WATER PUMP FACE SEAL ASSEMBLY

Abstract: A water pump face seal assembly (10) uses a wave spring (28) stamped from flat stock with drive tabs (54,56) which, besides providing contact force and wear take-up, also serves to maintain a square, concentric contact interface and to transfer torque with almost no lost-motion, isolating a joint between an elastomeric seal (30) and a seal casing (24) from twisting stress.

Description: Background of the Invention This invention relates to face seal assemblies in general as specified in the preamble of claim 1, for example as disclosed in US-A-4,451,049. Specifically it relates to such an assembly intended for use in a vehicle water pump. Vehicle water pumps have an impeller drive shaft that extends through a generally circular opening in a housing filled with cooling fluid. The annular gap created between the shaft and housing opening must be sealed against leakage. A primary seal face is fixed to either the housing opening or to the outer surface of the shaft, with a contact surface that is normal to the shaft axis. The face seal assembly has a mounting member, typically a metal sleeve, that is installed to the other of the housing opening or the outer surface of the shaft, and a secondary seal face that contacts the primary seal face and rotates relative to it. Therefore, the face seal assembly has two basic interfaces that must be kept fluid-tight, the installation interface and the seal face contact interface. There is no relative rotation at the installation interface, so it is relatively easy to maintain it fluid-tight. However, the contact interface involves very rapid relative rotation, besides being exposed to a hot, corrosive fluid and a high degree of abrasive grit, and has historically proved difficult to seal. The need to retain coolant is such that a high degree of seal torque has been acceptable at the contact interface in return for maintaining the integrity of the seal. Seal integrity at the contact interface is generally maintained by an axially-resilient spring that forces the primary and secondary seal faces strongly and continually together. The spring also provides axial wear take-up at the contact interface. Wear take-up, in turn, requires a degree of relative axial movement with time between the secondary seal face and the mounting member, so they cannot be axially fixed relative to one another. Generally, an axially-flexible sealing member has been used to provide the relative axial motion needed for wear take-up. The flexible sealing member is usually formed from an elastomeric material, and is often referred to as a bellows or a boot. The addition of the flexible sealing member to the assembly creates other potential problems that must be dealt with. Since the secondary seal face is not rigidly, directly joined to the mounting member, some means must be provided to mechanically transfer torque between the mounting member and the secondary seal face whilst still allowing the necessary relative axial motion to occur between the two. Any such torque transfer means almost inevitably involves some degree of circumferential lost motion. The flexible sealing member is generally not a good candidate for the torque transfer function, because it is flexible, and would wind up and be stressed. The addition of the flexible sealing member also creates two more interfaces that must be kept fluid-tight, one with the secondary sealing face, and one with the mounting member. The first of these interfaces is generally no problem, as the secondary seal face can be fairly easily embedded in a thick portion of the elastomeric sealing member. The interface between the mounting member and the elastomeric sealing member is more difficult, and bears the brunt of the twisting stress inherent in the torque transfer. This has prompted some seal designs to actually provide an extra, sliding seal at that interface to absorb the lost motion. Another potential problem caused by interposing a flexible sealing member between the mounting member and the secondary seal face is that it is more difficult to maintain radial concentricity between the two, which affects seal wear and efficiency. Despite the plethora of competing designs available both commercially and on paper, those skilled in the art will generally agree that state of the art water pump seal integrity and life leave ample room for improvement. Summary of the Invention A face seal assembly according to the present invention is characterised by the features specified in the characterising portion of claim 1. The invention provides a vehicle water pump face seal assembly of simple design and few components in which the various components co-operate to transfer torque efficiently and to maintain the integrity and alignment of the various interfaces, thereby giving a long-lasting and effective seal. In the preferred embodiment disclosed, a first seal casing includes a central mounting sleeve that press-fits in a fluid-tight manner to the shaft and an annular wall extending radially out from one end of the sleeve across a continuous fold of generally U-shaped cross-section. The wall terminates in a co-axial cylindrical flange that is axially slotted at three evenly-spaced locations. A second seal casing has a generally cylindrical skirt that surrounds the first casing sleeve. An annular wall that axially faces the first casing annular wall extends radially in from the skirt, terminating in a co-axial cylindrical flange that is also axially slotted at three evenly-spaced locations and which is diagonally opposed to the first casing flange. The diameters of the cylindrical flanges differ by a predetermined amount. An axially-resilient wave-spring is stamped out of flat stock with a width almost equal to the diameter difference between the casing flanges. Given its width, the spring is torsionally stiff, despite its axial resilience. The spring has three complete convolutions, giving six evenly-circumferentially-spaced flats, three on each axial side of the space envelope occupied by the spring. The opposed casing walls