CA1205305A - Coupled structure of constituting machine elements in machinery - Google Patents
Coupled structure of constituting machine elements in machineryInfo
- Publication number
- CA1205305A CA1205305A CA000420578A CA420578A CA1205305A CA 1205305 A CA1205305 A CA 1205305A CA 000420578 A CA000420578 A CA 000420578A CA 420578 A CA420578 A CA 420578A CA 1205305 A CA1205305 A CA 1205305A
- Authority
- CA
- Canada
- Prior art keywords
- pressure chamber
- tool post
- elongate member
- elements
- coupled
- 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.)
- Expired
Links
- 230000008878 coupling Effects 0.000 claims abstract description 30
- 238000010168 coupling process Methods 0.000 claims abstract description 30
- 238000005859 coupling reaction Methods 0.000 claims abstract description 30
- 230000007246 mechanism Effects 0.000 claims abstract description 27
- 239000012530 fluid Substances 0.000 claims abstract description 15
- 230000033001 locomotion Effects 0.000 claims description 5
- 150000001875 compounds Chemical class 0.000 abstract description 7
- 239000000463 material Substances 0.000 abstract 1
- 238000006073 displacement reaction Methods 0.000 description 14
- 208000002740 Muscle Rigidity Diseases 0.000 description 7
- 238000005299 abrasion Methods 0.000 description 5
- 238000003754 machining Methods 0.000 description 4
- 238000003801 milling Methods 0.000 description 4
- 238000005553 drilling Methods 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 208000036366 Sensation of pressure Diseases 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 229910052729 chemical element Inorganic materials 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 229940000425 combination drug Drugs 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000002542 deteriorative effect Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Classifications
-
- 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
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/25—Movable or adjustable work or tool supports
- B23Q1/26—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members
- B23Q1/34—Relative movement obtained by use of deformable elements, e.g. piezoelectric, magnetostrictive, elastic or thermally-dilatable elements
-
- 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
- B23Q1/00—Members which are comprised in the general build-up of a form of machine, particularly relatively large fixed members
- B23Q1/25—Movable or adjustable work or tool supports
- B23Q1/26—Movable or adjustable work or tool supports characterised by constructional features relating to the co-operation of relatively movable members; Means for preventing relative movement of such members
- B23Q1/34—Relative movement obtained by use of deformable elements, e.g. piezoelectric, magnetostrictive, elastic or thermally-dilatable elements
- B23Q1/36—Springs
Abstract
SPECIFICATION
TITLE OF INVENTION:
A coupled structure of constituting machine elements in machinery ABSTRACT OF THE DISCLOSURE:
A compound lathe is provided with a tool post (herein-after referred to as a machine element) and a tool post slide (hereinafter referred to as a machine element), and each of these machine elements is formed as a structure to be mutually coupled, and each machine element is provided with a coupling mechanism comprising a pressure chamber, a columnar member that receives the fluid pressure in the pressure chamber as a uniform tensile stress of axial direction, and a holder that is substantially made of a rigid material and being fixed to the tip of the columnar member so as to be shiftable only in the axial direction, and the coupling mechanism is integrally provided on each machine element to be mutually coupled by the base end portion of the columnar member and the holder to control the fluid pressure in the pressure chamber so that the positional relationship of each coupled machine element can be minutely adjusted.
TITLE OF INVENTION:
A coupled structure of constituting machine elements in machinery ABSTRACT OF THE DISCLOSURE:
A compound lathe is provided with a tool post (herein-after referred to as a machine element) and a tool post slide (hereinafter referred to as a machine element), and each of these machine elements is formed as a structure to be mutually coupled, and each machine element is provided with a coupling mechanism comprising a pressure chamber, a columnar member that receives the fluid pressure in the pressure chamber as a uniform tensile stress of axial direction, and a holder that is substantially made of a rigid material and being fixed to the tip of the columnar member so as to be shiftable only in the axial direction, and the coupling mechanism is integrally provided on each machine element to be mutually coupled by the base end portion of the columnar member and the holder to control the fluid pressure in the pressure chamber so that the positional relationship of each coupled machine element can be minutely adjusted.
Description
A PAIR OF MECHANICAL ELEMENTS COUPLED BY A CO~PLING MECHANISM
This invention relates to the combination of a pair of mechanical elements and a coupling mechanism for coupling the elements together, and to machinery incorporating such a com-bination.
