Patent Publication Number: US-9901968-B2

Title: Pipe bend die unit, and pipe bending apparatus having the unit

Description:
TECHNICAL FIELD 
     The present invention relates to a pipe bend die unit that is appropriate for bending a pipe, and a pipe bending apparatus having the unit. 
     BACKGROUND ART 
     As for working to bend a pipe, various kinds of working such as press bending, compression bending, extract bending, draw bending and the like are known heretofore, among which a rotary draw bending is most popular. According to an ordinary rotary draw bending, a pipe is held by a clamp die against a bend die with a groove formed on its outer peripheral surface, and the bend die and clamp die are rotated, with the pipe being pressed toward the bend die by means of a pressure die, then the pipe is moved in a tangential direction, thereby to be bent along the groove of the bend die, as disclosed in the second columns of Patent document 1, for example, and also disclosed in Patent document 2, in its paragraphs (0003)-(0006) and FIG. 11, wherein the bend die is described as a roll die. 
     In Patent document 2, with respect to a wiper or shoe provided for preventing a crinkling from being created on the inner side of a bent portion of the pipe, a specific wiper is proposed to do with wear or breakage caused by a sliding motion, as described in its paragraphs (0013) and (0014). Likewise, in Patent document 3, it is described in its paragraph (0005) as an object to provide a pipe bending apparatus having a wear resistance, being used for various kinds of pipes without causing a problem, and having a very long life without requiring adjusting operations very often, and such a pipe bending apparatus is proposed in its paragraph (0006) that is characterized in that the pipe bending apparatus has a bend die with its outer peripheral surface formed in a circular arc of a predetermined curvature to bend a pipe, a clamp member clamping the pipe with the bend die, and a wiper rotating the clamp member about the bend die to prevent a crinkling from being created when the pipe is bent, and that a tip end portion of the wiper in the rotating direction of the clamp member is extended along the curvature of the outer peripheral surface of the bend die beyond an initial point for bending the pipe. 
     Furthermore, in Patent document 4, with respect to a method and apparatus for quickly and accurately changing die sets for different-sized tubing to be bent or for different types of tube bending operations, it is described in its page 7 that a preassembled die set has been devised for tube bending apparatus wherein the die set is comprised of a bend die, clamp die and pressure die adapted to be mounted on a spindle of a tube bending table, the improvement comprising first means releasably interconnecting the pressure die and clamp die to the bend die in predetermined, aligned relation to one another and to the bend die, and handling means for engaging the die set in order to simultaneously lift and remove said dies comprising each die set from the table. And, it is described in its page 8 that many tube bending operations require the use of a wiper die and mandrel, which may also provide a part of each preassembled die set when needed, and such an embodiment that the wiper die is joined to the bend die by a wiper die arm is disclosed in its page 15 and FIG. 6. 
     PRIOR ART DOCUMENT 
     Patent Document 
     
         
         Patent document 1: U.S. Pat. No. 5,337,590 
         Patent document 2: 
         Japanese Patent Laid-open Publication No. 2004-9125 
         Patent document 3: 
         Japanese Patent Laid-open Publication No. 2008-246504 
         Patent document 4: 
         Japanese Patent Laid-open Publication No. Hei-11-512029 
       
    
     SUMMARY OF THE INVENTION 
     Problems to be Solved by the Invention 
     Although it is configured to form the crinkling intentionally in Patent document 1, in order to prevent the crinkling being created when the draw rotary bending is performed, a crinkling prevention is employed in general, so that the wiper is disposed in Patent documents 2, 3 and 4. Among them, each wiper as described in Patent documents 2 and 4 has a tip end portion formed into a wedge shape, and possible wear of the tip edge portion was concerned in Patent document 2, so that a counter measure has been considered. Particularly, there is a step along the initial line for bending the pipe, normally a line where a surface including a rotary axis of the bend die intersects an inner surface of a groove of the bend die, a crinkling resulted from the step cannot be avoided. In order to minimize this crinkling, it is necessary to maintain the wedge shape of the tip end portion of the wiper, especially necessary to make the tip end portion as thinner as possible, so that the wiper is fragile and lacks its durability. Furthermore, a periodic wear countermeasure is unavoidable, and frequent replacements are required. In addition, as an initial setting for the bending is difficult, skilled technique is required. Therefore, it is difficult to perform a large amount of bending operations continuously. 
     In contrast, according to Patent document 3, a wiper disclosed as one embodiment therein configures a part of a central die section out of bending die sections which were divided into three sections along a vertical direction, and it is formed with a recess portion of a circular arc cross section, as described in its Paragraphs (0025)-(0030). Consequently, it is described in its Paragraph (0032) that a tip end portion with an edge structure is not required, and that there will be no possibility for creating a step between the bend die and the wiper, the reason of which has not been explained. Supposing that, from a start to an end of bending operation applied to a pipe to be formed, out of the bending die sections divided into three sections along three planar surfaces parallel to a pipe axis, upper and lower side die sections perform the bending, and the central section performs as the wiper, thereby to perform separate operations, not only it is difficult to prevent the crinkling from being created, but also it is difficult to perform the bending operation appropriately. No disclosure can be found about a configuration for enabling a desired bending operation. 
     In the meantime, although it is described in Patent document 4 that the die set with the bend die, clamp die and pressure die being preassembled can be changed to perform bending operations in different forms, as described in its Page 11, a wiper die is not necessarily required. In other words, Patent document 4 focuses on a performance of changing dies, but never discloses such a die set that can change dies with the performance of appropriately preventing the crinkling from being created, nor discloses a pipe bend die unit that is appropriate for bending a pipe and a pipe bending apparatus having the pipe bend die unit. 
     Accordingly, it is an object of the present invention to provide a pipe bend die unit that can perform bending a pipe appropriately without creating a crinkling. And, it is another object of the present invention to provide a pipe bending apparatus having the pipe bend die unit which is appropriate for the bending. 
     It is a further object of the present invention to provide a pipe bend die unit that can perform bending a pipe appropriately without creating a crinkling, and perform changing dies easily, and to provide a pipe bending apparatus having the unit. 
     Means for Solving the Problems 
     To solve the above-described problems, the present invention comprises a bend die with a pipe-receiving groove of half-circular cross section formed on an outer peripheral surface of the bend die, the bend die being rotatable about a rotary axis, and the bend die comprises a clamp member having a first groove part of half-circular cross section on an outer peripheral surface of the clamp member with a fitting recess formed on the first groove part and extending in a peripheral direction by a first predetermined length on a planar surface perpendicular to the rotary axis, and a counter pressure member having a second groove part of half-circular cross section formed on an outer peripheral surface of the counter pressure member, and a fitting protrusion extending in a peripheral direction by a second predetermined length from a tip end portion of the second groove part, the fitting protrusion being positioned in the fitting recess so that the first and second groove parts combine to form the pipe-receiving groove of half-circular cross section, the counter pressure member and the clamp member being hingedly connected to one another so as to be rotatable relative to each other about the rotary axis. 
     In the pipe bend die unit as described above, it may be so configured that one part of the fitting protrusion is located at a foreside in an advancing direction of the pipe relative to a position where a bending operation of the pipe is initiated, and that an other part of the fitting protrusion is located at a backside in the advancing direction of the pipe relative to the position where the bending operation of the pipe is initiated. Or, it may be so configured that a fitting portion of the fitting protrusion that is positioned in the fitting recess is located at a foreside in an advancing direction of the pipe relative to a position where a bending operation of the pipe is initiated, and that a mating portion at which the first groove part of the clamp member and the second groove part of the counter pressure member mate is located at a backside in the advancing direction of the pipe relative to the position where the bending operation of the pipe is initiated. 
     It may be so configured that the counter pressure member has an annular rotary support portion mounted to be rotatable about the rotary axis, and that a part of the rotary support portion forms the fitting protrusion, and that the rotary support portion possesses an outer peripheral surface, the outer peripheral surface of the rotary support portion being a curved surface forming a part of the pipe-receiving groove of half-circular cross section. Furthermore, it may be so configured that the counter pressure member and the clamp member are hingedly connected by an axial member having a central axis passing through the fitting recess. 
     Also, in the pipe bend die unit as described above, it may be so configured that the clamp member has a circularly recessed portion forming the first groove part of half-circular cross section, the fitting recess extending in a peripheral direction on a planar surface perpendicular to the rotary axis, the fitting recess being located at a bottom center of the circularly recessed portion, the first groove part of half-circular cross section being continuous with the circularly recessed portion including a part of the fitting recess, and that the counter pressure member includes a curved surface portion formed on opposite sides of the planar surface, the curved surface portion being configured to contact the circularly recessed portion, the curved surface portion possessing an arch center on an axis offset from the rotary axis and perpendicular to the planar surface in a direction spaced from the rotary axis, the second groove part on the outer peripheral surface of the fitting protrusion possessing the half-circular cross section, with a bottom center of the second groove part being provided on the planar surface perpendicular to the rotary axis, next to the curved surface portion. 
     Furthermore, it may be so configured that one part of the fitting protrusion is located at a foreside in an advancing direction of the pipe relative to a position where a bending operation of the pipe is initiated, and that an other part of the fitting protrusion is located at a backside in the advancing direction of the pipe relative to the position where the bending operation of the pipe is initiated. 
