GB2223544A

GB2223544A - Feed-screw support structure

Info

Publication number: GB2223544A
Application number: GB8919718A
Authority: GB
Inventors: Hiroshi Narushima
Original assignee: Okuma Machinery Works Ltd
Current assignee: Okuma Corp
Priority date: 1988-03-14
Filing date: 1989-08-31
Publication date: 1990-04-11
Anticipated expiration: 2009-08-31
Also published as: GB2223544B; EP0377145A3; EP0377145A2; GB8919718D0

Description

2 2 -, -1) 5 4 4 FEED-SCREW SUPPORT STRUCTURE This invention relates to a

feed-screw support structure adapted to absorb the thermal expansion of the feed-screw of a saddle, table or the like in a machine tool, in particular, a machining center.

In a machine tool which is required to have particularly high dynamic performance, such as a machining center, it is known to increase the feed rigidity by supporting both ends of the male screw in such a manner as to preclude any movement in the axial direction, as shown in Fig. 12. Even if a ball screw is employed for the feed-screw, the screw will expand with heat if the machine is operated long since the heat generation due to the rolling friction of the ball will cause gradual temperature rise. In view of this, it is the normal practice, in a machine of the type in which both screw ends are fixed, to provide the screw with pre-tension for absorbing elongation. However, in a case where the machine is operated for a long time at high speed, this pre-tensioning alone cannot absorb the elongation completely, which leads to the generation of an excessive comressive force in the screw, resultng not onlv in deterioration in accuracy, but also in damage to the thrust bearing or an excessively shortened lifetime thereof. To cope with this, various methods of restraining the heat generation in the screw are being 2 - practiced. According to one such method, a hollow screw is employed through the central hole of which coolant is allowed to flow. In another method, the heat generation is restrained by means of an oil-mist lubrication system or the like in the ball nut portion.

Systems in which coolant is allowed to pass through the screw center require a coolant supply device, supply piping, etc., which leads to high cost. Furthermore, it has another problem involving a limit to the diameter and length of the screw. Oil-mist lubrication systems require a mist apparatus. Besides, it does not provide a satisfactory cooling effect.

According generally to the present invention, there is provided a feedscrew support structure of the type in which both ends of a feed-screw can be fixed in the axial direction, comprising a main-body member, a bearing-holder member at one end of the feedscrew and slidably arranged in the main-body member, means for fixing the axial position of the bearing-holder member relative to the main-body member, and for adjusting and refixing the axial position thereof in dependence on heat generation in the feed-screw.

In one embodiment, the axial position fixing means is a clamping member between the bearing-holder member and the main-body member, and the adjusting and refixing means is effective to unclamp and reclamp the clamping member.

In an alternative embodiment, the axial position fixing means is at least one piezoelectric element mounted axially to one side of the bearingholder member, the piezoelectric element being mounted in a bracket fixed to the main-body member, and the adjusting and refixing means is effective to vary and reset the applied voltage on the piezoelectric element.

By using the support structure of the present invention, it is possible to reduce or eliminate the problems experienced with the prior art systems. Such a feed-screw support structure makes it possible to cope with the thermal expansion of the feed-screw at low cost without involving any deterioration in the rigidity of the feed system, and requires no special cooling means nor imposes any limit to the diameter and length of the screw, and allows the associated machine to operate continuously and at high speed without problems.

In one specific embodiment of the invention, there is provided a feed-screw support structure comprising a mainbody member, a bearing-holder member at one end of the feed-screw slidably arranged in the above-mentioned main-body member, a clamping member provided between the above-mentioned bearing-holder member and the above-mentioned main-body member and adapted to fix these members, and a means for operating the above-mentioned clamping member in accordance with factors and matters related to heat generation in the feed-screw. When axial feed is not performed, the fixing of the bearing-holder member can be released.

