Abstract:
A radial press comprises two press yokes and eight crimping members. The yokes are arranged on a plane that is perpendicular to the press axis and are located diametrically opposite the press axis and can be moved towards each other in a straight line by means of a drive unit, whereby the direction of movement is perpendicular to the press axis. At least one part of the crimping members that are disposed in the yokes has slide surfaces that respectively cooperate with a control surface of one of the yokes or an adjacent crimping member in such a way that all of the crimping members can be moved in a uniform manner onto the press axis when the press yokes move closer to each other. Two crimping members arranged perpendicular to the direction of movement of the at least one movable press yoke are divided into two segments.

Description:
CROSS-REFERENCES TO RELATED APPLICATIONS  
       [0001]    This is a continuation of U.S. application Ser. No. 09/673,825, filed Oct. 20, 2000. 
     
    
     
       FIELD OF THE INVENTION  
         [0002]    The present invention relates to a radial press with two press yokes and eight crimping members, where the press yokes are arranged in a plane that is perpendicular to the press axis, are located diametrically opposite one another relative to the press axis, and can be moved towards one another in a straight line by means of a drive unit, in a direction of movement that runs perpendicular to the press axis, and where furthermore six of the crimping members mounted in the press yokes have slide surfaces that interact with a control surface of a press yoke or an adjacent crimping member, in each instance, in such a way that all of the crimping members are uniformly moved toward the press axis when the two press yokes move closer to one another, and wherein two of said eight crimping members are diametrically opposed to one another on said first press yoke and said second press yoke in the direction of movement of said first press yoke and are in a stationary position with respect to said respective press yoke.  
         BACKGROUND OF THE INVENTION  
         [0003]    Such a radial press is known from the German Offenlegungsschrift [laying-open statement] 4135465. As compared with those radial presses in which the crimping members are controlled by means of at least one conical pressure ring that is moved parallel to the press axis (e.g. DE-OS 2844475), radial presses of the type indicated above are characterized by a relatively low construction depth (expanse in the direction of the press axis); this is a decisive advantage with regard to application possibilities of the press. However, known radial presses of the type indicated above require a relatively large construction volume, for which reason only stand presses have been implemented until now, in which large hydraulic cylinders are arranged in the stand housing. This also holds true for the radial press known from U.S. Pat. No. 4,785,656. Furthermore, at least in the radial press of the type indicated above, according to DE-OS 4135465, only axial loading and unloading of the press is possible. This results in that only small-sized fittings may be attached to hoses with that radial press.  
         SUMMARY OF THE INVENTION  
         [0004]    The task on which the present invention is based is derived from these facts, and consists of creating a radial press of the type stated initially, that allows to attach larger fittings to hoses. A further object is to provide for a radial press of the type stated initially that can be implemented as a tool of an industrial robot.  
           [0005]    This task is accomplished, according to the invention, in that those two crimping members which are arranged perpendicular to the direction of movement of said first press yoke are divided into two crimping member segments, each of said crimping member segments being slidably guided along said first control surface of the associated first and second press yoke respectively. This design allows to open the radial press such far that larger dimensions fittings may be loaded and unloaded axially. In addition, the structure of the radial press according to the invention makes other particularly preferred further developments possible, which, as will be explained below, demonstrate very significant advantages for practical work, as compared with the state of the art.  
           [0006]    In accordance with a preferred further development, both press yokes of the radial press according to the invention are movable with respect to the housing. In this manner, a radial press with a dual press stroke is obtained, without the construction size increasing too greatly. This is particularly advantageous if a radial loading opening is provided (see below). Furthermore, in such a radial press according to the invention, equipped with two movable press yokes, it is advantageous that the press axis is not displaced during the pressing process, if the press is structured symmetrically. This is advantageous, in particular if the press is used in connection with an industrial robot. However, it should be emphasized at this point that a radial press according to the invention, equipped with two movable press yokes, by no means necessarily has to be structured symmetrically. Instead, the drive units assigned to the two press yokes can certainly be structured differently. In this case, one press yoke could be used for fast adjustment of the crimping members, while the other press yoke could be used for a power adjustment of the crimping members.  
           [0007]    In accordance with the radial press according to the invention, the latter has a common housing in which the first press yoke is guided so as to be movable. If the radial press according to the invention has (only) one movable press yoke, it is practical if the other press yoke is mounted fixed in place in the housing. In connection with the extremely compact construction of the radial press as explained above, such a common housing results in a high degree of rigidity, so that even relatively small radial presses can work at high forces.  
