CA2229239A1 - Suspension having reduced torsional mode gain and sensitivity - Google Patents
Suspension having reduced torsional mode gain and sensitivity Download PDFInfo
- Publication number
- CA2229239A1 CA2229239A1 CA002229239A CA2229239A CA2229239A1 CA 2229239 A1 CA2229239 A1 CA 2229239A1 CA 002229239 A CA002229239 A CA 002229239A CA 2229239 A CA2229239 A CA 2229239A CA 2229239 A1 CA2229239 A1 CA 2229239A1
- Authority
- CA
- Canada
- Prior art keywords
- suspension
- loadbeam
- flexure
- disk
- gain
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Classifications
-
- G—PHYSICS
- G11—INFORMATION STORAGE
- G11B—INFORMATION STORAGE BASED ON RELATIVE MOVEMENT BETWEEN RECORD CARRIER AND TRANSDUCER
- G11B21/00—Head arrangements not specific to the method of recording or reproducing
- G11B21/16—Supporting the heads; Supporting the sockets for plug-in heads
- G11B21/20—Supporting the heads; Supporting the sockets for plug-in heads while the head is in operative position but stationary or permitting minor movements to follow irregularities in surface of record carrier
- G11B21/21—Supporting the heads; Supporting the sockets for plug-in heads while the head is in operative position but stationary or permitting minor movements to follow irregularities in surface of record carrier with provision for maintaining desired spacing of head from record carrier, e.g. fluid-dynamic spacing, slider
-
- G—PHYSICS
- G11—INFORMATION STORAGE
- G11B—INFORMATION STORAGE BASED ON RELATIVE MOVEMENT BETWEEN RECORD CARRIER AND TRANSDUCER
- G11B5/00—Recording by magnetisation or demagnetisation of a record carrier; Reproducing by magnetic means; Record carriers therefor
- G11B5/48—Disposition or mounting of heads or head supports relative to record carriers ; arrangements of heads, e.g. for scanning the record carrier to increase the relative speed
- G11B5/4806—Disposition or mounting of heads or head supports relative to record carriers ; arrangements of heads, e.g. for scanning the record carrier to increase the relative speed specially adapted for disk drive assemblies, e.g. assembly prior to operation, hard or flexible disk drives
- G11B5/4833—Structure of the arm assembly, e.g. load beams, flexures, parts of the arm adapted for controlling vertical force on the head
Landscapes
- Supporting Of Heads In Record-Carrier Devices (AREA)
Abstract
An improved suspension for supporting a read/write head adjacent to a relatively moving storage medium in a disk drive is disclosed. The suspension includes a curved loadbeam or a curved flexure that reduces the magnitude of the gain in the first torsion resonant mode of oscillation when the Z-height of the loadbeam is configured for minimum sensitivity of the first torsion gain as a function the loadbeam Z-height, thereby providing a suspension capable of providing improved head position servo performance and improved manufacturing and assembly yields.
Description
SUSPENSION
HAVING REDUCED TORSIONAL MODE
GAIN AND SENSITIVITY
Field of the Invention This invention relates generally to a suspension for supporting a read/write head adjacent to a relatively moving recording medium in a disk drive. More particularly, the invention relates to a suspension including a structural member configured with a controlled curvature to reduce both the gain of torsional mode oscillations and the sensitivity of the torsional mode gain to certain suspension manufacturing variations.
Background The disk drive industry is extremely competitive and therefore, disk drive demand tends to be characterized by a high sensitivity to price per unit storage capacity. To achieve high data storage capacities within a particular disk drive package, multiple disk platters are typically mounted concentrically to a spindle 2 0 motor and operated in conjunction with a set of ganged heads, each of which is supported on a gimbal structure which forms a part of a suspension member (hereinafter, "suspension") The suspensions, in turn, are mounted to rigid actuator arms which are 2 5 connected to a common, rotatable structure typically known as an E-block.
The E-block is attached to a voice coil motor structure to form a mass-balanced, closed-loop servo positioning, rotary actuator structure capable of selectively positioning the ganged heads at various radial locations or tracks relative to the disks. Since the suspensions form a part of the mechanical 3 0 structure within the servo loop, the dynamic characteristics of the suspensions can limit the achievable servo system performance.
Copending U.S. Application Serial No. 08/249,525 entitled METHOD
FOR CHARACTERIZING AND CONTROLLING IN-PLANE STIFFNESS OF
DRIVE, the disclosure of which is hereby incorporated by reference, teaches 1.
that the spring and loadbeam of a suspension can be geometrically configured such that the first torsional resonance mode has a minimum or optimum sensitivity of gain with respect to handling and manufacturing tolerances.