     Or, it may be so configured that the counter pressure member has an annular rotary support portion mounted to be rotatable about the rotary axis, and a body portion formed integrally with the rotary support portion, the second groove part of half-circular cross section and the curved surface portion being provided on the body portion of the counter pressure member, a part of the rotary support portion being formed integrally with the body portion and extending outwardly in a radial direction of the rotary support portion, and that the rotary support portion forms the fitting protrusion, and the rotary support portion possesses an outer peripheral surface, the outer peripheral surface of the rotary support portion being a curved surface forming a part of the pipe-receiving groove of half-circular cross section. Particularly, it may be so configured that the second groove part of half-circular cross section of the body portion of the counter pressure member forms an obtuse angle with a side surface of an end portion of the second groove part formed next to the curved surface portion. It may be so configured that the counter pressure member comprises at least a first member and a second member, the rotary support portion constituting a main part of the first member, and the body portion constituting a main part of the second member, the counter pressure member being formed by combining the first member and the second member. 
     Also, in the pipe bend die unit as described above, the bend die may be configured by an upper section and a lower section divided by a surface perpendicular to the rotary axis, the fitting protrusion of the counter pressure member being disposed between the upper section and the lower section. 
     Also, in the pipe bend die unit as described above, it may be so configured that the counter pressure member is divided into at least two members, the at least two members being a mating member including the fitting protrusion and a rotary support member supported to be rotatable about the rotary axis, the mating member being detachably connected to the rotary support member. It may be so configured that the clamp member and the counter pressure member comprise a plurality of members divided by a plurality planes perpendicular to the rotary axis, and that the plurality of members are stacked to form the clamp member and the counter pressure member. Furthermore, it may further comprise a knock pin fixed to a predetermined position of the clamp member, to provide an initial relative position between the clamp member and the counter pressure member by a position where the counter pressure member abuts on the knock pin. 
     Also, the present invention is to provide a pipe bending apparatus that comprises a bend die having a pipe-receiving groove of half-circular cross section on an outer peripheral surface of the bend die, the bend die being rotatable about a rotary axis, a clamp die for clamping a pipe to be bent that is positioned in the pipe-receiving groove of the bend die, and a pressure die for pressing the pipe toward the bend die, and that the bend die comprises a clamp member having a first groove part of half-circular cross section on an outer peripheral surface of the clamp member with a fitting recess formed on the first groove part and extending in a peripheral direction by a first predetermined length on a planar surface perpendicular to the rotary axis, and a counter pressure member having a second groove part of half-circular cross section formed on an outer peripheral surface of the counter pressure member, and a fitting protrusion extending in a peripheral direction by a second predetermined length from a tip end portion of the second groove part, the fitting protrusion being positioned in the fitting recess so that the first and second groove parts combine to form the pipe-receiving groove of half-circular cross section, the counter pressure member and the clamp member being hingedly connected to one another so as to be rotatable relative to each other about the rotary axis, to configure a pipe bend die unit. 
     Also, in the pipe bending apparatus as described above, it may be so configured that one part of the fitting protrusion is located at a foreside in an advancing direction of the pipe relative to a position where a bending operation of the pipe is initiated, and that an other part of the fitting protrusion is located at a backside in the advancing direction of the pipe relative to the position where the bending operation of the pipe is initiated. 
     Furthermore, it may be so configured that the clamp member has a circularly recessed portion forming the first groove part of half-circular cross section, the fitting recess extending in a peripheral direction on a planar surface perpendicular to the rotary axis, the fitting recess being located at a bottom center of the circularly recessed portion, the first groove part of half-circular cross section being continuous with the circularly recessed portion including a part of the fitting recess, and that the counter pressure member includes a curved surface portion formed on opposite sides of the planar surface, the curved surface portion being configured to contact the circularly recessed portion, the curved surface portion possessing an arch center on an axis offset from the rotary axis and perpendicular to the planar surface in a direction spaced from the rotary axis, the second groove part on the outer peripheral surface of the fitting protrusion possessing the half-circular cross section, with a bottom center of the second groove part being provided on the planar surface perpendicular to the rotary axis, next to the curved surface portion. 
     Furthermore, it may be so configured that the counter pressure member has an annular rotary support portion mounted to be rotatable about the rotary axis, and a body portion formed integrally with the rotary support portion, the second groove part of half-circular cross section and the curved surface portion being provided on the body portion, a part of the rotary support portion being formed integrally with the body portion and extending outwardly in a radial direction of the rotary support portion, and that the rotary support portion forms the fitting protrusion, and the rotary support portion possesses an outer peripheral surface, the outer peripheral surface of the rotary support portion being a curved surface forming a part of the pipe-receiving groove of half-circular cross section. Also, the counter pressure member may comprise at least a first member and a second member, the rotary support portion constituting a main part of the first member, and the body portion constituting a main part of the second member, the counter pressure member being formed by combining the first member and the second member. 
     In the pipe bending apparatus as described above, it may be so configured that the counter pressure member and the clamp member are hingedly connected by an axial member having a central axis passing through the fitting recess. Also, the bend die may be configured by an upper section and a lower section divided by a surface perpendicular to the rotary axis, the fitting protrusion of the counter pressure member being disposed between the upper section and the lower section. 
     Also, in the pipe bending apparatus as described above, it may further comprise a knock pin fixed to a predetermined position of the clamp member, to provide an initial relative position between the clamp member and the counter pressure member by a position where the counter pressure member abuts on the knock pin. Furthermore, the apparatus may comprise a mandrel with a tip end portion thereof being inserted into the pipe, the mandrel being driven such that the tip end portion opposes the pressure die within a predetermined rotating region of the bend die. 
     Effects of the Invention 
     As the present invention is configured as described above, the following effects can be achieved. That is, according to the pipe bend die unit of the present invention, the bend die configuring it comprises a clamp member having a first groove part of half-circular cross section on an outer peripheral surface of the clamp member with a fitting recess formed on the first groove part and extending in a peripheral direction by a first predetermined length on a planar surface perpendicular to the rotary axis, and a counter pressure member having a second groove part of half-circular cross section formed on an outer peripheral surface of the counter pressure member, and a fitting protrusion extending in a peripheral direction by a second predetermined length from a tip end portion of the second groove part, the fitting protrusion being positioned in the fitting recess so that the first and second groove parts combine to form the pipe-receiving groove of half-circular cross section, and the counter pressure member and the clamp member are hingedly connected to one another so as to be rotatable relative to each other about the rotary axis. Therefore, the bending of the pipe can be achieved appropriately without causing the crinkling. Furthermore, if a plurality of pipe bend die units are prepared in accordance with various shapes of pipes to be bent, when a pipe is to be bent in a shape, a pipe bend die unit for the shape to be bent may be simply selected and changed, so that such a pipe bend die unit can be provided that its die change can be performed easily, and that no adjustment is required after the die change. 
     In the pipe bend die unit as described above, if such a configuration is employed that one part of the fitting protrusion is located at a foreside in an advancing direction of the pipe relative to a position where a bending operation of the pipe is initiated, and an other part of the fitting protrusion is located at a backside in the advancing direction of the pipe relative to the position where the bending operation of the pipe is initiated, or if such a configuration is employed that a fitting portion of the fitting protrusion positioned in the fitting recess is located at a foreside in an advancing direction of the pipe relative to a position where a bending operation of the pipe is initiated, and a mating portion at which the first groove part of the clamp member and the second groove part of the counter pressure member is located at a backside of the advancing direction of the pipe relative to the position where the bending operation of the pipe is initiated, smooth bending of the pipe can be achieved without causing the crinkling. 
     If the counter pressure member is formed to have an annular rotary support portion mounted to be rotatable about the rotary axis, it can be surely supported to be rotatable about the rotary axis. Particularly, it can be hingedly connected with the clamp member easily, and if it is so configured that a part of the rotary support portion forming the fitting protrusion, and that the rotary support portion possesses an outer peripheral surface, with the outer peripheral surface of the rotary support portion being a curved surface forming a part of the pipe-receiving groove of half-circular cross section, the counter pressure member can be formed as a single part with an appropriate shape. Also, if it is so configured that the counter pressure member and the clamp member are hingedly connected by an axial member having a central axis passing through the fitting recess, smooth bending of the pipe can be achieved without causing the crinkling. 
     In the pipe bend die unit as described above, if such a configuration is employed that the clamp member has a circularly recessed portion forming the first groove part of half-circular cross section, the fitting recess extending in a peripheral direction on a planar surface perpendicular to the rotary axis, the fitting recess being located at a bottom center of the circularly recessed portion, the first groove part of half-circular cross section being continuous with the circularly recessed portion including a part of the fitting recess, and that the counter pressure member includes a curved surface portion formed on opposite sides of the planar surface, the curved surface portion being configured to contact the circularly recessed portion, the curved surface portion possessing an arch center on an axis offset from the rotary axis and perpendicular to the planar surface in a direction spaced from the rotary axis, the second groove part on the outer peripheral surface of the fitting protrusion possessing the half-circular cross section, with a bottom center of the second groove part being provided on the planar surface perpendicular to the rotary axis, next to the curved surface portion, then, the tip end portion of the curved surface portion of the counter pressure member at the initial position for bending the pipe tightly contacts the circularly recessed portion of the clamp member, whereas a clearance is formed between the curved surface portion of the counter pressure member and the circularly recessed portion at other portions than the tip end portion, even if the relative rotational angle between the clamp member and the counter pressure member is changed. Therefore, the counter pressure member can be assembled with the clamp member easily and appropriately, without causing an interference with the circularly recessed portion, and a durability of the counter pressure member will be improved. 
