WO2002072295A1

WO2002072295A1 - Machine for manufacturing of objects

Info

Publication number: WO2002072295A1
Application number: PCT/SE2002/000395
Authority: WO
Inventors: Håkan OLSSON
Original assignee: Morphic Technologies Aktiebolag
Priority date: 2001-03-13
Filing date: 2002-03-07
Publication date: 2002-09-19
Also published as: SE0100835D0; SE518669C2; SE0100835L

Abstract

In a machine for manufacturing of objects which substantially consist of a formable material, such as metal and/or a ceramic material, by forming or other working of the formable working material by means of forming or machine tools, the tool is provided in a tool carrier, which consists of a tool shuttle (2), which is slideably provided on or in a machine stand and which can be moved along a first liniar path relative to the machine stand between different positions, which are set in advance. A balance shuttle (10), is movable in parallel with the path of the tool shuttle but in the opposite direction. The forces which the motion devices of the tool shuttle apply on the tool shuttle in order to achieve the movement of the tool shuttle are essentially equally large with the forces which the motion devices of the balance shuttle apply on the balance shuttle in order to achieve the counter-directed movement of the balance shuttle along the second path, in order that the applied forces shall balance each other, so that essentially no dynamic reaction forces are transferred to the machine stand.

Description

MACHINE FOR MANUFACTURING OF OBJECTS

TECHNICAL FIELD

The invention relates to a machine for manufacturing of objects which substantially consist of a formable material, such as metal and/or a ceramic material, by forming or other working of the formable working material by means of forming or machine tools.

BACKGROUND OF THE INVENTION

Swedish patent application 0003279-7 of the same applicant discloses an impact machine for forming a body with desired shape of a formable working material in a forming operation, said machine comprising a machine stand and, according to an embodiment, a tool carrier which has the shape of a shuttle, which comprises a plurality of equal forming tool units. The shuttle is movable in a machine stand and motion devises are provided for moving the shuttle to and fro operation stations of the tool units along a linear path of motion. The shuttle, including the tool units, may be very heavy, e.g. weigh 200 kg or more. In order that the machine shall have a desirably high production capacity, the shuttle with the said mass has to be moved at a very high velocity between the different operation stations, e.g. with a velocity of 1-2 m/s. In order quickly to reach the said velocity, e.g. in about 50 microseconds, very high acceleration forces- maybe several hundred kN-need to be applied on the shuttle by means of motion devices, which either may consist of motion devices mounted on separate foundations or of motion devices mounted on the machine stand. In the former case, the separate foundations must be made very strong and in a latter case, the machine stand must be made correspondingly strong in order to absorb the very large, dynamic reaction forces which the foundation and the machine stand, respectively, is subjected to, when the shuttle is accelerated and retarded, unless measures or devices are provided for eliminating the reaction forces.

DISCLOSURE OF THE INVENTION It is an object of the invention to address the above complex of problems. It is particularly a purpose to solve the said problems in connection with the machine which is disclosed in the said Swedish Patent application No. 0003279-7, but the usability of the invention is not limited specifically to that machine, and nor is that for which patent is sought in anyway limited to that application. To the contrary, the invention may find a wide use for various types of machines which comprise heavy elements which shall be moved quickly, often short distances, between different positions. The machine according to the invention thus comprises a machine stand and at least one tool or a tool part provided in a tool carrier, which comprises at least a first shuttle, in the following referred to as tool shuttle, which is slideably provided on or in the machine stand and which can be moved along a first liniar path relative to the machine stand between different positions, which are set in advance, said positions defining stations for performing operations in or by means of said tool in connection with the manufacturing of said object. Further characterising features of the invention are

- that first motion devises are provided to move at least said tool shuttle in both directions along said first linear path, - that at least one second shuttle, in the following referred to as balance shuttle, is movable along a second linear path parallel with the path of the tool shuttle,

- that second motion devices are provided to move at least said balance shuttle relative to the machine stand along said second linear path in connection with each movement which the first shuttle is caused to perform, simultaneously and with essentially the same duration as said movement but in the opposite direction, and

- that the force which said first motion devices apply on the tool shuttle in order to achieve the movement of the tool shuttle along the first path is essentially equally large with the force which said second motion devices apply on the balance shuttle in order to achieve the counter directed movement of the balance shuttle along the second path, in order that the applied forces shall balance each other, so that essentially no dynamic reaction forces are transferred to the machine stand.