Specifically, the sensitivity of the first torsion gain can be reduced by S controlling the Z-axis height of the end of load beam region adjacent to the spring. By thus reducing the sensitivity of the gain to manufacturing processes, the manufacturing yields of load beam fabrication and headstack assembly operations, for example, can be dramatically improved. This reduced gain sensitivity does not imply that the magnitude of the gain itself is reduced, however, thus such suspensions may not show improved absolute performance, notwithstanding the improvement in the consistency of the performance.
Thus a hitherto unresolved need exists for a suspension which exhibits 1 5 reduced first torsional gain sensitivity to manufacturing processes while concurrently providing a reduced nominal magnitude of gain to facilitate improved servo system performance.
Summary of the Invention A general object of the present invention is to provide a suspension for supporting a readiwrite head in a disk drive which overcomes limitations and drawbacks of the prior art.
2 5 A more specific object of the present invention is to provide a suspension for a disk drive that exhibits reduced nominal gain in the first torsional mode of oscillation.
Yet another object of the present invention is to provide a suspension 3 0 that achieves lower nominal gain at the point of minimum gain sensitivity.
An additional obj ect of the invention is to provide a suspension including a load beam or flexure having an imparted or optimized curvature to reduce the nominal gain at the point of minimum gain sensitivity.
An additional object of the present invention is to provide a method for manufacturing a suspension having a loadbeam and flexure combination which provide lower nominal first torsional gain at the point of minimum gain sensitivity.
These and other objects of the invention are realized in a fixed disk drive head and disk assembly including a data storage disk rotating at a predetermined angular velocity relative to a baseplate structure (i.e., a base), and an in-line rotary actuator structure rotatably mounted to the base and including an in-line head mounting structure or suspension for supporting and moving a read/write head at different radial locations relative to the disk, thereby defining a plurality of distinct data tracks in which information is ultimately recorded. In accordance with the present invention, the disk drive includes an improved suspension structure which includes a gimbaled flexure 1 5 attached to the distal end of a cantilevered, elongated loadbeam having rail type stiffeners. The loadbeam is connected to a leaf spring section which is supported by a mounting region located at the cantilevered end of the suspension. The leaf spring section may be pre-bent so that when the heads are mounted in the drive, the suspension is deflected to a generally straight 2 0 condition to allow for even closer disk to disk spacing. The loadbeam has a curvature, either directly formed during manufacture or imparted via the flexure mounting scheme, which reduces the nominal first torsion gain of the suspension at the point of lowest gain sensitivity.
2 S These and other objects, advantages, aspects, and features of the present invention will be more fully appreciated and understood upon consideration of the following detailed descriptions of a preferred embodiment presented in conjunction with the accompanying drawings.
3 0 Brief Description of the Drawing, In the Drawings:
FIG. 1 is a diagrammatic trimetric view of a prior art Type 8 head gimbal assembly (HGA).
FIG. 2 is a diagrammatic side elevation of a prior art Type 8 HGA.
FIG. 3 is a diagrammatic side elevation of an HGA having an imparted negative sag in the loadbeam in accordance with the principles of the present invention.
FIG. 4 is a side elevation of the distal end of an HGA in accordance with an alternative embodiment of the present invention.
FIG. S is a graph showing the results of finite element modeling wherein the maximum peak first torsion resonance gain (normalized at 1 kHz) is plotted as a function of suspension offset for various loadbeam and flexure configurations.
Detailed Descn_ption Figure 1 shows a conventional prior art head-gimbal-assembly (HGA) 10 which includes a "Type 8" suspension 12 and a supported read/write head 14.
Suspension 12 consists of a rigid planar baseplate 16, which may include an integral swaging boss 18 for mounting the suspension to an actuator ann (not shown), a spring section 20, a loadbeam 22, and gimbaled flexure 24 which is 2 0 attached to the distal, unsupported end of the suspension for pivotably supporting read/write head 14. Loadbeam 22 typically includes a pair of rails 26 along the lateral edges to stiffen the loadbeam structure. The configuration of rails 26 influences the resonant frequencies of HGA 10, hence rails 26 are typically designed to improve servo system performance by moving the 2 5 resonant frequencies of HGA 10 higher (to improve servo bandwidth) and away from the servo sampling frequency or its aliased variants.