In accordance with another specific aspect of the invention, there is provided a feed-screw support structure comprising a main-body member including bracket, piezoelectric elements, a bearing case at one end of the feed- screw arranged between the above-mentioned piezoelectric elements and restricted in the axial movement by the bracket of the above-mentioned main-body member, and a means for detecting factors related to heat generation in the feed-screw. Such a specific embodiment using piezoelectric elements allows fine and continuous -.4 -- control since it can be operated independ.ently of the axial feed of the machine. Also, no high-pressure oil source is needed, nor is there any maintenance problem such as oil leakage. The structure can be simpler.

Alternatively, the piezoelectric element may be provided only on the inner side, voltage being constantly applied thereto so as to provide the feed-screw with pre-tension. Using just one element enables simpler control and lowers 10 the cost.

With the structure in accordance with the invention, a temperature rise to a certain level as a result of heat generation in the feed-screw causes the clamping means to release the fixing of the bearing-holder, thereby temporarily allowing the elongation of the feed-screw. Alternatively, the bearing-holder may be normally kept free from the fixing of the clamping means, constantly allowing the elongation of the feed-screw. In that case, the bearing-holder is fixed only during axial feed. In the structure according to another aspect of the invention, a predetermined voltage is applied to the piezoelectric elements between which the bearing case is putted, any elongation corresponding to heat generation in the screw being absorbed by displacement of the piezoelectric elements.

Fig. 1 is a sectional view showing the structure of a bearing section in accordance with a first embodiment of 30 this invention; Fig. 2 is a flowchart of the program control of the hydraulic-expansion clamp cylinder used in this structure; Fig. 3 is a flowchart of the control process for 35 the same in which a timer is used; 1 Fig. 4 is a flowchart of the control process for -the same in which the screw-section temperature measured is utilised; Fig. 5 is a flowchart of the control process for the same in which the compressive force measured in the screw section is utilised; Fig. 6 is a flowchart of the control process for effecting unclamping during axial feed being not performed; Fig. 7 is a whole sectional view showing the first embodiment according to the invention; Fig. 8 is a sectional view showing a modification of the first embodiment; Fig. 9 is a sectional view showing the structure of a bearing section in accordance with a second embodiment of this invention; Fig. 10 is a flow2hart of the control process for the second embodiment in which the screw-section temperature measured is utilised; 20 Fig. 11 is a flowchart of the control process for the same in which the compressive force measured is utilised; and Fig. 12 is a sectional view showing the structure of a conventional bearing section.

Referring to Fig. 1, a support structure is shown at the tip end of a feed-screw 1. In the support structure on the motor side (not shown), it is designed such that a bearing bracket is fixed to a bed 2, as in the prior art structure of Fig. 12.

The structure includes a bed 2 to which a bracket 3 is fixed. A bearingholder 4 is fitted into this bracket 3 in such a manner as to 1 be sl-idabl.e in the axial direction. Further, a hydraulic-expansion.- clamp cylinder-5-is arranged between the small-diameter portion 4a of.the:bearing.holder 4 and the bracket 3 in such a manner as to be able ta make sliding movements. The hydraulic-expansion clamp cylinder 5 has a flange portion which is fixed to the bracket 3 by means of bolts. Further, the hydraulicexpansion clamp cylinder 5 has on its outer periphery an annular-recess portion Sa which constitutes an oil receiver. That side of the hydraulic-expansion clamp cylinder 5 which is -in contact with the small-diameter section 4a of the bearing holder 4 is formed as a deformable thin-walled portion. The annular-recess portion 5a is sealed on both sides by means of 0-rings 6 serving to prevent oil leakage, high-pressure oil being supplied to the annular-recess portion 5a through the duct 7 connected with an oil path 3a provided in the bracket 3. The bearing holder 4 serves to prevent axial movement of the feed screw while rotatably support- ing it through the intermediary of angular bearings 8 which are adapted to receive both thrust and radial loads. It goes without saying that the bearings may also be of the type consisting of one or more thrust bearing and one or more radial bearing which are separately provided.