5The present invention includes a coupling mechanism cap-able of providing a micro-displacement between the coupled elements that corrects or controls positional error generated due to thermal deformation or abrasion between the coupled elements. The type of elements which may he coupled in accordance with the present invention are for example a coup-ling portion of the base and the column of the drilling mach-ine or a coupling portion of the tool post or the tail stock and their slides, whereby the positional error due to thermal deformation or abrasion of the machinery is corrected without spoiling the rigidity in the coupling portions. Additionally the operational accuracy of the machinery can be maintained, and also, a controlled micro-displacement can be applied bet-ween the machine elements according to requirements to enabl~
the machinery to be more versatile in use.
20Heretofore, in a compound lathe, the tool post has been either fixed to the tool post slide or rotatably mounted thereto for rotation around a vertical axis (see Figure l), whilst transverse motion in a direction at right angles to the - spindle and the tool shaft was not allowed. In Figure l, the verticial direction of the drawing, hereinafter referred to as "Y axis direction". Accordingly, for example, when machining a key way, a milling cutter is normally mounted on the tool mounting shaft, and the width of the key way to be machined is controlled by the outside diameter of the milling cutter. When the cutter is worn, the width of the key way becomes narrow.
Also, if it is desired to increase the width of the key way it is normally necessary to exchange the cutter for a larger one.
An object of this invention is to retain the operation accuracy of the machinery by the correction of positional error due to thermal deformation or abrasion of the machinery .. ..
lZ~ O~
without spoiling the rigidity in the coupling portions where the machine elements are mutually coupled. Additionally, it is an object to provide controlled micro-displacement between coupled machine elements according to requirements.
Moreover, another object of this invention is to allow the micro-transer of the tool post in the Y-axis direction without spoiling the rigidity between the tool post and the tool post slide by coupling the tool post and the tool post slide in the compound lathe by means of a coupling mechanism of this invention, Thus when a key way is to be machined, correction of error o~ the dimension of the key way resulting from the abrasion wear of the milling cutter becomes possible, and as the result, a key way of an accurate width can be machined.
According to the present invention there is provided in combination, a pair of mechaniical elements and a coupling mechanism for coupling the elements together, the mechanism including a fluid pressure chamber formed in one of said ele-ments and an elongate member housed in said pressure chamber, the elongate member being fixed at one end to said one elemer.-and fixed at its opposite end to the other element so tha~
fluid pressure applied to said chamber causes relative move-ment between said elements and applies tensile stress to said member to cause it to stretch in an axial direction said one element and the elongate member being movably connected to one ~ another near to said opposite end of the elongate member to permit relative axial movement only.
Reference is now made to the accompanying drawings, in which:
~igure 1 is a side view schematically showing a compound lathe;
Figure 2 is a partial cross section showing a coupling mechanism accordinq to the present invention incorporated between a tool post and a tool post slide of a compound lathe;
Figure 3 is a block dia~ram showing a displacement quant-ity control unit for a tool post when coupled to a tool post slide by a coupling mechanism according to the present in-. ~, Sl.
)S30S
ventiorl;
~ igure ~ is a perspec~ive view schematically showing a drilling machine incorporating a coupling mechanism according to the present invention, which couples the column to the S base; and Figure 5 is a schematic perspective view of a lathe in-corporating a coupling mechanism according to the present in-vention between the tail stock, and its slide, and the tool post and its slide.
In Figure 1, there is shown a lathe W which is of gener-ally conventional construction except for the cou~ling mech-anism between tool post l and a tool post slide 2. The com-pound lathe W is provided with a bed 3, and is provided with a chuck mounted on the spindle. A cross slide 5 is mounted on tl~e bed 3 so as to be slidable in the axial direction of the spindle, and the tool post slide 2 coupled with the tool post l is mounted on the cross slide 5 so as to be slidable in a transverse direction to the axis of the spindle i.e. to the right or left as shown in Figure 1. The tool post slide 2 i-made ~o move slidably on the cross sllde 5 by a motor 6. T~l-tool post l is provided with a tool mounting shaft 7, and -.
milling cutter 3 is mounted on the tool mounting shaft 7, and the tool mounting shaft 7 is rotatably operated by a motor 9.