Provided that the first shuttle, i.e. the tool carrier, has a given mass and that the forces which act on the first shuttle and on the second shuttle or second shuttles, respectively, are equally large, the ratio between the accelerations of the shuttles will be invertedly proportional to the masses of the shuttles. The same condition applies also as far as the relation between the velocities of the shuttles are concerned. On the other hand the momentum of said at least a first and of said at least a second shuttle will be equally large, when momentum p** = m x v (the mass x the velocity). The fact that the momentums will be equally large in both directions (if some losses of energy in the system are neglected) is also typical in order that the dynamic forces will balance one another so that the stand will not be subjected to any substantial reaction forces.

Typically the motion devices of the machine are hydraulically acting devices. Said first motion devices comprise at least a first hydraulic piston, in the following referred to as tool shuttle piston, in a first hydraulic cylinder, in the following referred to as tool shuttle cylinder, and a first piston rod which extends through the tool shuttle cylinder and is fixedly connected to the tool shuttle. Further, according to said aspect of the invention, said second motion devices comprise at least a second hydraulic piston, in the following referred to as balance shuttle piston, in a second hydraulic cylinder, in the following referred to as balance shuttle cylinder, and a second piston rod which is parallel with the first piston rod and extends through the balance shuttle cylinder and is fixedly connected to the balance shuttle, and whereas the tool shuttle cylinder/cylinders and the balance shuttle cylinder/cylinders are stationarily secured relative to the stand.

Preferably, the shuttles are provided to move horizontally, wherein the resulting centres of gravity of the moveable masses of said tool shuttle and balance shuttles, respectively, which move in opposite direction, will lie in essentially the same vertical and horizontal planes, in order to avoid that any substantial dynamic movement forces will arise in connection with the movements of the shuttles. Due to the fact that such forces can be avoided, the piston rods and possible guides, guide rails or corresponding need not be made very powerful, and nor will it be necessary to dimension the machine stand in consideration of such forces.

According to a preferred embodiment, the machine comprises only one tool shuttle and only one balance shuttle, said tool shuttle and said balance shuttle turning one of their ends towards one another, and are movable towards and from one another. It is, however, possible to provide more shuttles; more tool shuttles as well as more balance shuttles. The machine may for example comprise at least one balance shuttle which is movable on each side of a single tool shuttle, or possibly a plurality of tool shuttles. Further, according to the preferred embodiment, a tool shuttle cylinder and a balance shuttle cylinder, and auxiliary piston rods, are provided on each side of the shuttles. According to the same, preferably chosen embodiment, the tool shuttle cylinder and the balance shuttle cylinder on each side of the shuttles are provided over one another, but it is also conceivable to provide them side by side on each side of the shuttles. In both cases, the arrangement provides a possibility to make the machine comparatively short in the direction of motion of the shuttles. In this embodiment, preferably only that section of each of the first piston rods, i.e. the piston rods which belong to the tool shuttle piston, which extend in the direction which corresponds to the direction of movement of the tool shuttle, away from the balance shuttle, is connected to the tool shuttle, and only that section of each of the second piston rods, i.e. those piston rods which belong to the balance shuttles, which extend in the direction which corresponds to the direction of movement of the balance shuttle, away from the tool shuttle, are connected to the balance shuttle. If the tool shuttle cylinder and the balance shuttle cylinder on each side of the shuttles, lie after one another, which also is possible, the two sections of the piston rods, on the other hand, are connected preferably to the respective shuttle.

According to an aspect of the invention the machine is further characterised in that the shuttles are provided to move horizontally along paths which comprise at least two stations, in which the shuttle shall be caused to stop, said stations, as far as the tool shuttle is concerned, comprising at least a forming station, in which the tool or tool part that is carried by the tool shuttle shall be caused to stop in a correct forming position relative to one or more stationary tools or tool parts provided in the forming station, that at least a first mechanical positioning device is provided for positioning the tool shuttle and thence the tool or tool part in a correct forming position in the forming station by direct or indirect mechanical contact between the positioning device and the tool shuttle, and that braking devices are provided for reducing the velocity of the tool shuttle from a high transport velocity to a much lower approach velocity within a braking distance, before the tool shuttle and the positioning device are caused to contact each other.

The machine can also be designed such that the tool shuttle and the balance shuttle are provided to be caused to stop also in one or more stations between the end stations, in which case mechanical and/or hydraulical positioning devices are provided for positioning the tool shuttle in desired positions in the intermediate stations.