While in this embodiment the bearing holder of the angular bearing is fixed by means of a hydraulicexpansion clamp cylinder, it is to be understood that the manner of above mentioned clamping and the configuration of the slidable portions with resPect-to the stationary ones are not restricted to those of this embodiment.

The timing with which the above mentioned hydraulic-expansion clamp cylinder 5 is unclamped may be determined in accordance with any one of the following methods:

(1) The timing may be determined by a program method inserted the data in the experiment from which the heat-generating condition is previously ascertained. The process follows the ilowchart of Fig. 2.

Suppose the M-code number, which is a motion command for making a NC machine work in desired func- tions, is MAA, for example. MAA is then read in Step Sl. In Step S2, an unclamp command is given to the hydraulic-expansion clamp cylinder 5. The high-pressure oil supplied through the duct 7 is then evacuated from the hydraulic-expansion clamp cylinder 5, the deformed body portion of the cylinder being restored to the state before expansion by virtue of the elasticity thereof. At this stage, the bearing holder 4 is displaced by a distance corresponding to the thermal expansion of the feed screw 1, the compressive force of the feed screw 1 being eliminated. In step S3, the unclamp state is verified when the pressure in the duct 7 is determined to be zero. In Step S4, a clamp- command is output, and the high-pressure oil is supplied again through the duct 1 7, caus.inq.the inner pressure-In the.annular-recessportion Sa-ofAhe hydraulic-.expansion clamp cylinder 5 to increase. As a result, the thin- walledTortion-is deformed to expand, thereby clamping the bearing holder 4. The clamp state is verified in Step S5 when the pressure in the duct 7 is determined to be high. An "MAA-complete" signal is output in Step S6.

(2) The unclamping timing may be decided by a method using a timer. The control process follows the flowchart of Fig. 3. If a cutting operation is performed when unclamping is desired, the operation is temporarily interrupted, or the unclamping is not effected until the operation is completed. The timer is started in Step S11. When, in Step 12, the condition: t 2-: to (t 0: set time determined through experiment or the like; t: accumulated machine operation time, or preferably, axial-feed-time accumulation) is satisfied, the timer is to operate. In Step S13-, a judgment is made as to whether or not axial feed is being effected. The judgment is made for not only the feed screw to be controlled but also the other axial-feed components. If the judgment result is YES, the step is repeated until the result becomes NO. When the judgment result in this step becomes NO, the axial-feed command is locked in Step S14, thereby stopping all the axial feed controls. In Step S15, an unclamp command is output, which causes the high-pressure oil in the duct 7 to be evacuated, thereby reducing the pressure in the duct z to zero and restoring the hydraulic-expansion clamp cylinder 5 to the state before expansion. It is determined with certainty, in Step S16, that the pressure in the duct 7 has been reduced to zero. At this stage, the feed screw is allowed to release thermal expansion, the compressive force of the screw being relieved. In Step S17, a clamp command is output, and, in Step S18, the clamp state is verified when the pressure in the duct 7 is determined to be high. In Step S19, the axial-feed-command lock is released, and the process is taken back to step Sll and then the timer is started again.

(3) The unclamping timing can also be determined by a method utilizing the difference between a reference temperature and the measured temperature of the male or female screw. The control process follows the flowchart of Fig. 4.