The tool post 1 and the tool post slide 2 are coupled by the coupling mechanism according to this invention as will be described in detail hereinafter.
In ~igure 2, the coupling mechanism for mutually coupling the post 1 and slide 2 (which may be generally described as being machine elements) is shown in detail. The coupling mechanism inclues a pressure chamber 10 formed in holder 15, and an elongate, preferably, columnar member 11 that is acted upon by the fluid pressure in the pressure chamber 10 as a uniform tensile stress in the axial direction. The holder 15 which forms part of the post 1 is substantially made of rigid materlal and is fixed to the tip 12 of the columnar member 11 and is interconnected with the base portion 13 of the columnar member 1~ so as to be relatively shiftable only in the axial ~Z053(~S
directioll. This is achieved by the portion 16a of base por-tion 13 being slidably received in the chamber or by a washer like spring plate 16. Accordingly, variation of the mutual micro-positional relationship of the coupled machine elements 1 and 2 is possible by utilizing the elastic deformation of the columnar member 11 caused by the fluid pressure in the pressure chamber 10. Since the'base portion 13 of the colum-nar chamber 11 and the holder 15 are interconnected to be relatively shiftable only in the axial direction by a washer like spring plate 16 or by portion 16a, slidingl~ engaging the chamber wall, the cutting reaction force working in a direc-tion at right angles to the Y axis is transmitted to the tool post slide 2, and no bending stress works'on the columnar mem-ber 11, and therefore, the rigidity in the coupled portion is assured, and also, an accurate linearity can be maintained between the fluid pressure in the pressure chamber 10 and dis-placement quantity of the machine element 1 in the Y axis di-rection.
r~ex~, this invention will be described by referring to embodiments shown in Figures 2 and 3.
The columnar member 11 of ~igure 2 is constructed in Such a way that the base end 14 is fixed to the tool post slide 2 by a bolt (not shown), and the tip 12 is fixed to the tool post 1 by means of the head member 17. The holding member 15 is integral with the tool post 1, and a cylindrical hole cent--- ering around the columnar member 11 ~is formed in the tool post, and a sleeve 18 is fitted within the cylindrical hole to : form the pressure chamber 10. The sleeve 18 is mounted so that the fluid pressure in the pressure chamber 10 does not work directly onto ~he tool post (which is a casting), and as a result, it is substantially an integral unit with the holder 15, and its lower end portion is slidable on the base portion 14 of the columnar member 11. ~he base portion 13 of the columnar member 11 and the holder 15 are interconnected so as to be movable only in the axial direction of the columnar mem-ber 11 by means of"the sliding portion 16a,-'but in order to increase the rigidity of the interlocking portion, the holder f~
~05305 15 and the base portion 13 of the columnar member 11 are conn-ected by the washer like spr.ing plate 16. The inside diamet-ral portion of the spr.ing plate 16 is sandwiched between the base end 14 of the columnar member 11 and the tool post slide
This invention relates to the combination of a pair of mechanical elements and a coupling mechanism for coupling the elements together, and to machinery incorporating such a com-bination.
5The present invention includes a coupling mechanism cap-able of providing a micro-displacement between the coupled elements that corrects or controls positional error generated due to thermal deformation or abrasion between the coupled elements. The type of elements which may he coupled in accordance with the present invention are for example a coup-ling portion of the base and the column of the drilling mach-ine or a coupling portion of the tool post or the tail stock and their slides, whereby the positional error due to thermal deformation or abrasion of the machinery is corrected without spoiling the rigidity in the coupling portions. Additionally the operational accuracy of the machinery can be maintained, and also, a controlled micro-displacement can be applied bet-ween the machine elements according to requirements to enabl~
the machinery to be more versatile in use.
20Heretofore, in a compound lathe, the tool post has been either fixed to the tool post slide or rotatably mounted thereto for rotation around a vertical axis (see Figure l), whilst transverse motion in a direction at right angles to the - spindle and the tool shaft was not allowed. In Figure l, the verticial direction of the drawing, hereinafter referred to as "Y axis direction". Accordingly, for example, when machining a key way, a milling cutter is normally mounted on the tool mounting shaft, and the width of the key way to be machined is controlled by the outside diameter of the milling cutter. When the cutter is worn, the width of the key way becomes narrow.