FIG. 2 shows a side view of the HGA shown in FIG. 1. Flexure 24 of FIG. 1 has been omitted for clarity. Loadbeam 22 is conventionally 3 0 manufactured and operated in a nominally flat state, however, as the rails are formed, there is an induced stress that causes the resultant loadbeam to bow somewhat. Spot welding operations may also affect loadbeam flatness due to localized annealing or recrystallization. For an uprail loadbeam design such as that shown in FIGS. 1 and 2, the fabrication induced beam bow 3 S typically causes the center of the loadbeam to be elevated, relative to the ends, on the order of 1 mil. FIG. 5, curve S0, shows a graph of the dynamic behavior of the nominally flat load beam of FIG.2 operating in conjunction with a conventionally mounted flexure. The curve 50 shows the maximum peak first torsion resonance gain (with respect to 0 dB at 1 kHz) as a function of the imparted suspension offset. Thus the HGA 10 of FIG.2 should be manufactured such that its loadbeam base is offset by -0.025 mm along the Z-axis in order to minimize the sensitivity of the first torsion gain (because the rate of change of the gain with respect to the offset is approximately zero at -0.025 mm offset). Although this operating point is not the point of lowest gain it nonetheless results in the least sensitivity of the gain and since manufacturing and assembly operations tend to re-adjust suspension offset, the selected operating point is likely to provide significantly better manufacturing yields than, for example, the offsets where a local minimum gain is achieved, because very slight variations in offset at the local minima tend to lead to dramatic and undesirable increases in first torsion gain. The selected operating point not only minimizes the variation in gain but also effectively defines an upper bound for the gain so that slight deviations from the optimum point may actually result in somewhat better mechanical performance.
FIG. 3 shows a side elevation of an HGA 30 in accordance with a 2 0 preferred embodiment of the present invention. In this embodiment of the present invention, the suspension 31 has an overall length in the longitudinal direction of about 20-30 millimeters and a transverse width on the order of about 5 millimeters at the widest region of the suspension which is typically at or near the mounting end of the suspension. The main suspension body 2 5 member is chemically etched from flat stainless steel sheet having a thickness on the order of about 60-75 microns. The etching operation defines the regions that will ultimately comprise the mounting area 32, spring 34, load beam 36, and rails 38.
3 0 After the suspension body member is etched, mechanical forming operations are employed to impart features generally perpendicular to the major surfaces of loadbeam 3 6, in this case, a laterally spaced apart pair of upswept rails 38. Also, during the mechanical forming operation, the loadbeam 36 is imparted with a slight negative curvature (i.e., negative "sag" with a radius of 3 5 curvature of about 236 mm) such that the central portion of the load beam is ultimately positioned about 3 mils closer to the disk than would be the case with a flat loadbeam. It should be noted that direction of the imparted curvature or sag (in accordance with the present invention) is opposite that which would normally occur during conventional uprail loadbeam fabrication.
Additionally, the magnitude of the imparted sag is about three times that which tends to occur during normal loadbeam fabrication.
A separately fabricated load plate 39 is typically turned or formed in a progressive die operation and is attached to suspension 31 via conventional means, e.g., spot welding. Similarly, a flexure (not shown) is conventionally 1 0 spot welded or otherwise affixed to the underside of the loadbeam 36 to complete suspension 31. Read/write head 40 is attached to the flexure to finish the fabrication of an HGA 30 in accordance with a preferred embodiment of the invention.
FIG. 5, curve 52, shows the first torsion gain of suspension 31 shown in FIG. 3 as a function of the imparted suspension offset. The optimal operating point of the sagged loadbeam embodiment of the present is about 3 dB lower in first torsion gain than a conventional Type 8 suspension.
2 0 FIG. 4 discloses an alternative preferred embodiment of an HGA 42 in accordance with the present invention. In this embodiment the loadbeam 43 is manufactured conventionally in a generally flat configuration, except that a protrusive feature 44 of about 0.08 mm height is manufactured onto either loadbeam 43 (or alternatively, on flexure 45) and is positioned between 2 5 loadbeam 43 and flexure 45 intermediate the longitudinal ends of flexure 45.
Flexure 45 is spot welded or otherwise affixed to the loadbeam at bonding points 46 at the proximal end of the flexure and at the location of the protrusive feature 44, which results in a curved flexure structure for supporting head 47.