Said braking devices are suitably hydraulic. According to a preferred embodiment, the braking devices comprise a braking chamber in each end of the balance shuttle cylinder, in which case the balance shuttle piston is provided with two end portions projecting in opposite directions, which end portions are dimensioned to be able to enter into a respective braking chamber while forming a narrow gap between said projecting end portions, which preferably are cylindrical, and the wall of the braking chamber which has a corresponding shape, through which gap the hydraulic fluid can be pressed back slowly in a direction towards the balance shuttle piston for the achievement of a desired braking action.

The said braking devices which are provided for reducing the velocity of the tool shuttle as that shuttle is approaching a station, and particularly when approaching intermediate stations, may also comprise valve members which will position the tool shuttle by a servo function, which causes a restriction of the flow of the hydraulic fluid. The valve members may possibly be completed with mechanical stops, which may be stationary or be provided to be brought to engage the tool shuttle. The latter case particularly applies when the tool shuttle shall be positioned very accurately in an intermediate station, in doing which movable stops or positioning members in the form of male members may be entered sideways into matching female members in the tool shuttle.

The machine according to the invention may comprise also a hydraulic circuit for controlling the movements of said hydraulic pistons and hence the movements of the shuttles. This circuit comprises valve organs. According to a preferred embodiment there is employed a modified valve of the type that is disclosed in the Swedish patent application 0002038-8 by the same applicant. The disclosure of said patent application is integrated into the present application by reference. According to the modification, this valve is designed as a 7-ports valve.

Further characteristic features and aspects of the invention will be apparent from the appending patent claims and from the detailed description of a preferred embodiment.

BRIEF DESCRIPTION OF DRAWINGS In the following description of a conceivable embodiment, reference will be made to the accompanying drawings, in which

Fig. 1 is a perspective view of an impact machine, in which the invention is employed; Fig. 2 schematically shows the hydraulic system of the machine for manoeuvring and controlling a tool shuttle and a balance shuttle; Fig. 2A schematically shows a valve unit in an other position than the position of the same valve unit in Fig. 2; and Fig. 3 schematically shows a pair of hydraulic cylinders and hydraulic pistons included in the hydraulic system in Fig. 1.

DETAILED DESCRIPTION OF AN EMBODIMENT

As an illustrative example of how the present invention can be used, there is shown in Fig. 1 a so called impact machine. This is a machine for the carrying out of working operations by the employment of a high kinetic energy, in the first place for metal working, such as cutting and punching, forming of metals, powder compaction, and similar operations. The machine comprises a stand 1 and a tool carrier 2, which carries a tool 3. The tool 3 according to the embodiment consists of a die. The working principle of the machine is based on the development of a very high kinetic energy of short duration of an upper ram 5 with an upper punch 6 and of a low ram 7 with a not shown lower punch, which are simultaneously stricken from above and from below, respectively, towards the die 3 and the working material which is placed in the mould cavity of the die. Devices for manoeuvring the rams 6, 7 do not form part of the invention and are not shown in the drawings.

The tool carrier 2 consists of a shuttle, in the following denominated tool shuttle. The tool shuttle according to the example is movable between two working stations; a forming station and a discharging station. In Fig. 1 and in Fig. 2, the tool shuttle 2 with the die 3 is shown in the forming station. The discharging station is located further at the rear as viewed in Fig. 1 and further to the right with reference to Fig. 2. In the discharging station, the formed product is pushed out from the tool. In the discharging station, the mould cavity of the die also can be filled with new working material. As an alternative, the filling can be performed in the forming station. Devices for discharging the formed product and for filling the mould cavity with new working material are not shown, since these devices per se do not form part of the invention.

For the movements of the tool shuttle 2 between the working stations, a pair of first hydraulic cylinders are provided, in the following denominated tool shuttle cylinders 9, one on each side of the tool shuttle 2. The tool shuttle cylinders 9 can develop very large forces, which are required in order to move the heavy tool shuttle 2 very quickly between the working stations. In order to avoid large dynamic forces to be developed in the system, which could be transferred to the stand 10, which therefore should need to be made very strong, there is, according to the invention, provided a balance shuttle 10 essentially in the same plane as the tool shuttle 2. When the tool shuttle 2 is in the forming station, the balance shuttle 10 is positioned with one end adjacent to one end of the tool shuttle, as is shown in Fig. 1 and Fig. 2. When the tool shuttle 2 is moved by means of the tool shuttle cylinders 2 from the forming station to the discharging station by means of a certain resulting force which is developed by the tool shuttle cylinders 9, the balance shuttle 10 is moved in the opposite direction, away from the tool shuttle 2 by means of a pair of second hydraulic cylinders, in the following denominated balance shuttle cylinders 11, which develop a resulting force acting on the balance shuttle, which force has a magnitude which is essentially equal to the magnitude of the force that the tool shuttle cylinders 9 develop, acting on the tool shuttle 2. The balance shuttle cylinders 11 are located under the tool shuttle cylinders 9. All hydraulic cylinders 9 and 11 are stationary and are fixed to the stand 1.