The temperature T of the feed screw can be ascertained by extracting the output of a temperature sensor through a slip ring or the like, or it can be detected by means of an infrared sensor. In Step S21, the temperature T 1 of the female screw before operation is measured. The temperature T 1 measured is established as the reference temperature T 0 In Step S22, the temperature T of the female screw is measured again. In Step S23, a judgment is made as to whether or not the difference between the measured temperature T and the reference temperature T 0 is either equal to or larger - 1,0 - 1 than a set value T 2 Ifthe re.sult.is NO, the procedure returns to Step S22, where the temperature i-s measured, the same judgment being repeated until the--result becomes YES. When the result is YES, a judgment is made in Step S24 as to whether or not axial feed is performed. If the result is YES, the judgment is repeated until it becomes NO. In Step S25, the axial feed command is locked. In Step S26, an unclamp command is output, which causes the high-pressure oil in the duct 7 to be evacuated, reducing the pressure in the duct 7 to zero. In Step 27, it is determined with certainty that the pressure in the duct 7 has been reduced to zero. The clamping of the hydraulic-expansion clamp cylinder 5 is then released, and the screw is allowed to relieve thermal expansion. In Step S28, a clamp command is output, which causes high-pressure oil to be supplied to the duct 7, thereby causing the hydraulic-expansion clamp cylinder 5 to be deformed to effect clamping. The pressure in the duct 7 is verified in Step S29. In Step S30, the axial-feed command is unlocked, which enables the machine to operate. Afterwards, this flow is repeated, establishing the first measured temperature T 1 in each cycles as the next reference temperature T 0 Instead of directly utilizing the temperature of the feed screw, it is also possible to indirectly utilize the temperature of the bearing portion or that of the female screw.

(4) The unclamping timing may also be determined 11 1 by a method utilizing the difference between a set value and the detected compressive force acting on the male screw or the bearing. The control process follows the flowchart of Fig. 5. The compressive force can be detected by means of resistance-wire-strain-gauge or piezoelectric elements. In Step S41, the compressive force F is detected. A judgment is made in Step S41 as to whether or not F 2'_! F 0 (F: detected compressive force; F 0: set value). If the judgment result is NO, the step is repeated until it becomes YES. It is determined in Step S43 whether axial feed is performed; if the result is YES, the step is repeated until it becomes NO. In Step S44, the axial-feed command is locked. In Step S45, an unclamp command is output, which causes the high- pressure oil in the duct 7 to be evacuated. It is verified in Step S46 that the pressure in the duct 7 has been reduced to zero. The clamping of the hydraulicexpansion clamp cylinder 5 is then released, and the screw is allowed to relieve thermal expansion. In Step S47, a clamp command is output, which causes highpressure oil to be supplied to the duct 7, thereby deforming the hydraulic-expansion clamp cylinder 5 to effect clamping. In Step S48, the clamp state is verified when the pressure in the duct 7 is determined to be high. In Step S49, the axial-feed command is unlocked, thereby setting the machine ready for axial feed. Afterwards, this flow is repeated.

(5) When unclamping is to be effected when a 1 cutting operation is not-performed, the flowchart of. Fig. 6 is followed. When no-axia:l.feed.' isperformed, the unclamp state is constantly maintained-. When in Step S51 an axial-feed command is output, it-is judged in Step S52 whether clamping is being effective or not. If the result is NO, a clamp command is output in Step S53, and high- pressure oil is supplied to the duct 7, thereby causing the hydraulic- expansion clamp cylinder 5 to be deformed to effect clamping. The clamp state is verified in Step S54 when the pressure in the duct 7 is determined to be high. Then, axial feed is executed in Step S55 as in the case where the result of Step S52 is YES, thus performing a predetermined working, etc. When the working has been completed in Step S56, an "axial-feed complete" command is output. An unclamp command is then output in Step S57, the high-pressure oil in the duct 7 being evacuated and the hydraulicexpansion clamp cylinder 5 restored to the state before deformation. The unclamp state is verified in Step S58 when the pressure in the duct 7 is determined to be zero. The next command is executed in Step S59.

When the position of the feed screw is determined by a means allowing direct absolute measurement, such trade names as Inductosyn and Magnescale, no particular correction has to be conducted for the elongation of the screw due to thermal expansion. However, when the positional detection is conducted on the basis of the turning of the screw, it is necessary to correct any X t 13 - 1 elongation of the screw. The correction is then conducted as follows: as shown in Fig. 7 first, the terminal position of the feed screw is ascertained before operating the machine by a sensor measuring an axial expanding value of the feed screw 1 at an outer end face of a bearing cover mounted on the bearing holder 4. Then, the terminal position of the screw after unclamping is determined, thereby obtaining the displacement Lú due to the elongation. It is necessary to add the correction amount d = WL) x LZ at each position Z in the entire length L of the feed screw to the corrected pitch-error value at each position ú. While in the above examples the verification of the clamp and unclamp states is effected by means a pressure switch for measuring the pressure in the duct, any other measuring means including a timer will serve the purpose as long as it has an equivalent measuring function.