           [0008]    The very compact structural design of the radial press according to the invention even makes it possible for the housing to have a radial loading opening on one side, in accordance with another preferred embodiment of the invention. Even the interruption in the (otherwise essentially closed) housing caused by such a radial loading opening on one side does not result in an impermissibly great reduction in rigidity of the radial press according to the invention, because of its extremely compact construction. However, the possibility of radial loading of the radial press is a very significant advantage, for practical work, as compared with those radial presses that can only be loaded axially, since in this way the radial press is also suitable for processing of work pieces that cannot be drawn through the die because of their complicated shape, for example if pressing is to be performed in the center of a hose. Also, the radial loading opening makes this further development of the radial press according to the invention particularly suitable for automated use, for example in that the radial press is arranged on the arm of an industrial robot, as a pressing die. Because of its radial loading opening, the radial press can be passed from the side over pre-installed work pieces, mounted in a suitable device. As compared with the state of the art, this allows a significant improvement in the efficiency of production, in that a plurality of work pieces is made available on a suitable device, for automatic processing with the radial press according to the invention. Axial loading, which was required until now, and can only be performed by hand, particularly in the case of soft pieces that bend easily, such as hoses or the like, can be eliminated when using a further development of the radial press according to the invention, with a radial loading opening as explained above.  
           [0009]    The radial loading opening on one side, as explained above, is arranged perpendicular to the direction of movement of the press yokes as they move towards one another and is adjacent to one of said two crimping members which is divided into two crimp member segments.  
           [0010]    Also with regard to as compact a construction of the radial press according to the invention as possible, another further development of the latter is characterized in that the at least one drive unit comprises a hydraulic piston that is guided in a segment of the housing structured as a hydraulic cylinder, forming a seal. For this purpose, the hydraulic piston can be wedge-shaped, in order to make a wedge gear mechanism available that acts to convert its movement into a movement of the press yoke in question. The result is an extreme degree of compactness of the radial press.  
           [0011]    The minimal dimensions of the radial press according to the invention, particularly its especially small construction height in the axial direction, make it possible that two or more radial presses can be arranged very closely next to each other. With a system of several radial presses of the type according to the invention, arranged in parallel, it is therefore possible to carry out even very closely adjacent pressing processes synchronously, which is a significant advantage for practical operations, because of the time that is gained. For this purpose, according to yet another further development of the invention, at least two radial presses according to the invention are mounted adjacent to each other on a common guide, at a distance along the press axis relative to each other, where the distance between the presses can be quickly adjusted, either manually or automatically, by means of a suitable structure of the guide. 
       
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS  
       [0012]    In the following, the present invention will be explained in greater detail, using two particularly preferred exemplary embodiments shown in the drawing. The drawing shows:  
         [0013]    [0013]FIG. 1 a longitudinal cross-section through a radial press with a cross slide, with the radial loading opening being open,  
         [0014]    [0014]FIG. 2 the radial press according to FIG. 1 during the closing process, with the radial loading opening already being closed,  
         [0015]    [0015]FIG. 3 the radial press according to FIG. 1 and  2  at the end of the pressing process, and  
         [0016]    [0016]FIG. 4 a longitudinal cross-section through a radial press according to the invention, with two cross slides. 
     
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS  
       [0017]    The radial press shown in FIG. 1 to  3  of the drawing comprises a housing  1  with an L-shaped footprint. The housing comprises a base element  2  and a two-part cover lid  3  that is screwed onto the former. In this connection, the housing essentially defines two cavities, namely a cube-shaped cavity  4  and a round, cylindrical cavity  5  that extends at a right angle to the former.  
         [0018]    Two press yokes  6  and  7  are contained in the cube-shaped cavity  4  of the housing  1 . In this connection, the lower press yoke  6  is rigidly connected with the housing by means of screws  8 . In contrast, the upper press yoke  7  is guided in the housing  1  so as to be movable, where the direction of movement of the two press yokes  6  and  7  relative to one another is indicated with the double arrow A.  
