A mechanism for suspending a head slider of a recording apparatus

Abstract: A suspension mechanism of a recording disk apparatus has a head slider mounted on a portion of a load beam (30) in the vicinity of the free end of the load beam through a gimbal spring (31). The gimbal spring has a central leg portion (35) and two side leg portions (33, 34), all of which are formed in parallel. The head slider is adhered to the top surface of the central leg portion (35) which is lifted from the side leg portions. A protrusion (42) formed on the load beam or on the central leg portion serves to transfer loading force generated by the load beam to the head slider by a universal joint connection. The gimbal spring is mounted on the load beam such that the longitudinal direction of the central leg portion is normal to the seek direction of the head slider.

Description: BACKGROUND OF THE INVENTION Field of the Invention The present invention relates to a recording apparatus such as a magnetic recording apparatus or an optical recording apparatus, each having airbearing head sliders (hereinafter simply referred to as a head slider) which is flexibly suspended by a suspension mechanism, carrying a magnetic or an optical transducer over a rotating disk with a constant spacing therebetween. Particularly, the invention relates to an improvement in a spring member of the suspension mechanism, usually referred to as a gimbal spring, for flexibly mounting the head slider on a load beam of the suspension mechanism. Prior Art As is widely known, in a magnetic or an optical recording apparatus, a magnetic or an optical transducer is carried by a head slider which is suspended by a suspension mechanism fixed to a rigid arm of a head positioner such that the transducer is controllably displaced over a rotating magnetic disk to access a target track of the disk. This is referred to as a seek operation, and the direction in which the head slider is transferred is referred to as a seek direction. Naturally, the seek direction is approximately radial with respect to the magnetic disk. The suspension mechanism comprises a head slide, a load beam and a gimbal spring. The head slider is mounted through the gimbal spring on the free end portion of the load beam which is secured to a rigid arm of the related head positioner at the other end portion. Before proceeding further, a brief survey is provided regarding various types of relative arrangement between the head positioner and the suspension mechanism, with respect to a seek direction of the head slider. Fig. 1 is a schematic plan view illustrting three types - A, B and C- of positional relationships or the relative arrangements between each head positioner and the relevant suspension mechanism with respect to a disk rotating around its center Q. The arrangement A is known as a linear type. A rigid arm 2 of a head positioner 1 is moved forward and rearward, namely reciprocally, in a seek direction 3 shown by a double arrow, thereby displacing a load beam and a head slider in the seek direction 3 with respect to a disk 12. The arrangement B is known as a swivelling type. A head positioner 4 is rotatable clockwise and counter-clockwise,(as shown by a sagittated arc) swivelling an arm 5. Thus, the head slider, which is suspended by a load beam 13, is displaced over the disk 12 along an arc, i.e. in a seek direction 6. The principal axis of the load beam 13 is in this case normal to that of the arm 5. The arrangement C is also referred to as of swivelling type. A head positioner 8 is rotatable clockwise and counter-clockwise, swivelling an arm 7 and a load beam 9. Thus the head slider 10 is displaced in a seek direction 11 relative to the disk 12, with the longitudinal lines of the load beam 9 and the arm 7 aligned. As is apparent from the figure, the seek directions 3, 6 and 11 are approximately along a radial direction of the magnetic disk 12. The linear type arrangement A requires a wide space and a to-and-fro motion of the head positioner, and consequently does not lend itself to a miniaturization of the associated structure. Arrangements B and C, therefore, are preferable for a compact type magnetic disk apparatus. However, the swivelling head positioner 4 of type B needs a relatively long arm 5, which tends to increase the rotational inertial moment of the arm 5, thereby adversely affecting high speed operation of the magnetic disk apparatus. Consequently, the current trend is now towards positioner 8 of the arrangement C for compact and high speed magnetic disk apparatus. The present invention essentially relates to mechanism for a head slider used in a head positioner of the arrangement C. A suspension mechanism for a head slider will now be described. The head slider is flexibly supported by a suspension mechanism. A typical suspension mechanism, referred to as a Whitney type suspension mechanism, is disclosed in the U.S. Patent, Serial N°. 