Abstract:
A locking tool or device that permits rapid installation and removal of a removable component from a component that is fixed to a housing or equipment. The interchangeable, and hence removable, components may be held in place by individual holders that provide secure axial locking means and quick radial removal means requiring no axial space for the removal of such components from the main base tool.

Description:
CROSS-REFERENCE TO RELATED APPLICATION 
     This application claims priority to provisional application Ser. No. 61/015,915, filed on Dec. 21, 2007, the entire contents of which are hereby expressly incorporated by reference for all purposes. 
    
    
     BACKGROUND 
     The orthopedic and laboratory industries, among others, use various tools to perform different functions such as drilling, reaming, scraping, filing, etc. Quick tool interchangeability and very little play between mating tool parts are important considerations in such industries and wherever quick-change connectors are used. At present, different tools can be quickly interchanged by manually removing and replacing a desired interchangeable component of the main base tool, which can universally attach to a variety of interchangeable components by means of a universal clamp or chuck. An example tool utilizing a quick-change connector is a drill where numerous rotary attachments such as reaming or burring attachments can be interchanged by axial removal and insertion. 
     The present embodiments simplify the method of assembling such tools by providing a rapid means for installing and removing such components. Interchangeable components being incorporated are held in place by individual holders that provide secure axial locking means and quick radial removal means requiring no axial, space for the removal of such components from the main base tool. In a typical orthopedic application, for example, interchangeable component holders may be installed in a stationary drill press or a portable drill, depending on the application. The holder is permanently secured to the drilling machine and the interchangeable component can be axially or radially installed, axially locked upon installation but radially removable. In the assembled position, the holder provides circumferential concentricity and the component is axially locked. 
     The axial locking means may comprise, for example, an axially mounted canted-coil spring, in either the stationary or the rotary portion of the holder combination. In some embodiments, a sleeve restricts radial movement and a non-cylindrical tongue of the interchangeable component and corresponding slot in the holder may allow rotational movement to be transferred between the component and holder. A combination of factors contributes to axial locking motion. The combination may include one or more of:
         The groove width is smaller than the coil height so that an interference occurs at assembly between the coil height and the groove width. The interference may range from no interference to approximately 25%, but is preferably between about 5-10% of the coil height so that the spring is firmly retained in the cavity, while at the same time allowing deflection of the spring along the minor axis during locking.   Interference between the groove height and the coil width along the major axis to reduce or prevent radial movement of the components. Such variation may range from no interference to approximately 15%, but more preferably is under 10%, such as less than 5%.   Deflection of the spring coils during assembly to achieve locking. The deflection may range from about 1% to the maximum safe deflection of the coil. The maximum safe deflection may be about 15-25% deflection along the minor axis, but not exceeding the safe deflection, that can cause permanent deformation of the spring&#39;s coils.   Tapered locking angle at the bottom of the groove. The taper may range from zero up to about 30%, but is preferably from approximately 5% to approximately 15% to provide a gradual locking action without achieving permanent deformation of the coil.       

     Aspects of the present embodiments include a number of different “rotary locking mechanisms with quick radial disassembly means.” with each providing certain useful advantages. The embodiments are configured as providing locking between a housing and a piston. In actual application of the embodiments as a mechanism for interchangeable tools, the holder and the interchangeable component(s) can correspond to either the piston and housing or housing and piston respectively in reference to the figures of the designs. Those of ordinary skill in the art will appreciate that the embodiments may be practiced other than as specifically described, and should not be limited to the embodiments described herein. 
     SUMMARY 
     The various embodiments of the present locking mechanism with quick disassembly means have several features, no single one of which is solely responsible for their desirable attributes. Without limiting the scope of the present embodiments as expressed by the claims that follow, their more prominent features now will be discussed briefly. 
     One embodiment of the present locking mechanism for use in quick-release applications comprises a housing including a longitudinal axis. A first end portion of the housing includes first and second furcations defining a slot therebetween. An inner surface of the first furcation includes a first groove therein. The locking mechanism further comprises a piston including a body section. A first end of the body section defines first and second shoulders. A tongue extends away from the shoulders along the longitudinal axis. A surface of the tongue includes a second groove therein. The locking mechanism further comprises a sleeve slidably engaging an outer surface of the piston body section. The locking mechanism further comprises a canted-coil spring. The locking mechanism further comprises a first configuration in which the tongue is disposed within the slot such that the furcations abut the shoulders and the first and second grooves are aligned, the canted-coil spring is disposed within the first and second grooves and is compressed by the first and second grooves, and the sleeve is positioned over at least a portion of a junction between the housing and the piston such that the sleeve engages the outer surface of the piston body section and outer surfaces of the furcations, thereby resisting relative motion of the housing and the piston in a direction perpendicular to the longitudinal axis. 