Also, if it is desired to increase the width of the key way it is normally necessary to exchange the cutter for a larger one.
An object of this invention is to retain the operation accuracy of the machinery by the correction of positional error due to thermal deformation or abrasion of the machinery .. ..
lZ~ O~
without spoiling the rigidity in the coupling portions where the machine elements are mutually coupled. Additionally, it is an object to provide controlled micro-displacement between coupled machine elements according to requirements.
Moreover, another object of this invention is to allow the micro-transer of the tool post in the Y-axis direction without spoiling the rigidity between the tool post and the tool post slide by coupling the tool post and the tool post slide in the compound lathe by means of a coupling mechanism of this invention, Thus when a key way is to be machined, correction of error o~ the dimension of the key way resulting from the abrasion wear of the milling cutter becomes possible, and as the result, a key way of an accurate width can be machined.
According to the present invention there is provided in combination, a pair of mechaniical elements and a coupling mechanism for coupling the elements together, the mechanism including a fluid pressure chamber formed in one of said ele-ments and an elongate member housed in said pressure chamber, the elongate member being fixed at one end to said one elemer.-and fixed at its opposite end to the other element so tha~
fluid pressure applied to said chamber causes relative move-ment between said elements and applies tensile stress to said member to cause it to stretch in an axial direction said one element and the elongate member being movably connected to one ~ another near to said opposite end of the elongate member to permit relative axial movement only.
Reference is now made to the accompanying drawings, in which:
~igure 1 is a side view schematically showing a compound lathe;
Figure 2 is a partial cross section showing a coupling mechanism accordinq to the present invention incorporated between a tool post and a tool post slide of a compound lathe;
Figure 3 is a block dia~ram showing a displacement quant-ity control unit for a tool post when coupled to a tool post slide by a coupling mechanism according to the present in-. ~, Sl.
)S30S
ventiorl;
~ igure ~ is a perspec~ive view schematically showing a drilling machine incorporating a coupling mechanism according to the present invention, which couples the column to the S base; and Figure 5 is a schematic perspective view of a lathe in-corporating a coupling mechanism according to the present in-vention between the tail stock, and its slide, and the tool post and its slide.
In Figure 1, there is shown a lathe W which is of gener-ally conventional construction except for the cou~ling mech-anism between tool post l and a tool post slide 2. The com-pound lathe W is provided with a bed 3, and is provided with a chuck mounted on the spindle. A cross slide 5 is mounted on tl~e bed 3 so as to be slidable in the axial direction of the spindle, and the tool post slide 2 coupled with the tool post l is mounted on the cross slide 5 so as to be slidable in a transverse direction to the axis of the spindle i.e. to the right or left as shown in Figure 1. The tool post slide 2 i-made ~o move slidably on the cross sllde 5 by a motor 6. T~l-tool post l is provided with a tool mounting shaft 7, and -.
milling cutter 3 is mounted on the tool mounting shaft 7, and the tool mounting shaft 7 is rotatably operated by a motor 9.
The tool post 1 and the tool post slide 2 are coupled by the coupling mechanism according to this invention as will be described in detail hereinafter.
In ~igure 2, the coupling mechanism for mutually coupling the post 1 and slide 2 (which may be generally described as being machine elements) is shown in detail. The coupling mechanism inclues a pressure chamber 10 formed in holder 15, and an elongate, preferably, columnar member 11 that is acted upon by the fluid pressure in the pressure chamber 10 as a uniform tensile stress in the axial direction. The holder 15 which forms part of the post 1 is substantially made of rigid materlal and is fixed to the tip 12 of the columnar member 11 and is interconnected with the base portion 13 of the columnar member 1~ so as to be relatively shiftable only in the axial ~Z053(~S
directioll. This is achieved by the portion 16a of base por-tion 13 being slidably received in the chamber or by a washer like spring plate 16. Accordingly, variation of the mutual micro-positional relationship of the coupled machine elements 1 and 2 is possible by utilizing the elastic deformation of the columnar member 11 caused by the fluid pressure in the pressure chamber 10. Since the'base portion 13 of the colum-nar chamber 11 and the holder 15 are interconnected to be relatively shiftable only in the axial direction by a washer like spring plate 16 or by portion 16a, slidingl~ engaging the chamber wall, the cutting reaction force working in a direc-tion at right angles to the Y axis is transmitted to the tool post slide 2, and no bending stress works'on the columnar mem-ber 11, and therefore, the rigidity in the coupled portion is assured, and also, an accurate linearity can be maintained between the fluid pressure in the pressure chamber 10 and dis-placement quantity of the machine element 1 in the Y axis di-rection.
r~ex~, this invention will be described by referring to embodiments shown in Figures 2 and 3.
