CA1327134C - Drive system for a cold pilger rolling mill - Google Patents
Drive system for a cold pilger rolling millInfo
- Publication number
- CA1327134C CA1327134C CA000540656A CA540656A CA1327134C CA 1327134 C CA1327134 C CA 1327134C CA 000540656 A CA000540656 A CA 000540656A CA 540656 A CA540656 A CA 540656A CA 1327134 C CA1327134 C CA 1327134C
- Authority
- CA
- Canada
- Prior art keywords
- crank
- connecting rod
- mass
- drive system
- rolling frame
- 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 - Lifetime
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B21/00—Pilgrim-step tube-rolling, i.e. pilger mills
- B21B21/005—Pilgrim-step tube-rolling, i.e. pilger mills with reciprocating stand, e.g. driving the stand
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmission Devices (AREA)
Abstract
ABSTRACT
The present invention relates to a drive system for a cold pilger rolling mill, incorporating equalisation of masses and moments, the driven crank being connected to the rolling frame through a connecting rod. In order to arrive at a compact, cost-effective and, as far as possible, lightly loaded structure for the drive system, it is proposed that the rolling frame (WG) be arranged directly above the crank gearing (RU) and the connect-ing rod (KO) be supported directly on the crank journal (3), so that the connecting rod effects moment equalisation with its total mass, and the crank (KU) effects equalisation of mass with its total mass.
The present invention relates to a drive system for a cold pilger rolling mill, incorporating equalisation of masses and moments, the driven crank being connected to the rolling frame through a connecting rod. In order to arrive at a compact, cost-effective and, as far as possible, lightly loaded structure for the drive system, it is proposed that the rolling frame (WG) be arranged directly above the crank gearing (RU) and the connect-ing rod (KO) be supported directly on the crank journal (3), so that the connecting rod effects moment equalisation with its total mass, and the crank (KU) effects equalisation of mass with its total mass.
Description
`` ,.^` 132713~
... .
The present lnventlon relates to a drlve system for a cold pilger rolling mlll, incorporating the means to balance ma~es and torques or moments.
DE-AS 27 40 279 descrlbes a cold pilger rolllng mill of this kind wherein, the crank mechanism i8 arranged to one side, relative to the rolling mlll. The crank is connected through a crankshaft offset to a balancing mas~ that i8 arranged above the crank mechanisD, this balanciny mass balancing out the operating torques or moment~. This phase shifted through 90 degrees -., . .~
relatlve to the crank, and the reciprocating movement is made po~sible by parallel guides. The rolling mill itself 18 coupled through a long connecting rod that 18 supported on one side, on the crank~haft offset.
The present invention aims to develop a compact, cost-effective design for the drive, this being sub~ected to reduced load~.
The present invention i8 a drive mechanism for a cold pilger rolling ~ill compriaing a roller ~tand that 1B connected to a driven crank in a crank mechanlsm by a connecting rod that i~
carried by an eccentric crank pin on said driven crank, characterlzed in tha~ the roller stand is located directly above the crank mechani~m and the connectlng rod 18 mounted directly on -6aid crank pin, the total ma~s of the connecting rod providing ~orque balancing and the total mass o~ said drlven crank providing mass balanclng.
.i The construction, which in total is vertical, makes it possible for the rolling frame to act on one ~lde and thu~ be 3a;. . . -. .:
7~q ,;',~,"
guided on the whole of the gear unit. This makes it possible to dispense with a connector rod that connects the rolling frame with the gear unit.
The connecting rod engages directly on the slide immediately below the rolling frame.
The mass that is required for balancing the moments is formed by the connecting rod itself. The centre of mass of the connecting rod is located above the point D of the positive guide.
The total mass of the connecting rod is reduced onto the point D, which means that the dimensions of the connecting rod can be kept small (flat construction). ~;
The connecting rod rotates by P and contributes - -to improved uniformity of the total system by virtue of its moment of mass inertia QKO- Because of the design and arrangement of the connecting rod the planes of the centre of mass of the moment equalisation, of the mass equalisation, and of the rolling frame are brought a6 close together as is possible. As a result of this it has been made possible to arrive at a compact structure and relatively light loading within the gear unit.
