US20080105071A1 - Device for linearly moving a useful mass - Google Patents
Device for linearly moving a useful mass Download PDFInfo
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- US20080105071A1 US20080105071A1 US11/695,380 US69538007A US2008105071A1 US 20080105071 A1 US20080105071 A1 US 20080105071A1 US 69538007 A US69538007 A US 69538007A US 2008105071 A1 US2008105071 A1 US 2008105071A1
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- mass
- pinion
- spindle
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- compensating
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q5/00—Driving or feeding mechanisms; Control arrangements therefor
- B23Q5/22—Feeding members carrying tools or work
- B23Q5/34—Feeding other members supporting tools or work, e.g. saddles, tool-slides, through mechanical transmission
- B23Q5/38—Feeding other members supporting tools or work, e.g. saddles, tool-slides, through mechanical transmission feeding continuously
- B23Q5/40—Feeding other members supporting tools or work, e.g. saddles, tool-slides, through mechanical transmission feeding continuously by feed shaft, e.g. lead screw
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/28—Counterweights, i.e. additional weights counterbalancing inertia forces induced by the reciprocating movement of masses in the system, e.g. of pistons attached to an engine crankshaft; Attaching or mounting same
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
- F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
- F16H25/20—Screw mechanisms
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2232/00—Nature of movement
- F16F2232/04—Rotary-to-translation conversion
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18568—Reciprocating or oscillating to or from alternating rotary
- Y10T74/18576—Reciprocating or oscillating to or from alternating rotary including screw and nut
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/1967—Rack and pinion
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/19698—Spiral
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/19698—Spiral
- Y10T74/19702—Screw and nut
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/19698—Spiral
- Y10T74/19702—Screw and nut
- Y10T74/19721—Thread geometry
- Y10T74/19726—Thread pitch varies over axial length
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/19698—Spiral
- Y10T74/19828—Worm
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/19—Gearing
- Y10T74/19642—Directly cooperating gears
- Y10T74/19698—Spiral
- Y10T74/19828—Worm
- Y10T74/19837—Intermittent motion
Definitions
- the present invention relates to a device for linearly moving a useful mass and by decoupling the momentum generated during the movement of the useful mass from the machine or machine foundation.
- a device for linearly moving a useful mass includes at least one spindle, at least one drive rotating the at least one spindle, a first spindle nut coupled with the useful mass and moving the useful mass in a first direction, and a second spindle nut coupled with a compensating mass and moving the compensating mass synchronously with the useful mass in a second direction opposite to the first direction, so that a momentum of the useful mass is compensated by a momentum of the compensating mass.
- a device for linearly moving a useful mass includes at least one toothed rack, at least one pinion engaging with the toothed rack, and at least one drive rotatably driving the pinion.
- a pinion is coupled with the useful mass, and a pinion is coupled with a compensating mass and moves the compensating mass synchronously with the useful mass in a second direction opposite to the first direction, so that a momentum of the useful mass is compensated by a momentum of the compensating mass.
- the useful mass and the compensating mass can be moved in cooperation with a spindle that has two threads with an opposite lead, whereby the thread pitch for driving the compensating mass is smaller than the thread pitch for driving the useful mass.
- the travel of the compensating mass is thus kept small and the compensating mass can move at a relatively low speed, which advantageously reduces the power requirement.
- the useful mass and the compensating mass can also be moved by using corresponding spindle/spindle-nut assemblies associated with drives.
- Mechanical coupling elements can be employed to maintain a linear alignment between the assemblies and absorb the forces generated in the two spindles.
- the mechanical coupling element can be implemented either by providing a rotatable connection between the spindles or by connecting both spindles with each other through a base frame, or both.
- one pinion in the device employing a rack/pinion assembly, one pinion can have more closely spaced teeth while the other pinion has more widely spaced teeth.
- one pinion can have a smaller diameter while the other pinion can have a larger diameter.