     Another embodiment of the present locking mechanism for use in quick-release applications comprises a housing including a longitudinal axis. A first end portion of the housing includes first and second furcations defining a slot therebetween. An inner surface of the first furcation includes a first groove therein. An inner surface of the second furcation includes a second groove therein. The locking mechanism further comprises a piston including a body section. A first end of the body section defines first and second shoulders. A tongue extends away from the shoulders along the longitudinal axis. A surface of the tongue includes a continuous perimeter groove therein. The locking mechanism further comprises a sleeve slidably engaging an outer surface of the piston body section. The locking mechanism further comprises a canted-coil spring disposed within the continuous perimeter groove. The locking mechanism further comprises a first configuration in which the tongue is disposed within the slot such that the furcations abut the shoulders and the continuous perimeter groove is aligned with the first and second grooves, the canted-coil spring is disposed within the first and second grooves and is compressed by the first and second grooves, and the sleeve is positioned over at least a portion of a junction between the housing and the piston such that the sleeve engages the outer surface of the piston body section and outer surfaces of the furcations, thereby preventing relative motion of the housing and the piston in a direction perpendicular to the longitudinal axis. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The various embodiments of the present locking mechanism now will be discussed in detail with an emphasis on highlighting the advantageous features. These embodiments depict the novel and non-obvious locking mechanism shown in the accompanying drawings, which are for illustrative purposes only. These drawings include the following figures, in which like numerals indicate like parts: 
         FIG. 1A  is a cross-sectional front elevation view of one embodiment of a housing portion of the present locking mechanism; 
         FIG. 1B  is a cross-sectional front elevation view of one embodiment of a piston portion of the present locking mechanism; 
         FIG. 1C  is a cross-sectional front elevation view of the housing portion and the piston portion of  FIGS. 1A and 1B  in an assembled configuration; 
         FIG. 1D  is a top plan view of the housing portion and the piston portion of  FIGS. 1A and 1B  in a partially disassembled configuration; 
         FIG. 1E  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIGS. 1A and 1B  taken through the line E-E in  FIG. 1C ; 
         FIG. 1F  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIGS. 1A and 1B  taken through the line F-F in  FIG. 1D : 
         FIG. 1G  is a detail view of the portion of  FIG. 1C  indicated by the circle G; 
         FIG. 1H  is a cross-sectional top plan view of the housing portion and the piston portion of  FIGS. 1A and 1B  taken through the line H-H in  FIGS. 1A and 1B : 
         FIG. 1J  is a cross-sectional front elevation view of the housing portion and the piston portion of  FIGS. 1A and 1B  in an assembled configuration and including an alternative embodiment of the sleeve portion; 
         FIG. 1K  is a cross-sectional front elevation view of the housing portion and the piston portion of  FIGS. 1A and 1B  in an assembled configuration and including an alternative embodiment of the sleeve portion; 
         FIG. 1L  is a detail view of the portion of  FIG. 1J  indicated by the circle L: 
         FIG. 1M  is a front elevation view of the axially-canted-coil spring  FIG. 1A : 
         FIG. 1N  is a front elevation view of the radially-canted-coil spring  FIG. 1A : 
         FIG. 2A  is a cross-sectional front elevation view of another embodiment of the present locking mechanism in an assembled configuration: 
         FIG. 2B  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 2A  taken through the line B-B in  FIG. 2A ; 
         FIG. 2C  is a cross-sectional front elevation view of the locking mechanism of  FIG. 2A  in an improperly assembled configuration: 
         FIG. 3A  is a cross-sectional front elevation view of another embodiment of the present locking mechanism in an assembled configuration: 
         FIG. 3B  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 3A  taken through the line B-B in  FIG. 3A : 
         FIG. 3C  is a detail view of the portion of  FIG. 3A  indicated by the circle C; 
         FIG. 3D  is a detail cross-sectional bottom plan view of an axial spring portion of  FIG. 3A , taken through the line D-D in  FIG. 3A ; 
         FIG. 3E  is a detail cross-sectional bottom plan view of an axial spring portion of  FIG. 3A , taken through the line E-E in  FIG. 3A ; 
         FIG. 4  is a cross-sectional front elevation view of another embodiment of the present locking mechanism in an assembled configuration; 
         FIG. 5A  is a cross-sectional front elevation view of another embodiment of the present locking mechanism in an assembled configuration: 
         FIG. 5B  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 5A  taken through the line B-B in  FIG. 5A : 
         FIG. 5C  is a detail view of the portion of  FIG. 5A  indicated by the circle C; 
         FIG. 5D  is a detail view of the portion of  FIG. 5A  indicated by the circle D; 
         FIG. 6A  is a cross-sectional front elevation view of another embodiment of the present locking mechanism in an assembled configuration: 
         FIG. 6B  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 6A  taken through the line B-B in  FIG. 6A ; 
         FIG. 6C  is a detail view of the portion of  FIG. 6A  indicated by the circle C: 
         FIG. 6D  is a detail view of the portion of  FIG. 6A  indicated by the circle D: 
         FIG. 7A  is a cross-sectional front elevation view of another embodiment of the present locking mechanism in an assembled configuration; 
         FIG. 7B  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 7A  taken through the line B-B in  FIG. 7A ; 
         FIG. 7C  is a front elevation view of the axially-canted-coil spring of  FIG. 7A : 
         FIG. 8A  is a cross-sectional front elevation view of another embodiment of the present locking mechanism in an assembled configuration: 
         FIG. 8B  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 8A  taken through the line B-B in  FIG. 8A ; 
         FIG. 9A  is a cross-sectional front elevation view of another embodiment of the present locking mechanism in an assembled configuration: 
         FIG. 9B  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 9A  taken through the line B-B in  FIG. 9A ; 
         FIG. 10  is a front perspective view another embodiment of the present locking mechanism in an assembled configuration; 
         FIG. 10A  is a cross-sectional front elevation view of die housing portion of the locking mechanism of  FIG. 10 ; 
         FIG. 10B  is a cross-sectional front elevation view of the piston portion of the locking mechanism of  FIG. 10 ; 
         FIG. 10C  is a cross-sectional front elevation view of the housing portion and the piston portion of  FIGS. 10A and 10B  in a partially assembled configuration; 
         FIG. 10D  is a cross-sectional front elevation view of the housing portion and the piston portion of  FIGS. 10A and 10B  in a fully assembled, configuration; 
         FIG. 10E  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 10D  taken through the line E-E in  FIG. 10D ; 
         FIG. 10F  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 10C  taken through the line F-F in  FIG. 10C ; 
         FIG. 10G  is a detail view of the portion of  FIG. 10D  indicated by the circle G; 
         FIG. 11  is a front perspective view another embodiment of the present locking mechanism in an assembled configuration; 
         FIG. 11A  is a cross-sectional front elevation view of the housing portion of the locking mechanism of  FIG. 11 ; 
         FIG. 11B  is a cross-sectional front elevation view of the piston portion of the locking mechanism of  FIG. 11 ; 
         FIG. 11C  is a cross-sectional front elevation view of the housing portion and the piston portion of  FIGS. 11A and 11B  in a partially assembled configuration; 
         FIG. 11D  is a cross-sectional front elevation view of the housing portion and the piston portion of  FIGS. 11A and 11B  in a fully assembled configuration; 
         FIG. 11E  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 11D  taken through the line E-E in  FIG. 11D ; 
         FIG. 11F  is a cross-sectional left side elevation view of the housing portion and the piston portion of  FIG. 11C  taken through the line F-F in  FIG. 11C ; and 
         FIG. 11G  is a detail view of the portion of  FIG. 11D  indicated by the circle G. 