The slide guide and the positive guide lie in approxi-mately the same plane. This has been made po~sible by an inter-ruption of the positive guide. The positive guide i~ required only in the end positions in order to maintain the direction of ro'ation of the connecting rod and the crank. An optimal setting for the geometrical arrangement and the loading of the bearings and the trunnions has been arrived at by supporting the connecting rod on the crank.
The embodiment shown in Figure 3 represents a modified embodiment incorporating an epicyclic gear train and crank (PKG).
The construction of this PKG is almost identical to the first embodiment of a double slide gear (DG) described heretofore, but differs in that there is no positive guide. This has been re-placed by an epicyclic gear train that consists of a sun gear and an internally toothed ring. The sun gear is fixed on the crank journal and rotates on the ring gear because of the rotational motion of the crank. The superpositioning of the rotational -motion of the sun gear and the crank results in a precisely opposite direction of rotation of the connecting rod. The -~-.: ..
opposing rotational movement with the angular velocity ~=w and maintenance of the existing geometrical conditions results in a di6placement of the point B (rolling frame).
The disadvantages of the conventional double slider ~ -~
gearing, and the advantages of the double slider gearing and of the epicyclic gear train according to the present invention are ... . .
compared in point form below.
.:" ,' .:"
.; .
Conventional Double Slide Double Slide Gearing or Epi-Gearing cyclic Gearing-crank according --to the present invention - Horizontal construction - The vertical and assym-requires a thrust- or metrical construction means : ,-, . ..
connector rod. that no thrust rods are required.
~ .
. . .
- 3 - ~
13271~
- The great di6tance between - The mass required for the planes of the centres of balancing moments is provided mass lead to very high loading by the mass of the connecting of the bearings and journals. rod.
- Costly bearings for the - The elevated mass inertia crank, connecting rod, equal- moment of the connecting rod --isation of moments, and the contributes to improved rolling frame. uniformity of the overall system. ~ -- The centre of mass of the connecting rod extends beyond the point D. Because of the mass that i5 reduced onto the point D, the total mass and the in~talled height of the con-necting rod are reduced.
:
- The planes of the centres of gravity of the mass and moment ;~
equalisation and of the rolling frame are æeparated by a rela-tively short distance. This reduces the loading on the bearings and the journals.
' ' -. :- ~'' '-1 3 2 7 1 3 ~
- Interruption of the po~itive -~
guidance eliminates the yreat demand for precision in the two guides relative to each other.
. :.' - There iR no need for storing or releasing potential energy :
. :. , since gravity acts in the .
direction of the main axis of rotation.
.. . .
- In the case of the epicyclic. -~
gear train-crank, the po~itive ...
guidance i8 completely elim- .
.. . ...
inated.
~ " ',: ~, . ;
, .
- The guidance of the connecting rod within the positive guide is . ~.
effected by means of a cam follower.
- The number of bearings is ;~
considerably reduced (from 12 to 5).
.' .''-., ,'.
, The present invention is described in greater detail below on the basis of the drawings of two embodiments appended hereto, wherein:-Figures la, lb show schematically a cross-section and a plan view respectively of the first embodiment of the drive according to the present invention (double slide gearing);
Figure 2 shows a cross-section through an embodiment of this first drive;
Figures 3a, 3b show the movement of the connecting rod and crank in two positions;
Figures 4a, 4b show schematically a cross-section and a plan view respectively of a second embodiment of the drive according to the present invention (epicyclic-crank drive);
Figure 5 i8 a cross-section through an embodiment of this second drive.
The first embodiment, with the so-called double slide drive, will be explained first.
The rolling frame (WG) can move within a slide guide (Sch). The rolling frame is connected to the connecting rod (K0) through a journal; this connecting rod is arranged beneath the ~ -rolling frame and runs about a vertical axis.