     In the pipe bend die unit as described above, if it is so configured that one part of the fitting protrusion is located at a foreside in an advancing direction of the pipe relative to a position where a bending operation of the pipe is initiated, and an other part of the fitting protrusion is located at a backside in the advancing direction of the pipe relative to the position where the bending operation of the pipe is initiated, smooth bending of the pipe can be achieved without causing the crinkling. 
     If the counter pressure member is formed to have an annular rotary support portion mounted to be rotatable about the rotary axis, and a body portion formed integrally with the rotary support portion, the second groove part of half-circular cross section and the curved surface portion being provided on the body portion, a part of the rotary support portion being formed integrally with the body portion and extending outwardly in a radial direction of the rotary support portion, the counter pressure member can be surely supported to be rotatable about the rotary axis, and can be hingedly connected with the clamp member easily. 
     In addition, as a part of the rotary support portion is formed to extend outwardly in a radial direction of the rotary support portion, stress concentration applied to the rotary support portion can be relieved, so that durability of the counter pressure member will be improved. As the rotary support portion is configured to form the fitting protrusion, and the outer peripheral surface of the rotary support portion is configured to be a curved surface forming a part of the pipe-receiving groove of half-circular cross section, the counter pressure member can be formed as a single part with an appropriate shape. Particularly, if the second groove part of half-circular cross section of the body portion of the counter pressure member forms an obtuse angle with a side surface of an end portion of the second groove part formed next to the curved surface portion, a good durability can be ensured. Furthermore, if the counter pressure member is configured to comprise at least a first member and a second member, the rotary support portion constituting a main part of the first member, and the body portion constituting a main part of the second member, the counter pressure member being formed by combining the first member and the second member, when the rotary support portion is worn, only the first member may be changed, so that not only the changing work will be made easily, but also a cost down can be achieved from a long term viewpoint. 
     On the other hand, if the bend die is configured by an upper section and a lower section divided by a surface perpendicular to the rotary axis, and the fitting protrusion of the counter pressure member is disposed between the upper section and the lower section, although number of parts will be increased comparing the aforementioned configurations, each part can be manufactured with a particular accuracy as required in accordance with a performance of each part, so that each part can be manufactured easily. 
     In the pipe bend die unit as described above, if the counter pressure member is configured to be divided into at least two members, and it is configured that the at least two members are a mating member including the fitting protrusion and a rotary support member supported to be rotatable about the rotary axis, and that the mating member is detachably connected to the rotary support member, then, only the mating member can be changed as required, so that a countermeasure against its wearing can be made easily. In the case where the clamp member and the counter pressure member comprise a plurality of members divided by a plurality planes perpendicular to the rotary axis, and the plurality of members are configured to be stacked to form the clamp member and the counter pressure member, the clamp member and counter pressure member can be configured by stacking the plurality of parts, and a hinged connection between them can be configured at the same time. If a knock pin fixed to a predetermined position of the clamp member is further comprised, and a position where the counter pressure member abuts on the knock pin is provided for an initial relative position between the clamp member and the counter pressure member, then, the pipe bend die unit, wherein the initial relative position between the clamp member and the counter pressure member is set in advance, can be provided. 
     And, a pipe bending apparatus according to the present invention comprises the pipe bend die unit configured as described before, a clamp die for clamping the pipe to be bent with the pipe-receiving groove of its bend die, and a pressure die for pressing the pipe toward the bend die, and it is so configured that bending of the pipe is performed by rotating the bend die and the clamp die, with the pipe being pressed in the bending direction by the pressure die. Therefore, the bending of the pipe can be achieved appropriately without causing the crinkling. Furthermore, if a plurality of pipe bend die units are prepared in accordance with various shapes of pipes to be bent, when a pipe is to be bent in a shape, a pipe bend die unit for the shape to be bent may be simply selected and changed, so that the die change can be performed easily, and that no adjustment is required after the die change. Therefore, an automatic die change by means of a robot can be made. 
     In the pipe bending apparatus as described above, if such a configuration is employed that one part of the fitting protrusion is located at a foreside in an advancing direction of the pipe relative to a position where a bending operation of the pipe is initiated, and an other part of the fitting protrusion is located at a backside in the advancing direction of the pipe relative to the position where the bending operation of the pipe is initiated, smooth bending of the pipe can be achieved. 
     Particularly, if the counter pressure member has a circularly recessed portion forming the first groove part of half-circular cross section, the fitting recess extending in a peripheral direction on a planar surface perpendicular to the rotary axis, the fitting recess being located at a bottom center of the circularly recessed portion, the first groove part of half-circular cross section being continuous with the circularly recessed portion including a part of the fitting recess, and that the counter pressure member includes a curved surface portion formed on opposite sides of the planar surface, the curved surface portion being configured to contact the circularly recessed portion, the curved surface portion possessing an arch center on an axis offset from the rotary axis and perpendicular to the planar surface in a direction spaced from the rotary axis, the second groove part on the outer peripheral surface of the fitting protrusion possessing the half-circular cross section, with a bottom center of the second groove part being provided on the planar surface perpendicular to the rotary axis, next to the curved surface portion, then, the tip end portion of the curved surface portion of the counter pressure member at the initial position for bending the pipe tightly contacts the circularly recessed portion of the clamp member, whereas a clearance is formed between the curved surface portion of the counter pressure member and the circularly recessed portion at other portions than the tip end portion, even if the relative rotational angle between the clamp member and the counter pressure member is changed. Therefore, the counter pressure member can be assembled with the clamp member easily and appropriately, without causing an interference with the circularly recessed portion, and a durability of the counter pressure member will be improved. 
     If the counter pressure member served for the pipe bending apparatus as described above has an annular rotary support portion mounted to be rotatable about the rotary axis, and a body portion formed integrally with the rotary support portion, and formed with the groove of half-circular cross section and the curved surface portion, with a part of the rotary support portion formed integrally with the body portion being formed to extend outwardly in a radial direction of the rotary support portion, it can be surely supported to be rotatable about the rotary axis, and it can be hingedly connected with the clamp member easily. In addition, as a part of the rotary support portion is formed to extend outwardly in a radial direction of the rotary support portion, stress concentration applied to the rotary support portion can be relieved, so that durability of the counter pressure member will be improved. As the rotary support portion of the counter pressure member is configured to form the fitting protrusion, and the outer peripheral surface of the rotary support portion is configured to be a curved surface forming a part of the pipe-receiving groove of half-circular cross section, the counter pressure member can be formed as a single part with an appropriate shape. 
     Furthermore, if the counter pressure member is configured to comprise at least a first member and a second member, the rotary support portion constituting a main part of the first member, and the body portion constituting a main part of the second member, the counter pressure member being formed by combining the first member and the second member, when the rotary support portion is worn, only the first member may be changed, so that not only the changing work will be made easily, but also cost down can be achieved from a long term viewpoint. Also, if the counter pressure member and the clamp member are hingedly connected by an axial member having a central axis passing through the fitting recess, smooth bending of the pipe can be achieved without causing the crinkling. 
     Furthermore, if the bend die is configured by an upper section and a lower section divided by a surface perpendicular to the rotary axis, and the fitting protrusion of the counter pressure member is disposed between the upper section and the lower section, each part can be manufactured with a particular accuracy as required in accordance with a performance of each part, so that each part can be manufactured easily. 
     In the pipe bending apparatus as described above, if a knock pin fixed to a predetermined position of the clamp member is further comprised, and a position where the counter pressure member abuts on the knock pin is provided for an initial relative position between the clamp member and the counter pressure member, then, the pipe bend die unit, wherein the initial relative position between the clamp member and the counter pressure member is set in advance, can be provided, and no adjustment after the die change is required. Furthermore, if there is provided a mandrel with a tip end portion thereof being inserted into the pipe, to be driven such that the tip end portion opposes the pressure die within a predetermined rotating region of the bend die, bending work with a small bending radius can be made easily, and limit for bending the pipe can be improved at a large extent. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a perspective view showing a pipe bending apparatus according to an embodiment of the present invention. 
         FIG. 2  is a front view of a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 3  is a plan view of a pipe bending apparatus showing its starting state of a bending operation according to an embodiment of the present invention. 
         FIG. 4  is a plan view of a pipe bending apparatus showing its finishing state of a bending operation according to an embodiment of the present invention. 
         FIG. 5  is a perspective sectional view of a pipe bending apparatus showing its finishing state of a bending operation according to an embodiment of the present invention. 
         FIG. 6  is a perspective view showing a clamp member for use in a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 7  is a side view of a clamp member for use in an embodiment of the present invention. 
         FIG. 8  is a perspective view showing a counter pressure member for use in a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 9  is a plan view of a counter pressure member for use in an embodiment of the present invention. 
         FIG. 10  is a cross sectional view as viewed from “B” in  FIG. 9  showing a counter pressure member for use in an embodiment of the present invention. 
         FIG. 11  is a right side view of a counter pressure member for use in an embodiment of the present invention. 