- the pinions can move on two racks that face each other in opposite directions. The racks with the more widely spaced teeth and/or the larger diameter is connected with the useful mass, while the other pinion with the more closely spaced teeth and/or the smaller diameter drives the compensating mass.
- FIG. 1 is a schematic illustration of a first embodiment of a spindle assembly according to the present invention, including a single drive and a ball roller spindle with opposite lead;
- FIG. 2 is a schematic illustration of a second embodiment of a spindle assembly according to the present invention, including two driven ball roller spindles connected by a mechanical coupling;
- FIG. 3 is a schematic illustration of a first embodiment of a rack/pinion assembly with separate drives for the useful mass and the compensating mass;
- FIG. 4 is a schematic illustration of a second embodiment of a rack/pinion assembly with a single drive and pinions having different diameters/tooth spacings.
- FIG. 1 there is shown a first embodiment of the invention with a single solid spindle SP 1 coupled to a drive A 1 , in the present example a direct drive.
- the spindle SP 1 can rotate, for example, with a speed w in the rotation direction indicated by a curved arrow.
- the exemplary spindle SP 1 has a left-handed threaded section 12 with a relatively high pitch h N and a right -handed threaded section 14 with a pitch hi that is comparatively smaller than the pitch h N .
- the threaded section 12 engages with a spindle nut SM 1 that is connected with a useful mass NM 1 , as indicated by a heavy line.
- the useful mass NM 1 has an exemplary physical mass m.
- a spindle nut SM 2 that is mechanically connected with a compensating mass GM 1 having an exemplary physical mass M.
- the spindle SP 1 rotates with the rotation speed ⁇ , then the opposing lead of the spindle thread causes the spindle nuts SM 1 and SM 2 to move in opposite directions, as indicated in FIG. 1 , with corresponding speeds v N and v I . It follows:
- the compensating mass GM 1 and the physical mass M associated therewith should be made as large as possible and the corresponding pitch h I as small as possible for the following two reasons:
- a small travel path for moving this additional element advantageously also reduces the size of the required installation space.
- the work to be performed by the system increases linearly with the mass and as the square of the speed.
- the transferred momentum increases linearly with both the mass and the speed. In other words, for the same transferred momentum, the required work doubles when the mass is doubled and the speed remains the same, whereas four times the work is required when the speed doubles and the mass remains the same. Making the compensating mass as large as possible is therefore advantageous to decrease the energy consumption.
- FIG. 2 illustrates another embodiment using two spindles SP 2 and SP 3 having the same pitch.
- this embodiment requires two drives A 2 and A 3 , with the drive A 2 driving the spindle SP 2 and the drive A 3 driving the spindle SP 3 .
- the spindle SP 2 engages with a spindle nut SM 3 that is connected with a useful mass NM 2 , as indicated by a heavy line.
- the spindle SP 3 engages with a spindle nut SM 4 that is connected with a compensating mass GM 2 .
- the curved arrows indicate the rotation speeds ⁇ 2 and ⁇ 3 which are preferably different from each other for the reasons listed above.
- the straight arrows indicate the corresponding speeds v N and v I of the masses NM 2 and NM 3 .
- Corresponding physical masses (not indicated in FIG. 2 ) are associated with the masses NM 2 and NM 3 , with the compensating mass GM 2 preferably being significantly greater than the useful mass NM 2 , as before.
- the spindle SP 2 is connected via a coupling K, for example an articulated joint, with the spindle SP 3 in such a way that the spindle SP 2 is collinear with the spindle SP 3 .
- the axial forces of the two spindles SP 2 and SP 3 are then compensated over a short travel path.
- the spindle SP 3 has an identical pitch and also the same thread direction (or lead) as the spindle SP 2 .
- the desired linear speed v I of the compensating mass GM 2 which is preferably smaller than the speed v N of the useful mass NM 2 and in the opposite direction can be easily obtained by rotating the drive A 3 that is connected with a spindle SP 3 in the opposite direction to drive A 2 .