Fig. 8 shows a modification of the first embodiment.

The modification is arranged to add to the first embodiment a coned disk spring at the right end of the small diameter portion 4a of the bearing holder 4 in Fig. 8 so as to press it and, furthermore, provides the oil pressure expanding clamp tube with a bottom portion thereof so as to receive the coned disk spring at the right side of the spring. When the structure of the modification is in an unclamping state, the feed 1 1 screw is pulled by the coned disk-spring. Keeping the above condition, which the feed screw is pulled by the coned disk spring, the feed screwis clamped-and operated to revolve. Due to a long time operating heat generates in the feed screw and thus the feed screw is expanded with thermal expansion. The expansion in the feed screw, however, is absorbed so as to be set off the previous tension.

A second embodiment of the invention will now be described with reference to Fig. 9. This embodiment includes a bearing bracket 11 which is fixed to the bed 2 at a position corresponding to the tip-end bearing of the feed screw 1. The bearing bracket 11 has a bottom portion in which a hole for passing the feed screw 1 is provided. A bearing case 13 containing angular bearings 12 for the feed screw is fitted into the hole of the bearing bracket 11 in such a manner as to be slidable in the axial direction. The inner rings of the angular bearings 12 are fixed by means of nuts 14 engaged with the male screw at the screw end, and the outer rings of the angular bearings 12 are fixed by means of an outer-ring-fixing cover 15. A compressiveforce detector 19 is embedded in this outer-ring-fixing cover 15. Provided between the end surface of the bearing case 13 and the bottom of the bearing bracket 11 is a piezoelectric element 16. Another piezoelectric element 17 is provided between the outer-ring-fixing cover 15 and an outer cover 18, which is pressed against 1 the piezoelectric element 17. It is known that these piezoelectric elements will be elongated in accordance with the voltage applied to them. In this example, the initial voltage is set at zero for the piezoelectric element 16, whereas the piezoelectric element 17 is elongated beforehand by applying the maximum voltage to it.

(1) The unclamping control in this embodiment can be conducted on the basis of the male-screw temperature measured. The control process will be described with reference to the flowchart of Fig. 10. In Step S61, the reference temperature T 0 is measured by means of a thermometer provided on the machine body, which is not affected by the temperature of the feed screw 1. In Step S62, the temperature T of the male screw is measured. In Step S63, the elongation of the screw A, corresponding to T - T 0 is calculated. In Step S64, the voltage AE causing a displacement of the piezoelectric element corresponding to LZ is calculated. In Step S65, a voltage obtained by adding the voltage AE16 of the piezoelectric element 16 corresponding to AZ to the initially applied voltage E 0 16 is applied to the piezoelectric element 16. Likewise, in Step S66, a voltage obtained by subtracting the voltage AE17 of the piezo- electric element 17 corresponding to AZ from the initially applied voltage E 0 17 is applied to the piezoelectric element 17. This step is repeated until the value of T-T 0 becomes constant.