         [0019]    Eight crimping members, in total, are mounted in the two press yokes  6  and  7 . In this connection, each crimping member consists of a block member  11  to  16  and a replaceable crimp member replacement part  52 . The six block members  9 ,  10 ,  13 ,  14 ,  15 , and  16  are not divided, while, as will be explained in greater detail below, the block members  11  and  12  of two crimping members are each divided into two segments  11   a  and  11   b ,  12   a  and  12   b , respectively. A spiral spring  23  is arranged between every two adjacent block members, in a corresponding pocket, in each instance. The block member  9  is mounted fixed in place in the lower press yoke  6 , and the block member  10  is mounted fixed in place in the upper press yoke  7 . The block members  11  and  12  are divided, as briefly mentioned above, and comprise the segments  11   a  and  11   b ,  12   a  and  12   b , respectively. The block member segments  11   a  and  12   a  assigned to the upper press yoke  7  are guided so as to be movable along the support surfaces  17 , which enclose an angle of 45° with the direction A of movement. Analogously, the block member segments  11   b  and  12   b  assigned to the lower press yoke  6  are mounted so as to be movable along the support surfaces  18 . In this connection, guide elements  19  are provided to guide the block member segments  11   a ,  11   b ,  12   a , and  12   b , and these are connected with the upper press yoke  7  and the lower press yoke  6  by means of a screw  20 , in each instance. In this connection, the guide elements  19  and the related block member segments engage with each other via a T guide; in addition to guiding the block member segments, the guide elements  19  limit the sliding movement of the block member segments on the support surfaces  17  and  18 , respectively, in the maximum open position shown in FIG. 1. In this connection, the block member segments  11   a  and  12   a  assigned to the upper press yoke  7  are each guided by two guide elements  19 , which are arranged at a distance from one another in such a way that the guide elements  19  that serve to guide the block member segments  11   b  and  12   b  assigned to the lower press yoke  6  can each penetrate into the space between two opposite guide elements when the press is closed (FIG. 3).  
         [0020]    The block members  13  to  16  are each guided on a support surface  21  of the upper press yoke  7  and lower press yoke  6 , and, on the other hand, on a support surface  22  of the adjacent block member segment  11   a ,  11   b ,  12   a , or  12   b.    
         [0021]    The division of the block members  11  and  12  into the block member segments  11   a  and  12   a , assigned to the upper press yoke  7 , on the one hand, and the block member segments  11   b  and  12   b , assigned to the lower press yoke  6 , on the other hand, is related to the radial loading opening  24  provided on one side of the housing  1 . This opening is defined, in each instance, by a recess  26  provided in the side walls  25  that define the cube-shaped cavity  4  of the housing, and a perforation  27  of the cover lid  3 . When the press is open (FIG. 1), a work piece to be processed can be placed into the press through the radial loading opening  24 . When the press is closed (FIG. 2), the block member segments  11   a  and  11   b , as well as  12   a  and  12   b , come together to form a block member, in each instance. In this connection, an adjustment projection  28  of the block member segments  11   a  and  12   a , in each instance, enters into a corresponding adjustment recess  29  of the block member segments  11   b  and  12   b ; in this manner, the block member segments that are assigned to one another are precisely aligned relative to one another when the press is closed.  
         [0022]    The drive unit  30  of the radial press comprises a cross slide  31  that is guided to be movable within the round, cylindrical cavity  5 . In this connection, the direction B of movement of the cross slide  31  is perpendicular to the direction A of movement of the upper press yoke  7 . A deflection device  32 , structured as a wedge gear mechanism, serves to transfer the movement of the cross slide  31  into a movement of the upper press yoke  7 . The wedge gear mechanism comprises a slanted guide  33  in the form of a T profile, and a corresponding slanted guide  34  of the upper press yoke  7  that is in engagement with the slanted guide  33  of the cross slide  31 .  
         [0023]    The cross slide  31  is structured as a hydraulic piston that is sealed with ring seals  35  relative to the inside wall of the round, cylindrical cavity  5  of the housing  1 . A hydraulic work space  36 , which is defined by the cross slide lid  37 , the housing lid  38 , the piston rod  39 , and the cylindrical segment  40  of the housing  1 , serves as the power drive for the cross slide  31 . A connection bore  41  opens into the hydraulic work space  36 ; the hydraulic work space  36  can be connected with a source for a pressure medium via this bore.  
         [0024]    The cross slide  31  has a longitudinal bore  42 . The sealing head  43  of the piston rod  39  is guided in this bore, forming a seal. In this connection, the seal is formed by means of two ring seals  44 . The sealing head  43  divides the longitudinal bore  42  of the cross slide into two hydraulic work spaces, namely an advancing work space  45  and a retraction work space  46 . In this connection, the latter is defined by the inside wall of the longitudinal bore  42 , the outside wall of the piston rod  39 , the sealing head  43 , and the cross slide lid  37 . In this connection, the two hydraulic work spaces  45  and  46  are components of a so-called fast drive, with which the cross slide  31  can be moved to quickly close and open the press at a relatively high speed. For this purpose, the piston rod  39  has two hydraulic channels  47  and  48 . In this connection, the hydraulic channel  47  is connected with the hydraulic work space  45 , and the hydraulic channel  48  is connected with the hydraulic work space  46 . The two hydraulic channels  47  and  48  can be connected with a source for a pressure medium via connection nipples  49  and  50 .  