         FIG. 12  is a front view of a counter pressure member for use in an embodiment of the present invention. 
         FIG. 13  is a rear view of a counter pressure member for use in an embodiment of the present invention. 
         FIG. 14  is a cross sectional view sectioned along C-C line in  FIG. 9  showing a counter pressure member for use in an embodiment of the present invention. 
         FIG. 15  is a perspective view of parts for assembling a pipe bend die unit according to another embodiment of the present invention. 
         FIG. 16  is a perspective view of a pipe bend die unit according to another embodiment of the present invention. 
         FIG. 17  is a front view of a clamp member for use in another embodiment of the present invention. 
         FIG. 18  is a left side view of a clamp member for use in another embodiment of the present invention. 
         FIG. 19  is a perspective view showing a pipe which was bent by use of a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 20  is a plan view of a counter pressure member for use in a further embodiment of the present invention. 
         FIG. 21  is a partially sectioned view of a pipe bend die unit showing its starting state of a bending operation according to a further embodiment of the present invention. 
         FIG. 22  is a perspective view of a pipe bend die unit showing its starting state of a bending operation according to a further embodiment of the present invention. 
         FIG. 23  is a partially sectioned perspective view of a pipe bend die unit showing a sectional view at the center of its groove bottom portion when starting a bending operation according to a further embodiment of the present invention. 
         FIG. 24  is a partially sectioned perspective view of a pipe bend die unit showing a sectional view at a position spaced from the center of its groove bottom portion when starting a bending operation according to a further embodiment of the present invention. 
         FIG. 25  is a partially sectioned perspective view of a pipe bend die unit showing a sectional view at a position spaced from the center of its groove bottom portion after starting a bending operation according to a further embodiment of the present invention. 
         FIG. 26  is a partially sectioned perspective view of a pipe bend die unit showing a sectional view at a position spaced from the center of its groove bottom portion when finishing a bending operation according to a further embodiment of the present invention. 
         FIG. 27  is a perspective view of a counter pressure member, as viewed from its rotary support portion, for use in a further embodiment of the present invention. 
         FIG. 28  is a perspective view of a counter pressure member, as viewed from its second groove part, for use in a further embodiment of the present invention. 
         FIG. 29  is a plan view of a counter pressure member for use in a further embodiment of the present invention. 
         FIG. 30  is a cross sectional view as viewed from “B” in  FIG. 29  showing a counter pressure member for use in a further embodiment of the present invention. 
         FIG. 31  is a rear view of a counter pressure member for use in a further embodiment of the present invention. 
         FIG. 32  is a cross sectional view sectioned along C-C line in  FIG. 31  showing a counter pressure member for use in a further embodiment of the present invention. 
         FIG. 33  is a perspective view enlarging a bottom portion of second groove part of a counter pressure member for use in a further embodiment of the present invention. 
         FIG. 34  is a perspective view showing an assembled state of a counter pressure member for use in a further embodiment of the present invention. 
         FIG. 35  is a perspective view showing an assembled state of a counter pressure member for use in a yet further embodiment of the present invention. 
         FIG. 36  is a perspective view showing parts for assembling a counter pressure member according to a yet further embodiment of the present invention. 
         FIG. 37  is a perspective view showing a counter pressure member for use in a pipe bend die unit according to a further embodiment of the present invention. 
         FIG. 38  is a perspective view showing a further embodiment of a counter pressure member for use in a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 39  is a perspective view showing a clamp member and counter pressure member for use in a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 40  is a perspective view showing a pipe bend die unit according to a further embodiment of the present invention. 
         FIG. 41  is a perspective view showing a pipe bending apparatus according to a further embodiment of the present invention. 
         FIG. 42  is a perspective view showing a working state of an automatic pipe bending apparatus using a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 43  is a perspective view showing a die change preparation state of an automatic pipe bending apparatus using a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 44  is a perspective view showing a die change starting state of an automatic pipe bending apparatus using a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 45  is a perspective view showing a die changing state of an automatic pipe bending apparatus using a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 46  is a sectional view showing a pipe bending state of a pipe bending apparatus using a pipe bend die unit according to an embodiment of the present invention. 
         FIG. 47  is a sectional view enlarging a part of  FIG. 46 . 
         FIG. 48  is a sectional view showing a pipe bending state of a rotary drawing bend apparatus having a prior bend die and a wiper. 
         FIG. 49  is a sectional view enlarging a part of  FIG. 48 . 
     
    
    
     EMBODIMENTS FOR CARRYING OUT THE INVENTION 
     Hereinafter, will be explained desirable embodiments of the present invention referring to drawings.  FIG. 1  shows a pipe bend die unit according to an embodiment of the present invention, and shows a pipe bending apparatus further comprising a clamp die  200  and a pressure die  300  according to an embodiment of the present invention. The pipe bend die unit has a bend die  100 , which is formed with a pipe-receiving groove of half-circular cross section (configured by first and second groove parts  11 ,  21  as will be described later), and which is rotated about a rotary axis (A). And, according to the pipe bending apparatus, it is so configured that a pipe (P) to be bent is clamped between the bend die  100  and the clamp die  200 , and forwardly driven with being pressed toward the bend die  100  by the pressure die  300 , thereby to bend the pipe (P) by means of compressing load and axially pressing load. Although a mechanism for applying the axially pressing load to the pipe (P) to be forwardly driven is omitted in  FIG. 1 , the mechanism is indicated by a reference ( 1   a ) shown in  FIGS. 42-45  as will be described later. 
     According to the present embodiment, the bend die  100  has a clamp member  10  and a counter pressure member  20 . As shown in  FIGS. 1 and 2 , the clamp member  10  is formed with the first groove part  11  of half-circular cross section, and a fitting recess  12  of a predetermined width is formed on the first groove part  11  to extend in a peripheral direction by a first predetermined length on a planar surface perpendicular to the rotary axis (A). And, the clamp member  10  is formed integrally with a base portion  13 , to which an axial member  60  is fixed so as to provide the rotary axis (A), and a holding member  70  is fixed to the clamp member  10 . Furthermore, a knock pin  80  is fixed to a predetermined position of the base portion  13 , as will be described later. 
     As shown in  FIGS. 6 and 7 , the above-described clamp member  10  has a circularly recessed portion  10   b  to form the first groove part  11  of half-circular cross section, and the fitting recess  12  extending in a peripheral direction on a planar surface perpendicular to the rotary axis (A). The fitting recess  12  is located at the bottom center of the circularly recessed portion  10   b . The first groove part  11  of half-circular cross section is continuous with the circularly recessed portion  10   b  including a part of the fitting recess  12 . That is, the clamp member  10  has a clamp portion  10   a , with a planar surface of the clamp portion  10   a  connected to the clamp die  200 , and the circularly recessed portion  10   b  formed continuously next to the clamp portion  10   a , and a base portion  13  is formed integrally with the clamp portion  10   a  and the circularly recessed portion  10   b.    
     Accordingly, the first groove part  11  possesses a continuous half-circular cross section, with a groove part  11   a  of half-circular cross section formed on the clamp portion  10   a  and a groove part  11   b  of half-circular cross section formed on the circularly recessed portion  10   b . Furthermore, on the groove part  11   a , a plurality of clamp grooves are formed peripherally to ensure holding the pipe (P), in the same manner as the inner peripheral surface of the clamp die  200 . And, on a central portion (axial central portion) of the first groove part  11 , the fitting recess  12  is formed to extend from a portion next to the groove part  11   a  by about 270 degree in a peripheral (circumferential) direct ion of the groove part  11   b . Although the camp member  10  of the present embodiment is formed integrally with the bend die  100  as a part of the bend die  100 , it may be made separately and connected to the bend the  100 , as described later with reference to  FIGS. 15-18 . 
     On the other hand, as shown in  FIGS. 1 and 2 , the counter pressure member  20  is formed with the second groove part  21  of half-circular cross section on its outer peripheral surface, and a fitting protrusion  22  extending in a peripheral direction by a predetermined length from a tip end portion of the second groove part  21 . When the fitting protrusion  22  is positioned in the fitting recess  12 , the pipe-receiving groove of half-circular cross section is formed by the combination of the first groove part  11  of the clamp member  10  and the second groove part  21  of the counter pressure  20 . As shown in  FIG. 3 , the counter pressure member  20  has a rotary support portion  23 , which is rotatably supported by the axial member  60  (rotary axis (A)), and a part of the rotary support portion  23  configures the fitting protrusion  22 . Therefore, the outer peripheral surface of the rotary support portion  23  is formed into a curved surface, to form the pipe-receiving groove of half-circular cross section, together with the first groove part  11  of the clamp member  10 . 
     The above counter pressure member  20  is formed as shown in  FIGS. 8-14 . That is, a curved surface portion (counter pressure portion)  20   a  positioned to be capable of contacting the circularly recessed portion  10   b  and the rotary support portion  23  rotatably supported about the rotary axis (A) are formed integrally, and a part of the rotary support portion  23  configures the fitting protrusion  22 . Therefore, the outer peripheral surface of the rotary support portion  23  is formed into a curved surface, to form the pipe-receiving groove of half-circular cross section, together with the first groove part  11  of the clamp member  10 . That is, the counter pressure member  20  is formed with a second groove part  21  of half-circular cross section, and the end surface of the second groove part  21  contacting the first groove part  11  of the clamp member  10  is formed to be curved according to its front view, as indicated by a contacting portion (R) in  FIG. 2 . Although the curved surface portion  20   a  is formed with its thickness being gradually reduced, it is not continuously made extremely thin, because it is integrally formed with the rotary support portion  23  at a portion where the fitting protrusion  22  is extended, thereby to ensure a sufficient strength. 