- the rotation speeds ⁇ 2 and ⁇ 3 can be adjusted according to the desired compensation.
- the force in such system can be readily compensated by varying the rotation speed ⁇ 3 of the drive A 3 , without requiring a change in the compensating mass GM 3 .
- spindle/spindle-nut system can also include ball roller spindles.
- FIG. 3 shows a third embodiment of the invention which employs a rack and pinion system instead of a spindle/spindle-nut system.
- This embodiment employs a stationary toothed rack ZS 1 which engages with pinions R 1 and R 2 .
- the exemplary useful mass NM 3 is moved in a linear direction parallel to the rack ZS 1 by a rotary drive A 4 coupled to pinion R 1 at a speed v N .
- the rotary drive A 4 rotates with an angular rotation speed ⁇ 4 as indicated by a curved arrow.
- a compensating mass GM 3 is moved on the rack ZS 1 in the opposite direction of the useful mass NM 3 by a rotary drive A 5 coupled to pinion R 2 at a speed v I .
- the rotary drive A 5 rotates with an angular rotation speed ⁇ 5 in the opposite sense as the rotary drive A 4 .
- This arrangement eliminates or at least reduces undesired forces from being introduced by the toothed rack ZS into the machine.
- the equations for the physical motion listed above can be similarly applied to the rack/pinion configuration.
- FIG. 4 depicts yet another embodiment using two toothed racks ZS 2 and ZS 3 and two pinions R 3 and R 4 commonly driven by a drive A 6 .
- Pinion R 3 engages with rack ZS 2
- pinion R 4 engages with rack ZS 3 .
- the racks ZS 2 and ZS 3 can be aligned parallel with each other, with the toothed section either facing each other or facing in the same direction.
- Other arrangements are also feasible, such as racks that are not parallel to each other and/or employ gears between pinions R 3 and R 4 .
- the rack/pinion combinations ZS 2 /R 3 and ZS 3 /R 4 can either have different tooth spacings (pitch) or the pinions R 3 and R 4 can have different diameters, or both.
- the teeth of the pinion R 3 and the rack ZS 2 have a wider spacing than the teeth of the pinion R 4 and the rack ZS 3 .
- pinion R 3 has preferably a greater diameter than pinion R 4 . Accordingly, a compensating mass GM 4 connected with the rack ZS 3 is moved at a speed v I that is smaller than and in the opposite direction to the speed v N of the useful mass NM 4 connected to rack ZS 2 .
Abstract
A device for linearly moving a useful mass is described. Typically, when a large useful mass is moved, relatively large forces are transferred by a spindle or a toothed rack to the corresponding machine or machine frame. These forces can be compensated by moving a compensating mass in the opposite direction of the useful mass.
Description
- This application is a divisional of prior filed copending U.S. application Ser. No. 10/783,965, filed Feb. 20, 2004, the priority of which is hereby claimed under 35 U.S.C. §120, and which claims the priority of German Patent Application, Serial No. 103 07 308.6, filed Feb. 20, 2003, pursuant to 35 U.S.C. 119(a)-(d), the contents of which are incorporated herein by reference.
- The present invention relates to a device for linearly moving a useful mass and by decoupling the momentum generated during the movement of the useful mass from the machine or machine foundation.
- Devices of this type have been used since many years with machine tools. It is also known that dynamic processes used to accelerate useful masses along linear axes produce significant forces that have to be transferred to or absorbed by the machine bed or machine foundation. Dynamic movements along one axis can accidentally be transferred through the machine bed to another axis, which can result in processing inaccuracies, in particular workpieces that have low-quality surfaces. In addition, when a rotary motion is transformed into a translational motion—either by a transformation through a ball roller spindle or alternatively a rack/pinion assembly—the forces generated by the linear element can result in a loss in stiffness of the entire system. The transformation from a rotary motion into a translational motion is in general also associated with a significant loss in stiffness, which can be aggravated by the elasticity of the machine bed and/or the support of the drive train. This limits the dynamic characteristic of the machine, unless substantial changes are made in the machine design.