As can be seen from Figures la, lb, and 2~ the con-necting rod (K0) has a cam follower (1), by means of which the connecting rod (K0) is guided in the positive guides (2). How-ever, these positive guides (2) are only provided in the area of the end positions of the cam follower (1) or the connecting rod (R0), respectively. The connecting rod (K0) is connected with the crank (KU) through the crank journal (3). Figure lb shows the ` 1327131 :
. -movements of the crank (KU), connecting rod (KO) and slide (4) ~-(i.e., of the rolling frame). In these Figures la, lb and the following Figures 3a to 4b, x and y are the slide coordinates, SWG, SKo, and SAG are the centres of mass of the rolling frame WG, the connecting rod KO, and the equalizing mass MA, P and P ~-are the directions of rotation of WG, K0, and KU; R stands for the `
radii of the articulation between the connections WG, KO, and KU, -~ -Sch is the guide for the rolling frame WG, and Z is the vertical axis in which the rolling frame, the connecting rod, and the crank lie. ^~
Figures 3a and 3b serve to better clarify the sequence of movement; these drawings show the connecting rod (KO) and the crank (KU) in different positions relative to each other. As - -Figure 2 shows, the crank (KU~ is connected to the drive 8 (not shown herein) through a suitable gear train arrangement (5 - 7).
The second embodiment, shown in Figures 4a, 4b, and 5 -~
differs from the first embodiment in that an epicyclic gear and crank arrangement i8 used in place of the positive guide. -~
A sun pinion (9) is fixed on the crank journal (3) of the crank (KU); this sun pinion runs around an internally toothed ring (10) that surrounds the crank (KU~. As is shown in ~igure 4b, this arrangement means that because of the super-imposition o~ the movements of the crank (KU) and the sun pinion (~1 the connecting rod (KO) will move in the opposite direction.
The displacement of the point B on the rolling frame results from the kinematic consideration for equally large, opposing rotational motions, with due consideration of the geometry set out in Figure 4b.
- 7 - ~;
.". .'~ :'
... .
The present lnventlon relates to a drlve system for a cold pilger rolling mlll, incorporating the means to balance ma~es and torques or moments.
DE-AS 27 40 279 descrlbes a cold pilger rolllng mill of this kind wherein, the crank mechanism i8 arranged to one side, relative to the rolling mlll. The crank is connected through a crankshaft offset to a balancing mas~ that i8 arranged above the crank mechanisD, this balanciny mass balancing out the operating torques or moment~. This phase shifted through 90 degrees -., . .~
relatlve to the crank, and the reciprocating movement is made po~sible by parallel guides. The rolling mill itself 18 coupled through a long connecting rod that 18 supported on one side, on the crank~haft offset.
The present invention aims to develop a compact, cost-effective design for the drive, this being sub~ected to reduced load~.
The present invention i8 a drive mechanism for a cold pilger rolling ~ill compriaing a roller ~tand that 1B connected to a driven crank in a crank mechanlsm by a connecting rod that i~
carried by an eccentric crank pin on said driven crank, characterlzed in tha~ the roller stand is located directly above the crank mechani~m and the connectlng rod 18 mounted directly on -6aid crank pin, the total ma~s of the connecting rod providing ~orque balancing and the total mass o~ said drlven crank providing mass balanclng.
.i The construction, which in total is vertical, makes it possible for the rolling frame to act on one ~lde and thu~ be 3a;. . . -. .:
7~q ,;',~,"
guided on the whole of the gear unit. This makes it possible to dispense with a connector rod that connects the rolling frame with the gear unit.
The connecting rod engages directly on the slide immediately below the rolling frame.
The mass that is required for balancing the moments is formed by the connecting rod itself. The centre of mass of the connecting rod is located above the point D of the positive guide.
The total mass of the connecting rod is reduced onto the point D, which means that the dimensions of the connecting rod can be kept small (flat construction). ~;
The connecting rod rotates by P and contributes - -to improved uniformity of the total system by virtue of its moment of mass inertia QKO- Because of the design and arrangement of the connecting rod the planes of the centre of mass of the moment equalisation, of the mass equalisation, and of the rolling frame are brought a6 close together as is possible. As a result of this it has been made possible to arrive at a compact structure and relatively light loading within the gear unit.
The slide guide and the positive guide lie in approxi-mately the same plane. This has been made po~sible by an inter-ruption of the positive guide. The positive guide i~ required only in the end positions in order to maintain the direction of ro'ation of the connecting rod and the crank. An optimal setting for the geometrical arrangement and the loading of the bearings and the trunnions has been arrived at by supporting the connecting rod on the crank.
The embodiment shown in Figure 3 represents a modified embodiment incorporating an epicyclic gear train and crank (PKG).