The columnar member 11 of ~igure 2 is constructed in Such a way that the base end 14 is fixed to the tool post slide 2 by a bolt (not shown), and the tip 12 is fixed to the tool post 1 by means of the head member 17. The holding member 15 is integral with the tool post 1, and a cylindrical hole cent--- ering around the columnar member 11 ~is formed in the tool post, and a sleeve 18 is fitted within the cylindrical hole to : form the pressure chamber 10. The sleeve 18 is mounted so that the fluid pressure in the pressure chamber 10 does not work directly onto ~he tool post (which is a casting), and as a result, it is substantially an integral unit with the holder 15, and its lower end portion is slidable on the base portion 14 of the columnar member 11. ~he base portion 13 of the columnar member 11 and the holder 15 are interconnected so as to be movable only in the axial direction of the columnar mem-ber 11 by means of"the sliding portion 16a,-'but in order to increase the rigidity of the interlocking portion, the holder f~
~05305 15 and the base portion 13 of the columnar member 11 are conn-ected by the washer like spr.ing plate 16. The inside diamet-ral portion of the spr.ing plate 16 is sandwiched between the base end 14 of the columnar member 11 and the tool post slide
2, and is fixed to the side of the tool post slide 2, and its outside diametral portion is sandwiched between the lower end portion of the holder 15 and the holding member 19, and is fixed to the side of the holder 15. Reference numerals 20, 21, 22 denote pressure oil supply holes provided in the tool post slide 2 and the columnar member 11, and numerals 23 and 24 denote liquid sealing units, and numeral 25 shown by imaginary line denotes a workpiece.
In the foregoing structure~ when the operating pressure o~ oil supplied to the pressure chamber 10 is high, the press-ure produces a uniform tensile stress in the axial directionof the columnar member 11. The tool post 1 is displaced by a micro-quantity in the upper direction in Figure 2 on account of the resulting elastic distortion of the columnar member 11 so that micro-displacement in the Y 2xis direction can be applied to the tool mounting shaft 7.
The pressure oil supply unit to the pressure chamber lt and the control system are shown in Figure 3, and numeral 2~
denotes a cylinder of the pressure oil supply unit, and 27 denotes a plunger moving back and forth in the cylinder 26, and 28 denotes a screw formed in~egral with the plunger 27, - and 29 denotes a gear meshed with the screw 28, and 30 denotes a gear meshed with the gear 29, and 31 denotes a DC motor for driving the gear 30, and 32 denotes an oil pressure pipe. The DC motor 31 rotates by the s~rvo control that is operated by the control unit to be described hereinafter, and rotates the gear 29 supported b~ the frame (not shown) by means of the bearing 33, and causes the non-rotating plunger 27 to move back and forth to change the pressure of the operating oil to be supplied to the pressure chamber 10, and change the quant-ity of displacement of the tool post 1 in the Y axis di-rection. ~ -I'he quantity of displacement of the tool post 1 is de-~Z~53~S
--6--tected by the differential transformer 34, and is applied to the differential amplifier 36 through the insulated amplifier 35, and on the other hand, the instruction data applied from the NC device or other instruction device ~not shown) is app-lied to the differential amplifier 36 through the D-A convert-er, and the servo amplifier controls the DC motor 31 by the differential signal. ~hen the output of the differential amplifier 36 becomes within a fixed allowable value, the coin-cidence signal from the comparator 37 is outputted to the in-struction device, and the position in the Y axis direction ofthe tool post 1 and the tool 8 is set at the instructed pos-ition.
As described in the foregoing, the position of the tool post 1 is corrected in the Y axis direction or is displaced, and machining error due to the thermal deformatlon of the loaded workpiece 25 or machining error due to the abrasion of the tool 8 is corrected or machining with accuracy according to the difference of various fitting dimensions such as a kev way or the like can be achieved by the displacement of tne too~ post 1 ir. the Y axis dlrection, but as the uniform ter-sile stress only is applied to the columnar member 11 by t~e construction mentioned in the foregoing, the accurate linear relationship between the pressure of the pressure oil to he supplied to the pressure chamber 10 and the displacement o~
the tool post 1 is assured whereby the control of the quantity of displacement can be carried out easily with extreme accuracy.