act as stop surfaces, compressing the spring between them, which in turn are biased apart by the flats of the spring. The spring fits very closely between the flanges, maintaining the casings nearly coaxial to one another. Each spring flat also includes a drive tab that fits very closely within a respective casing flange slot, thereby interlocking the casings mechanically so that torque can be transferred between them with little lost motion. Completing the assembly is an elastomeric sealing member, which has a radially inner central sleeve portion and a thickened, annular front ring in which a secondary seal face is embedded. The front of the elastomer sealing member fits closely within the second casing skirt and wall. The end of the sleeve portion is crimped tightly into the fold of the first casing, creating a fluid-tight interface and retaining the casings together as a unit. After installation, the compressed spring maintains the contacting seal faces fluid-tight as well as substantially square to the shaft axis and co-axial thereto, minimizing wear. The torsional stiffness of the spring assures that torque is transferred from the first casing to the second with little lost motion or wind-up of the sealing member, isolating the crimp joint from stress and maintaining its fluid-tightness. Thus, all the components of the seal co-operate to give a smooth-running and long-lasting unit. It is, therefore, a general object of the invention to provide a water pump face seal assembly of simple construction, in which a small number of components co-operate to give improved operation and life. It is another object of the invention to provide such a seal assembly by using a torsionally-stiff wave-spring that interlocks a pair of casings in such a way as to transfer torque with little lost motion, thereby isolating a fluid-tight joint between one seal casing and an elastomeric sealing member from stress. It is yet another object of the invention to provide such an assembly in which the wave-spring is formed of flat stock with a width that fits closely between a pair of radially-opposed cylindrical flanges on the casings, thereby keeping them square and co-axial to one another and to the pump shaft. It is still another object of the invention to provide such an assembly in which the end of a sleeve portion of the elastomeric seal member is crimped to one of the casings so as to retain the casings together prior to installation, whilst also providing a fluid-tight joint after installation that is isolated from twisting stress by the torsionally-stiff wave-spring. Description of the Preferred Embodiment These and other objects and features of the invention will appear from the following written description, and from the drawings, in which: Figure 1 is a cross-sectional view of a preferred embodiment of the invention after installation, showing a portion of a shaft and housing opening; Figure 2 is a sectional view taken along the line 2-2 of Figure 1; Figure 3 is an exploded perspective view of two casings and a spring of the invention prior to assembly. Referring first to Figure 1, a preferred embodiment of a face seal assembly of the invention is indicated generally at 10. Assembly 10 is used in conjunction with a water pump housing 12 and a rotatable water pump shaft 14 that extends through a circular opening 16 in housing 12. More specifically, shaft 14 extends through a ceramic primary seal face 18 mounted fluid-tight within opening 16 by a retainer 20, thereby creating an annular space 22 that must be sealed. Shaft 14 would be supported for co-axial rotation by a bearing fixed to the housing 12, not illustrated. Seal assembly 10 is installed to and turns with shaft 14, in a manner more fully described below. It should be understood, however, that primary seal face 18 could instead be fixed to shaft 14, whilst seal assembly 10 could be installed in housing opening 16, with suitable changes in size, of course. The version disclosed is felt to be most practical, however, as the primary seal face 18 is thereby exposed on one side to ambient temperatures, so that it can run cooler and is more accessible. The four basic components of the assembly 10 are a first casing, indicated generally at 24, a second casing surrounding it and indicated generally at 26, a wave-spring indicated generally at 28, and an elastomeric sealing member indicated generally at 30. Details of these four components will be next described. Referring next to Figures 1 and 3, first casing 24 is integrally stamped from sheet-steel with a central mounting sleeve 32 sized so as to make a tight press-fit with the outer surface of shaft 14, thus serving as a mounting member. An annular wall 34 normal to the axis of sleeve 32 is integral to the outside of a continuous cylindrical fold 36 of generally U-shaped cross-section at the left end of sleeve 32 as seen in Figure 1. It will be noted by comparing Figure 3 to Figure 1 that the inner surface of fold 36 is straight prior to assembly, but is deformed out on its inner surface at 38 after assembly, for a purpose described below. Annular wall 34 terminates in a co-axial cylindrical flange 40 that extends axially to the right as seen in Figure 1 and which is axially slotted at three evenly-spaced locations 42. The fold 36 is sufficiently rigid that when sleeve 32 is installed on shaft 14, wall 34 is maintained perpendicular to the axis of shaft 14, and flange 40 is kept co-axial to shaft 14. Still referring to Figures 1 and 3, second casing 26 is also integrally stamped of sheet-steel, with a generally cylindrical skirt 44 that surrounds sleeve 32. An annular wall 46 integral with skirt 44 terminates in a co-axial cylindrical flange 48 of smaller diameter than flange 40 that extends axially opposite to flange 48. Flange 48 is also axially slotted at three evenly-spaced locations 50. At the installation position of Figure 1, the annular walls 34 and 46 are axially opposed to one another, while the flanges 40 and 48 are diagonally opposed with a predetermined radial spacing equal to half their diameter