It is believed that this flexure attachment scheme imparts a degree of negative 3 0 sag to loadbeam 43. Although this curved flexure embodiment results in somewhat higher nominal gain than the curved loadbeam embodiment, this embodiment may be easier to implement while still providing about a 2 dB first torsion gain reduction relative to a convention Type 8 suspension, as shown in curve 54 of FIG. 5.
s In summary, the instant invention provides a suspension for an actuator in a disk drive that concurrently provides both reduced first torsion gain and reduced first torsion gain sensitivity relative to prior art suspensions. The reduced first torsion gain improves potential head position servo system performance while the decreased gain sensitivity improves manufacturing yields. Thus the present invention facilitates the design and fabrication of cheaper and higher performance disk drives.
Although the present invention has been described in terms of the presently preferred embodiments, it should be understood that the instant disclosure is not to be interpreted as limiting. Various alterations and modifications will no doubt become apparent to those skilled in the art after having read the above disclosure. For example, although the present disclosure is presented in the context of uprail type suspension designs, the teachings are also applicable to downrail designs. Accordingly, it is intended that the appended claims be interpreted as covering all alterations and modifications as fall within the true spirit and scope of the invention.
HAVING REDUCED TORSIONAL MODE
GAIN AND SENSITIVITY
Field of the Invention This invention relates generally to a suspension for supporting a read/write head adjacent to a relatively moving recording medium in a disk drive. More particularly, the invention relates to a suspension including a structural member configured with a controlled curvature to reduce both the gain of torsional mode oscillations and the sensitivity of the torsional mode gain to certain suspension manufacturing variations.
Background The disk drive industry is extremely competitive and therefore, disk drive demand tends to be characterized by a high sensitivity to price per unit storage capacity. To achieve high data storage capacities within a particular disk drive package, multiple disk platters are typically mounted concentrically to a spindle 2 0 motor and operated in conjunction with a set of ganged heads, each of which is supported on a gimbal structure which forms a part of a suspension member (hereinafter, "suspension") The suspensions, in turn, are mounted to rigid actuator arms which are 2 5 connected to a common, rotatable structure typically known as an E-block.
The E-block is attached to a voice coil motor structure to form a mass-balanced, closed-loop servo positioning, rotary actuator structure capable of selectively positioning the ganged heads at various radial locations or tracks relative to the disks. Since the suspensions form a part of the mechanical 3 0 structure within the servo loop, the dynamic characteristics of the suspensions can limit the achievable servo system performance.
Copending U.S. Application Serial No. 08/249,525 entitled METHOD
FOR CHARACTERIZING AND CONTROLLING IN-PLANE STIFFNESS OF
DRIVE, the disclosure of which is hereby incorporated by reference, teaches 1.
that the spring and loadbeam of a suspension can be geometrically configured such that the first torsional resonance mode has a minimum or optimum sensitivity of gain with respect to handling and manufacturing tolerances.
Specifically, the sensitivity of the first torsion gain can be reduced by S controlling the Z-axis height of the end of load beam region adjacent to the spring. By thus reducing the sensitivity of the gain to manufacturing processes, the manufacturing yields of load beam fabrication and headstack assembly operations, for example, can be dramatically improved. This reduced gain sensitivity does not imply that the magnitude of the gain itself is reduced, however, thus such suspensions may not show improved absolute performance, notwithstanding the improvement in the consistency of the performance.
Thus a hitherto unresolved need exists for a suspension which exhibits 1 5 reduced first torsional gain sensitivity to manufacturing processes while concurrently providing a reduced nominal magnitude of gain to facilitate improved servo system performance.
Summary of the Invention A general object of the present invention is to provide a suspension for supporting a readiwrite head in a disk drive which overcomes limitations and drawbacks of the prior art.
2 5 A more specific object of the present invention is to provide a suspension for a disk drive that exhibits reduced nominal gain in the first torsional mode of oscillation.
Yet another object of the present invention is to provide a suspension 3 0 that achieves lower nominal gain at the point of minimum gain sensitivity.
An additional obj ect of the invention is to provide a suspension including a load beam or flexure having an imparted or optimized curvature to reduce the nominal gain at the point of minimum gain sensitivity.
An additional object of the present invention is to provide a method for manufacturing a suspension having a loadbeam and flexure combination which provide lower nominal first torsional gain at the point of minimum gain sensitivity.