3.931.641, published on Jan. 6, 1976, and N°. 4.167.765, published on Sept. 11, 1979, both issued to Watrous. The latter suspension mechanisms have a combined load beam comprising a holding section, a resilient spring section and a substantially rigid section connected to the spring section at one end. At the other end of the rigid section of the load beam, there is fixed a substantially rectangular flexture having a central finger. A head slider is fixed to the central finger, engaging with a rotating magnetic disk with a predetermined spacing therebetween. The spacing is maintained by balancing aerodynamic force provided by an air flow caused by the rotating disk with the resilient force loaded by the relevant load beam. The above described Whitney type is also referred to as a Watrous type, and the flexture is usually referred to as a gimbal spring. Fig. 2(a) and Fig. 2(b) respectively show a partial plan view and a side view of a Whitney type suspension mechanism. The whole structure of the suspension mechanism is as described above. A spring member 21, henceforth referred to as a gimbal spring, is welded to the end portion of both sides flanged rigid portion 20 of the associated load beam at four points 23 located at a supporting portion 21a of the gimbal spring 21. A magnetic transducer 22 (illustrated with chain lines) is fixed to a tongue-like or finger-like central section 21b of the gimbal spring 21. As can be seen from Fig. 2(a), the central section 21b is connected to a cross leg supported in a cantilever suspension, and extending in the longitudinal direction of the load beam. When the head slider 22 is moved in a seek direction shown by arrow 25, i.e. in the direction of the longitudinal center line of the load beam, or in the longitudinal direction of the central section 21b, the mechanical vibration characteristics of the gimbal spring 21 enhances the stability of the seek operation of the head slider 22. But when the seek operation is in a direction 26 normal to the direction 25, or normal to the longitudinal line of the central section 21b, the mechanical vibration characteristics are considerably unfavorable. This is basically attributed to a low resonant frequency of the gimbal spring 21 in the seek direction 26. The gimbal spring 21 should be designed to have a high resonant frequency in the seek direction since, in general, a low frequency resonant vibration of the gimbal spring 21 is accompanied by a rather larger vibration amplitude, and conversely a high frequency resonant vibration is accompanied by a favorably smaller amplitude. The applicant has performed a computer simulation with regard to mechanical vibration applied to a gimbal spring, and from which were produced diagrams representing vibration mode of the various types of gimbal springs. Fig. 3 is a diagram representing a simulated vibration mode of the gimbal spring of Fig. 2(a) in a seek direction 25 that is in parallel with the longitudinal direction of the central section 21b. The resonant frequency is approximately 37 kHz, which is sufficiently high to obtain a stable floating movement of the head slider 21 over the rotating disk in a seek direction. Fig. 4 is a diagram of the same in a seek direction 26 which is normal to the longitudinal direction of the central section 21b. The resonant frequency is approximately 5 kHz, which is unfavorably low and causes an unstable seek operation of the head slider 21. In both diagrams, small circles denote the points over the simulated gimbal spring deformed by vibration, and underlying dotted figure denotes original positions of the corresponding points of the gimbal spring subjected to no vibration. Points 27 and 28 indicate the locations where the central section is fixed to a load beam and to a head slider respectively. Consequently, the gimbal spring 21 of Fig. 2(a) is applicable to a suspension mechanism of a recording apparatus having a swivelling head positioner disposed as in the arrangement B shown in Fig. 1, whereby a stable movement of the head slider in floating during a seek operation is assured since the seek direction 6 corresponds to the direction 25 of Fig. 2(a). On the other hand, the gimbal spring 21 is not applicable to the suspension mechanism of the arrangement C, since the head slider is, in this case, displaced in the direction 11 