     
    
    
     DETAILED DESCRIPTION 
     The detailed description set forth below in connection with the appended drawings is intended as a description of the presently preferred embodiments of a simple release locking mechanism and is not intended to represent the only forms in which the present embodiments may be constructed or used. The description sets forth the features and the steps for constructing and using the simple release locking mechanism of the present embodiments. It is to be understood, however, that the same or equivalent functions and structures may be accomplished by different embodiments that are also intended to be encompassed within the spirit and scope of the embodiments. As denoted elsewhere herein, like element numbers are intended to indicate like or similar elements or features. 
     Unless specifically noted, it is intended that the words and phrases in the specification and the claims be given their ordinary and accustomed meaning to those of ordinary skill in the applicable arts. If any other special meaning is intended for any word or phrase, the specification will clearly state and define the special meaning. In particular, most words have a generic meaning. If it is intended to limit or otherwise narrow the generic meaning, specific descriptive adjectives will be used to do so. Absent the use of special adjectives, it is intended that the terms in this specification and claims be given their broadest possible, generic meaning. For example, unless the context indicates otherwise, a canted-coil spring can be either an axial or a radial canted-coil spring. It can also be a hybrid, with characteristics of both axial and radial springs. It can also have different configurations, such as round, oval, square, etc. 
     The illustrated embodiments of the present locking mechanism discussed herein include canted coil springs. In certain embodiments the coil springs may be radially canted, while in certain other embodiments the coil springs may be axially canted. In still further embodiments the coil springs may be both radially canted and axially canted. Canted coil springs are described in detail in U.S. Pat. Nos. 4,655,462; 4,826,144; 4,876,781; 4,907,788; 4,915,366; 4,964,204; 5,139,243; 5,160,122; 5,503,375; 5,615,870; 5,709,371; 5,791,638; and 7,055,812. The contents of each of the foregoing patents are hereby incorporated by reference herein. 
       FIGS. 1A-1H  and  1 J- 1 M illustrate one embodiment of the present locking mechanism  100 . With reference to  FIGS. 1A and 1B , the locking mechanism  100  includes a generally cylindrical housing  101  having a longitudinal axis  103 . The housing  101  comprises a first furcation  102  and a second furcation  104  in a first end portion. The first and second furcations  102 ,  104  define a slot  106  therebetween. The slot  106  is an open space that is shaped substantially as a rectangular parallelepiped, being bounded along three faces by the housing  101  and the furcations  102 ,  104 , and being open along the remaining three faces. Those of ordinary skill in the art will appreciate that in alternative embodiments the slot  106  may have other configurations. With reference to  FIGS. 1A and 1H , an inner surface  107  of the first furcation  102  includes a taper bottom groove  108  that retains a linear axially-canted-coil spring  110 . The spring length runs perpendicular to the longitudinal axis  103 . The linear canted-coil spring  110  is illustrated in further detail in  FIG. 1M . In other embodiments, the tapered bottom groove may be located on the second furcation  104 . 
     The locking mechanism  100  further includes a generally cylindrical piston  112  configured to assemble in-line with the housing  101 . The piston  112  includes a body section  114  and a longitudinal axis  103 . A piston tongue  116  extends away from the body section  114 , defining first and second shoulders  118  to either side of the tongue  116 . In the illustrated embodiment, the tongue  116  is shaped substantially as a rectangular parallelepiped. However, with reference to  FIG. 1E , two opposite faces of the tongue  116  are convex so that when the tongue  116  is disposed in the slot  106  an outer surface of the slot  106 /tongue  116  junction is substantially cylindrical. Those of ordinary skill in the art will appreciate that in alternative embodiments the tongue  116  may have other shapes. 
     With reference to  FIGS. 1A and 1B , a first face  120  of the tongue  116  includes a flat bottomed groove  122 . The groove  122  receives the linear canted-coil spring  110  when the locking mechanism  100  is in the assembled configuration of  FIG. 1C . The groove  122  contributes to the locking action in the locking mechanism  100 , as explained in further detail below. 