difference. Wave spring 28 is stamped from flat spring-steel stock with a width that is close to that radial spacing. Given its width, spring 28 is torsionally stiff, but is axially resilient, with three complete convolutions that create six evenly, circumferentially-spaced flats 52, three on each axial side. Each flat 52 has an integral square tab, three inner tabs 54, and three outer tabs 56 altogether. Tabs 54 and 56 each have a width just less than the widths of slots 42 and 50 respectively. The final component of assembly 10, elastomeric sealing member 30, is moulded with a central sleeve portion 58 and a thicker ring 60 at the front in which a secondary seal face 62 is firmly embedded. These four basic components co-operate to give an easily-assembled unit with improved operation, as will be next described. Referring next to Figures 1 and 2, to assemble the components, ring 60 is pressed into skirt 44, fitting tightly enough to prevent relative rotation therebetween. Then outer spring tabs 56 are fitted within first casing slots 42, and the second casing wall 46 is moved co-axially towards the first casing wall 34 and twisted as necessary until the spring inner tabs 54 enter the slots 50, which mechanically interlocks the walls 34 and 46. This is continued until the end of sleeve 58 enters the casing fold 36 as far as possible, compressing spring 28. The walls 34 and 46 are held in that position temporarily manually, or by a suitable jig, with no tension on the sleeve 58, until the fold 36 can be deformed radially outwards at 38 with a suitable tool, such as an arbor press. First casing wall 34, since it lies in a plane normal to the axis of sleeve 32 and is nearly axialy aligned with fold 36, acts to significantly radially stiffen the outside of fold 36 during this step, so that it need not be backed up or supported. Once fold 36 is deformed outwards at 38, as best seen in Figure 1, the end of elastomeric sleeve 58 will be mechanically locked to first casing 24, fluid-tight within fold 36. Then the holding force on the opposed casing walls 34 and 46 can be released, whereupon spring 28 can expand between the stop surfaces provided by the opposed walls 34 and 46. Spring 28 will expand until elastomeric sleeve 58 is taut. The assembly 10 thus effectively becomes one unit as sleeve 58 cannot be easily pulled from the crimped fold 36. If desired, the primary seal face 18 and its retainer 20 can be further united to the assembly 10 by turning the right end of sleeve 32 outwards, as shown at 64. To install the assembly 10, it is pushed axially into the annular space 22 along with the retainer 20. Retainer 20 and primary seal face 18 are pushed in slightly farther, so that sleeve 58 goes from tension to slight compression, creating a slight bulge shown at 66. Bulge 66 rests inside second casing flange 48, and so is protected from contact with any sharp edges of the spring 28. Referring next to Figure 1, after installation, the seal assembly 10 rotates one to one with shaft 14. There is enough area in contact between the inner surface of sleeve 32 and the outer surface of shaft 14 that the installation interface they form is fluid-tight. Spring 28 maintains the contact interface between the seal faces 18 and 62 fluid-tight. There is a good deal of area in contact between the spring flats 52 and the inner surfaces of the opposed casing walls 34 and 46, more so than would be the case with a spring formed of round wire or a flat stock spring of lesser width. As a consequence, the second casing 26 is very stably supported against tilting off-axis relative to first casing 24, and the secondary sealing face 62 is thereby kept perpendicular to the axis of shaft 14. This helps to decrease wear at the contact interface. Another consequence of the width of spring 28 is that the inner and outer edges of the spring flats 52, as well a small portion of spring 28 to either side of each flat 52, rests within the diagonally-opposed flanges 40 and 48 with a very little radial clearance. Therefore, second casing 26 cannot move eccentrically relative to first casing 24 to any great degree, nor can the contacting seal faces 18 and 62, which also serves to reduce wear. Referring next to Figure 2, it will be noted that the spring tabs 54 and 56 rest within their respective casing slots 42 and 50 with a very small clearance. The clearance is enough that the spring 28 can expand axially without binding to compensate for wear at the contact face, but the casings 24 and 26 will not be able to twist relative to one another to any appreciable degree. Thus, torque is transferred from the sleeve 32 to the second casing 26 very efficiently, with little lost motion. This prevents any significant twisting stress at the juncture between the elastomeric sleeve 58 and fold 36, keeping that interface fluid-tight. Thus, despite the small number and simplicity of the components, there is a high degree of co-operation between and amongst them, contributing to improved and lengthened operation of the water pump face seal assembly. Variations of the preferred embodiment disclosed could be made. As already mentioned, the seal assembly 10 and primary seal face 18 could be reversed. A narrower wave spring, even one formed from round stock that did not fit as closely between the flanges 40 and 48, would still be torsionally stiffer than a coil spring, for example. Thus, it would still act as an efficient means to transfer torque between the first and second casings, protecting the juncture between the elastomeric sealing member and the first casing. However, making the wave spring 28 from flat stock with the width shown adds an extra level of co-operation between the components in terms of concentricity control and in terms of controlling the contact interface. A different type of joint between the sealing member and the first casing could be used, such as adhesive. The crimped fold 36 shown is very simple, practical, and convenient to form, however, and serves to unite the various components without jeopardizing their relative alignment and concentricity.