Under the shuttles 2 and 10 there are a pair of horizontal, parallel rails 13, which rest on and are connected to a pair of strong plates 14, in the following denominated rail beds. The rail beds 14 are fixed to the stand 1. During their movements, the shuttles 2 and 10 are provided to roll on the rails 13. For this purpose a number of small ball bearing carriages under the shuttles are fixed to the shuttles and rest on the rails 13.

The tool shuttle 2, including the die 3 and any further components included in the die, and the pistons and the piston rods of the tool shuttle have a mass equal to that of the balance shuttle 10 including the pistons and piston rods of the balance shuttle; i.e. in other words the masses which move in opposite directions are equally large. Further, those elements which comprise the movable masses which move in opposite directions, are so dimensioned and placed relative to the rails 13, that their centres-of-gravity will lie in the same horizontal and vertical planes; this also having the purpose to avoid dynamic reaction forces which could cause unbalanced conditions in the machine when the shuttles are moved.

In Fig. 2 and Fig. 3 one of the two tool shuttle cylinders 9 and one of the balance shuttle cylinders 11 are shown schematically. It should be understood that the two tool shuttle cylinders and the two balance shuttle cylinders 11 are identically designed and that the hydraulic circuit of one of the tool shuttle cylinders 9 and of one of the balance shuttle cylinders 11, which circuit is schematically shown in Fig. 2, is connected in parallel to an equal circuit of the cylinders on the opposite side of the shuttles. It should also be understood that these two circuits, which are connected in parallel, are served by a joint valve unit which is shown schematically in Fig. 2 and is designated 16.

In each tool shuttle cylinder 9 there is a tool shuttle piston 17 with a first piston rod 18, which extends through the tool shuttle cylinder 9. Each piston rod 18 has a front section 19, which is visible in Fig. 1, and a rear section 20, which is shown in Fig. 3, extending to the right in that drawing. Moreover, in Fig. 3 a first hydraulic chamber on one side of the tool shuttle piston 17 is designated VI and a second hydraulic chamber on the other side of the piston 17 is designated V2.

In each balance shuttle cylinder 11 there is a balance shuttle piston 22 with a projecting cylindrical portion 23 and 24, respectively, on each side of the piston 22. With reference to Fig. 3, a first hydraulic chamber Bl is provided in the balance shuttle cylinder 11, and on the opposite side of the piston 22 there is a second hydraulic chamber B2. Moreover, at the end of the hydraulic chamber Bl there is a first cylindrical braking chamber 25, and at the end of the hydraulic chamber B2 there is a second cylindrical braking chamber 26. The braking chambers 25 and 26 are so dimensioned that they can receive said projecting chambers 23 and 24, respectively, of the braking shuttle piston

22, and said braking chambers and said projection portions moreover are so dimensioned that there is formed a narrow, angular gap between said projecting portions

23, 24 and the cylindrical wall of the respective braking chambers 25 and 26, when said projection portions 23 and 24, respectively, are entered into the braking chambers.

The piston rod 28 of the braking shuttle piston 22 has a front section 29, which is visible in Fig. 1, and extends to the left in Fig. 2 and in Fig. 3 and a right hand section 30, which is not visible in Fig. 1 but which extends to the right in Fig. 2 and Fig. 3.