     With continued reference to  FIGS. 1A and 1B , the outer surface  124  of the piston  112  includes a circumferential groove  126 . The circumferential groove  126  receives a circular or garter radially-canted-coil spring  128 . The circular radially-canted-coil spring  128  is illustrated in greater detail in  FIG. 1N . 
     In one embodiment, the circular canted-coil spring  128  may be secured inside the circumferential groove  126  by controlling a spring squeeze between the groove  126  and the spring  128 . In alternative embodiments, or in the event the spring  128  does not have enough squeeze, the ends of the groove  126  could be pinned or staked such as to cap the channel of the groove to retain the spring  128  therein. 
     A generally cylindrical sleeve  130  is mounted over the outer surface  124  of the piston  112 . The sleeve  130  is slidable along the outer surface  124  between the retracted position, of  FIG. 1B  and the closed position of  1 C. In the retracted position the sleeve  130  is spaced apart from the circular canted-coil spring  128  on a side of the spring  128  opposite the tongue  116 . In the closed position the sleeve  130  covers the spring  128  to retain the housing  101  and the piston  112  in the assembled configuration, as described in further detail below. 
     To assemble the illustrated locking mechanism  100 , the tongue  116  is inserted into the slot  106  as illustrated in  FIG. 1C . The tongue  116  may be inserted into the slot  106  by relative axial movement of the housing  101  and the piston  112 , as shown by the arrow  132  in  FIGS. 1A ,  1 B and  1 H. The tongue  116  is inserted into the slot  106  until the ends of the furcations  102 ,  104  contact the shoulders  118 . In this configuration the groove  122  in the tongue  116  at least partially aligns with the groove  108  in the inner surface  107  of the first furcation  102 . The linear canted-coil spring  110  is thus compressed between the two grooves  108 ,  122  as shown in the detail view of  FIG. 1G . The compressed spring  110  provides locking action that prevents the axial separation of the housing  101  and the piston  112 , as described in further detail, below. 
       FIG. 1G  shows the manner in which the axial locking occurs. First, the groove width (G.W.) is smaller than the coil height (C.H.). Second, a base  134  of the groove  108  is tapered such that a depth of the groove increases with increasing distance from a second end portion  136  ( FIG. 1C ) of the housing  101 . The taper bottom groove  108  facilitates the counter-clockwise rotation of the linear canted-coil spring  110  as the tongue  116  is inserted axially into the slot  106 . Further the relative dimensions of groove width and coil height in combination with the taper bottom groove also retards the reverse rotation of the coil spring  110  as the tongue  116  is withdrawn axially from the slot  106 , as occurs when a tensile force is applied to the locking mechanism  100 . Consequently, a greater force is required to remove the tongue  116  axially from the slot  106  than is required to insert the tongue  116  axially into the slot  106 . The magnitude of the difference between the insertion force and the removal, force can be adjusted by adjusting the relative dimensions of groove width and coil height and the angle  144  of the taper bottom groove  108 . In certain embodiments the angle  144  of the taper bottom groove  108  may be tapered to produce a spring in a convex initial position. In other embodiments, the angle produces a spring in a concave initial position. In still other embodiments the magnitude of the removal force may be so great that the tongue  116  cannot be removed axially from the slot  106  without destroying the spring  110 . These concepts are described in detail in U.S. Pat. Nos. 4,678,210; 5,082,390; 5,411,348; 5,545,842; 6,749,358; 6,835,084; 7,055,812, 7,070,455 and 7,195,523, all of which are incorporated herein by reference. 
     To complete the assembly of the locking mechanism, the sleeve  130  is slid along the piston  112  from the retracted position of  FIG. 1B  to the closed position of  1 C. In the closed position an end  138  of the sleeve  130  abuts a shoulder  140  on the housing  101  to prevent further movement of the sleeve  130  toward the housing  101 . In the closed position the sleeve  130  covers the spring  128  and compresses the spring  128  into the circumferential groove  126 , Friction between the spring  128  and the sleeve  130  thus resists sliding movement of the sleeve  130  away from the housing  101 . The inner surface of the sleeve  130 , however, is smooth. Thus, the sleeve  130  is not locked against sliding movement relative to the piston  112 . Rather, sliding movement relative to the piston  112  is merely retarded by the friction between the spring  128  and the sleeve  130 . In the closed position the sleeve  130  also covers the junction between the tongue  116  and the slot  106 . In inner surface of the sleeve  130  contacts the outer surfaces of the furcations  102 ,  104  and the tongue  116 , as illustrated in the cross-sectional view of  FIG. 1E . The sleeve  130  thus prevents relative movement of the housing  101  and the piston  112  in a direction perpendicular to the longitudinal axis  103 . In the assembled configuration, the housing  101  and the piston  112  are thus locked because they cannot be separated from one another in either the axial direction (parallel to the longitudinal axis  103 ) or the radial direction (perpendicular to the longitudinal axis  103 ). 
     With reference to  FIGS. 1A ,  1 B,  1 C and  1 G, it is possible to insert the tongue  116  into the slot  106  in a configuration in which the piston  112  is rotated 180° about its longitudinal axis from the configuration shown in  FIG. 1C . In this reversed configuration, locking action may not occur between the housing  101  and the piston  112  because the groove  122  in the tongue  116  would not align with the groove  108  in the slot  106 . Therefore, in order to ensure locking action the piston  112  is preferably inserted into the housing  101  in the orientation shown in  FIGS. 1A-1C  in which the grooves  108 ,  122  line up. In one example embodiment, a longitudinally aligned combination tongue-and-group is incorporated for alignment purposes, which would run parallel to but offset from the longitudinal axis of the piston, instead of the current orthogonal configuration to the longitudinal axis of the piston. In alternative embodiments, external markers may be provided as alignment indicia. 
