 remains constant.

[0052] Alternatively, the outer ring of bearing B3 can be configured to be integrally formed with the ring gear 312. In other words, the bearing has only one inner ring and no separate outer ring.

[0053] Although the foregoing description illustrates the assembly according to this application in conjunction with specific applications such as winches and speed reducers, this application is not limited thereto. Those skilled in the art will envision a variety of other specific applications to which the assembly according to this application is applicable. Furthermore, although the ring gear is described herein as being rotatable about a central axis relative to a spindle, depending on the specific application requirements, the spindle may be configured to be rotatable about the central axis or fixed circumferentially relative to the central axis (i.e., unable to rotate about it). In other words, where applicable, at least one of the ring gear and the spindle may be configured to be rotatable about the central axis relative to the other.

[0054] Although several embodiments of this application have been described with reference to the accompanying drawings, it will be understood by those skilled in the art that various modifications can be made to the above embodiments without departing from the scope defined by the appended claims. The above embodiments are provided merely as examples to illustrate the technical solutions of this application and are not intended to limit the scope of protection of this application. Features or elements described in one embodiment may be incorporated into another embodiment unless they contradict existing features or elements in another embodiment. Furthermore, the specific wording of features and the possible use of reference numerals in the appended claims are not intended to limit the scope of protection claimed.

Claims

1. An axial mounting distance adjustable assembly, characterized by, The assembly (21, 31) defines a central axis (C-C) and comprises: a first component and a second component coaxially positioned along the central axis, one of the first and second components being rotatable relative to the other one around the central axis; a float seal assembly (213, 313) arranged between the first and second components to provide a floating seal therebetween and defining a float seal gap (G2, G3) between the float seal assembly and the first component; wherein the second component is configured to be axially movable relative to the first component along the central axis while maintaining an axial dimension of the float seal gap unchanged.

2. The assembly of claim 1, wherein, An acting portion is arranged on a radially facing side of the second component towards the first component, the acting portion being configured for effecting the axial movement of the second component relative to the first component.

3. The assembly of claim 2, wherein, The acting portion is in the form of an acting face radially extending from the radially facing side of the second component.

4. The assembly of claim 3, wherein, The assembly further comprises a bearing configured to be axially fixed relative to the first component, the bearing having: a first bearing ring configured to be fixed relative to the first component or one-piece therewith, and a second bearing ring configured to cooperate with the second component and to remain axially fixed and selectively abut against or away from the acting face with the axial movement of the second component relative to the first component.

5. The assembly of claim 4, wherein: the acting face is configured in the form of an axial side wall of a recess (212G) radially extending from the radially facing side of the second component away from the central axis, the recess having an axial dimension; and at least a portion of the second bearing ring is arranged within the recess and is configured to selectively abut against or away from the axial side wall of the recess.

6. The assembly of claim 4, wherein: the acting face is configured in the form of an axial side wall of a protrusion (212P) radially extending from the radially facing side of the second component towards the central axis, the protrusion having an axial dimension; and the second bearing ring is configured to selectively abut against or away from the axial side wall of the protrusion.

7. An assembly according to claim 5 or 6, wherein The assembly further comprises a stopper (R2, R3) arranged in axial abutment with the bearing, the stopper being provided with a boss (R21, R31) extending from a radially outer side thereof away from the central axis, the boss being configured to selectively axially abut against and away from the acting face.

8. An assembly according to any one of claims 4 to 6, wherein, The float seal assembly comprises: two seal components configured to axially abut against each other; a float seal seat configured to house at least a portion of one of the two seal components and to define the float seal gap between the float seal seat and the first component.

9. The assembly of claim 8, wherein, The float seal seat is configured to be fixed relative to the second bearing ring.

10. The assembly of claim 9, wherein, The floating seal carrier is configured to be disposed on the same side of the seal member as the second bearing race.

11. The assembly of claim 9, wherein, The floating seal carrier is configured to be disposed on opposite sides of the seal member from the second bearing race, and a portion of the floating seal carrier extends through the seal member along the central axis to the second bearing race.

12. The assembly of any of claims 1-6, wherein, At least one of the first and second components is rotatable relative to the other about the central axis.

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