The valve unit is shown only symbolically in Fig. 2 and in Fig. 2A. As has been mentioned in the disclosure of the invention in the foregoing, a valve of the type that is disclosed in the Swedish patent application 0002038-8 of the same applicant, but modified to a 7-ports valve, can be employed as a valve unit 16. A conduit A leads from the valve unit 16 to a port 33 of the first hydraulic chamber VI of the tool shuttle cylinder 9. The conduit A, in the shown position of the valve unit 16, is connected to a pressure source 9 for the supply of a hydraulic fluid. An equal conduit A leads in a corresponding mode in parallel to that tool shuttle cylinder 9 which is coupled in parallel to the tool shuttle cylinder 9 shown in Fig. 2 on the opposite side on the tool shuttle. Analogue conditions apply for the other hydraulic conduits and will therefore not be repeated in the further description of the hydraulic system which is schematically shown in Fig. 2. From a port 34 at the end of the second hydraulic chamber V2 on the opposite side of the tool shuttle piston 17, a hydraulic conduit B leads via the valve unit 16 and a hydraulic conduit C to a port 35 of the first hydraulic chamber Bl of the balance shuttle cylinder 11 adjacent to the first braking chamber 25. From a correspondingly located port 36 of the second hydraulic chamber 52, a hydraulic conduit D leads to the valve unit 16 and from that valve unit further on to a tank T or accumulator in the position of the valve unit 16 according to Fig. 2.

A strangled by-pass-conduit 27 extends between a port 45 of the hydraulic chamber B 1 adjacent to the braking chamber 25 to a port 46 of the hydraulic chamber B2 adjacent to the braking chamber 26. The ends of the rear piston rod sections 20 of the tool shuttle cylinders 9 are connected to the rear end of the tool shuttle 2 via a rigid link 40. The said connection links 40 extend over the rails 13. The front piston rod portions 19 belonging to the tool shuttle cylinder 9 abut a stationary, mechanical stop 41 in the position shown in Fig. 2. These two mechanical stops 41 are adjustably fixed to the rail beds 14, as is shown in Fig. 1. In a corresponding way a pair of equal mechanical stops are provided in the rear part of the machine, adjustably fixed to the rail beds 14. One of these mechanical stops 42 is shown in Fig. 1.

The ends of the front piston rods 29 of the balance shuttle cylinders 11 are rigidly connected to the balance shuttle 10 via links 43. One of these links 43 is schematically shown in Fig. 2.

As is shown in Fig. 1, the links 43 comprise a plate 43 A, which extends through a longitudinal slot 44 in the two rail beds 14. The plates 43a are connected to the balance shuttle 10 on the bottom side thereof.

The tool shuttle 2, including the tool 3, weighs about 270 kg according to the described example. When the tool shall be exchanged, the comparatively heavy unit can be transported to a work bench. This problem can easily be solved due to the arrangement including a rail-mounted tool shuttle, namely by means of a simple transport trolley which is provided with rails on the same level and having the same width as the rails 13.

Upon removal of the connection links 40 between the piston rod sections 20 and the tool shuttle 2, and when the trolley has been wheeled so that its rails abut the rails 13, the tool shuttle 2 can be rolled over to the trolley, which then is wheeled to the place where the change of tools shall be carried out.

The working mode of the machine during a cycle comprising moving the tool shuttle 2 to and fro between the two working stations shall now be described. The starting position is assumed to be the position shown in Fig. 1 and Fig. 2. The tool shuttle 2 then is positioned in the forming station. The ends of the front (left in Fig. 2) piston rod sections 19 of the tool shuttle cylinder 9 abut the stationary, mechanical end stops 41. Before the end stops are fixed to the rail beds 14, they are set with a great accuracy, so that the die 3 will be centred with great accuracy relative to the upper punch 6 and to the not shown lower punch. The tool shuttle pistons 17 are in their left hand end positions with reference to Fig. 2, while the balance shuttle pistons 22 are in their right hand end positions. The balance shuttle 10, which has the same mass as the tool shuttle 2 is in a position adjacent to the tool shuttle 2. Between the shuttles there is a gap of about 10 mm.

When the valve unit 16 is in the position shown in Fig. 2, the hydraulic conduit A is connected to the pressure source P, wherein hydraulic fluid is driven into the first hydraulic chamber VI of the tool shuttle cylinder 9, where it develops a pressure of 300 bar according to the example. This causes the tool shuttle piston 17 to be forced to the right, initiating a movement of the tool shuttle 2 rear-wise with reference to Fig. 1 and to the right with reference to Fig. 2. A counter-pressure of 150 bar is developed in the second hydraulic chamber V2 of the tool shuttle cylinder. The differential pressure, which acts driving upon the tool shuttle piston 17, thus is 150 bar. The same pressure acts driving on the balance shuttle piston 22 therein that hydraulic fluid is driven into the first hydraulic chamber Bl of the balance shuttle cylinder 11 via the hydraulic conduits B and C, at the same time as the hydraulic fluidum of the second hydraulic chamber B2 is discharged through the conduit D to tank T or accumulator. Due to the fact that the areas of the pistons 17 and 22 are equally large, therefore an equally large force is developed on the balance shuttle pistons 22 as on the tool shuttle pistons 17. The balance shuttle 10 therefore is driven to the left with reference to Fig. 2 with the same velocity as the tool shuttle 2 is moved to the right. Since the masses of the shuttles also are equally large, the forces balance one another, so that no dynamic reaction forces arise when the shuttles are accelerated.