- It would be desirable and advantageous to provide devices of this type so as to reduce and/or compensate disturbances caused by the motion transformation.
- It would also be desirable and advantageous to provide an improved device for moving useful masses, which obviates prior art shortcomings and is able to specifically reduce the momentum transferred to the machine or machine foundation and compensate for disturbances caused by the transformation from rotary to translational motion.
- According to one aspect of the invention, a device for linearly moving a useful mass includes at least one spindle, at least one drive rotating the at least one spindle, a first spindle nut coupled with the useful mass and moving the useful mass in a first direction, and a second spindle nut coupled with a compensating mass and moving the compensating mass synchronously with the useful mass in a second direction opposite to the first direction, so that a momentum of the useful mass is compensated by a momentum of the compensating mass.
- According to another advantageous aspect of the invention, a device for linearly moving a useful mass includes at least one toothed rack, at least one pinion engaging with the toothed rack, and at least one drive rotatably driving the pinion. A pinion is coupled with the useful mass, and a pinion is coupled with a compensating mass and moves the compensating mass synchronously with the useful mass in a second direction opposite to the first direction, so that a momentum of the useful mass is compensated by a momentum of the compensating mass.
- According to an advantageous feature of the invention, the useful mass and the compensating mass can be moved in cooperation with a spindle that has two threads with an opposite lead, whereby the thread pitch for driving the compensating mass is smaller than the thread pitch for driving the useful mass. The travel of the compensating mass is thus kept small and the compensating mass can move at a relatively low speed, which advantageously reduces the power requirement.
- According to an advantageous feature of the invention, the useful mass and the compensating mass can also be moved by using corresponding spindle/spindle-nut assemblies associated with drives. Mechanical coupling elements can be employed to maintain a linear alignment between the assemblies and absorb the forces generated in the two spindles. The mechanical coupling element can be implemented either by providing a rotatable connection between the spindles or by connecting both spindles with each other through a base frame, or both.
- According to an advantageous feature of the invention, in the device employing a rack/pinion assembly, one pinion can have more closely spaced teeth while the other pinion has more widely spaced teeth. Alternatively or in combination, one pinion can have a smaller diameter while the other pinion can have a larger diameter. The pinions can move on two racks that face each other in opposite directions. The racks with the more widely spaced teeth and/or the larger diameter is connected with the useful mass, while the other pinion with the more closely spaced teeth and/or the smaller diameter drives the compensating mass.
- Other features and advantages of the present invention will be more readily apparent upon reading the following description of currently preferred exemplified embodiments of the invention with reference to the accompanying drawing, in which:
-
FIG. 1 is a schematic illustration of a first embodiment of a spindle assembly according to the present invention, including a single drive and a ball roller spindle with opposite lead; -
FIG. 2 is a schematic illustration of a second embodiment of a spindle assembly according to the present invention, including two driven ball roller spindles connected by a mechanical coupling; -
FIG. 3 is a schematic illustration of a first embodiment of a rack/pinion assembly with separate drives for the useful mass and the compensating mass; and -
FIG. 4 is a schematic illustration of a second embodiment of a rack/pinion assembly with a single drive and pinions having different diameters/tooth spacings. - Throughout all the Figures, same or corresponding elements are generally indicated by same reference numerals. These depicted embodiments are to be understood as illustrative of the invention and not as limiting in any way. It should also be understood that the drawings are not necessarily to scale and that the embodiments are sometimes illustrated by graphic symbols, phantom lines, diagrammatic representations and fragmentary views. In certain instances, details which are not necessary for an understanding of the present invention or which render other details difficult to perceive may have been omitted.