       FIGS. 1D and 1F  illustrate a method of disassembling the housing  101  and the piston.  112  from one another. The reader will note that the cross-sectional view of  FIG. 1F  is taken through the line F-F in  FIG. 1D , but  FIG. 1F  has been rotated 90° counter-clockwise from the orientation shown in  FIG. 1D . To disassemble the housing  101  and the piston  112  from, one another, first the sleeve  130  is slid along the piston  112  from the closed position ( FIG. 1C ) to the retracted position ( FIG. 1D ). Next, the housing  101  and the piston  112  are moved relative to one another in the radial direction (perpendicular to the longitudinal axis  103 , as indicated by the arrows  142  in  FIGS. 1D and 1F ). The compressed linear spring  110  resists, but does not prevent, relative sliding movement of the housing  101  and the piston  112 . These components can thus be separated from one another by relative radial movement once the locking sleeve  130  is moved to the retracted position. 
       FIGS. 1J ,  1 K, and  1 L illustrate alternate configurations for the present locking mechanism  146 ,  148 . With reference to  FIGS. 1J and 1L , in the illustrated embodiment  146  the sleeve  150  includes a circumferential groove  152  on its inner surface. When the sleeve  150  is slid to the locked position ( FIG. 1J ), the groove  152  at least partially aligns with a circumferential taper bottom groove  154  in the piston  156 . The groove  152  thus receives an axially canted-coil spring  158  and compresses the axially canted-coil spring  158  between the groove  152  and the groove  154 . The compressed spring  158  resists, but does not prevent the sleeve  150  from sliding away from the housing  101  and out of the locked position. In contrast to the taper bottom groove  108  illustrated in  FIG. 1G , the taper bottom groove  154  tapers in the opposite direction. Thus, as the sleeve  150  slides to the right relative to the piston  156  in  FIG. 1L , the sleeve  150  moves across the groove  154  from its deep end  160  toward its shallow end  162 . There is thus room for the spring  158  to rotate clockwise under the influence of friction from the groove  152  and the inner surface of the sleeve  150 . 
       FIG. 1K  illustrates another embodiment  148  in which the piston  164  does not include a circumferential groove retaining a circular coil spring. Instead, the piston  164  includes an end portion  166  having an enlarged outer diameter. The sleeve  168  includes an annular shoulder  170  formed at a junction between a first inner diameter portion  172  and a second inner diameter portion  174 . A coil spring  176  (or similar resilient member) is held in compression between the enlarged end portion  166  and the annular shoulder  170 . The compressive force in the spring  176  holds the sleeve  168  in the closed position in which it covers the junction between the furcations  102 ,  104  and the tongue  116 . An operator may squeeze the sleeve  168  with his hand (or with a tool) to slide the sleeve  168  along the piston  164  toward the enlarged end portion  166  until it no longer covers the junction between the furcations  102 ,  104  and the tongue  116 . With the sleeve  168  no longer covering the junction, the housing  101  and piston  164  may be separated by relative movement in the radial direction (perpendicular to the longitudinal axis  103 ). 
       FIGS. 2A-2C  illustrate another embodiment of the present locking mechanism  200 . The locking mechanism  200  includes many of the same features described above with respect to the locking mechanism  100  illustrated in  FIGS. 1A-1H  and  1 J- 1 M. Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIG. 2A , in the locking mechanism  200  the tongue  202  of the piston  204  is offset from the longitudinal axis  103 . The slot  206  of the housing  208  is similarly offset from the longitudinal axis  103 . The offset of the tongue  202  and the slot  206  contribute to proper alignment of the housing  208  and the piston  204 . If the housing  208  and the piston  204  are misaligned, as shown in  FIG. 1C , the misalignment will be obvious to the operator. 
     In the locking mechanism  200  the sleeve  210  includes an enlarged end portion  212  spaced from the housing  208 . The enlarged end portion  212  provides a bearing surface  214  for the operator&#39;s hand or a tool, facilitating the sliding movement of the sleeve  210  aware from the closed position of  FIG. 2A . 
       FIGS. 3A-3E  illustrate another embodiment of the present locking mechanism  300 . The locking mechanism  300  includes many of the same features described above with respect to the locking mechanisms  100 ,  200  illustrated in  FIGS. 1A-1H ,  1 J- 1 M and  2 A- 2 C. Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIGS. 3A-3D , in the locking mechanism  300  a first surface  301  the tongue  302  of the piston  304  includes a taper bottom groove  306  chat retains a linear axially-canted-coil spring  308 . A first surface  310  of the first furcation  312  of the housing  314  includes a flat bottomed groove  316 . Accordingly, with reference to  FIGS. 1G and 3C  the configuration of the grooves  306 ,  316  in the locking mechanism  300  is the reverse of the configuration of the grooves  108 ,  122  in the locking mechanism  100 . However, the function of the grooves  306 ,  316  is identical to the function of the grooves  108 ,  122 , which is described in detail above and will not be repeated here. With reference to  FIGS. 3D and 3E , the taper bottom groove  306  may extend perpendicular to the longitudinal axis  103  ( FIG. 3D ), or it may lie at a non-perpendicular to the longitudinal axis  103  ( FIG. 3E ). The linear canted-coil spring  308  assumes the same angle to the longitudinal axis  103  as the groove  306 . Those of ordinary skill in the art will appreciate that the illustrated angles for the taper bottom groove  306  and linear canted-coil spring  308  are applicable to all of the present embodiments, regardless of whether they are specifically discussed with respect to any particular embodiment. 