The stroke length of the balance shuttle pistons 22 are somewhat shorter than those of the tool shuttle pistons 17. When the projection portion 24 of the respective balance shuttle piston enters the left hand braking chamber 27, the tool shuttle pistons 17 have not yet reached their right hand end positions. Causing a braking action, the projection portion 24 is pressed into the braking chamber 26, generating a counter-pressure in the first hydraulic chamber Bl of the balance shuttle cylinders, which counter-pressure is transferred via the hydraulic conduits C and B to the second hydraulic chamber V2 of the tool shuttle cylinders 9, braking the tool shuttle pistons 17 and thence also braking the tool shuttle 2.

When the balance shuttle pistons 22 have reached their end positions to the left with reference to Fig. 2, and each projecting portion 24 has touched the bottom of its braking chamber 26, the tool shuttle pistons 17 have not yet completely reached their right hand, Fig. 2, end positions. The hydraulic conduit A is still connected to the pressure source 5 which exerts an active force on the tool shuttle pistons 17. Hydraulic oil is still pressed from the hydraulic chambers V2 via the hydraulic conduits B and C into the first hydraulic chamber Bl of the balance shuttle cylinders 11, but due to the fact that the balance shuttle pistons 22 now do not move, as they have reached their left hand end positions, the hydraulic fluid is driven from the hydraulic chamber B 1 through the strangled by-pass-conduit 27 into the second hydraulic chamber B2 and from that chamber through the conduit D to tank T or accumulator. The flow through the strangled by-pass-conduit 27 is very small and causes the tool shuttle pistons 17 to inch slowly to the right, Fig. 2, until said rigid connection links to the tool shuttle 2 touch the right hand/rear, stationary end stops 42. These, like the left/front end stops 41 are set with great accuracy before they have been fixed in their positions. When the connection links 40 are brought to contact the end stops 42, the tool shuttle 2 therefore has been positioned in the discharging station with great accuracy.

When the working operations in the discharged station have been completed, the valve unit 16 is shifted according to a control program for automatic operation of the machine, such that the valve unit instead adopts the position which is shown symbolically in Fig. 2A. This initiates a return of the tool shuttle 2 and the balance shuttle 10 to the starting positions which are shown in Fig. 1 and Fig. 2. The function is completely analogous with that one which has been described above and should therefore not require any detailed description. However, it should be mentioned that in this case it is the left hand/front, free ends of the piston rod portions of the tool shuttle pistons 17 which are caused to contact the stationary end stops 41 in the forming station of the tool shuttle 2.

In the described example, when each shuttle with its accompanying movable motion devices has a mass of about 270 kg, an acceleration force of 50 kN was exerted on each shuttle. These forces accelerated the shuttles to a velocity of 1 m/s. The pathways of movement were 400 mm, the breaking distances were about 10 mm, and the finishing inch distances were about 5 mm. The inching velocity was about 0.1 m/s. Generally speaking, a machine according to the invention normally operates with acceleration forces of 10-100 kN acting on the shuttles, braking distances of 5-20 mm, and inching distances of the tool shuttle of 3-10 mm.

Since the machine according to the invention operates against stationary mechanical stops in the two ends of the tool shuttle 2, small leakages in the hydraulic system do not play any roll for the function of the machine. In the example, the tool shuttle 2 and the balance shuttle 10 have equal masses, the tool shuttle pistons 17 and the balance shuttle pistons 22 have equal areas, and also the resulting pressures which act on the pistons are equally large. This implies that the resulting velocities of the tool shuttle 2 and of the balance shuttle 10 will be equally large. This, however, is not a prerequisite for the functioning for the machine. What is essential is that the forces which act driving on the tool shuttle 2 and on the balance shuttle 10 are equally large, as well as the momentums p^def = m χ _V (the mass x the velocity), as has been mentioned in the disclosure of the invention. If the basic principles of the invention are maintained, namely that the dynamic forces are balanced such that the stand 1 is not subjected to any essential reaction forces, the machine thus may be modified in various ways within the scope of the invention.