These and other objects of the invention are realized in a fixed disk drive head and disk assembly including a data storage disk rotating at a predetermined angular velocity relative to a baseplate structure (i.e., a base), and an in-line rotary actuator structure rotatably mounted to the base and including an in-line head mounting structure or suspension for supporting and moving a read/write head at different radial locations relative to the disk, thereby defining a plurality of distinct data tracks in which information is ultimately recorded. In accordance with the present invention, the disk drive includes an improved suspension structure which includes a gimbaled flexure 1 5 attached to the distal end of a cantilevered, elongated loadbeam having rail type stiffeners. The loadbeam is connected to a leaf spring section which is supported by a mounting region located at the cantilevered end of the suspension. The leaf spring section may be pre-bent so that when the heads are mounted in the drive, the suspension is deflected to a generally straight 2 0 condition to allow for even closer disk to disk spacing. The loadbeam has a curvature, either directly formed during manufacture or imparted via the flexure mounting scheme, which reduces the nominal first torsion gain of the suspension at the point of lowest gain sensitivity.
2 S These and other objects, advantages, aspects, and features of the present invention will be more fully appreciated and understood upon consideration of the following detailed descriptions of a preferred embodiment presented in conjunction with the accompanying drawings.
3 0 Brief Description of the Drawing, In the Drawings:
FIG. 1 is a diagrammatic trimetric view of a prior art Type 8 head gimbal assembly (HGA).
FIG. 2 is a diagrammatic side elevation of a prior art Type 8 HGA.
FIG. 3 is a diagrammatic side elevation of an HGA having an imparted negative sag in the loadbeam in accordance with the principles of the present invention.
FIG. 4 is a side elevation of the distal end of an HGA in accordance with an alternative embodiment of the present invention.
FIG. S is a graph showing the results of finite element modeling wherein the maximum peak first torsion resonance gain (normalized at 1 kHz) is plotted as a function of suspension offset for various loadbeam and flexure configurations.
Detailed Descn_ption Figure 1 shows a conventional prior art head-gimbal-assembly (HGA) 10 which includes a "Type 8" suspension 12 and a supported read/write head 14.
Suspension 12 consists of a rigid planar baseplate 16, which may include an integral swaging boss 18 for mounting the suspension to an actuator ann (not shown), a spring section 20, a loadbeam 22, and gimbaled flexure 24 which is 2 0 attached to the distal, unsupported end of the suspension for pivotably supporting read/write head 14. Loadbeam 22 typically includes a pair of rails 26 along the lateral edges to stiffen the loadbeam structure. The configuration of rails 26 influences the resonant frequencies of HGA 10, hence rails 26 are typically designed to improve servo system performance by moving the 2 5 resonant frequencies of HGA 10 higher (to improve servo bandwidth) and away from the servo sampling frequency or its aliased variants.
FIG. 2 shows a side view of the HGA shown in FIG. 1. Flexure 24 of FIG. 1 has been omitted for clarity. Loadbeam 22 is conventionally 3 0 manufactured and operated in a nominally flat state, however, as the rails are formed, there is an induced stress that causes the resultant loadbeam to bow somewhat. Spot welding operations may also affect loadbeam flatness due to localized annealing or recrystallization. For an uprail loadbeam design such as that shown in FIGS. 1 and 2, the fabrication induced beam bow 3 S typically causes the center of the loadbeam to be elevated, relative to the ends, on the order of 1 mil. FIG. 5, curve S0, shows a graph of the dynamic behavior of the nominally flat load beam of FIG.2 operating in conjunction with a conventionally mounted flexure. The curve 50 shows the maximum peak first torsion resonance gain (with respect to 0 dB at 1 kHz) as a function of the imparted suspension offset. Thus the HGA 10 of FIG.2 should be manufactured such that its loadbeam base is offset by -0.025 mm along the Z-axis in order to minimize the sensitivity of the first torsion gain (because the rate of change of the gain with respect to the offset is approximately zero at -0.025 mm offset). Although this operating point is not the point of lowest gain it nonetheless results in the least sensitivity of the gain and since manufacturing and assembly operations tend to re-adjust suspension offset, the selected operating point is likely to provide significantly better manufacturing yields than, for example, the offsets where a local minimum gain is achieved, because very slight variations in offset at the local minima tend to lead to dramatic and undesirable increases in first torsion gain. The selected operating point not only minimizes the variation in gain but also effectively defines an upper bound for the gain so that slight deviations from the optimum point may actually result in somewhat better mechanical performance.