       FIG. 4  illustrates another embodiment of the present locking mechanism  400 . The locking mechanism  400  includes many of the same features described above with respect to the locking mechanisms  100 ,  200 ,  300  illustrated in  FIGS. 1A-1H ,  1 J- 1 M,  2 A- 2 C and  3 A- 3 E. Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIG. 4 , in the locking mechanism  400  the tongue  402  of the piston  404  includes a step defined by a first portion  406  having a relatively shorter length and a second portion  408  having a relatively longer length. The slot  410  in the housing  412  similarly includes a step defined by a first portion  414  having a relatively lesser depth and a second portion  416  having a relatively greater depth. The steps contribute to proper alignment of the housing  412  and the piston  404 . The tongue  402  may only be inserted completely within the slot  410  when the tongue first portion  406  is aligned with the slot first portion  414  and the tongue second portion  408  is aligned with the slot second portion  416 . If the housing  412  and the piston  404  are misaligned, the misalignment will be obvious to the operator. 
       FIGS. 5A-5D  illustrate another embodiment of the present locking mechanism  500 . The locking mechanism  500  includes many of the same features described above with respect to the locking mechanisms  100 ,  200 ,  300 ,  400  illustrated in  FIGS. 1A-1H ,  1 J- 1 M,  2 A- 2 C,  3 A- 3 E and  4 . Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIGS. 5A ,  5 B and  5 D, in the locking mechanism  500  a first surface  502  of the first furcation  504  of the housing  506  includes a taper bottom groove  508  that retains a linear axially-canted-coil spring  510 . A first surface  512  of the tongue  514  of the piston  516  includes a flat bottomed groove  518 . With reference to  FIGS. 5A-5C , in the locking mechanism  500  a first surface  520  of the second furcation  522  of the housing  506  includes a taper bottom, groove  524  that retains a linear canted-coil spring  510 . A second surface  526  of the tongue  514  of the piston  516  includes a flat bottomed groove  528 . The function of the grooves  508 ,  518 ,  524 ,  528  is identical to the function of the grooves  108 ,  122 , which is described in detail above and will not be repeated here. However, because the locking mechanism  500  includes two linear canted-coil springs  510  and associated grooves, in certain embodiments it may provide greater axial holding power than the locking mechanisms including only one linear canted-coil spring and associated grooves. 
       FIGS. 6A-6D  illustrate another embodiment of the present locking mechanism  600 . The locking mechanism  600  includes many of the same features described above with respect to the locking mechanisms  100 ,  200 ,  300 ,  400 ,  500  illustrated in  FIGS. 1A-1H ,  1 J- 1 M  2 A- 2 C,  3 A- 3 E,  4  and  5 A- 5 D. Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIGS. 6A-6C , in the locking mechanism  600  a first surface  602  of the tongue  604  of the piston  606  includes a taper bottom groove  608  that retains a linear axially-canted-coil spring  610 . A first surface  612  of the first furcation  614  of the housing  616  includes a fiat bottomed groove  618 . With reference to  FIGS. 6A ,  6 B and  6 D, in the locking mechanism  600  a second surface  620  of the tongue  604  of the housing  606  includes a taper bottom groove  622  that retains a linear canted-coil spring  610 . A first surface  624  of the second furcation  626  of the piston  616  includes a flat bottomed groove  628 . The function of the grooves  608 ,  618 ,  622 ,  628  is identical to the function of the grooves  306 ,  316 , which is described in detail above and will not be repeated here. However, because the locking mechanism  600  includes two linear canted-coil springs  610  and associated grooves, in certain, embodiments it may provide greater axial holding power than the locking mechanisms including only one linear canted-coil spring and associated grooves. 
       FIGS. 7A-7C  illustrate another embodiment of the present locking mechanism  700 . The locking mechanism  700  includes many of the same features described above with respect to the locking mechanisms  100 ,  200 ,  300 ,  400 ,  500 ,  600  illustrated in  FIGS. 1A-1H ,  1 J- 1 M,  2 A- 2 C,  3 A- 3 E,  4 ,  5 A- 5 D and  6 A- 6 D. Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIGS. 7A and 7B , the locking mechanism  700  includes a piston  702  having a tongue  704 . With reference to  FIG. 7B , the tongue  704  has a square cross-section. The locking mechanism  700  further includes a housing  706  having a first furcation  708  and a second furcation  710 . A slot  712  defined between the first and second furcations  708 ,  710  is sized and configured to receive the square tongue  704  in locking engagement. 
     With continued reference to  FIGS. 7A and 7B , the square tongue  704  includes a circumferential taper bottom groove  714  that extends around all four outer faces of the square tongue  704 . The circumferential taper bottom groove  714  receives and retains a circular, axially-canted-coil spring  716 . The circular, axially-canted-coil spring  716  is illustrated in greater detail in  FIG. 7C . 