     And, an outer peripheral surface  22   a  of the fitting protrusion  22 , i.e., the outer peripheral surface of the rotary support portion  23  is formed into a curved surface as shown in  FIGS. 8 and 10-14 . When the fitting protrusion  22  is fitted into the fitting recess  12  of the clamp member  10 , thereby to form a part of the half-circular cross section of the first groove part  11  of the clamp member  10 , the pipe-receiving groove of half-circular cross section is formed by them. The rotary support portion  23  of the present embodiment is made in an annular shape, while it may be made in C-shape, with a portion except for the fitting protrusion  22  being cut out to provide a space. 
     The clamp member  10  and counter pressure member  20  as configured above are hingedly connected about the rotary axis (A), and rotatably supported relative to each other about the axial member  60  (rotary axis (A)). According to the present embodiment, the clamp member  10  is supported to be rotated against the counter pressure member  20 , which is fixed to a predetermined position of a support device (not shown). As shown in  FIG. 2 , the clamp member  10  and the counter pressure member  20  are hingedly connected, such that a fitting portion (F) of the fitting protrusion  22  that is fitted in the fitting recess  12 , which portion (F) is not included on planar surfaces perpendicular to the rotary axis (A), i.e., two planar surfaces parallel to the plane perpendicular to the paper surface of  FIG. 2  including (H) shown in  FIG. 2 , is located at a foreside (right side of (S) in  FIG. 2 ) in an advancing direction of the pipe (P) relative to an initial position (indicated by a vertical one-dotted chain line (S) in  FIG. 2 ) where a bending operation of the pipe (P) is initiated, and a mating portion (R) of the first groove part  11  of the clamp member  10  and the second groove part  21  of the counter pressure member  20  in a rotating direction is located at a backside (left side of (S) in  FIG. 2 ) of the advancing direction of the pipe (P). In other words, the fitting portion (F) of the fitting protrusion  22  fitted into the fitting recess  12  in a rotating direction is located at the foreside in an advancing direction of the pipe (P) relative to the position where the bending operation of the pipe (P) is initiated, and the mating portion (R) of the first groove part  11  of the clamp member  10  and the second groove part  21  of the counter pressure member  20  in the rotating direction is located at a backside of the advancing direction of the pipe (P) relative to the position where the bending operation of the pipe is initiated. 
     Consequently, with the fitting protrusion  22  of the counter pressure member  20  being fitted into the fitting recess  12  of the clamp member  10 , the axial member  60  configuring the rotary axis (A) is inserted through the rotary support portion  23  to be fixed to the base member  13 , and fixed to the holding member  70 , thereby to configure the bend die  100  as shown in  FIG. 1 . Furthermore, a knock pin  80  is fixed to a predetermined position of the base portion  13  of the clamp member  10 , so that an initial relative position between the clamp member  10  and the counter pressure member  20  is provided by a position where the counter pressure member  20  abuts on the knock pin  80 . On the other hand, the clamp die  200  and the pressure die  300  are arranged as shown in  FIG. 1 , and disposed to be close to or away from the bend die  100 , respectively. 
     As shown in  FIGS. 1 and 2 , as the pipe bend die unit is configured by the bend die  100  with the clamp member  10  and the counter pressure member  20  placed at the initial relative position, if a plurality of pipe bend die units are provided for various shapes of the pipes (P) to be bent, in case of bending the various shapes of pipes, it is only required to select and change the bend die unit for the shape of the pipe to be bent, so that a so-called die change can be made easily. Particularly, as the initial relative position between the clamp member  10  and counter pressure member  20  can be set by the knock pin  80  in advance, no adjustment after the die change is required, so that it can be adjusted easily without any skilled technique. In addition to the pipe bend die unit as described above, if an assembly is configured by further comprising the clamp die  200  and pressure die  300 , it is possible to provide a pipe bend die assembly for performing the die change and adjustment easily. 
     Referring to  FIGS. 1-5 , the overall operation of the pipe bending apparatus having the pipe bend die unit as described above will be explained hereinafter. At the outset, with the counter pressure member  20  being held at the initial relative position to contact the knock pin  80 , a portion to be bent of the body portion of the pipe (P) is placed at the bend starting position as indicated by (S) in  FIG. 2  of the bend die  100 , a known mandrel as indicated by (M) in  FIGS. 1 and 5  is inserted into the pipe (P). The mandrel (M) has balls (M 1 ) and (M 2 ) pivotally mounted on its tip end portion, as its cross sectional view is shown in  FIG. 5 , where a hutching is omitted to define each part clearly. The balls (M 1 ) and (M 2 ) are inserted into the pipe (P), and driven to be disposed between the bend die  100  and the clamp die  200  (and pressure die  300 ) within a predetermined rotating region of the bend die  100 . Next, the clamp die  200  and pressure die  300  are driven toward the bend die  100 , the tip end portion of the pipe (P) is clamped between the clamp member  10  of the bend die  100  and the clamp die  200 , and the body portion of the pipe (P) is compressed between the counter pressure member  20  of the bend die  100  and the pressure die  300 , as shown in  FIG. 3 . 
     Then, with the tip end portion of the pipe (P) being clamped between the clamp member  10  and the clamp die  200 , the pipe (P) is forwardly driven, with the body portion of the pipe (P) being pressed to the counter pressure member  20  by the pressure die  300 , and also the clamp die  200  and the clamp member  10  are rotated about the rotary axis (A), so that the pipe (P) is bent to be rolled around the outer peripheral surface of the rotary support portion  23  (the outer peripheral surface  22   a  of the fitting protrusion  22 ), thereby to form the pipe (P) bent in such a shape as shown in  FIGS. 4 and 5 . During this operation, a large pressure is applied to the pipe (P) in its longitudinal direction and radial direction. With the pipe bend die unit according to the present embodiment being employed, however, the inner side wall of the bent pipe (P) is prevented from being thickened due to its compressed deformation, and the outer side wall of the bent pipe (P) is thickened and prevented from being thinned, so that an appropriate thickness of the pipe wall can be maintained even at the bent portion. 
     As described before, the bend die  100  served for the pipe bend die unit of the present embodiment comprises the clamp member  10  and counter pressure member  20 , which are hingedly connected about the rotary axis (A), and rotatably supported relative to each other about the rotary axis (A). Therefore, as the pipe (P) is being bent, the clamp member  10  can be rotated relatively to the counter pressure member  20  about the rotary axis (A), with the counter pressure member  20  being pressed by the pressure die  300  through the pipe (P). Consequently, the clamp member  10  is rotated from the initial bending position (as indicated by (S) in  FIG. 2 ) for the pipe (P) in a circumferential direction spaced from the counter pressure member  20 . 
     Then, the counter pressure member  10  and the clamp member  20  are hingedly connected, such that the fitting portion (indicated by (F) in  FIG. 2 ) of the fitting protrusion  22  that is fitted in the fitting recess  12 , which portion is not included on planar surfaces perpendicular to the rotary axis (A), is located at the foreside in the advancing direction of the pipe (P) relative to the position (S) where the bending operation of the pipe (A) is initiated, and the mating portion (indicated by (R) in  FIG. 2 ) of the first groove part  11  of the clamp member  10  and the second groove part  21  of the counter pressure member  20  in the rotating direction is located at the backside of the advancing direction of the pipe (A), whereby a step possibly caused between the clamp member  10  and counter pressure member  20  is made small. Therefore, even if relatively large longitudinal load and compressed load comparing with the prior art are applied to the pipe (P), a plastic deformation caused by bending it can be controlled appropriately, which will be described later in detail referring to  FIGS. 46-47 . 
     Consequently, although the pipe (P) which was bent by use of the pipe bend die unit of the present embodiment is formed with a thick portion (protruded portion) as shown in  FIG. 19  at a position corresponding to the fitting portion and the fitting protrusion  22 , the portions next to the fitting portion will be formed in a smooth curved surface. Practically, thickness of a portion as indicated by a thin line in  FIG. 19  is changed gradually, and deformed material is fitted into the fitting portion (indicated by (F) in  FIG. 2 ) to form a thick portion (TP 1 ), and thick portions (TP 2  and TP 3 ) along the mating portion (indicated by (R) in  FIG. 2 ). However, the portion as indicated by the thin line in  FIG. 19  is formed in a smooth curved surface, so that it does not correspond to the crinkling, and therefore, the thick portions (TP 1 , TP 2  and TP 3 ) will not be created. Rather, the bent pipe with the thick portions (TP 1 , TP 2  and TP 3 ) being formed is proved to be the one which was formed by use of the pipe bend die unit of the present embodiment, to provide a proof of forming quality. 