The foregoing embodiment is used for correcting or ad-justing the position of the tool post 1 in the Y axis direc-tion of a compound lathe W. It will be appreciated that thecoupling mechanism according to the present invention is suit-able for use in any mechanism or machinery where a high rigid-ity and accuracy in position of the coupling is required. For example, the drilling machine B shown in Figure 4 is such that the column 38 and the base portion 39 are~coupled by the coup-ling mechanism 40 of this invention, and the angle of the co1-umn 38 can be adjusted minutely and correctly by supplying oil .~
~` .
~zoS3~S
pressure selectively to the respective coupling mechanisms 40..... 40. ~umeral 47 of ~igure 4 denotes the support plate, and the column 38 is fixed to the support plate 47, and the support plate 47 and the base 39 are coupled by the coupling 5 mechanisms 40 ....... 40. Also, in the lathe T shown in Figure 5, the tail stock 41 and its tail stock slide 42 are coupled by using the coupling mechanisms 40 ..... 40 of this invention in horizontal direction, so that the spindle 43 and the tail stock 41 may be displaced in minute angle in the horizontal plane to perform correction of the taper of the workpiece 25 or degree of its cylindrical shape, and moreover, in case the tool post 44 and the tool post slide 45 are coupled by using the coupling mechanisms 40 ..... 40 of this invention in hori-zontal direction, so that the cutting tool ~6 may be stati-cally or dynamically moved back and forth to correct the d1-mension difference of the outside diameter of the workpiece 25 or to correct its roundness. Numeral 48 of Figure 5 de-notes the bed, and 49 denotes the base, and 50 denotes the machine case in ~hich the spindle drive mechanism i5 built in.
The columnar member 11 ir, the coupling mechanism of thl lnvention has high rigidity in the axial direction, and the possible displacement quantity of the coupled machine elemen~s is less than 1 milimeter. The control of the displacement quantity is possibly carried out with the accuracy in the order of 1 micron, and the fluid pressure to be supplied to the pressure chamber 10 is practically set at high pressure of about 500 to 700 kg per square centimeter. In this high pressure fluid as mentioned in the foregoing, the compressing property by the air to be mixed into the fluid becomes a major factor of deteriorating the control accuracy of the displace-ment quantity, particularly, the dynamic control accuracy. In order to avoid deterioration of control accuracy by the air present in the fluid, it is desirable to minimize the volume of the pressure chamber 10. This may be achieved by inserting a sleeve 51 into the pressure chamber 10 to reduce the volume of the pressure chamber 10 as shown in the imaginary line in Figure 2.
~, " .
In the foregoing structure~ when the operating pressure o~ oil supplied to the pressure chamber 10 is high, the press-ure produces a uniform tensile stress in the axial directionof the columnar member 11. The tool post 1 is displaced by a micro-quantity in the upper direction in Figure 2 on account of the resulting elastic distortion of the columnar member 11 so that micro-displacement in the Y 2xis direction can be applied to the tool mounting shaft 7.
The pressure oil supply unit to the pressure chamber lt and the control system are shown in Figure 3, and numeral 2~
denotes a cylinder of the pressure oil supply unit, and 27 denotes a plunger moving back and forth in the cylinder 26, and 28 denotes a screw formed in~egral with the plunger 27, - and 29 denotes a gear meshed with the screw 28, and 30 denotes a gear meshed with the gear 29, and 31 denotes a DC motor for driving the gear 30, and 32 denotes an oil pressure pipe. The DC motor 31 rotates by the s~rvo control that is operated by the control unit to be described hereinafter, and rotates the gear 29 supported b~ the frame (not shown) by means of the bearing 33, and causes the non-rotating plunger 27 to move back and forth to change the pressure of the operating oil to be supplied to the pressure chamber 10, and change the quant-ity of displacement of the tool post 1 in the Y axis di-rection. ~ -I'he quantity of displacement of the tool post 1 is de-~Z~53~S
--6--tected by the differential transformer 34, and is applied to the differential amplifier 36 through the insulated amplifier 35, and on the other hand, the instruction data applied from the NC device or other instruction device ~not shown) is app-lied to the differential amplifier 36 through the D-A convert-er, and the servo amplifier controls the DC motor 31 by the differential signal. ~hen the output of the differential amplifier 36 becomes within a fixed allowable value, the coin-cidence signal from the comparator 37 is outputted to the in-struction device, and the position in the Y axis direction ofthe tool post 1 and the tool 8 is set at the instructed pos-ition.