         [0025]    If the completely open press (FIG. 1), with the radial loading opening  24  fully exposed, is closed by moving the cross slide  31 , the position of the block members  9  to  16  remains unchanged, relative to the related press yoke  6  or  7 , until the block member segments  11   a  and  11   b , as well as  12   a  and  12   b , come together (FIG. 2). If the two press yokes  6  and  7  are moved further towards one another, this results in a uniform movement of all the crimping members (block members plus crimping member replacement parts), as known from the state of the art, in the direction of the press axis, where the block members  11  to  16  slide on the related support surfaces of the press yoke in question, or on an adjacent block member, with their slide surfaces, in each instance.  
         [0026]    The radial press according to FIG. 4 differs from the radial press shown in FIGS.  1  to  3  and explained above primarily in that two cross slides  53  are provided. Both cross slides  53  are each guided so as to be movable in a cylindrical segment  40  of the housing  1  (double arrow B). Analogously, both press yokes  54  are also guided so as to be movable in the housing  1  (double arrow A).  
         [0027]    Analogous to the deflection device  32  implemented in the radial press according to FIGS.  1  to  3 , a wedge gear mechanism is provided as the deflection device  32 , in each instance, also in the case of the radial press according to FIG. 4. This mechanism is structured as a forced coupling of the cross slide  53  in question with the related press yoke  54 , in each instance, in that the slanted guides  33  and  34  of the cross slide  53  and the press yoke  54  are structured in T shape and are in engagement with each other. In the exemplary embodiment shown in FIG. 4, the wedge angles of the two wedge gear mechanisms are identical, so that the two press yokes  54  are moved towards one another at the same speed when there is a synchronous movement of the two cross slides  53 , so that the press axis  51  does not shift as the press is closed (or opened).  
         [0028]    Furthermore, the radial press according to FIG. 4 differs significantly from the one according to FIGS.  1  to  3  in terms of the structure of the cross slide  53 , particularly in connection with the fast drive. Here, each cross slide  53  has two longitudinal bores  55  that are directed in opposite directions from one another and offset relative to one another, each of them structured as a dead-end bore. A piston rod  56  is guided in each longitudinal bore  55 , forming a seal, where the seal is formed by means of a ring seal  57 . Of the two piston rods  56  assigned to each cross slide  53 , one is rigidly connected with the cover lid  3 , which again is in two parts, and the other is rigidly connected with a housing lid  38  that closes off the cylindrical segment  40  of the housing  1  in question. Each of the two piston rods  56  has a hydraulic channel  58  passing through it, which opens into the hydraulic work space formed by the related longitudinal bore  55 . Both hydraulic channels  58  can be connected with a source for a pressure medium, not shown, via a connection nipple  59 , in each instance. As compared with the version of the fast drive implemented in the radial press according to FIGS.  1  to  3 , the version shown in FIG. 4 has the advantage of a spatial separation of the fast drive for opening the press, on the one hand, and the fast drive for closing the press, on the other hand. For power pressing, the same high pressure can be applied to the work space  36  that acts on the face of the cross slide  53 , which space is provided exclusively for the power drive, and into which the connection bore  41  opens, as well as to the hydraulic work space provided for the fast drive in the closing direction, without any risk that hydraulic fluid can penetrate into the hydraulic work space that is assigned to the fast drive for opening the press, to which no pressure is applied during pressing. With this background, in connection with sealing the cross slide  53  relative to the piston rods  56 , significantly less effort is required than in the case of the design according to FIGS.  1  to  3 . Also, differing from the cross slide  31  of the radial press according to FIG. 1 to  3 , the cross slide  53  itself can be structured in one piece.  
         [0029]    Aside from the fact that in the radial press according to FIG. 4, the removable crimping member replacement parts  52  (see FIG. 1 to  3 ) are not shown, there is no basic deviation of the radial press according to FIG. 4 from the one according to FIGS.  1  to  3 , other than the differences explained above. This particularly holds true for the division of the block members  11  and  12  into two segments  11   a  and  11   b ,  12   a  and  12   b , respectively, which is provided in connection with the radial loading opening  24 . To avoid repetition, reference is therefore made to the explanations for FIGS.  1  to  3 .  
         [0030]    At this point, it is noted once again that the radial presses shown in the drawings are merely exemplary, particularly preferred embodiments of the invention. It is evident that comprehensive modifications are possible within the scope of the present invention. For example, the at least one cross slide can be moved by means of a spindle driven by an electric motor, instead of by means of a hydraulic drive. Also, for example, an articulated lever gear mechanism or an eccenter can convert the movement of the at least one cross slide into a movement of the related press yoke, instead of the wedge gear mechanism. Furthermore, in application cases where radial loading of the radial press is not required, the loading opening can be eliminated, and in this case, a division of the corresponding crimping members is obviously not required. Finally, it is optional, within the scope of the present invention, whether the crimping members are made in one piece or, as explained above, comprise a block member and a replaceable crimping member replacement part, in each instance.