FIG. 3 shows a side elevation of an HGA 30 in accordance with a 2 0 preferred embodiment of the present invention. In this embodiment of the present invention, the suspension 31 has an overall length in the longitudinal direction of about 20-30 millimeters and a transverse width on the order of about 5 millimeters at the widest region of the suspension which is typically at or near the mounting end of the suspension. The main suspension body 2 5 member is chemically etched from flat stainless steel sheet having a thickness on the order of about 60-75 microns. The etching operation defines the regions that will ultimately comprise the mounting area 32, spring 34, load beam 36, and rails 38.
3 0 After the suspension body member is etched, mechanical forming operations are employed to impart features generally perpendicular to the major surfaces of loadbeam 3 6, in this case, a laterally spaced apart pair of upswept rails 38. Also, during the mechanical forming operation, the loadbeam 36 is imparted with a slight negative curvature (i.e., negative "sag" with a radius of 3 5 curvature of about 236 mm) such that the central portion of the load beam is ultimately positioned about 3 mils closer to the disk than would be the case with a flat loadbeam. It should be noted that direction of the imparted curvature or sag (in accordance with the present invention) is opposite that which would normally occur during conventional uprail loadbeam fabrication.
Additionally, the magnitude of the imparted sag is about three times that which tends to occur during normal loadbeam fabrication.
A separately fabricated load plate 39 is typically turned or formed in a progressive die operation and is attached to suspension 31 via conventional means, e.g., spot welding. Similarly, a flexure (not shown) is conventionally 1 0 spot welded or otherwise affixed to the underside of the loadbeam 36 to complete suspension 31. Read/write head 40 is attached to the flexure to finish the fabrication of an HGA 30 in accordance with a preferred embodiment of the invention.
FIG. 5, curve 52, shows the first torsion gain of suspension 31 shown in FIG. 3 as a function of the imparted suspension offset. The optimal operating point of the sagged loadbeam embodiment of the present is about 3 dB lower in first torsion gain than a conventional Type 8 suspension.
2 0 FIG. 4 discloses an alternative preferred embodiment of an HGA 42 in accordance with the present invention. In this embodiment the loadbeam 43 is manufactured conventionally in a generally flat configuration, except that a protrusive feature 44 of about 0.08 mm height is manufactured onto either loadbeam 43 (or alternatively, on flexure 45) and is positioned between 2 5 loadbeam 43 and flexure 45 intermediate the longitudinal ends of flexure 45.
Flexure 45 is spot welded or otherwise affixed to the loadbeam at bonding points 46 at the proximal end of the flexure and at the location of the protrusive feature 44, which results in a curved flexure structure for supporting head 47.
It is believed that this flexure attachment scheme imparts a degree of negative 3 0 sag to loadbeam 43. Although this curved flexure embodiment results in somewhat higher nominal gain than the curved loadbeam embodiment, this embodiment may be easier to implement while still providing about a 2 dB first torsion gain reduction relative to a convention Type 8 suspension, as shown in curve 54 of FIG. 5.
s In summary, the instant invention provides a suspension for an actuator in a disk drive that concurrently provides both reduced first torsion gain and reduced first torsion gain sensitivity relative to prior art suspensions. The reduced first torsion gain improves potential head position servo system performance while the decreased gain sensitivity improves manufacturing yields. Thus the present invention facilitates the design and fabrication of cheaper and higher performance disk drives.
Although the present invention has been described in terms of the presently preferred embodiments, it should be understood that the instant disclosure is not to be interpreted as limiting. Various alterations and modifications will no doubt become apparent to those skilled in the art after having read the above disclosure. For example, although the present disclosure is presented in the context of uprail type suspension designs, the teachings are also applicable to downrail designs. Accordingly, it is intended that the appended claims be interpreted as covering all alterations and modifications as fall within the true spirit and scope of the invention.
Claims (15)
1. A suspension for supporting a read/write head adjacent to a disk in a disk drive, the suspension comprising:
a mounting region at an end of the suspension;
a leaf spring connected to the mounting region;
an elongated, generally planar loadbeam connected to the leaf spring, the loadbeam having a proximal end adjacent the leaf spring and a distal end, wherein a cross section of the loadbeam taken along a central longitudinal axis of the loadbeam is concave toward the disk; and flexure means attached to the distal end of the loadbeam, the flexure means including a gimbal for pivotably supporting the read/write head.
a mounting region at an end of the suspension;
a leaf spring connected to the mounting region;
an elongated, generally planar loadbeam connected to the leaf spring, the loadbeam having a proximal end adjacent the leaf spring and a distal end, wherein a cross section of the loadbeam taken along a central longitudinal axis of the loadbeam is concave toward the disk; and flexure means attached to the distal end of the loadbeam, the flexure means including a gimbal for pivotably supporting the read/write head.