Claims

PATENT CLAIMS

1. A machine for manufacturing of objects which substantially consist of a formable material, such as metal and/or a ceramic material, by forming or other working of the formable working material by means of forming or machine tools, c h a r a c t e r i s e d in that the machine comprises a machine stand (1) and at least one tool (3) or a tool part provided in a tool carrier, which comprises at least a first shuttle, in the following referred to as tool shuttle (2), which is slideably provided on or in the machine stand and which can be moved along a first liniar path relative to the machine stand between different positions, which are set in advance, said positions defining stations for performing operations in or by means of said tool in connection with the manufacturing of said object, that first motion devises (9, 17, 20, 40) are provided to move at least said tool shuttle (2) in both directions along said first linear path, - that at least one second shuttle, in the following referred to as balance shuttle

(10), is movable along a second linear path parallel with the path of the tool shuttle, that second motion devices (11, 22, 29, 43) are provided to move at least said balance shuttle (10) relative to the machine stand (1) along said second linear path in connection with each movement which the first shuttle is caused to perform, simultaneously with and with essentially the same duration as said movement but in the opposite direction, and that the force which said first motion devices apply on the tool shuttle in order to achieve the movement of the tool shuttle along the first path is essentially equally large as the force which said second motion devices apply on the balance shuttle in order to achieve the counter-directed movement of the balance shuttle along the second path, in order that the applied forces shall balance each other, so that essentially no dynamic reaction forces are transferred to the machine stand.

2. A machine according to claim l. c h a r a t e r i s e d in that the motion devices are hydraulically acting devices.

3. A machine according to claim 2, c h a r a t e r i s e d in that said first motion devices comprise at least a first hydraulic piston, in the following referred to as tool shuttle piston (17), in a first hydraulic cylinder, in the following referred to as tool shuttle cylinder (9), and a first piston rod (18) which extends through the tool shuttle cylinder and is fixedly connected to the tool shuttle (2), that said second motion devices comprise at least a second hydraulic piston, in the following referred to as balance shuttle piston (22), in a second hydraulic cylinder, in the following referred to as hydraulic shuttle cylinder (11), and a second piston rod (28) which is parallel with the first piston rod and extends through the balance shuttle cylinder and is fixedly connected to the balance shuttle (10), and whereas the tool shuttle cylinder/cylinders and the balance shuttle cylinder/cylinders are stationarily secured relative to the stand.

4. A machine according to claim 3,charaterised in that the shuttles are provided to move horizontally, and that the resulting points of gravity of the moveable masses of said tool and balance shuttles, respectively, which move in opposite direction, will lie in essentially the same vertical and horizontal planes, in order to avoid that any substantial dynamic movement forces will arise in connection with the movements of the shuttles.

5. A machine according to claim 4, charaterised in that it comprises only one tool shuttle and only one balance shuttle, and that the tool shuttle and the balance shuttle turn one of their ends towards one another and are moveable towards and away from one another.

6. A machine according to claim 4, charaterised in that it comprises at least one balance shuttle movable on each side of a tool shuttle.

7. A machine according to any of claims 4-6, charaterised in that a tool shuttle cylinder and a balance shuttle cylinder are provided on each side of the shuttles.

8. A machine according to claim 5 and 7, charaterised in that the tool shuttle cylinders and the balance shuttle cylinders on each side of the shuttles at least partly are provided over one another or side by side, that only that section (20) of each of the first piston rods which extend out in a direction corresponding to the motion direction of the tool shuttle, away from the balance shuttle, is connected to the tool shuttle (2), and that only that section (29) of each of the other piston rods which extend out in a direction which corresponds to the direction of movement of the balance shuttle, away from the tool shuttle, is connected to the balance shuttle (10).

9. A machine according to any of claims 1-8, charaterised in that the shuttles are provided to move horizontally along pathways, comprising at least two stations, in which the shuttle are caused to stop, which stations as far as the tool shuttle is concerned comprise at least a forming station, where the tool or the tool part which is carried by the tool shuttle shall be caused to stop in a correct forming position relative to one or more stationary tools or tool parts in the forming station, that at least a first mechanical position organ (41) is provided for positioning the tool shuttle and hence of the tool or of the tool part in a desired, correct forming position in the forming station through direct or indirect mechanical contact between the positioning organ and the tool shuttle, and that braking organs (25, 26, 27) are provided to reduce the velocity of the tool shuttle from a high velocity of movement to a much lower arrival velocity within a braking distance before the tool shuttle and the positioning organ are caused to contact one another.