corresponding to direction 26 of Fig. 2(a). As previously described, arrangement C is the most suitable for a compact and high speed magnetic recording apparatus. An improved gimbal spring suitable for seek operation in all directions has been needed in the art. Of course, it may be considered that the problem of unstable movement of the head slider during the seek operation might be solved by horizontally turning the direction of the gimbal spring 21 shown in Fig. 2(a) through a right angle with respect to the load beam 20. However, this idea is not practical on account of the small area of a portion of the load beam 20 in the vicinity of the free end of the load beam 20 and the resulting asymmetrical structure of the load beam-gimbal spring assembly. An example of a simplified head suspension mechanism is disclosed in IBM Technical Disclosure Bulletin Vol. 30, N°. 2, July 1987, pages 766-768. The mechanism uses separate resilient structures for providing the pitch and rolling displacements of the head. The attention here is to overcome applied moments to the head about its roll axis during data access displacements, by having that axis pass through - or even below - the head's center of gravity. SUMMARY OF THE INVENTION An object of the present invention is to provide an improved head slider suspension mechanism for accessing tracks of a rotating disk of a compact and high speed recording disk apparatus. Another object of the present invention is to provide a head slider suspension mechanism having a gimbal spring through which a transducer is displaced as it is flexibly lifted over the cooperating rotating disk by the suspension mechanism during seeking operations of the head slider. Still another object of the present invention is to provide a head slider suspension mechanism having an improved gimbal spring carrying a head slider which allows a relatively easy and stable pitching and rolling movements of the head slider, particularly in the seek operation of the head slider. Still another object of the present invention is to provide an improved suspension mechanism for a recording disk apparatus in which the transducer is easily and accurately mounted on a gimbal spring, reducing associated manufacturing costs. A more particular object of the present invention is to provide a gimbal spring featuring good high mechanical resonant frequency in the inherent seek direction of the head slider, so enabling the head slider to perform a stable and exact seek operation with allowable small pitching and rolling movements. The above objects are achieved by a suspension mechanism as defined in claim 1. BRIEF DESCRIPTIONS OF THE DRAWINGS The advantages and features of the present invention will be apparent upon reading of the following descriptions and claims with reference to drawings wherein, like reference numerals denote like parts, and: Fig. 1 is a schematic plan view illustrating positional relationships of the arrangements of three tyes A, B and C between each head positioner and the relevant suspension mechanism with respect to a disk 12, Fig. 2(a) and Fig 2(b) are respectively a partial plan view and a partial side view, illustrating the structure of a Whitney type suspension mechanism, Fig. 3 is a diagram representing the vibration mode of the gimbal spring of Fig. 2(a) moved in the longitudinal direction of the relevant load beam, Fig. 4 is a diagram representing the vibration mode of the gimbal spring of Fig. 2(a) moved in the lateral direction, Fig. 5 is a partial plan view of a suspension mechanism of the present invention illustrating a gimbal spring mounted on a load beam, Fig. 6 is a cross-sectional side view of the suspension mechanism of Fig. 5 taken along a line X-X shown in Fig. 5, Fig. 7 is a partial perspective view of the suspension mechanism of Fig. 5, Fig. 8 is a cross-sectional view of the suspension mechanism of Fig. 5, taken along a line Y-Y shown in Fig. 5, Fig. 9 is a diagram representing the vibration mode of the gimbal spring of Fig. 5 which is moved in the longitudinal direction of the central leg portion of the gimbal spring, obtained by a computer simulation, Fig. 10 and Fig. 11 are substantially schematic cross-sectional views of the head slider of Fig. 5, taken along the line X-X, illustrating the rolling movements in opposite sides of the head slider, Fig. 12 is a substantially schematic cross-sectional view of the head slider of Fig. 5, taken along the line Y-Y, illustrating the pitching movement of the head slider, Fig. 13 is a diagram representing the vibration mode of the gimbal spring of Fig. 5 moved in another direction, Fig. 14 is a partial