     With reference to  FIG. 7A , inner surfaces  717  of the first and second furcations  708 ,  710  each include a respective flat bottom groove  718 . Thus, when the square tongue  704  is inserted into the slot  712  as shown in  FIG. 7A , the circular, axially-canted-coil spring  716  is compressed along two portions of its length. Those portions are the first portion  720  ( FIG. 7B ) that lies between a first one of the flat bottom grooves  718  and a first length of the circumferential, taper bottom groove  714  and the second portion  722  ( FIG. 7B ) that lies between a second one of the flat bottom grooves  718  and a second length of the circumferential taper bottom groove  714 . The interaction of the grooves  714 ,  718  and the compressed spring portions  720 ,  722  prevents the axial separation of the housing  706  and the piston  702  in the same manner as described above with respect to the previous embodiments. The housing  706  and the piston  702  may be separated by relative radial movement as also described above with respect to the previous embodiments. 
       FIGS. 8A-8B  illustrate another embodiment of the present locking mechanism  800 . The locking mechanism  800  includes many of the same features described above with respect to the locking mechanisms  100 ,  200 ,  300 ,  400 ,  500 ,  600 ,  700  illustrated in  FIGS. 1A-1H ,  1 J- 1 M,  2 A- 2 C,  3 A- 3 E,  4 ,  5 A- 5 D,  6 A- 6 D and  7 A- 7 C. Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIGS. 8A and 8B , the locking mechanism  800  includes a piston  802  having a tongue  804 . With reference to  FIG. 8B , the tongue  804  has an oval cross-section comprising opposite flat sections  803  and opposite arcuate sections  805 . The locking mechanism  800  further includes a housing  806  having a first furcation  808  and a second furcation  810 . A slot  812  defined between the first and second furcations  808 ,  810  is sized and configured to receive the oval tongue  804  in locking engagement in which the opposite flat sections  803  engage inner surfaces  817  of the first and second furcations  808 ,  810 . 
     With continued reference to  FIGS. 8A and 8B , the oval tongue  804  includes a circumferential taper bottom groove  814  that extends around the opposite flat sections  803  and the opposite arcuate sections  805 . The circumferential taper bottom groove  814  receives and retains a circular, axially-canted-coil spring  816 . 
     With reference to  FIG. 8A , the first and second furcations  808 ,  810  each include a respective flat bottom groove  818 . Thus, when the oval tongue  804  is inserted into the slot  812  as shown in  FIG. 8A , the circular, axially-canted-coil spring  816  is compressed along two portions of its length. Those portions are the first portion  820  ( FIG. 8B ) that lies between a first one of the fiat bottom grooves  818  and a first length of the circumferential taper bottom groove  814  and the second portion  822  ( FIG. 8B ) that lies between a second one of the flat bottom grooves  818  and a second length of the circumferential taper bottom groove  814 . The interaction of the grooves  814 ,  818  and the compressed spring portions  820 ,  822  prevents the axial separation of the housing  806  and the piston  802  in the same manner as described above with respect to the previous embodiments. The housing  806  and the piston  802  may be separated by relative radial movement as also described above with respect to the previous embodiments. 
       FIGS. 9A-9B  illustrate another embodiment of the present locking mechanism  900 . The locking mechanism  900  includes many of the same features described above with respect to the locking mechanisms  100 ,  200 ,  300 ,  400 ,  500 ,  600 ,  700 ,  800  illustrated in  FIGS. 1A-1H ,  1 J- 1 M,  2 A- 2 C,  3 A- 3 E,  4 ,  5 A- 5 D,  6 A- 6 D,  7 A- 7 C and  8 A- 8 B. Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIGS. 9A and 9B , the locking mechanism  900  includes a piston  902  having a tongue  904 . With reference to  FIG. 9B , the tongue  904  has a round cross-section. The locking mechanism  900  further includes a housing  906  having a first furcation  908  and a second furcation  910 . A slot  912  defined between the first and second furcations  908 ,  910  is sized and configured to receive the round tongue  904  in locking engagement. 
     With continued reference to  FIGS. 9A and 9B , the round tongue  904  includes a circumferential taper bottom groove  914 . The circumferential taper bottom groove  914  receives and retains a circular, axially-canted-coil spring  916 . 
     With reference to  FIG. 9A , the first and second furcations  908 ,  910  each include a respective flat bottom groove  918 . Thus, when the round tongue  904  is inserted into the slot  912  as shown in  FIG. 9A , the circular, axially-canted-coil spring  916  is compressed along two portions of its length. Those portions are the first portion  920  ( FIG. 9B ) that lies between a first one of the flat bottom grooves  918  and a first length of the circumferential taper bottom groove  914  and the second portion  922  ( FIG. 9B ) that lies between a second one of the flat bottom grooves  918  and a second length of the circumferential taper bottom groove  914 . The interaction of the grooves  914 ,  918  and the compressed spring portions  920 ,  922  prevents the axial separation of the housing  906  and the piston  902  in the same manner as described above with respect to the previous embodiments. The housing  906  and the piston  902  may be separated by relative radial movement as also described above with respect to the previous embodiments. 
       FIGS. 10-10G  illustrate another embodiment of the present locking mechanism  1000 . The locking mechanism  1000  includes many of the same features described above with respect to the locking mechanisms  100 ,  200 ,  300 ,  400 ,  500 ,  600 ,  700 ,  800 ,  900  illustrated in  FIGS. 1A-1H ,  1 J- 1 M,  2 A- 2 C,  3 A- 3 E,  4 ,  5 A- 5 D,  6 A- 6 D,  7 A- 7 C,  8 A- 8 B and  9 A- 9 B. Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIGS. 10-10B , the locking mechanism  1000  includes a piston  1002  having a tongue  1004 . With reference to  FIG. 10E , the tongue  1004  has a round cross-section. The locking mechanism  1000  further includes a housing  1006  having a first furcation  1008  and a second furcation  1010  ( FIGS. 10 and 10E ). A wall portion  1011  extends between the first and second furcations  1008 ,  1010  to form a substantially U-shaped cross-section. A slot  1012  bounded by the furcations  1008 ,  1010  and the wall portion  1011  is sized and configured to receive the round tongue  1004  in locking engagement. 