     As described above, according to the pipe bending apparatus having the pipe bend die unit of the present embodiment, a smooth bending can be achieved without causing a crinkling. In other words, by appropriately controlling the plastic forming caused by the bending appropriately, the bending of the pipe (P) can be achieved appropriately without causing the crinkling. Consequently, provided that a diameter of a pipe (P) is “d” and a bending radius is “r”, for example, a pipe (P) with such an extraordinarily small bending radius that “r/d” is smaller than 1 can be easily formed. As an alternative to the aforementioned pipe bending apparatus, it may be so configured that the clamp member  10  is fixed, and that the counter pressure member  20  is rotated about the rotary axis (A). 
     Furthermore, as for the pipe bend die unit installed on the pipe bending apparatus as described above, if a plurality of pipe bend die units are prepared in accordance with various shapes of pipes to be bent, when a pipe is to be bent in a shape, a specific pipe bend die unit for the shape to be bent may be simply selected and changed, so that its die change can be performed easily. As the clamp member  10  and counter pressure member  20  configuring the pipe bend die unit have been placed at the initial relative position, no adjustment is required after the die change. Accordingly, the pipe bend die unit can be used for an automatic pipe bending apparatus, so that an automatic die change can be performed by a robot, which will be described later referring to  FIGS. 42-45 . 
       FIGS. 15-18  relate to another embodiment of the present invention, wherein in contrast to the clamp portion  10   a  that is formed integrally with the clamp member  10 , the portion forming the clamp portion  10   a  is made as a separate body (indicated by “ 10   y ” in  FIG. 15  and so on), and connected to a main body  10  (indicated by “ 10   x ” in  FIG. 15  and so on) configuring the circularly recessed portion  10   b . For example, as shown in  FIG. 15 , the main body  10   x  is configured by an upper section  40  and a lower section  50 , which are divided by a surface perpendicular to the rotary axis (A), and connected to the separate body  10   y , thereby to configure the clamp member  10 . That is, the axial member  60  is disposed to penetrate a center hole  42  of the upper section  40 , the rotary support portion  23  of the counter pressure member  20  and a center hole  52  of the lower section  50 , and, after an upper portion of the axial member  60  is penetrated through a center hole  71  of the holding member  70 , the holding member  70  is fixed to the upper section  40 , thereby to be in such an assembled state as shown in  FIG. 16 . The clamp portion  10   y  is fixed to the main body  10   x  (the upper section  40  and lower section  50 ), with screws (not shown) being inserted from fixing holes  14  and  15 , and meshed with screw holes  41  and  51  of the upper section  40  and lower section  50 . With respect to other configuration, it is the same as the aforementioned embodiment, so that its explanation is omitted herein, with the same reference numerals given to substantially the same members as described before. 
       FIGS. 17 and 18  illustrate the separately made clamp portion  10   y , the first groove part  11  and fitting recess  12  of which are formed in the same shapes as those of the clamp member  10  as shown in  FIGS. 1 and 2 . That is, the half-circular cross section of the first groove part  11  is formed in the same shape as the half-circular cross section of the second groove part  21  of the counter pressure member  20 , so that the first groove part  11  and second groove part  21  form the pipe-receiving groove of a continuous half-circular cross section. And, the fitting protrusion  22  of the counter pressure member  20  is positioned in the fitting recess  12 , so that they can smoothly contact the outer peripheral surface of the pipe (P) to be bent. 
     According to the embodiment as shown in  FIGS. 15-18 , therefore, the clamp member  10  is configured by the main body  10   x , which is configured by the upper section  40  and lower section  50 , and the clamp portion  10   y . The fitting recess  12  is configured by a cutout portion of the clamp portion  10   y , and a clearance between the upper section  40  and lower section  50 . With the fitting protrusion  22  of the counter pressure member  20  being positioned in the fitting recess  12 , the bend die  100  is configured. Hereinafter, the clamp member  10  includes the member configured by the main body  10   x  and clamp portion  10   y , except otherwise described specifically. 
       FIGS. 20-36  relates to a pipe bend die unit according to a further embodiment of the present invention, wherein the same reference numerals are given to those members corresponding to the members as shown in  FIGS. 1-18 . According to the present embodiment, the counter pressure member  20  has a curved surface portion  20   a , which is formed on each of opposite sides of the planar surface that is perpendicular to the rotary axis (A) including the bottom center of the circularly recessed portion  10   b , i.e., the planar surface including (H) as shown in  FIG. 2  and corresponding to the paper surface of  FIG. 2  (hereinafter, simply referred to as “planar surface (H)”), and which is configured to contact the circularly recessed portion  10   b . The curved surface portion  20   a  possesses an arch center on an axis that is offset from the rotary axis (A) perpendicular to the planar surface (H) in a direction spaced from the rotary axis (A). Also, the counter pressure member  20  is formed with the second groove part  21  of half-circular cross section, with the bottom center of the second groove part  21  being provided on the planar surface (H) on its outer peripheral surface, and the fitting protrusion  22  extending in the peripheral direction by a predetermined length from the tip end portion of the second groove part  21 . When the fitting protrusion  22  is positioned in the fitting recess  12 , the pipe-receiving groove of half-circular cross section is formed by the first groove part  11  of the clamp member  10  and the second groove part  21  of the counter pressure member  20 . Hereinafter, will be explained the configuration of the counter pressure member  20  including the rotary support portion  23 , with reference to  FIG. 20  and so on. 
     As shown in  FIG. 20 , the curved surface portion  20   a  is provided on the opposite sides of the above planar surface (H) corresponding to the paper surface of  FIG. 20 , and its arch center is provided on an axis (OC), which is offset from the rotary axis (A) perpendicular to the planar surface (H) in the direction spaced from the rotary axis (A). The axis (RC) as shown in  FIG. 20  corresponds to the rotary axis (A). In  FIG. 20 , on the second groove part  21  of the half-circular cross section as indicated by a broken line, there is positioned the pipe (P) having a center axis (PC) thereof as indicate by a two-dotted chain line, so that the axis (RC) and axis (OC) are positioned on a one dotted chain line (V) including the initial position (S) for bending the pipe (P) and extending vertically, and that the distance between the axes corresponds to the offset amount (d). In  FIG. 20 , although only the curved surface portion  20   a  formed at one side relative to the planar surface (H) appears, the other curved surface portion of the same shape with the curved surface portion  20   a  is formed at the other side, i.e., the reverse side of the paper surface of  FIG. 20 . 
     Particularly, the curved surface portion  20   a  has a maximum arch of radius (ra) and minimum arch of radius (rb) as shown in  FIG. 20 , and formed to expand so as to provide the curved surface to be capable of contacting the first groove part  11  of half-circular cross section (at the initial position). That is, as shown in  FIG. 21 , at the initial position (S) for bending the pipe (P), the fitting protrusion  22  and the curved surface portion  20   a  contact the whole surface of the circularly recessed portion  10   b  (first groove part  11 ), and at the position remote from the plane (H), a clearance (“G” as shown in  FIG. 21 ) is formed between the curved surface portion  20   a  and the circularly recessed portion  10   b .  FIG. 21  shows a sectional view at the position spaced from the plane (H) by a predetermined distance, i.e., at the position spaced from the plane including the central axis (PC) in  FIG. 20  toward the reverse side (downward in  FIG. 2 ), by a predetermined distance. 
     Accordingly, the tip end portion of the curved surface portion  20   a  of the counter pressure member  20  tightly contacts the circularly recessed portion  10   b  at the initial position (S) for bending the pipe (P), and the clearance (G) is formed between the curved surface portion  20   a  and the circularly recessed portion  10   b , as described above, at other portions than the tip end portion. As a result, the counter pressure member  20  can be easily and appropriately assembled with the clamp member  10 , which is formed by the upper die  40  and lower die  50  in this embodiment, without causing an interference with the circularly recessed portion  10   b . As the counter pressure member  20  does not slide on the circularly recessed portion  10   b  at other portions than the tip end portion, no frictional loss will be caused, so that a durability of the counter pressure member  20  in particular will be improved. When the curved surface portion  20   a  is formed, it should be avoided to employ any arch center other than the axis (OC) as described above, because otherwise the appropriate contact will not be obtained. For example, if the arch center is positioned on such an axis (not shown) that is perpendicular to the plane (H) and offset in the direction spaced from the rotary axis (A), and also offset in the direction perpendicular thereto, any appropriate clearance will not be provided. 
       FIGS. 22-26  illustrate the states of relative movement between the clamp member  10  and the counter pressure member  20 .  FIG. 22  illustrates the initial state,  FIG. 23  illustrates the sectional view at the plane (H), and  FIGS. 24-26  illustrate the sectional views at the position spaced from the plane (H), i.e., spaced from the plane including the central axis (PC) in  FIG. 20  toward the reverse side (downward in  FIG. 2 ), by the predetermined distance. As shown in  FIGS. 24-26 , even if the relative rotational angle between the clamp member  10  and the counter pressure member  20  is varied, there exists the clearance (G) between the curved surface portion  20   a  of the counter pressure member  20  and the circularly recessed portion  10   b . Therefore, the counter pressure member  20  can be easily and appropriately assembled into the clamp die  10 , without causing the interference with the circularly recessed portion  10   b , and the durability of the counter pressure member  20  will be improved. 