- Turning now to the drawing, and in particular to
FIG. 1 , there is shown a first embodiment of the invention with a single solid spindle SP1 coupled to a drive A1, in the present example a direct drive. The spindle SP1 can rotate, for example, with a speed w in the rotation direction indicated by a curved arrow. The exemplary spindle SP1 has a left-handed threadedsection 12 with a relatively high pitch hN and a right -handed threadedsection 14 with a pitch hi that is comparatively smaller than the pitch hN. The threadedsection 12 engages with a spindle nut SM1 that is connected with a useful mass NM1, as indicated by a heavy line. The useful mass NM1 has an exemplary physical mass m. In the right -handed threaded 14 of the spindle SP1 engages with a spindle nut SM2 that is mechanically connected with a compensating mass GM1 having an exemplary physical mass M. When the spindle SP1 rotates with the rotation speed ω, then the opposing lead of the spindle thread causes the spindle nuts SM1 and SM2 to move in opposite directions, as indicated inFIG. 1 , with corresponding speeds vN and vI. It follows: -
- and since the compensating mass moves in the opposite direction
-
- The force FN required to accelerate the useful mass NM1 with the physical mass m is:
-
- whereas the force FI required to accelerate the compensating mass GM1 with the physical mass M is:
-
- The forces FN and FI are fully compensated if |FN|=|FI|, i.e. both forces have the same magnitude. This is the case when the product of mass and spindle pitch are equal:
-
M·hI=m·hN - Advantageously, the compensating mass GM1 and the physical mass M associated therewith should be made as large as possible and the corresponding pitch hI as small as possible for the following two reasons:
- On one hand, a small travel path for moving this additional element advantageously also reduces the size of the required installation space. On the other hand, it is known from mechanical principles that the work to be performed by the system increases linearly with the mass and as the square of the speed. Conversely, the transferred momentum increases linearly with both the mass and the speed. In other words, for the same transferred momentum, the required work doubles when the mass is doubled and the speed remains the same, whereas four times the work is required when the speed doubles and the mass remains the same. Making the compensating mass as large as possible is therefore advantageous to decrease the energy consumption.
-
FIG. 2 illustrates another embodiment using two spindles SP2 and SP3 having the same pitch. However, this embodiment requires two drives A2 and A3, with the drive A2 driving the spindle SP2 and the drive A3 driving the spindle SP3. As in the first embodiment depicted inFIG. 1 , the spindle SP2 engages with a spindle nut SM3 that is connected with a useful mass NM2, as indicated by a heavy line. Likewise, the spindle SP3 engages with a spindle nut SM4 that is connected with a compensating mass GM2. The curved arrows indicate the rotation speeds ω2 and ω3 which are preferably different from each other for the reasons listed above. The straight arrows indicate the corresponding speeds vN and vI of the masses NM2 and NM3. Corresponding physical masses (not indicated inFIG. 2 ) are associated with the masses NM2 and NM3, with the compensating mass GM2 preferably being significantly greater than the useful mass NM2, as before. The spindle SP2 is connected via a coupling K, for example an articulated joint, with the spindle SP3 in such a way that the spindle SP2 is collinear with the spindle SP3. The axial forces of the two spindles SP2 and SP3 are then compensated over a short travel path. - As described above, the spindle SP3 has an identical pitch and also the same thread direction (or lead) as the spindle SP2. The desired linear speed vI of the compensating mass GM2 which is preferably smaller than the speed vN of the useful mass NM2 and in the opposite direction can be easily obtained by rotating the drive A3 that is connected with a spindle SP3 in the opposite direction to drive A2. The rotation speeds ω2 and ω3 can be adjusted according to the desired compensation.
- When the useful mass is changed, the force in such system can be readily compensated by varying the rotation speed ω3 of the drive A3, without requiring a change in the compensating mass GM3.