The construction of this PKG is almost identical to the first embodiment of a double slide gear (DG) described heretofore, but differs in that there is no positive guide. This has been re-placed by an epicyclic gear train that consists of a sun gear and an internally toothed ring. The sun gear is fixed on the crank journal and rotates on the ring gear because of the rotational motion of the crank. The superpositioning of the rotational -motion of the sun gear and the crank results in a precisely opposite direction of rotation of the connecting rod. The -~-.: ..
opposing rotational movement with the angular velocity ~=w and maintenance of the existing geometrical conditions results in a di6placement of the point B (rolling frame).
The disadvantages of the conventional double slider ~ -~
gearing, and the advantages of the double slider gearing and of the epicyclic gear train according to the present invention are ... . .
compared in point form below.
.:" ,' .:"
.; .
Conventional Double Slide Double Slide Gearing or Epi-Gearing cyclic Gearing-crank according --to the present invention - Horizontal construction - The vertical and assym-requires a thrust- or metrical construction means : ,-, . ..
connector rod. that no thrust rods are required.
~ .
. . .
- 3 - ~
13271~
- The great di6tance between - The mass required for the planes of the centres of balancing moments is provided mass lead to very high loading by the mass of the connecting of the bearings and journals. rod.
- Costly bearings for the - The elevated mass inertia crank, connecting rod, equal- moment of the connecting rod --isation of moments, and the contributes to improved rolling frame. uniformity of the overall system. ~ -- The centre of mass of the connecting rod extends beyond the point D. Because of the mass that i5 reduced onto the point D, the total mass and the in~talled height of the con-necting rod are reduced.
:
- The planes of the centres of gravity of the mass and moment ;~
equalisation and of the rolling frame are æeparated by a rela-tively short distance. This reduces the loading on the bearings and the journals.
' ' -. :- ~'' '-1 3 2 7 1 3 ~
- Interruption of the po~itive -~
guidance eliminates the yreat demand for precision in the two guides relative to each other.
. :.' - There iR no need for storing or releasing potential energy :
. :. , since gravity acts in the .
direction of the main axis of rotation.
.. . .
- In the case of the epicyclic. -~
gear train-crank, the po~itive ...
guidance i8 completely elim- .
.. . ...
inated.
~ " ',: ~, . ;
, .
- The guidance of the connecting rod within the positive guide is . ~.
effected by means of a cam follower.
- The number of bearings is ;~
considerably reduced (from 12 to 5).
.' .''-., ,'.
, The present invention is described in greater detail below on the basis of the drawings of two embodiments appended hereto, wherein:-Figures la, lb show schematically a cross-section and a plan view respectively of the first embodiment of the drive according to the present invention (double slide gearing);
Figure 2 shows a cross-section through an embodiment of this first drive;
Figures 3a, 3b show the movement of the connecting rod and crank in two positions;
Figures 4a, 4b show schematically a cross-section and a plan view respectively of a second embodiment of the drive according to the present invention (epicyclic-crank drive);
Figure 5 i8 a cross-section through an embodiment of this second drive.
The first embodiment, with the so-called double slide drive, will be explained first.
The rolling frame (WG) can move within a slide guide (Sch). The rolling frame is connected to the connecting rod (K0) through a journal; this connecting rod is arranged beneath the ~ -rolling frame and runs about a vertical axis.
As can be seen from Figures la, lb, and 2~ the con-necting rod (K0) has a cam follower (1), by means of which the connecting rod (K0) is guided in the positive guides (2). How-ever, these positive guides (2) are only provided in the area of the end positions of the cam follower (1) or the connecting rod (R0), respectively. The connecting rod (K0) is connected with the crank (KU) through the crank journal (3). Figure lb shows the ` 1327131 :
. -movements of the crank (KU), connecting rod (KO) and slide (4) ~-(i.e., of the rolling frame). In these Figures la, lb and the following Figures 3a to 4b, x and y are the slide coordinates, SWG, SKo, and SAG are the centres of mass of the rolling frame WG, the connecting rod KO, and the equalizing mass MA, P and P ~-are the directions of rotation of WG, K0, and KU; R stands for the `
radii of the articulation between the connections WG, KO, and KU, -~ -Sch is the guide for the rolling frame WG, and Z is the vertical axis in which the rolling frame, the connecting rod, and the crank lie. ^~
Figures 3a and 3b serve to better clarify the sequence of movement; these drawings show the connecting rod (KO) and the crank (KU) in different positions relative to each other. As - -Figure 2 shows, the crank (KU~ is connected to the drive 8 (not shown herein) through a suitable gear train arrangement (5 - 7).