     According to the present embodiment, the counter pressure member  20  has a support member  26  as shown in  FIG. 34 , while it may be formed integrally with the support portion fixed to the aforementioned support device (not shown), as shown in  FIG. 8 . As shown in  FIGS. 27-34 , the counter pressure member  20  is integrally formed with a main body portion  24  and connecting portion  25  so as to be connected to the support member  26 . As the fundamental configuration of the counter pressure member  20  is the same as that as disclosed in  FIGS. 1-26 , common reference numerals are used in  FIG. 27  and so on, and its overall configuration is indicated as the counter pressure member  20 . 
     As shown in  FIG. 27 , the counter pressure member  20  of the present embodiment has the aforementioned rotary support portion  23 , and the main body portion  24 , which is formed integrally with rotary support portion  23 , and formed with the second groove part  21  of half-circular cross section and the curved surface portion  20   a . And, a rib  23   a  is formed to extend from at least a peripheral part of the rotary support portion  23  integrally formed with the main body portion  24 . As shown in  FIG. 29 , the rib  23   a  is formed to extend in a tangential direction to an annular part of the rotary support portion  23 , and a contacting surface  23   b  is formed at its tip end to contact a supporting surface  26   b  (indicated by two-dotted chain line) of the support member  26 . Also, the connecting portion  25  integrally formed with the main body portion  24  is formed in parallel with the tangential direction to the annular part of the rotary support portion  23 , and a contacting surface  25   a  is formed to contact a supporting surface  26   a  (indicated by two-dotted chain line) of the support member  26 . In  FIG. 29 , as the support surfaces  26   a  and  26   b  are orthogonal to each other, the contacting surface  25   a  and contacting surface  23   b  are formed so as to be orthogonal to each other. However, these surfaces may be formed in accordance with the connecting structure of the support member  26  with the connecting portion  25  and rib  23   a.    
     The above-described rib  23   a  is provided for relieving stress concentration applied to a bottom portion of the rotary support portion  23  at a boundary with the curved surface portion  20   a , because it is not possible to thicken the bottom portion more than is necessary, in order to avoid any interference with other devices. For example, when the pipe (P) is bent, a load (L) is supposed to be applied to the rotary support portion  23  as indicated by a blank arrow in  FIG. 34 . However, its component force (La) is applied to the rib  23   a , whereas its component force (Lb) is applied to the fitting protrusion  22 , so that the stress concentration applied to the bottom portion of the rotary support portion  23  will be cancelled. Furthermore, on the rib  23   a , as shown in  FIGS. 27 and 29 , between the bottom portion of the rotary support portion  23  and the contacting surface  25   a , there is formed a large cross section portion  23   c , the cross section area of which is formed so as to be decreased gradually up to the contacting surface  25   a . The large cross section portion  23   c  is formed so as to avoid the interference with other devises, when the bending angle of the pipe (P) is set to be large. Therefore, the rib  23   a  may be formed in such a shape and cross section area that can ensure the necessary component force (Lb). 
     According to the counter pressure member  20  of the present embodiment, a plan view of which is shown in  FIG. 29 , a view as viewed from “B” of which is shown in  FIG. 30 , and a rear view of which is shown in  FIG. 31 , the outer peripheral surface  22   a  of the fitting protrusion  22 , i.e., the outer peripheral surface of the rotary support portion  23  is formed in the curved surface, the end face of the second groove  21  is curved in shape as viewed from the rear (or front) surface, and formed into a straight line as viewed from “B”, and the rib  23   a  appears in  FIG. 31 . In  FIG. 29 , an inclined angle (θa) of the straight line portion as viewed from “B” against the straight line (V) line as indicated by one-dotted chain line in  FIG. 20  is provided according to diameter and wall thickness of the pipe (P) to be bent. In the case where the wall thickness of the pipe (P) is relatively large to its diameter, the inclined angle is set to be large, and in the case where the wall thickness of the pipe (P) is relatively small, the inclined angle is set to be small. 
     As shown in  FIG. 32  sectioned along C-C line of  FIG. 31 , an obtuse angle is provided for an angle (θb) between the second groove part  21  of half-circular cross section of the main body portion  24  and a side surface  21   a  of an end portion of the second groove part  21  formed next to the curved surface portion  20   a . Consequently, durability of the end portion of the second groove part  21  according to the counter pressure member  20  is improved, comparing with a usual case where a right or acute angle is provided for the angle (θb). Also, instead of the boundary of the second groove part  21  of the main body portion  24  and the side surface  21   a  of its end portion being set to be straight, a cross section with a smoothly curved line may be employed, so that the durability of the end portion of the second groove part  21  is further improved. In  FIGS. 31 and 32 , “ 24   a ” indicates the outer surface of the main body  24 . Furthermore, as shown in  FIG. 33 , a curved surface portion  21   b  is formed on the boundary between the curved surface portion  20   a  and the rotary support portion  23 , so that the stress concentration, which is applied to the portion  21   b  when the pipe (P) is bent, is relieved. 
     Although the counter pressure member  20  has the rotary support portion  23  and the main body portion  24  integrally formed therewith as described above, a large load is applied to the rotary support portion  23  through the pipe (P) to be bent, whereby the wear is unavoidable, so that its replacement will be required after a long term use of it. In view of this, it may be so configured that the counter pressure member  20  to be fixed to the support member  26  is further divided into a first member  20   x , which includes a main part of the rotary support portion  23  and connecting portion  25 , and a second member  20   y , which includes a part  23   y  of the rotary support portion  23  and the main body portion  24 , and that they are connected by bolts for example, thereby to configure the counter pressure member  20 . Consequently, in the case where the rotary support portion  23  is worn, only the second member  20   y  including the worn part  23   y  may be replaced, so that the replacement is easily made, and that an inexpensive counter pressure member  20 , and therefore an inexpensive bend die unit  100 , can be provided in view of a long term use of it, to result in a cost down. 
       FIG. 37  illustrates a yet further embodiment of the counter pressure member  20 , which is indicated by “ 20   v ”, and an axial portion  23   s  served as the rotary axis (A) is integrally formed with the rotary support member  23  of the counter pressure member  20 . The upper part and lower part of the axial portion  23   s  are rotatably supported on the upper section  40  and lower section  50  as shown in  FIG. 15  for example, respectively. Consequently, the axial member  60  as shown in  FIG. 15  and etc. is not be required, so that the pipe bend die unit can be manufactured easily at low cost. 
     As shown in  FIG. 38 , the counter pressure member  20  may be divided into two members of a mating member  20   w  including the fitting protrusion portion  22   w  and a rotary support member  20   z  supported to be rotatable about the rotary axis (A), in such a manner that the mating member  20   w  is detachably connected to the rotary support member  20   z . Consequently, in the case where the counter pressure member  20  is required to be replaced, only the mating member  20   w  may be used for a repair part to be replaced as described above, so that an inexpensive unit as a whole can be configured. As for the rotary support member  20   z , it may be configured by a rotary support portion  23   z  and a pair of bearing members  24   z ,  24   z  fixed thereto. 
     Or, as shown in  FIG. 39 , the clamp member  10  and the counter pressure member  20  may be configured by a plurality of parts divided by planes perpendicular to the rotary axis (A), respectively, and stacked one over another to produce a clamp member  10   p  and a counter pressure member  20   p . That is, by stacking the plurality of parts, the clamp member  10   p  and counter pressure member  20   p  can be configured, and a hinged connection between them can be configured at the same time. 
     Or, as shown in  FIG. 40 , the upper section  40  and the lower section  50  may be supported by a common support member  90 . Consequently, supporting strength required for the axial member  60  can be provided within the pipe bend die unit. Therefore, a head portion of the axial member  60  is not required to be fixed separately, a die change can be made easily, and any concern about interference with other devices is not needed, so that the die change can be made more easily. 
     Furthermore, as shown in  FIG. 41 , a plurality of bend dies  101 ,  102  and  103  each having the clamp member  10  and the counter pressure member  20  may be stacked and supported about the rotary axis (A). In each clamp member  10  and counter pressure member  20 , they are configured to be hingedly connected about the rotary axis (A), respectively. According to each die, compressive stress is appropriately applied to the inner side of bent portion of the pipe (P), as described before, so that bending of each pipe (P) can be achieved simultaneously and appropriately, without causing the crinkling. According to the present embodiment, each clamp member  10  is supported by a common base  30 , and each counter pressure member  20  is supported by a common support member  92 . Therefore, by means of a single knock pin  80 , the initial relative position between each clamp member  10  and each counter pressure member  20  can be easily set, and no adjustment after the die change is required. It may be so configured that each clamp member  10  is fixed, and that each counter pressure member  20  is movable thereto. 
     Next will be explained about an example of a production line for an automotive pipe bending apparatus using the pipe bend unit as disclosed in  FIG. 1  and so on, with reference to  FIGS. 42-45 .  FIG. 42  shows a bend working state of the pipe (P),  FIG. 43  shows the die change preparing state of the pipe bend unit that is formed in the same configuration as that shown in  FIG. 16 , and that is indicated by “DU” to show an automatic working unit,  FIG. 44  shows the die change starting state, and  FIG. 45  shows the die changing state. At the outset, the automatic pipe bending apparatus will be roughly explained with reference to  FIG. 42 . The automatic pipe bending apparatus  1  of the present embodiment is equipped with a mechanism  1   a  for applying the axial pressure load, in addition to the bend die  100 , clamp die  200 , pressure die  300  and etc. as shown in  FIG. 1 . Next to the pipe bending apparatus  1 , there is placed a robot device  2  for supplying the pipe (P) to be formed, and placing it at a predetermined initial position. Furthermore, next to the robot device  2 , there is placed a pipe placing table  3  for placing thereon the material to be formed, and the formed pipe (P). Between the pipe placing table  3  and the robot device  2 , there is placed a clamping jig placing table  4  for placing thereon a clamping jig (MH), temporarily. And, next to the pipe bending apparatus  1  and robot device  2 , there is placed a pipe bend die unit placing table  5  (hereinafter simply referred to as a unit table  5 ) for placing thereon the pipe bend unit (DU), hereinafter simply referred to as a unit (DU). 