plan view of a suspension mechanism of the modified embodiment illustrating a gimbal spring and the assembly relationship thereof between a head slider and a load beam, Fig. 15 is a cross-sectional side view of the suspension mechanism of Fig. 14, taken along a line Z-Z shown in Fig. 14, Fig. 16 is a plan view of a modified gimbal spring having a rounded gimbal form, and Fig. 17 is a cross-sectional side view of another modified gimbal spring. DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment according to the present invention is described with reference to drawings of Fig. 5 to Fig. 8. The arrangement of a suspension mechanism and a head positioner of the embodiment is of the type C described hereabove. Fig. 5 is a partial plan view of a suspension mechanism of the embodiment, illustrating a gimbal spring mounted on a load beam. Fig. 6 is a cross-sectional side view of the suspension mechanism of Fig. 5, taken along a line X-X shown in Fig. 5. Fig. 7 is a partial perspective view of the suspension mechanism of Fig. 5. Fig. 8 is a cross-sectional view of the suspension mechanism of Fig. 5, taken along a line Y-Y shown in Fig. 5. The seek direction of the head slider 32 is shown by an arrow 44 which is parallel with the line Y-Y. A head slider 32 shown with chain lines, is carried by a gimbal spring 31 mounted on the free end portion of a load beam 30 which has a relatively rigid structure by virtue of flanged portions at both sides thereof. As shown in the plan view of Fig. 5, the gimbal spring 31 comprises a first side leg portion 33 with projecting portion, forming a mounting tab 38, a second side leg portion 34 with another mounting tab 39, a raised central leg portion 35, and two cross leg portions 35 and 36. The first and second side leg portions 33 and 34, are located on both sides of the central leg portion 35. The three leg portions, 33, 34 and 35, are disposed in parallel, being spatially separated from each other by two slits 43, and being connected to each other at the opposite ends of the three leg portions 33, 34 and 35 by the transversing cross leg portions 36 and 37, thereby forming a gimbal spring 31. As will be readily understood from Fig. 6 and Fig. 7, the side leg portions 33 and 34, and the mounting tabs 38 and 39 lie on the same base plane F. The central leg portion 35 is supported at both ends thereof by the cross leg portions 36 and 37, lying on a plane elevated from the base plane F by a step difference s. Both cross leg portions 36 and 37 respectively have folded raised portions 36a and 37a normal to the base plane F of the gimbal spring 31 to elevate the central leg portion 35. In addition, portions 36a and 37a serve to reduce the width B of the whole gimbal spring 31 without degrading the flexing function that would otherwise be provided by a gimbal spring plate formed in a flat plane by extending the gimbal spring 31. The gimbal spring 31 is made of a resilient metal foil, such as stainless steel foil having a thickness of approximately 30 microns. Typical dimensions of the gimbal spring shown in Fig. 7, given as a non-limiting example, are as follows: longitudidinal length A - approximately 5mm, lateral length B - approximately 1.5mm, width W₁ of the central leg portion 35 - approximately 0.6mm and width W₂ of the cross leg portions 36 and 37 - approximately 0.5mm. The load beam 30 has an upraised dimple 42 and an aligning hole 30a in a portion adjacent to the free end thereof. Both are located on the longitudinal center line of the load beam 30. The mounting tab 38 has also an aligning hole 38a having the same inner diameter as that of the hole 30a. The gimbal spring 31 is fixed to the end portion of the load beam 30 by welding the mounting tabs 38 and 39 to the top surface of the load beam 30 at, e.g. five points 40 and e.g. three points 41 as shown in Fig. 5 and Fig. 6. In this way, the position of the gimbal spring 31 relative to the load beam 30, in the longitudinal direction thereof, is precisely obtained by aligning the hole 38a of the mounting tab 38 with the hole 30a of the load beam 30. The mounting tabs 38 and 39 have sufficient spot welding areas to enable the gimbal spring 31 to be easily and securely spot welded to the load beam 30. On the top surface of the load beam 30, in the vicinity of the free end thereof, a pivot-like raised dimple 42 or a load protrusion 42 is pressed thereinto as shown in Fig. 5, Fig. 6 and Fig. 8. The dimple 42 is formed on the longitudinal center line X-X of the load beam 30. The height of the dimple typically ranges from 10 to 100 microns. The dimple 42 is located such that, when the gimbal