2. The suspension of claim 1, wherein the loadbeam further includes stiffening rail means along a lateral edge.
3. The suspension of claim 2, wherein the rail means extend away from the disk.
4. The suspension of claim 2, wherein the rail means extend toward the disk.
5. The rail of claim 1, wherein a radius of curvature of the cross section is about 236 mm.
6. A cantilevered suspension for supporting a read/write head adjacent to a disk in a disk drive, the suspension comprising:
a mounting region at a proximal end of the suspension;
a leaf spring connected to the mounting region;
an elongated, generally planar loadbeam connected to the leaf spring; and an elongated, generally planar flexure having a proximal end and a distal end, the proximal end of the flexure being attached coplanarly to a bottom surface of the loadbeam and the distal end of the flexure including a gimbal for pivotably mounting the read/write head, wherein the bottom surface of the loadbeam includes a protrusion, the protrusion interposing and separating a central portion of the flexure from the bottom surface of the loadbeam.
a mounting region at a proximal end of the suspension;
a leaf spring connected to the mounting region;
an elongated, generally planar loadbeam connected to the leaf spring; and an elongated, generally planar flexure having a proximal end and a distal end, the proximal end of the flexure being attached coplanarly to a bottom surface of the loadbeam and the distal end of the flexure including a gimbal for pivotably mounting the read/write head, wherein the bottom surface of the loadbeam includes a protrusion, the protrusion interposing and separating a central portion of the flexure from the bottom surface of the loadbeam.
7. The suspension of claim 6, wherein the loadbeam further includes stiffening rail means along a lateral edge.
8. The suspension of claim 7, wherein the rail means extend away from the disk.
9. The suspension of claim 7, wherein the rail means extend toward the disk.
10. The suspension of claim 6, wherein the protrusion has a height of about 3 mils.
11. A cantilevered suspension for supporting a read/write head adjacent to a disk in a disk drive, the suspension comprising:
a mounting region at a proximal end of the suspension;
a leaf spring connected to the mounting region;
an elongated, generally planar loadbeam connected to the leaf spring and having an unsupported end; and an elongated, generally planar flexure having a proximal end and a distal end, a proximal end of the flexure being attached coplanarly to a lower surface of the loadbeam and the distal end of the flexure including a gimbal for pivotably mounting the read/write head, wherein an upper surface of the flexure includes a protrusion, the protrusion interposing and separating a central portion of the flexure from the lower surface of the loadbeam.
a mounting region at a proximal end of the suspension;
a leaf spring connected to the mounting region;
an elongated, generally planar loadbeam connected to the leaf spring and having an unsupported end; and an elongated, generally planar flexure having a proximal end and a distal end, a proximal end of the flexure being attached coplanarly to a lower surface of the loadbeam and the distal end of the flexure including a gimbal for pivotably mounting the read/write head, wherein an upper surface of the flexure includes a protrusion, the protrusion interposing and separating a central portion of the flexure from the lower surface of the loadbeam.