- Alternatively, instead of connecting the two spindles SP2 and SP3 with a coupling, frames or other components disposed between the two drive systems can also be employed to absorb the forces. The spindle/spindle-nut system can also include ball roller spindles.
-
FIG. 3 shows a third embodiment of the invention which employs a rack and pinion system instead of a spindle/spindle-nut system. This embodiment employs a stationary toothed rack ZS1 which engages with pinions R1 and R2. The exemplary useful mass NM3 is moved in a linear direction parallel to the rack ZS1 by a rotary drive A4 coupled to pinion R1 at a speed vN. The rotary drive A4 rotates with an angular rotation speed ω4 as indicated by a curved arrow. A compensating mass GM3 is moved on the rack ZS1 in the opposite direction of the useful mass NM3 by a rotary drive A5 coupled to pinion R2 at a speed vI. The rotary drive A5 rotates with an angular rotation speed ω5 in the opposite sense as the rotary drive A4. This arrangement eliminates or at least reduces undesired forces from being introduced by the toothed rack ZS into the machine. The equations for the physical motion listed above can be similarly applied to the rack/pinion configuration. - It will be understood that at least two racks can be used instead of the single rack depicted in
FIG. 3 . -
FIG. 4 depicts yet another embodiment using two toothed racks ZS2 and ZS3 and two pinions R3 and R4 commonly driven by a drive A6. Pinion R3 engages with rack ZS2, whereas pinion R4 engages with rack ZS3. The racks ZS2 and ZS3 can be aligned parallel with each other, with the toothed section either facing each other or facing in the same direction. Other arrangements are also feasible, such as racks that are not parallel to each other and/or employ gears between pinions R3 and R4. Since it is desirable, as discussed above, to move the useful mass NM4 and the compensating mass GM4 at different linear speeds vN and vI, respectively, the rack/pinion combinations ZS2/R3 and ZS3/R4 can either have different tooth spacings (pitch) or the pinions R3 and R4 can have different diameters, or both. Preferably, the teeth of the pinion R3 and the rack ZS2 have a wider spacing than the teeth of the pinion R4 and the rack ZS3. Likewise, pinion R3 has preferably a greater diameter than pinion R4. Accordingly, a compensating mass GM4 connected with the rack ZS3 is moved at a speed vI that is smaller than and in the opposite direction to the speed vN of the useful mass NM4 connected to rack ZS2. - While the invention has been illustrated and described in connection with currently preferred embodiments shown and described in detail, it is not intended to be limited to the details shown since various modifications and structural changes may be made without departing in any way from the spirit of the present invention. The embodiments were chosen and described in order to best explain the principles of the invention and practical application to thereby enable a person skilled in the art to best utilize the invention and various embodiments with various modifications as are suited to the particular use contemplated.
- What is claimed as new and desired to be protected by Letters Patent is set forth in the appended claims and includes equivalents of the elements recited therein:
Claims (3)
1. A device for linearly moving a useful mass, comprising:
at least one first toothed rack;
at least one first pinion engaging with the toothed rack and coupled to the useful mass;
at least one first drive rotatably driving the at least one pinion for moving the useful mass along the toothed rack; and
a compensating mass movable synchronously with the useful mass in a second direction opposite to the first direction, so that a momentum of the useful mass is compensated by a momentum of the compensating mass.
2. The device of claim 1 , further comprising a second pinion in engagement with the toothed rack for support of the compensating mass, and a second drive rotatably driving the second pinion, wherein the first and second pinions are constructed to have different diameters, or different tooth spacing, or both.