spring 31 is mounted on the load beam 30 by spot welding, the dimple 42 becomes inserted in the space underneath the central leg portion 35 and the tip of the dimple 42 comes into contact with the rear surface of the central leg portion 35 at a point 0, which is exactly centered with respect to the opposite cross leg portions 36 and 37. In cases where the height of the dimple 42 is larger than the step difference s between the base plane F of the gimbal spring 31 and the top surface of the central leg portion 35, the central leg portion 35 and those parts of the side leg portions 33 and 34 that freely extend from the portion secured to the load beam 30 may be warped in opposite directions, concave to each other, so as to form a slightly ellipsoidal profile, as exaggeratedly shown in Fig. 8. In cases where the height of the dimple 42 is smaller than the step difference s, then a small space gap may be present between the dimple 42 and the rear surface of the central leg portion 35. Both cases are envisageable for flexibly suspending the head slider 32 over a rotating disk by virtue of the flexible structure of the suspension mechanism, and in particularly that of the gimbal spring 31. Preferably the height of the dimple 42 and the step difference s are made to coincide. As shown in Fig. 8, the head slider 32 is mounted on the top surface of the central leg portion 35 by adhering the bottom surface of the head slider 32 to the top surface of the central leg portion 35, e.g. with a chemical adhesive material 49. The center of gravity of the head slider 32 is normally aligned with the contact point 0. Even if the top surface of the central leg portion 35 is warped convexly, forming small clearances between the top surface of the central leg portion 35 and the bottom surface of the head slider 32, these clearances can be easily filled in with the adhesive material. Thus the head slider 32 is steadily mounted on the central leg portion 25 of the gimbal spring 31. A conventional adhesive such as a thermoplastic adhesive may be used. The step difference s between the base plane F of the gimbal spring 31 and the central leg portion 35 facilitates precise mounting of the head slider 32 to the gimbal spring 31. With the above-described structure of the suspension mechanism of the recording disk apparatus, resilient force is loaded to the head slider 31. The force is applied to the surface of a recording disk employed in the apparatus when the disk is stationary. When the disk is in rotation, the resilient loading force is balanced with an aerodynamic force caused by running air flow adjacent to the surface of the rotating disk. As a result, the head slider 32 is lifted over the disk with a predetermined spacing. As previously described, the resilient loading force is generated by the resilient section of the load beam 30, being transferred to the head slider 32 through a universal joint connection formed at the point 10 between the dimple 42 and the rear surface of the central leg portion 35 of the gimbal spring 31. The universal joint connection provides freedom of action of the slider for rolling and pitching thereof in an airbearing operation of the head slider 32. Consequently, the loading force is applied through the single contact point 0 at the center of the central leg portion 35 of the gimbal spring 31. The central leg portion 35 is supported at both of its ends by the cross leg portions 36 and 37. From a mechanical aspect, it is to be noted that most of the welding points 40 and 41, namely fixing points of the gimbal spring 31 to the load beam 30, and the contact point 0, namely the loading point 0, are located on the line X-X which is directed normal to the seek direction 44, and that the welding points 40 and 41 are located at both sides of the loading point 0. The longitudinal direction of the central leg portion 35 to which the head slider 32 is mounted, coincides with the seek direction 44, and the central leg portion 35 are elevated from the base plane F of the gimbal spring 31 and supported at both ends thereof. Fig. 9 is a computer simulation diagram representing the vibration mode of a gimbal spring, the dimensions of which are the same as those of the gimbal spring 31 of Fig. 5, where the seek direction 44 is taken in the longitudinal direction of the central leg portion 35. In the diagram, the points 45 and 46 represent the fixing points of the gimbal spring 31 to the load beam 30, and point 47 represents the fixing point of the head slider 32 to the gimbal spring 31. According to the simulation, the resonant frequency is shown to be approximately 38 kHz, i.e. sufficiently