10. A machine according to claim 9, c h a r a t e r i s e d in that mechanical positioning organs (41, 42) are provided for positioning the tool shuttle in desired positions in the two end stations of the tool shuttle, and that braking organs are provided to reduce the velocity of the tool shuttle from a very high velocity of movement to a much lower arrival velocity before the tool shuttle is braked to stop and positioning in the end stations.

11. A machine according to claim 9, c h a r at e r i s e d in that the tool shuttle and the balance shuttle are provided to be caused to stop also in one or more stations between the end stations, and that mechanical and/or hydraulic positioning devices are provided for positioning the tool shuttle in desired positions in the intermediate station(s).

12. A machine according to any of claims 9-11, c h a r a t e r i s e d in that said braking organs are hydraulic.

13. A machine according to claim 10 and 12, c h a r a t e r i s e d in that said braking organs for reducing the velocity of the tool shuttle to a desired arrival velocity before the tool shuttle is caused to stop in the two end stations comprise a braking chamber (25, 26) in each end of the balance shuttle cylinder, and that the two end portions (23, 24) of the balance shuttle piston are dimensioned to be able to enter into their respective braking chamber, forming a narrow gap between the cylindrical end portion of the end of the balance shuttle piston and the cylindrical wall of the braking chamber, through which gap the hydraulic fluid slowly can be pressed back in a direction towards the balance shuttle piston and thence provide a desired braking action.

14. A machine according to claim 11 and 12, c h a r a t e r i s e d in that said braking organs for reducing the velocity of the shuttles before the tool shuttle goes all the way to an intermediate station comprise valve means which strangles the flow of hydraulic fluid, and that mechanical stops, which are adjustably fixable in the direction of movement of the shuttles but movable in their cross direction, are provided to position the tool shuttle with a great accuracy in the intermediate station by being caused to engage a matching positioning organ on the tool shuttle or on the motion device of the tool shuttle.

15. A machine according to claim 1-14, c h a r at e r i s e d in that said at least one tool shuttle cylinder (9) and said at least one balance shuttle cylinder (11) are coupled in series in a hydraulic circuit which comprises a first hydraulic chamber (VI) in the tool shuttle cylinder on one side of the tool shuttle piston (17), said first hydraulic chamber (VI) being connectable to a pressure source (P) for hydraulic fluid in order to act as a plus chamber when connected to said pressure source for moving the tool shuttle in a first direction; a second hydraulic chamber (V2) in the tool shuttle cylinder on the opposite side of the tool shuttle piston; a first hydraulic chamber (VI) on one side of the balance shuttle piston (22) in the balance shuttle cylinder, said first hydraulic chamber being connectable to the second hydraulic chamber (V2) of the tool shuttle cylinder in order to act as a plus chamber for moving the balance shuttle in the opposite direction relative to the tool shuttle, when the first hydraulic chamber (VI) of the tool shuttle cylinder is connected to the pressure source and the second hydraulic chamber of the tool shuttle cylinder is connected to the first hydraulic chamber (Bl) of the balance shuttle cylinder; a second hydraulic chamber (B2) on the other side of the balance shuttle piston, said second hydraulic chamber (B2) of the balance shuttle cylinder being connectable to tank (T) or to accumulator, when the first hydraulic chamber (VI) of the tool shuttle cylinder is connected to the pressure source; and valve means (16) which are provided alternatingly, in a first valve position, to connect the pressure source to the first hydraulic chamber (VI) of the tool shuttle cylinder, the second hydraulic chamber (V2) of the tool shuttle cylinder to the first hydraulic chamber (Bl) of the balance shuttle cylinder, and the second hydraulic chamber (B2) of the balance shuttle cylinder to tank or accumulator, and, in a second valve position, to connect the pressure source to the second hydraulic chamber (V2) of the tool shuttle cylinder, the first hydraulic chamber (VI) of the tool shuttle cylinder to the second hydraulic chamber (B2) of the balance shuttle cylinder, and the first hydraulic chamber (Bl) of the balance shuttle cylinder to tank or accumulator.

16. A machine according to claim 13 and 15, charaterised in that said braking organs comprise a strangled by-pass-conduit (27) between the first and second hydraulic chambers (Bl, B2) of the balance shuttle cylinder, including ports (45, 46) adjacent to said braking chambers.

17. A machine according to claim 1, charaterised in that the shuttles are provided to move horizontally on at least two parallel, horizontal rails (13) or roller ways.