     According to the robot device  2 , the clamping jig (MH) is mounted on a tip end of a robot arm  2   a  through an auto tool changer (ATC). On the opposite ends of the clamping jig (MH), mounted are clamp mechanisms for clamping the pipe (P) to be detachable, one of which is capable of clamping the pipe (P) to be formed, and the other one of which is capable of clamping the formed pipe (P).  FIG. 42  shows such a state that the pipe (P) is being formed by the pipe bending apparatus  1 , and that the robot device  2 , with the clamping jig (MH) clamping the pipe (P) to be formed, is supplying the pipe (P) to the pipe bending apparatus  1 , and also waiting for receiving the formed pipe (P) therefrom. 
     Next,  FIG. 43  shows such a state that the robot device  2  is removing the clamping jig (MH) from the tip end of the robot arm  2   a , and placing it on the clamping jig placing table  4  temporarily, and waiting for changing the unit (DU). According to the pipe bending apparatus  1 , the unit (DU) is clamped by a pair of unit holders  1   b ,  1   b , which will be rotated and retracted to unclamp the unit (DU). And,  FIG. 44  shows such a state that the unit (DU) to be changed is being removed from the pipe bending apparatus  1 . In this respect, another auto tool changer (ATC) is mounted on the tip end of the unit (DU), and fitted with the auto tool changer (ATC) mounted on the tip end of the robot arm  2   a , so that the unit (DU) is hanged at the tip end of the robot arm  2   a , as shown in  FIG. 45 . 
     Consequently, a new unit (DU) is removed from the unit table  5  by means of the robot arm  2   a , and transferred to the pipe bending apparatus  1  as shown in  FIG. 45 . On the unit table  5 , various kinds of the unit (DU) are placed at designated positions according to a program for a moving locus of the robot arm  2   a , so that the unit (DU) is selected from the units on the unit table  5  by the robot arm  2   a  according to a die change order, and installed on the pipe bending apparatus  1 . 
     The die change of the unit (DU) for the pipe bending apparatus  1 , i.e., changing and installing the unit (DU), and operation of the pipe bending apparatus  1 , i.e., bending the pipe (P) can be automated, and the unit (DU) can be provided with intelligence to expect a more advanced automation. For example, it may be so configured that various kinds of sensors or cameras are installed on the unit (DU), or a laser beam is applied, and that working data are measured at real time to be stored in a memory tip or the like embedded in the unit (DU). Or, it may be so configured that a communication means embedded in the unit (DU) is transmitting serial working data to a line-controller or the like, to store the data therein. In the case where it is so configured that the working data are stored in the memory tip or the like embedded in the unit (DU), the working data may be transmitted by wire to the line-controller or the like through the robot device  2 , or may be stored in the pipe bending apparatus  1 . Furthermore, it may be so configured that a remote counting of the formed products under a license for bending the pipe by means of the unit (UD) may be performed by transmitting the working data through the aforementioned communication means. According to the automatic operation and/or automatic die change, therefore, the positions or states of the unit (DU) can be traced sequentially, and also more effective working conditions, automatic operation and/or automatic die change can be provided by analyzing the stored data, thereby to contribute an automatic factory system. According to the automatic die change line as described above, only the unit (DU) was selected as a target for the die change, while it may be so configured that the automatic change of the pressure die, clamp die, and mandrel as well can be made adequately by robot means depending on difference of diameters of the pipes to be formed according to the die change, or difference in thickness of the pipes (with the same diameter). 
     Next,  FIGS. 46 and 47  show a state of the pipe being bent according to the pipe bending apparatus using the pipe bend die unit as shown in  FIG. 1  and so on, whereas  FIGS. 48 and 49  show a state of the pipe being bent according to the rotary draw bending apparatus using the prior bend die and wiper, to be compared with the present embodiment. At the outset, in order to form a pipe with a small bending radius, it is required to apply a large pressure in the axial direction and radial direction of the pipe. Particularly, in order to apply the large pressure in the radial direction, the configuration as shown in  FIG. 46  requires such a mechanism as to be capable of opposing against a large load applied to the pipe (P) by the pressure die  300 . 
     According to the present invention, it is so configured that the bend die  100  of the aforementioned embodiment, especially the counter pressure member  20  hingedly connected to the clamp member  10  functions as that mechanism, so as to be capable of opposing the large load by the pressure die  300  sufficiently. As shown in  FIG. 46 , axially pressing load (indicated by “FL”) and compressing load (indicated by “PL”) are applied to the pipe (P). According to the present embodiment, sufficient pressure proof strength against the large load by the pressure die  300  can be ensured, because the clamp member  10  and the counter pressure member  20  are hingedly connected as shown in  FIG. 2 , such that the fitting portion (F) of the fitting protrusion  22  that is fitted in the fitting recess  12 , which portion (F) is not included in the planar surfaces perpendicular to the rotary axis (A), is located at the foreside in an advancing direction of the pipe (P) relative to the initial position of bending operation (S), as shown in  FIG. 2 , and the mating portion (R) of the first groove part  11  of the clamp member  10  and the second groove part  21  of the counter pressure member  20  is located at the backside of the advancing direction of the pipe (P). Furthermore, in such a state that the mandrel (M) (ball mandrels M 1  and M 2 ) is inserted into the pipe (P), the compressing load (PL) applied to the pipe (P) can be made larger, so that the bending radius of the pipe (P) can be made minimum. 
     Also, as enlarged in  FIG. 47 , in order to avoid reduction of thickness at the outer side of the pipe (P) caused by bending the pipe (P), it is so configured that the axially pressing load (FL) is applied to the pipe (P), so that the pipe (P) is fed with material, thereby to enlarge its thickness. At the inner side of the pipe (P) to be bent, however, a friction force (indicated by a leftward arrow “FR” in  FIG. 47 ) is caused by the compressing load (PL) against the axially pressing load (FL), so that the thickness will be increased by that friction force (FR). Furthermore, if the axially pressing load (FL) is applied in the state that the mandrel (M) has been inserted into the pipe (P), the pipe (P) is advanced (moved to the rightward in  FIG. 47 ) in such a state as being compressed between the mandrel (M) and the counter pressure member  20 , so that the thickness will be more largely increased, with squeezing operation being added by both of the members. 
     In contrast, according to the rotary bending apparatus using the prior bend die and wiper for preventing the crinkling, it is arranged in such a manner that the wedge shaped wiper (W) will squeeze into a clearance between the pipe (P) and bend die (D) as shown in  FIG. 48 , the tip end of the wiper (W) is made extremely thin, so as to reduce the clearance between the pipe (P) and wiper (W) as small as possible, so that the wiper (W) is likely to be fragile. Therefore, if the large load by the pressure die  300  is continuously applied to the wiper (W), its tip end will be deformed or destroyed, to enlarge the clearance between the same and the pipe (P), thereby to cause the crinkling. In order to avoid the crinkling, it is required to maintain the extremely thin tip end of the wiper (W), so that a periodical change of the wiper (W) and a change for a destroyed one have been necessarily required. Also, as the pipe is bent to avoid the crinkling from being caused, the radius of the pipe (P) to be bent is limited, so that the maximum radius of the pipe (P) to be made will be approximately 2 of the aforementioned r/d ratio, at most. 
     According to the prior rotary bending apparatus, although the bending of the pipe (P) is performed in the state that the mandrel (M) has been inserted into the pipe (P), and the friction force (FR) is caused as shown in  FIG. 49 , no sliding motion is made between the pipe (P) and bend die (D) basically, but a following motion of the pipe (P) is made in response to rotating motion of the bend die (D), so that increase of the thickness cannot be expected by the friction force (FR).  FIGS. 48 and 49  are prepared to simply show operation and effect according to the prior art, to be compared with the operation and effect according to the present invention using the pipe bend die unit.  FIGS. 48 and 49  are not intended to imply that such known apparatuses are comparable to the pipe bend die unit of the present invention. 
     DESCRIPTION OF CHARACTERS 
     
         
           1  pipe bending apparatus 
           2  robot device 
           3  pipe placing table 
           4  clamping jig placing table 
           5  pipe bend die unit placing table 
           10  clamp member 
           10   a  clamp portion 
           10   b  circularly recessed portion 
           11  first groove part 
           12  fitting recess 
           13  base portion 
           20  counter pressure member 
           20   a  curved surface portion 
           21  second groove part 
           22  fitting protrusion 
           23  rotary support portion 
           40  upper section 
           50  lower section 
           60  axial member 
           70  holding member 
           80  knock pin 
           100  bend die 
           200  clamp die 
           300  pressure die 
         A rotary axis 
         P pipe 
         M mandrel