high. As can be seen from the diagram, each side leg portion is fixed at an area extending between three points 46. Such adhesion between the side leg portions, 33 and 34, and the surface of the load beam 30 is only possible in a simulation, since the adhesion cannot be achieved by spot welding. However, it is found by the computer simulation that the above-described adhesion of the simulation preferable, to obtain a higher resonant frequency of the gimbal spring 31. In practice, the tabs 38 and 39 for extending the welding area are usable for spot welding. Thus, the suspension mechanism of the embodiment is useful for a compact recording disk apparatus having a suspension mechanism of the arrangement of type C and a high speed seek operation. Fig. 10 and Fig. 11 are substantially schematic cross-sectional views of the head slider 32 taken along the line Y-Y shown in Fig. 5, illustrating a rolling movement of the head slider 32 in a rolling direction R during a seek operation in the seek direction 44. The rectangular figures of chained lines in the drawings represent the normal position of the head slider 32. The head slider 32 is slightly rotated counter-clockwise in Fig. 10, and clockwise in Fig. 11. Fig. 12 is a substantially schematic cross-sectional view of the head slider 32, taken along the line X-X of Fig. 5, illustrating a pitching movement of the head slider 32 in a pitching direction P during a seek operation performed in the direction 44. The head slider 32 is slightly rotated clockwise in this figure. This rolling movement and the pitching movement of the head slider 31 around the dimple 42 are effectively damped by a resisting force provided by the gimbal spring 31. The resisting force is caused by bending or torsional stress in the leg portions of the gimbal 31 corresponding to the movement of the head slider 32. Fig. 13 is a computer simulation diagram representing the vibration mode of the gimbal spring 31 of Fig. 5. In the simulation, the seek direction 48 is taken in a direction X-X normal to the longitudinal direction of the central leg portion 35. In the diagram, the points 45, 46 and 47 represent the same fixing points as those of Fig. 9. The resonant frequency in the seek direction 48 is approximately 10kHz, i.e. suitably higher than the 5 kHz of the previously described gimbal spring of prior art, implying some possible application to a suspension mechanism movable in the seek direction 48 normal to the longitudinal direction of the central leg portion 35. In the following, a modified embodiment is disclosed. Fig. 14 is a partial plan view of a suspension mechanism of the modified embodiment illustrating the assembly relationship between a gimbal spring, a head slider 32 and a load beam 30, wherein the longitudinal direction of the head slider 32 and the gimbal spring 33 is rotated by a right angle as compared with that of Fig. 5. Fig. 15 is a cross-sectional side view of the suspension mechanism of Fig. 14, taken along a line Z-Z shown in Fig. 14. The line Z-Z coincides with the longitudinal center line of a load beam 30 and that of a central leg portion 35 of a gimbal spring 31A. Naturally, the suspension mechanism of this type is applied to a recording disk apparatus having a swivelling head positioner of the type B arrangement. Thus the seek direction 49 coincides with the direction of the longitudinal center line of the load beam 30, while the seek direction 44 of the suspension mechanism of Fig. 5 is normal to the longitudinal center line of the load beam 30. In order to mount the gimbal spring 31A on the load beam 30, the length of a mounting tab 34A is shortened to reduce the whole width L of the gimbal spring 31A so as to adapt to the short width of the load beam 30. Fig. 16 is a plan view of a modified gimbal spring 31B. The gimbal spring need not be rectangular when seen from the top. The gimbal spring 31B has a rounded shape and comprises a central leg portion 35B, and side leg portions 33B and 34B, as shown in Fig. 16. Another form can be adopted for simlifying manufacture of the gimbal spring and its assembly to the load beam. A loading protrusion may be formed on a gimbal spring instead of a load beam. Fig. 17 is a cross-sectional side view of a modified gimbal spring 31C taken along the longitudinal center of its central leg portion 35C. The loading protrusion 42C is formed in the substantially central portion of the central leg portion 31C, and is in contact with the top surface of a load beam 30C at a loading point 0 in the vicinity of the free end of the load beam 30C, when the gimbal spring 31C is mounted on the load beam 30C.