- 16 1 (2) Control may also conducted.- on the basis, of the compressive force of the bearing. The control, process will be described with reference to the flowchart.

of Fig. 11. In Step S71, the compressive force F is measured by means of a compressive-force detector 19 shown in Fig. 9. In Step S72, a judgment is made as to whether or not the set compressive force F 0 is equal to the compressive force F measured. If the judgment result is YES, the procedure returns to Step S71, repeating the same step. If the result is NO, it is judged in Step S73 whether F > F 0" If the result is YES, the voltage of the piezoelectric element 16 is raised in Step S74, lowering the voltage of the piezoelectric element 17 such that the detected conpressive pressure F is equal to the setting compressive pressure F 0 if the result is NO, the voltage of the piezoelectric element 16 is lowered in Step S75, raising the voltage of the piezoelectric element 17 such as the above. Afterwards, the procedure returns to Step S71, the same steps being repeated such that F is equal to F 0 1 A

Claims

A feed-screw support structure of the type in which both ends of a feedscrew can be fixed in the axial direction, comprising a main-body member, a bearing-holder member at one end of the feed-screw and slidably arranged in the main-body member, means for fixing the axial position of the bearing-holder member relative to the main-body member, and for adjusting and refixing the axial position thereof in dependence on heat generation in the feed-screw.
2. A feed-screw support structure according to Claim 1, wherein the axial position fixing means is a clamping member between the bearing-holder member and the main-body member, and the adjusting and refixing means is effective to unclamp and reclamp the clamping member.
3. A feed-screw support structure according to Claim 2, wherein the clamping member is a hydraulically actuated clamping ring surrounding the bearing-holder member.
4. A feed-screw support structure according to Claim 1, wherein the axial position fixing means is at least one piezoelectric element mounted axially to one side of the bearingholder member, the piezoelectric element being mounted in a bracket fixed to the main-body member, and the adjusting and refixing means is effective to vary and reset the applied voltage on the piezoelectric element.
5. A feed-screw support structure according to Claim 4, and including two piezoelectric elements mounted in the bracket to either side of the bearing-holder.
6. A feed-screw support structure of the type in which both ends of a feed-screw are fixed in the axial direction, comprising: a.main-body member, a - bearing-holder member at the one end of the feed-screw slidably arranged in said main-body member, a clamping member provided between said bearing-holder member and said main-body member and adapted to fix these members, means for operating said clamping member in accordance with factors and matters related to heat generation in the feed-screw, said bearing-holder member being normally held in a stationary condition by means of said clamping member, the feed-screw being allowed to relieve thermal expansion by temporarily releasing said stationary condition when heat generation in the feed-screw takes place to a relatively large degree.
7. A feed-screw support structure of the type in which both ends of a feed-screw are fixed in the axial direction, comprising: a main-body member including a bracket, piezoelectric elements, a bearing case at the one end of the feed-screw arranged between said piezoelectric -20 elements and restricted in the axial movement by the bracket of said main-body member, and a means for measuring factors related to heat generation in the feed-screw, fine adjustment of the bearing in the axial direction being effected by varying the voltage of said piezoelectric elements by said means.
8. A feed-screw support structure substantially as hereinbefore described with reference to Figure 1 of the accompanying drawings.
9. A feed-screw support structure substantially as hereinbefore described with reference to Figure 8 of the accompanying drawings.
10. A feed-screw support structure substantially as hereinbefore described with reference to Figure 9 of the k 19 - accompanying drawings.
11. A method of operating a feed-screw support structure according to any one of Claims 1 to 3, 6, 8 or 9, wherein, during normal operation, the bearing-holder is clamped by means of the clamping member and wherein, on heat generation in the feed- screw exceeding a predetermined amount, the clamping is released to allow relief of thermal expansion in the feed-screw and is then reclamped.
12. A method of operating a feed-screw support structure according to any one of Claims 1 to 3, 6, 8 or 9, wherein the bearing-holder member is normally kept in a released state and the clamping member is only actuated when a cutting operation is being carried out.
13. A method of operating a feed-screw support structure according to Claim 1 and substantially as hereinbefore specifically described with reference to any one of Figures 2 to 6, 10 and 11.

Published:L990 at The Patent Office. State House. 66'71 High HoIborn. LondonWC1R4TP Further copies rikvbe obtained from The Patent Office Sz:es Branch. St Ma-,,, Cray. Orpington. Kent BR5 3RD. Printed by Multiplex technicues ltd, St Ma-y Cray. Kent. Con 187