3. The device of claim 1 , further comprising a second toothed rack and a second pinion mounted on the second toothed rack and operated by the first drive, said compensating mass being coupled to the second toothed rack, said first and second pinions having different diameters, or different tooth spacing, or both so as to move the first and second toothed racks linearly in opposite directions.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/695,380 US20080105071A1 (en) | 2003-02-20 | 2007-04-02 | Device for linearly moving a useful mass |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10307308A DE10307308B4 (en) | 2003-02-20 | 2003-02-20 | Device for the linear method of a useful mass |
DE10307308.6 | 2003-02-20 | ||
US10/783,965 US7421922B2 (en) | 2003-02-20 | 2004-02-20 | Device for linearly moving a useful mass |
US11/695,380 US20080105071A1 (en) | 2003-02-20 | 2007-04-02 | Device for linearly moving a useful mass |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/783,965 Division US7421922B2 (en) | 2003-02-20 | 2004-02-20 | Device for linearly moving a useful mass |
Publications (1)
Publication Number | Publication Date |
---|---|
US20080105071A1 true US20080105071A1 (en) | 2008-05-08 |
Family
ID=32841751
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/783,965 Expired - Fee Related US7421922B2 (en) | 2003-02-20 | 2004-02-20 | Device for linearly moving a useful mass |
US11/695,380 Abandoned US20080105071A1 (en) | 2003-02-20 | 2007-04-02 | Device for linearly moving a useful mass |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/783,965 Expired - Fee Related US7421922B2 (en) | 2003-02-20 | 2004-02-20 | Device for linearly moving a useful mass |
Country Status (2)
Country | Link |
---|---|
US (2) | US7421922B2 (en) |
DE (1) | DE10307308B4 (en) |
Cited By (5)
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CN102092006A (en) * | 2010-12-17 | 2011-06-15 | 上海机床厂有限公司 | Rotary driving mechanism for grinding crankshafts through grinding machine and using method thereof |
US20110157577A1 (en) * | 2007-10-01 | 2011-06-30 | Maskless Lithography, Inc. | Alignment system for various materials and material flows |
US8763771B2 (en) | 2011-09-30 | 2014-07-01 | Siemens Aktiengesellschaft | Active oscillation damper without direct acceleration detection |
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DE19743578A1 (en) * | 1997-09-30 | 1999-04-01 | Hofmann Mes Und Auswuchttechni | Method of balancing a rotating body |
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US6314707B1 (en) * | 2000-01-06 | 2001-11-13 | Cyril A. Ryan | Balanced reciprocating, brush cutting, mower attachment |
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- 2003-02-20 DE DE10307308A patent/DE10307308B4/en not_active Expired - Fee Related
-
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2007
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US6210097B1 (en) * | 1999-06-25 | 2001-04-03 | Samsung Electronics Co., Ltd. | Burden loading robot having balancer for compensating for off-center loading of weight |
Cited By (6)
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US20110157577A1 (en) * | 2007-10-01 | 2011-06-30 | Maskless Lithography, Inc. | Alignment system for various materials and material flows |
CN102092006A (en) * | 2010-12-17 | 2011-06-15 | 上海机床厂有限公司 | Rotary driving mechanism for grinding crankshafts through grinding machine and using method thereof |
US8763771B2 (en) | 2011-09-30 | 2014-07-01 | Siemens Aktiengesellschaft | Active oscillation damper without direct acceleration detection |
US9885280B2 (en) | 2013-03-05 | 2018-02-06 | Siemens Aktiengesellschaft | Internal combustion engine having a linear generator and rotary generator |
CN107559376A (en) * | 2017-08-08 | 2018-01-09 | 郑州轻工业学院 | A kind of movable additional mass induction becomes the vibration absorber and method of characteristics of mode |
CN107559376B (en) * | 2017-08-08 | 2018-12-28 | 郑州轻工业学院 | A kind of movable additional mass induction becomes the vibration absorber and method of characteristics of mode |
Also Published As
Publication number | Publication date |
---|---|
DE10307308B4 (en) | 2006-11-30 |
US7421922B2 (en) | 2008-09-09 |
US20040187621A1 (en) | 2004-09-30 |
DE10307308A1 (en) | 2004-09-09 |
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Legal Events
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STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |