US3078742A

US3078742A - Metal working apparatus

Info

Publication number: US3078742A
Application number: US796097A
Authority: US
Inventors: Ernest J Svenson
Original assignee: Odin Corp; WF and John Barnes Co
Current assignee: Babcock and Wilcox Co; Odin Corp
Priority date: 1959-02-27
Filing date: 1959-02-27
Publication date: 1963-02-26
Anticipated expiration: 1980-02-26

Description

Feb. 26, 1963- E. J. SVENSON METAL WORKING APPARATUS 18 Sheets-Sheet 1 Filed Feb. 2'7, 1959 Feb. 26, 1963 E. J. SVENSON 3,078,742

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Feb. 26,1963 E. J. SVENSON METAL WORKING APPARATUS 18 Sheets-Sheet 13 Filed Feb. 27, 1959 Feb. 26, 1963 E. J. SVENSON METAL WORKING APPARATUS 18 Sheets-Sheet 15 Filed Feb. 27. 1959 NEWWMQ v INVENTOR as; J. wewwz BY Feb. 26, 1963 Filed Feb. 27. 1959 E. J. SVENSON METAL WORKING APPARATUS 18 Sheets-Sheet 16 Feb. 26, 1963 Filed Feb. 27, 1959 E'. J. SVENSON METAL WORKING APPARATUS 18 She ets-Sheet 17 Feb. 26, 1963 E. J. svENspN METAL WORKING APPARATUS 18 Sheets-Sheet 18 Filed Feb. 27, 1959 INVENTOR. fined Jfflerwam United States Patent 3,078,742. METAL WORKING APPARATUS Ernest J. Svenson, Rockford, Ill., assignor, by mesne assignments, of one=half to W. F. and John Barnes Cornpany, Rockford, 111., a corporation of Illinois, and onehalf to Odin Corporation, Rockford, 111., a corporation of Illinois Filed Feb. 27, 1959, Ser. No. 796,097 23 Claims. (Cl. 77-335) The present invention relates to machine tools and more particularly to self-contained machine tool units and controls.

Many worth-while advantages are gained by using hydraulic systems in machine tools, particularly in selfcontained machine tool units, to control and to power movements which operate machine tools in relation to workpieces. For this reason, much effort and ingenuity have gone into the development of hydraulic control and power systems for self-contained machine tool units that are advanced and retracted in relation to a workpiece by a hydraulic motor controlled by hydraulic control structure incorporated into the hydraulic power system which includes the hydraulic motor.

However, the use of hydraulic control and power systems in this environment has pointed up a number of problems which have not been previously overcome on an altogether satisfactory basis. One such problem has been that of progressive heating of the hydraulic fluid during use of the machines. Increasing temperature of the hydraulic fluid not only changes the viscosity of the fluid, upsetting operation of the hydraulic system, but it also changes the temperature of major components of the machine structure and in this manner affects the positional relationships of fundamental machine parts. Some of the effects and results of heating of the hydraulic fluid in machine tools of this character include the following:

(1) Variation in the speed at which cutting tools are moved relative to a workpiece,

(2) Changes in the alignment of cutting tools relative to workpieces,

(3) The causation of bending actions between cutting tools and workpieces resulting in scoring and breaking down of structural parts, and

(4) Numerous difficulties arising from an undue reduction of the viscosity of the fluid, such, for example, as fluid leakage with the necessity for replenishing the hydraulic fluid supply, fire hazards, and a general contamination of the environment creating hazards to the operating personnel and requiring increased care and maintenance of the machinery.

Prior efforts to minimize the effect of progressively increasing hydraulic fluid temperatures attending the operation of machines equipped with such hydraulic systems have included the practice of operating a machine an hour or more before it is actually put into use in order to obtain some semblance of a stabilized temperature level. This expedient is not only expensive but is by no means wholly effective since the fluid temperature still changes after production is started. Other attempts have been made to provide means for compensating for changes in the viscosity of the fluid incident to changes in the fluid temperature. However, such approaches have lacked much to be desired in that they only partially compensate for the efiects of temperature variation and do not eliminate temperature increases or many undesirable effects of temperature increases.

As a matter of fact, the problems associated with the use of hydraulic control and actuating systems in machine tools have been so serious as to lead some manufacturers to abandon the use of such systems, at the sacriice fice of their advantages, and go back to the use of mechanical drives.

One object of my invention is to provide an improved machine tool with an improved hydraulic control and actuating system which will operate with great etficiency and effectiveness without significantly heating the hydraulic fluid used in the system, thereby eliminating the difficulties and problems previously associated with progressively increasing fluid temperatures in this environment.

Another object of my invention is to provide an improved machine tool having an improved hydraulic control and actuating system which makes the full power of the system continuously available for moving major components of the machine in relation to a workpiece even at a rapid traverse speed while at the same time eliminating the generation of heat to any appreciable degree in the fluid under all operating conditions.

A further object of my invention is to provide in a machine tool an improved hydraulic control and actuating system of the character set forth in the above object which is hydraulically alive and immediately responsive under all operating conditions to any demands made on the system.

A further object is to provide in self-contained machine tool unit an improved hydraulic control and actuating system, which under all operating conditions is immediately responsive to an electrical circuit control (operable from either a local or remote station) to immediately change the operating condition or cycle of the unit.

A further object is to provide an improved self-contained machining unit including an improved hydraulic actuation system which affords a more precise control over the feeding movement of the unit relative to a workpiece.

Another object of my invention is to provide improved control means for self-contained machine tool units which facilitates servicing of the control structure by relatively unskilled personnel in a manner which effectively avoids down time of the machining apparatus for servicing of the control structure.

Still another object is to provide improved machine tool control structure which can be serviced without danger of exposure to high voltages.

Still another object is to provide improved machine tool control structure which makes advantageous use of the capabilities of my improved self-contained machining units recited above.

Other objects and advantages of my invention will become apparent from the following description, taken with reference to the accompanying drawings, in which:

FIG. 1 is a partially sectioned side elevation of a selfcontained machine tool unit constructed in accordance with my invention;

FIG. 2 is a rear end elevation of the unit taken with reference to line 2-2 of FIG. 1;

FIG. 3 is a fragmentary longitudinal sectional view of the unit taken along the line 3--3 of FIG. 2;

FIG. 4 is a transverse sectional view taken along the line 4-4 of FIG. 1;

PEG. 5 is a fragmentary sectional view taken generally along the line 5-5 of FIG. 4 and showing components of the rapid traverse pump and the pilot pump;

FIG. 6 is a fragmentary sectional view taken generally along the line 66 of FIG. 5;

FIG. 7 is a sectional view taken along the broken line 7-7 of FIG. 6;

FIG. 8 is a fragmentary end view of the auxiliary and traversing pumps taken with reference to the line 8-8 in FIG. 6;

- FIG. 9 is a fragmentary sectional view taken generally along the line 99 of FIG. 4 and showing feed pump control structure;

FIG. 10 is a detail view on an enlarged scale showing coacting spiral gears used in the driving transmission;

FIG. 11 is a bottom view of the self-contained slide assembly taken with reference to line 1111 in FIG. 1;

FIG. 12 is a fragmentary lower end view of the translatory head taken with reference to the line 12-12 of FIG. 1;

FIG. 13 is a diagrammatic illustration of hydraulic actuating and control circuits used to controllably translate the slide assembly 12 along its support base;

FIG. 14 is a vertical sectional view of the master control valve assembly for the unit taken along the line 14-44 of FIG. 2;

FIG. 15 is a sectional view of the valve assembly taken along the line 1515 of FIG. 14;

FIG. 16 is a fragmentary sectional View taken along the line 1616 of FIG. 15;

FIG. 17 is a partially sectioned front view of the valve assembly;

FIG. 18 is a partially sectioned and somewhat simplified perspective view of the valve assembly;

FIG. 19 is a simplified vertical sectional view of the valve assembly showing the positional relationship of major parts positioned for energizing the actuator to effect feeding movement of a slide assembly;

FIG. 19A is a diagrammatic illustration of the hydraulic circuit corresponding to the valve positions in FIG. 19;

FIG. 20 is a fragmentary sectional view illustrating one hydraulic pilot control for the main valve;

FIG. 20A is a diagrammatic illustration of the hydraulic circuit of FIG. 20;

FIG. 21 is a fragmentary sectional view illustrating another hydraulic pilot control for the main valve;

FIG. 21A is a diagrammatic illustration of the hydraulic circuit of FIG. 21;

FIG. 22 is a simplified sectional view of the valve assembly corresponding to FIG. 19 but illustrating the position of the valves for traversing the slide assembly rearwardly;

FIG. 22A is a diagrammatic illustration of the hydraulic circuit of FIG. 22;

FIG. 23 is a fragmentary sectional view showing the main valve in neutral position;

FIG. 23A is a diagrammatic illustration of the hydraulic circuit of FIG. 23;

FIG. 24 is a view similar to FIG. 22 but illustrating the position of valve parts for rapidly traversing the slide assembly forward;

FIG. 24A is a diagrammatic illustration of the hydraulic circuit of FIG. 24;

FIG. 25 is a view similar to FIG. 24 but illustrating the valve element in neutral position;

FIG. 26 is a partially sectioned view taken from the line 2626 in FIG. 2 and showing internal components of a manifold;

FIG. 27 is a fragmentary sectional view taken along the line 2727 of FIG. 26;

FIG. 28 is a fragmentary view taken along the line 2828 of FIG. 26;

FIG. 29 is a lay-out of a portion of the hydraulic system coacting with the master valve assembly and illustrating specific components of this system in cross section;

FIG. 30 is a simplified cross sectional view illustrating the relationship of hydraulic passages associated with one end of the main control element when the latter is in rapid traverse forward position;

FIG. 31 is a view similar to FIG. 30 but showing the main valve control element shifted to feed position;

FIG. 32 is a view similar to FIG. 30 but showing the valve element in rapid traverse return position;

FIG. 33 is a view similar to FIG. 30 but showing the valve element in neutral position;

FIG. 34 is a fragmentary sectional view taken along the line 34--34 in FIG. 31;

FIG. 35 is a partially sectioned perspective view of the end of the valve element illustrated in FIGS. 32-64;

FIG. 36 is a diagrammatic illustration of control circuits used to control the individual machining units in conjunction with an automatic machining installation;

FIG. 37 is a continuation of the circuit diagram of FIG. 36;

FIG. 38 is a diagram of power circuits for a plurality of machining units and associated automatic machining structure;

FIG. 39 is a diagram of solenoid circuitsused in controlling machining apparatus;

FIG. 40 is a continuation of the diagram of FIG. 39;

FIG. 41 is a continuation of the diagram of FIG. 40;

FIG. 42 is a fragmentary side view showing a modified form of gears used to connect the power shaft with the drive shaft;

FIG. 43 is a fragmentary circumferential view showing the periphery of one of the gears of FIG. 42;

FIG. 44 is a fragmentary sectional view taken generally along the line 44-44 of FIG. 42;

FIG. 45 is a fragmentary sectional view taken along the slightly curving line 45-45 of FIG. 43 following the root of one of the gear teeth;

FIG. 46 is a fragmentary sectional view taken along the diagonal line 4646 of FIG. 43; and

FIG. 47 is a fragmentary sectional view taken along the line 4747 of FIG. 43.

General Description of Self-Contained Machine Tool Unit Having reference to the drawings in greater detail, the self-contained machine tool unit 10, FIG. 1, constructed in accordance with my invention comprises a self-energized, self-controlled, and self-propelled machining head or slide assembly 12 supported for translation on a pair of longitudinal ways 16 on an elongated base 14. The base 14 is designed for installation on a larger bed (not shown).

The forward end 18 of the translatable slide assembly 12 is designed to carry a multiple spindle head or other machining attachment 20 (indicated in phantom in FIG. 1) which is powered by the slide assembly and translated toward and away from a workpiece (not shown) by controlled self-propelled movement of the slide assembly along the ways 16.

The slide assembly 12 comprises a main frame or housing 22 slideably supported on the ways 16 and surmounted on its rear end by an electric driving motor 24. The motor is connected by guarded V-belts 26 with a pulley 28, FIG. 3, on the rearwardly protruding end of a longitudinal power shaft 30 extending centrally through the housing 22. Support for the motor 24 is provided by a mount 32 which can be tipped about a hinge axis 34, FIG. 2, by a threaded adjusting element 37, FIG. 1, to vary the tension in the belts 26.

The housing 22 is formed by a hollow casting, denoted by the same reference numeral, which is internally shaped and adapted as will presently appear to define a reservoir 36 for lubricating oil and a reservoir 38 for hydraulic fluid, FIG. 3, which are completely isolated from each other so as to prevent the interchange of liquid from one to the other.

The lubricating oil reservoir 36 comprises space within a relatively large transmission chamber 39 in the forward end of the housing 22 and a hollow longitudinal shaft housing 40 extending rearwardly from the transmission Iczlizirntger to the rear end of the housing 22 as shown in The rear end of the power shaft 36 is supported in the rear end of the shaft housing 40 by an anti-friction hearing 42. Annular seals 44 adjacent bearing 42 prevent the escape of lubricating oil around the shaft 30.

The power shaft 30 extends through the shaft housing

Claims

1. A MACHINING UNIT COMPRISING, IN COMBINATION A MOVABLE MACHINING ASSEMBLY, MEANS FOR SUPPORTING SAID ASSEMBLY FOR MOVEMENT RELATIVE TO A WORKPIECE, A HYDRAULIC ACTUATING CYLINDER FOR MOVING SAID ASSEMBLY, A HIGH VOLUME RAPID TRAVERSE PUMP, A POSITIVE DISPLACEMENT FEED PUMP, VALVE MEANS FOR CONNECTING SAID PUMPS TO OPERATE SAID CYLINDER AND INCLUDING A MASTER VALVE HAVING A PLURALITY OF POSITIONS INCLUDING A FEEDING POSITION, SAID VALVE MEANS INCLUDING A SLAVE VALVE HAVING A PLURALITY OF POSITIONS INCLUDING A FEEDING POSITION, CONTROL MEANS FOR SAID SLAVE VALVE HYDRAULICALLY INTERCONNECTED WITH SAID MASTER VALVE TO LOCATE THE SALVE VALVE IN THE FEEDING POSITION THEREOF AS AN INCIDENT TO MOVEMENT OF THE MASTER VALVE INTO THE FEEDING POSITION THEREOF, HYDRAULIC CONTROL MEANS ASSOCIATED WITH SAID SLAVE VALVE TO EFFECT UPON MOVEMENT OF THE LATTER INTO SAID FEEDING POSITION THEREOF CONNECTIONS BETWEEN THE INTAKE AND OUTLET OF SAID FEED PUMP AND HYDRAULICALLY OPPOSITE SIDES OF SAID HYDRAULIC MOTOR, AND MEANS INTERCONNECTING SAID FEED PUMP WITH SAID SLAVE VALVE TO UNLOAD THE BACK PRESSURE ON THE FEED PUMP WHEN THE SLAVE VALVE IS IN A POSITION OTHER THAN SAID FEEDING POSITION THEREOF.