Claims: A suspension mechanism for a suspending a transducer over a rotating recording disk with a predetermined spacing therebetween, said suspension mechanism comprising: a load beam (30) having a holding section, a resilient section (7) and a rigid section (30) connected to each other in the recited order, said load beam being secured to said rigid arm at said holding section; a head slider (32) for carrying said transducer, and a gimbal spring (31) fixed to a portion of said rigid section of said load beam in the vicinity of the free end of said load beam, characterized in that said gimbal spring (31) comprises: i) a central leaf spring (35) longitudinally extending substantially in the seek direction and having a top surface on which said head slider (32) is adhered, ii) side leaf springs (33, 34) located in parallel with and and at opposite sides with respect to said central leaf spring (35), central portions of said side leaf springs being fixed to said rigid beam at fixing points (40, 41); and iii) folded legs (36, 37) joining each longitudinal end of said central leaf spring (35) with the respective longitudinal ends of said side leaf springs (33, 34), and raising said central leaf spring from said side leaf springs; a load protrusion (42, 42c) extending in a space between said rigid section of the load beam and a bottom surface of said central leaf spring, opposite said top surface on which said head slider (31) is carried, said load protrusion being located substantially along a center line of said head slider, said fixing points (40, 41) and said protrusion (42) being substantially aligned at a normal to or along the seek direction so that said head slider can effect pitching and rolling movements about said protrusion, and in that said head slider (32) is adhered at said top surface of said central leaf spring (35). The suspension mechanism of claim 1, wherein said gimbal spring (31) is formed as a monolithic member. The suspension mechanism of claim 1, further comprising mounting tab means (38, 39) extending outwardly from central portions of said side leaf springs (34, 35) for fixing said gimbal (31) to said rigid section of the load beam (30). The suspension mechanism of claim 3, wherein said mounting tab means comprise two mounting tabs (38, 39) extending from respecitve side leaf springs at either side of said central leaf spring (35). The suspension mechanism of claim 3, wherein said fixing points (40, 41) are located on and on either side of the axis (X-X′) passing through the the contact point (O) of said protrusion (42). The suspension mechanism of claim 1, wherein the zone delimited by said mounting points (40, 41) has a width dimension that is parallel to, and relatively small in comparison with the length dimension of said gimbal (31) so as to allow said side leaf springs (33, 34) to bend. The suspension mechanism of claim 1, wherein the height of said protrusion (42) is higher than the step difference of said central leaf spring (35) from said side leaf springs (34, 35). The suspension mechanism of claim 1, wherein the height of said protrusion (42) is substantially equal to the step difference of said central leaf spring (35) from said side leaf springs (34, 35). A suspension mechanism of claim 1, characterized in that said gimbal spring (31) is made of a plate of resilient material having uniform thickness. A suspension mechanism of claim 1, characterized in that the longitudinal direction of said central leg portion (35) is normal to the substantially longitudinal center line of said load beam. A suspsension mechanism of claim 1, characterized in that said head slider (32) is adhered to the top surface of said central leg portion (35) using adhesive material.

Inventors: OHWE TAKESHI, TAKAHASHI MINORU SHINJO KOPORA, YONEOKA SEIJI, OHWE, TAKESHI, TAKAHASHI, MINORU SHINJO KOPORASU 405, 21-20, YONEOKA, SEIJI
Applicants: FUJITSU LTD, FUJITSU LIMITED
Application year: 1989
Main classification: G11B5
IPC codes: G11B21, G11B5