     With reference to  FIGS. 10B and 10C , the round tongue  1004  includes a circumferential taper bottom groove  1014 . The circumferential taper bottom groove  1014  receives and retains a circular, axially-canted-coil spring  1016 . 
     With reference to  FIG. 10A , the first and second furcations  1008 ,  1010  and the wall portion  1011  include a flat bottom groove  1018 . Thus, when the round tongue  1004  is inserted, into the slot  1012  as shown in  FIGS. 10C and 10D , the circular, axially-canted-coil spring  1016  is compressed along approximately half its length in the areas that abut the groove  1018  in the first and second furcations  1008 ,  1010  and the wall portion  1011  ( FIG. 10E ). The interaction of the grooves  1014 ,  1018  and the compressed spring  1016  prevents the axial separation of the housing  1006  and the piston  1002  in the same manner as described above with respect to the previous embodiments. The housing  1006  and the piston  1002  may be separated by relative radial movement as also described above with respect to the previous embodiments and as shown in  FIG. 10F . 
       FIGS. 11-11G  illustrate another embodiment of the present locking mechanism  1100 . The locking mechanism  1100  includes many of the same features described above with respect to the locking mechanisms  100 ,  200 ,  300 ,  400 ,  500 ,  600 ,  700 ,  800 ,  900 ,  1000  illustrated in  FIGS. 1A-1H ,  1 J- 1 M,  2 A- 2 C,  3 A- 3 E,  4 ,  5 A- 5 D,  6 A- 6 D,  7 A- 7 C,  8 A- 8 B,  9 A- 9 B and  10 - 10 G. Accordingly, the discussion below will focus on only the differences between the embodiments. With reference to  FIGS. 11-11B , the locking mechanism  1100  includes a piston  1102  having a tongue  1104 . With reference to  FIG. 11E , the tongue  1104  has a round cross-section. The locking mechanism  1100  further includes a housing  1106  having a first furcation  1108  and a second furcation  1110  ( FIGS. 11 and 11E ). A wall portion  1111  extends between the first and second furcations  1108 ,  1110  to form a substantially U-shaped cross-section. A slot  1112  bounded by the furcations  1108 ,  1110  and the wall portion  1111  is sized and configured to receive the round tongue  1104  in locking engagement. 
     With reference to  FIGS. 11B and 11C , the round tongue  1104  includes a circumferential taper bottom groove  1114 . The circumferential taper bottom groove  1114  receives and retains a circular, axially-canted-coil spring  1116 . 
     With reference to  FIG. 11A , the first and second furcations  1108 ,  1110  and the wall portion  1111  include a fiat bottom groove  1118 . Thus, when the round tongue  1104  is inserted into the slot  1112  as shown in  FIGS. 11C and 11D , the circular, axially-canted-coil spring  1116  is compressed along approximately half its length in the areas that abut the groove  1118  in the first and second furcations  1108 ,  1110  and the wall portion  1111  ( FIG. 11E ). The interaction of the grooves  1114 ,  1118  and the compressed spring  1116  prevents the axial separation of the housing  1106  and the piston  1102  in the same manner as described above with respect to the previous embodiments. The housing  1106  and the piston  1102  may be separated by relative radial movement as also described above with respect to the previous embodiments and as shown in  FIG. 11F . 
     Unlike the previous embodiments, the locking mechanism  1100  does not include a circumferential groove in the body portion  1120  ( FIG. 10 ) of the piston  1102 . However, the locking mechanism  1100  includes a sleeve  1122  shaped substantially as a cylinder having a flat side wall  1124 . With reference to  FIGS. 11D and 11E , when the sleeve  1122  is slid toward the housing  1106  into the locked position, the flat side wall  1124  compresses a portion of the spring  1116  into the circumferential groove  1118 . Friction between the spring  1116  and the inner surface of the flat side wall  1124  resists sliding movement of the sleeve  1122  away from the locked position. 
     In certain aspects of the present embodiments, the housing is part of a rotating or reciprocating shaft of equipment or an appliance, such as a drill or a food mixer, and the piston is part of a removable component, such as a chuck. In another embodiment, the piston is part of a rotating or reciprocating shaft of equipment or an appliance, and the housing is part of a removable component. In yet other aspects of the present embodiments, the removable component may be provided with a bore, a socket, a key, a groove, or other mechanical means known in the art for coupling to a tool such as a drill bit, a saw blade, or a food mixer blade, for example. 
     Although limited embodiments of simple release locking mechanisms and their components have been specifically described and illustrated herein, many modifications and variations will be apparent to diose skilled in the art. For example, different spring material, different spring size, and multiple rows of springs may be used without deviating from the spirit and scope of the present embodiments. Furthermore, it is understood and contemplated that features specifically discussed for one simple release locking mechanism may be adopted for inclusion with another simple release locking mechanism, provided the functions are compatible. Accordingly, it is to be understood that the simple release locking mechanisms and their components constructed according to principles of these embodiments may be embodied other than as specifically described herein. The embodiments are also defined in the following claims.