As described in the foregoing, the position of the tool post 1 is corrected in the Y axis direction or is displaced, and machining error due to the thermal deformatlon of the loaded workpiece 25 or machining error due to the abrasion of the tool 8 is corrected or machining with accuracy according to the difference of various fitting dimensions such as a kev way or the like can be achieved by the displacement of tne too~ post 1 ir. the Y axis dlrection, but as the uniform ter-sile stress only is applied to the columnar member 11 by t~e construction mentioned in the foregoing, the accurate linear relationship between the pressure of the pressure oil to he supplied to the pressure chamber 10 and the displacement o~
the tool post 1 is assured whereby the control of the quantity of displacement can be carried out easily with extreme accuracy.
The foregoing embodiment is used for correcting or ad-justing the position of the tool post 1 in the Y axis direc-tion of a compound lathe W. It will be appreciated that thecoupling mechanism according to the present invention is suit-able for use in any mechanism or machinery where a high rigid-ity and accuracy in position of the coupling is required. For example, the drilling machine B shown in Figure 4 is such that the column 38 and the base portion 39 are~coupled by the coup-ling mechanism 40 of this invention, and the angle of the co1-umn 38 can be adjusted minutely and correctly by supplying oil .~
~` .
~zoS3~S
pressure selectively to the respective coupling mechanisms 40..... 40. ~umeral 47 of ~igure 4 denotes the support plate, and the column 38 is fixed to the support plate 47, and the support plate 47 and the base 39 are coupled by the coupling 5 mechanisms 40 ....... 40. Also, in the lathe T shown in Figure 5, the tail stock 41 and its tail stock slide 42 are coupled by using the coupling mechanisms 40 ..... 40 of this invention in horizontal direction, so that the spindle 43 and the tail stock 41 may be displaced in minute angle in the horizontal plane to perform correction of the taper of the workpiece 25 or degree of its cylindrical shape, and moreover, in case the tool post 44 and the tool post slide 45 are coupled by using the coupling mechanisms 40 ..... 40 of this invention in hori-zontal direction, so that the cutting tool ~6 may be stati-cally or dynamically moved back and forth to correct the d1-mension difference of the outside diameter of the workpiece 25 or to correct its roundness. Numeral 48 of Figure 5 de-notes the bed, and 49 denotes the base, and 50 denotes the machine case in ~hich the spindle drive mechanism i5 built in.
The columnar member 11 ir, the coupling mechanism of thl lnvention has high rigidity in the axial direction, and the possible displacement quantity of the coupled machine elemen~s is less than 1 milimeter. The control of the displacement quantity is possibly carried out with the accuracy in the order of 1 micron, and the fluid pressure to be supplied to the pressure chamber 10 is practically set at high pressure of about 500 to 700 kg per square centimeter. In this high pressure fluid as mentioned in the foregoing, the compressing property by the air to be mixed into the fluid becomes a major factor of deteriorating the control accuracy of the displace-ment quantity, particularly, the dynamic control accuracy. In order to avoid deterioration of control accuracy by the air present in the fluid, it is desirable to minimize the volume of the pressure chamber 10. This may be achieved by inserting a sleeve 51 into the pressure chamber 10 to reduce the volume of the pressure chamber 10 as shown in the imaginary line in Figure 2.
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Claims (6)
1. In combination, a pair of mechanical elements and a coup-ling mechanism for coupling the elements together, the mech-anism including a fluid pressure chamber formed in one of said elements and an elongate member housed in said pressure cham-ber, the elongate member being fixed at one end to said one element and fixed at its opposite end to the other element so that fluid pressure applied to said chamber causes relative movement between said elements and applies tensile stress to said member to cause it to stretch in an axial direction said one element and the elongate member being movably connected to one another near to said opposite end of the elongate member to permit relative axial movement only.