The second embodiment, shown in Figures 4a, 4b, and 5 -~
differs from the first embodiment in that an epicyclic gear and crank arrangement i8 used in place of the positive guide. -~
A sun pinion (9) is fixed on the crank journal (3) of the crank (KU); this sun pinion runs around an internally toothed ring (10) that surrounds the crank (KU~. As is shown in ~igure 4b, this arrangement means that because of the super-imposition o~ the movements of the crank (KU) and the sun pinion (~1 the connecting rod (KO) will move in the opposite direction.
The displacement of the point B on the rolling frame results from the kinematic consideration for equally large, opposing rotational motions, with due consideration of the geometry set out in Figure 4b.
- 7 - ~;
.". .'~ :'
Claims (3)
1. A drive mechanism for a cold pilger rolling mill comprising a roller stand that is connected to a driven crank in a crank mechanism by a connecting rod that is carried by an eccentric crank pin on said driven crank, characterized in that the roller stand is located directly above the crank mechanism and the connecting rod is mounted directly on said crank pin, the total mass of the connecting rod providing torque balancing and the total mass of said driven crank providing mass balancing.
2. A drive mechanism according to claim 1, characterised in that the connecting rod is guided in restraint guides in the region of its extreme positions of movement.
3. A drive mechanism according to claim 1, characterised in that said driven crank comprises part of a planet gear, that a pinion is located on the crank pin and connected securely thereto, which pinion meshes with an internal-toothed ring gear surrounding said crank in such a manner that the superposition of the rotational motion of said pinion and said crank imparts to said connecting rod an opposing rotational motion.
Priority Applications (11)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3613036A DE3613036C1 (en) | 1986-04-15 | 1986-04-15 | Drive for cold pilger roll mill |
| DE3706129A DE3706129C1 (en) | 1987-02-23 | 1987-02-23 | Drive for a cold pilger rolling mill with mass and torque compensation |
| PCT/DE1987/000277 WO1988010160A1 (en) | 1986-04-15 | 1987-06-18 | Drive mechanism for cold pilger rolling mills |
| JP62503592A JPH07108407B2 (en) | 1986-04-15 | 1987-06-18 | Drive for cold pilger mill |
| EP87903858A EP0366648B1 (en) | 1986-04-15 | 1987-06-18 | Drive mechanism for cold pilger rolling mills |
| AT87903858T ATE71315T1 (en) | 1986-04-15 | 1987-06-18 | DRIVE FOR A COLD PILING ROLLING MILL. |
| CA000540656A CA1327134C (en) | 1986-04-15 | 1987-06-26 | Drive system for a cold pilger rolling mill |
| EP87730137A EP0280001B1 (en) | 1987-02-23 | 1987-10-29 | Drive system for cold pilger mills with compensation of mass and momentum |
| JP63025540A JPS63207406A (en) | 1987-02-23 | 1988-02-05 | Drive for cold pilger mill with weight and torque balancer |
| US07/159,191 US4858458A (en) | 1987-02-23 | 1988-02-23 | Drive for a pilger cold-rolling mill with balancing of masses and moments |
| US07/455,421 US5076088A (en) | 1986-04-15 | 1989-12-18 | Drive for a pilger cold rolling mill |
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE3613036A DE3613036C1 (en) | 1986-04-15 | 1986-04-15 | Drive for cold pilger roll mill |
| PCT/DE1987/000027 WO1987004357A1 (en) | 1986-01-25 | 1987-01-23 | Tennis line sensor (tls) |
| DE3706129A DE3706129C1 (en) | 1987-02-23 | 1987-02-23 | Drive for a cold pilger rolling mill with mass and torque compensation |
| CA000540656A CA1327134C (en) | 1986-04-15 | 1987-06-26 | Drive system for a cold pilger rolling mill |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1327134C true CA1327134C (en) | 1994-02-22 |
Family
ID=27426484
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000540656A Expired - Lifetime CA1327134C (en) | 1986-04-15 | 1987-06-26 | Drive system for a cold pilger rolling mill |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1327134C (en) |
-
1987
- 1987-06-26 CA CA000540656A patent/CA1327134C/en not_active Expired - Lifetime
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |
Effective date: 20110222 |