12. The suspension of claim 11, wherein the loadbeam further includes stiffening rail means along a lateral edge.
13. The suspension of claim 12, wherein the rail means extend away from the disk.
14. The suspension of claim 12, wherein the rail means extend toward the disk.
15. The suspension of claim 11, wherein the protrusion has a height of about 3 mils.
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP96923542A EP0845141A1 (en) | 1995-08-18 | 1996-06-28 | Suspension having reduced torsional mode gain and sensitivity |
| JP9509264A JPH11511284A (en) | 1995-08-18 | 1996-06-28 | Suspension with reduced torsional mode gain and sensitivity |
| PCT/US1996/011095 WO1997007502A1 (en) | 1995-08-18 | 1996-06-28 | Suspension having reduced torsional mode gain and sensitivity |
| US08/937,566 US6104572A (en) | 1995-08-18 | 1997-09-25 | Suspension having reduced torsional mode gain and sensitivity |
| CA002229239A CA2229239A1 (en) | 1995-08-18 | 1998-02-11 | Suspension having reduced torsional mode gain and sensitivity |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US51690195A | 1995-08-18 | 1995-08-18 | |
| CA002229239A CA2229239A1 (en) | 1995-08-18 | 1998-02-11 | Suspension having reduced torsional mode gain and sensitivity |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2229239A1 true CA2229239A1 (en) | 1999-08-11 |
Family
ID=31947251
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002229239A Abandoned CA2229239A1 (en) | 1995-08-18 | 1998-02-11 | Suspension having reduced torsional mode gain and sensitivity |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0845141A1 (en) |
| JP (1) | JPH11511284A (en) |
| CA (1) | CA2229239A1 (en) |
| WO (1) | WO1997007502A1 (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6556382B1 (en) | 1996-03-29 | 2003-04-29 | Hutchinson Technology, Inc. | Mass balancing for optimizing suspension resonance performance |
| US5991122A (en) * | 1996-09-24 | 1999-11-23 | Hutchinson Technology Incorporated | Method for designing a suspension having weakening structures for resonance-optimized side profile |
| JP5197780B2 (en) | 2010-11-02 | 2013-05-15 | サンコール株式会社 | Magnetic head suspension |
| JP5318162B2 (en) * | 2011-03-28 | 2013-10-16 | サンコール株式会社 | Magnetic head suspension |
| JP5296174B2 (en) * | 2011-05-20 | 2013-09-25 | サンコール株式会社 | Magnetic head suspension |
| JP5554305B2 (en) * | 2011-09-26 | 2014-07-23 | サンコール株式会社 | Magnetic head suspension and manufacturing method thereof |
| US8917482B2 (en) * | 2012-07-11 | 2014-12-23 | HGST Netherlands B.V. | Distribution of mass in vertical axis for HGA flexure mode control |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5065268A (en) * | 1989-12-22 | 1991-11-12 | Seagate Technology, Inc. | Load beam having an additional bend in a head-gimbal assembly |
-
1996
- 1996-06-28 EP EP96923542A patent/EP0845141A1/en not_active Withdrawn
- 1996-06-28 WO PCT/US1996/011095 patent/WO1997007502A1/en not_active Application Discontinuation
- 1996-06-28 JP JP9509264A patent/JPH11511284A/en active Pending
-
1998
- 1998-02-11 CA CA002229239A patent/CA2229239A1/en not_active Abandoned
Also Published As
| Publication number | Publication date |
|---|---|
| WO1997007502A1 (en) | 1997-02-27 |
| EP0845141A1 (en) | 1998-06-03 |
| JPH11511284A (en) | 1999-09-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7016159B1 (en) | Disk drive head suspension with spring rails for base plate microactuation | |
| JP4188793B2 (en) | Dual stage suspension with PZT actuator | |
| USRE39478E1 (en) | Magnetic head suspension assembly fabricated with integral load beam and flexure | |
| US20010043443A1 (en) | Suspension for disc drive | |
| EP0302615A1 (en) | A head suspension assembly for a magnetic record disk store | |
| US20050201014A1 (en) | Magnetic head suspension | |
| US6104572A (en) | Suspension having reduced torsional mode gain and sensitivity | |
| US6995953B2 (en) | Head gimbal assembly high performance shock limiter | |
| JPH0798949A (en) | Suspension system | |
| US5734525A (en) | Head suspension with torsion spring region | |
| US6417996B1 (en) | Gimbal for a head of a disc drive with vertical limiter | |
| US20230260541A1 (en) | Low Profile Suspension Design | |
| US5914835A (en) | Head suspension with modified spring region for improved load control | |
| US6650505B2 (en) | Method and apparatus for improved roll static angle adjustment | |
| US6480459B2 (en) | Suspension design including shaped gimbal arms having a reduced mass portion along a length thereof | |
| CA2229239A1 (en) | Suspension having reduced torsional mode gain and sensitivity | |
| USH1425H (en) | Head suspension assembly having improved frequency response, accurate head positioning and minimized flying variation | |
| US5877923A (en) | Head suspension assembly | |
| US6055131A (en) | Magnetic head suspension having selected thicknesses for enhancing rigidity | |
| US7586714B2 (en) | Head suspension with rails and support extensions | |
| KR19990037679A (en) | Suspension with reduced torsional mode gain and sensitivity | |
| JP3528074B2 (en) | Head suspension | |
| EP0827619A1 (en) | Suspension design for supporting a low mass read/write head | |
| US20030202285A1 (en) | Laminated suspension load beam design with dual primary metal layers sandwiching intermediate secondary layer | |
| US7298589B2 (en) | HDD suspension and method including contoured rail and ports |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Discontinued |