Claims: A face seal assembly (10) for sealing a generally annular space (22) formed between an opening (16) in a fluid-filled housing (12) and an outer surface of a rotatable cylindrical shaft (14) that extends through said opening (16), said face seal assembly (10) comprising: a primary seal face (18) adapted to be fixed to one of said fluid housing opening (16) and said shaft outer surface; a first casing (24) having a cylindrical sleeve (32) sized to fit non-turnably and fluid-tight to the other of said fluid housing opening (16) and shaft outer surface and also having a stop surface (34) fixed to said sleeve (32) facing in one axial direction; a second casing (26) surrounding said first casing sleeve (32) including a stop surface (46) axially opposed to said first casing stop surface (34); a spring (28) which is compressed between said first and second casing stop surfaces (34,46) so as to bias them axially apart; and an elastomeric sealing member (30) having a first portion (58) joined fluid-tight to said first casing (24) and a second portion (60) that is non-turnably held inside said second casing (26) and which holds a secondary seal face (62) resiliently pressed against said primary seal face (18) under the bias of said spring; characterised in that said spring (28) is an axially-resilient wave spring that is torsionally stiff, and said wave spring (28) is mechanically interlocked with said first casing (24) and with said second casing (26) so as to efficiently transmit torque from said first casing (24) to said second casing (26) with substantially no lost motion by virtue of the torsional stiffness of said spring (28), so that said annular space (22) is completely sealed relative to said fluid-filled housing (12), and the sealing juncture of said first portion (58) of the elastomeric sealing member (30) and said first casing (24) is substantially isolated from stress by virtue of the efficient transmission of torque by said wave spring (28). A face seal assembly according to claim 1, characterised in that said first casing (24) also has a wall extending radially out from said sleeve (32) generally normal to the axis of said sleeve (32), which wall constitutes said stop surface (34), and which terminates in a cylindrical flange (40) extending therefrom in one axial direction; said second casing (26) has a generally cylindrical skirt (44) and a wall extending radially inwardly from said skirt (44) generally normal to the axis of said skirt (44), which wall constitutes said stop surface (46), and which terminates in a cylindrical flange (48) which extends therefrom in the opposite axial direction to said cylindrical flange (40) of the first casing (24) and is of lesser diameter than said cylindrical flange (40) of the first casing (24), and said wave spring (28) is an axially-resilient, generally annular wave spring that is formed of flat stock with a width substantially equal to half the difference in diameters between said casing flanges (40,48), and which therefore will fit closely between said cylindrical flanges (40,48) when it is compressed between said casing walls (34,46) to bias them apart, the close fit of said wave spring between said casing flanges (40,48) maintaining said casings substantially co-axial to one another. A face seal assembly according to claim 1, characterised in that said first casing (24) has an integral wall extending radially out from said sleeve (32) generally normal to the axis of said sleeve (32) which is joined to said sleeve (32) at a fold (36) of generally U-shaped cross-section, which wall constitutes said stop surface (34); said second casing (26) has a generally cylindrical skirt (44) and a wall extending radially inwards from said skirt (44) generally normal to the axis of said skirt (44), which wall constitutes said stop surface (46); said first portion (58) of the elastomeric sealing member (30) is crimped tightly into said first casing fold (36) so as to provide a fluid-tight juncture and so as to retain said sealing member (30) to said first casing (24), and said second portion of the elastomeric sealing member (30) is a radially outer portion that is non-turnably held inside said second casing skirt (44) and wall (46) and which holds said secondary seal face (62) therein.

Inventors: BAKER, STEVEN FOSTER, TENGOWSKI, JOSEPH LEONARD
Applicants: GENERAL MOTORS CORPORATION
Application year: 1989
Main classification: F16J15
IPC codes: F16J15