2. The combination according to Claim 1 wherein the elongate member is in the form of a column.
3. The combination according to Claim 1 wherein said elongate member and said one element are connected to one another via a spring washer.
4. The combination according to Claim 1, 2 or 3 wherein the opposite end of the elongate member slidingly engages with the wall of the fluid chamber.
5. The combination according to claim 1, wherein the pressure chamber is defined by a sleeve which in use is inserted into a bore formed in said one element.
6. The combination according to Claim 5 wherein a further sleeve is incorporated within said pressure chamber in order to reduce the volume of the pressure chamber defined by said sleeve.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2052982A JPS58137542A (en) | 1982-02-10 | 1982-02-10 | Supporting structure for tool rest of combined lathe |
| JP57-20529 | 1982-02-10 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1205305A true CA1205305A (en) | 1986-06-03 |
Family
ID=12029678
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000420578A Expired CA1205305A (en) | 1982-02-10 | 1983-01-31 | Coupled structure of constituting machine elements in machinery |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS58137542A (en) |
| CA (1) | CA1205305A (en) |
| DE (1) | DE3304463A1 (en) |
| FR (1) | FR2521049B1 (en) |
| GB (1) | GB2114478B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1992001533A1 (en) * | 1990-07-24 | 1992-02-06 | Hamai Co., Ltd. | System for controlling postures of structures and machine tools |
| JP4198825B2 (en) * | 1999-06-08 | 2008-12-17 | トーヨーエイテック株式会社 | Grinding equipment |
| EP1787749B1 (en) | 2004-04-23 | 2008-10-08 | Schott AG | A device for machining microstructures |
| JP5519124B2 (en) * | 2008-06-17 | 2014-06-11 | 株式会社ヴァレオジャパン | Processing apparatus and processing method for simultaneously processing both surfaces of workpiece |
| CN108907871B (en) * | 2018-07-11 | 2020-11-06 | 台州市诚驰机电有限公司 | Machining equipment and machining process method of multi-angle high-pressure atomizing fan-shaped nozzle |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR1238368A (en) * | 1959-06-30 | 1960-08-12 | Machine tool called work unit | |
| DE1264929B (en) * | 1961-11-22 | 1968-03-28 | Ramisch & Co Dr | Device for machining crowning or hollow machining of essentially cylindrical workpieces |
| CH435864A (en) * | 1963-05-16 | 1967-05-15 | Ernst Heinkel Aktiengesellscha | Device for the position-determined releasable connection of two machine parts |
| FR1432219A (en) * | 1965-04-30 | 1966-03-18 | Process for the micrometric machining of any parts, any device for implementing the present process or similar process, as well as machine tools or other precision devices provided with this device | |
| GB1140166A (en) * | 1967-05-13 | 1969-01-15 | Marwin Machine Tools Ltd | Stressing of load-bearing members |
| FR1588597A (en) * | 1968-09-20 | 1970-04-17 | ||
| JPS5345034B2 (en) * | 1974-06-05 | 1978-12-04 | ||
| DD139225A1 (en) * | 1978-10-13 | 1979-12-19 | Stollberg Horst Heinrich | AUTOMATICALLY CONTROLLABLE FINISHING DEVICE, ESPECIALLY FOR TOOLING MACHINES |
-
1982
- 1982-02-10 JP JP2052982A patent/JPS58137542A/en active Granted
-
1983
- 1983-01-31 CA CA000420578A patent/CA1205305A/en not_active Expired
- 1983-02-09 FR FR8302057A patent/FR2521049B1/en not_active Expired - Fee Related
- 1983-02-09 GB GB08303516A patent/GB2114478B/en not_active Expired
- 1983-02-09 DE DE19833304463 patent/DE3304463A1/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| FR2521049A1 (en) | 1983-08-12 |
| DE3304463A1 (en) | 1983-08-18 |
| GB2114478A (en) | 1983-08-24 |
| GB8303516D0 (en) | 1983-03-16 |
| JPH0356858B2 (en) | 1991-08-29 |
| JPS58137542A (en) | 1983-08-16 |
| FR2521049B1 (en) | 1992-02-21 |
| GB2114478B (en) | 1985-10-30 |
| DE3304463C2 (en) | 1990-08-09 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |